CN112683564B - Method for calculating rated refrigerating capacity deviation of air conditioner at different wind speeds - Google Patents
Method for calculating rated refrigerating capacity deviation of air conditioner at different wind speeds Download PDFInfo
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Abstract
The invention discloses a method for calculating rated refrigerating capacity deviation of an air conditioner at different wind speeds, and belongs to the technical field of air conditioner refrigerating capacity testing. The invention discloses a method for calculating rated refrigerating capacity deviation of an air conditioner under different wind speeds in a dry-wet bulb temperature sampler at an air return inlet, which comprises the following steps: s1, measuring the air supply parameter, the air return parameter and the circulating air quantity of the air conditioner by using an air enthalpy method; s2, calculating by using a sensitivity coefficient to obtain uncertainty components, and evaluating the influence degree of each component on the experimental result of the step S1; s3, carrying out test simulation on the uncertainty component with the largest influence; s4, calculating the influence degree of the influence factor on the refrigerating capacity of the tested air conditioner by using a method of a control variable; and S5, selecting a reference wind speed, and determining a formula to calculate the deviation of the rated refrigerating capacity of the air conditioner at different wind speeds. The invention provides a new calculation mode, which can realize the calculation of the deviation of the rated refrigerating capacity of the air conditioner at different wind speeds and fills the blank of the field.
Description
Technical Field
The invention relates to the technical field of air conditioner refrigerating capacity testing, in particular to a method for calculating rated refrigerating capacity deviation of an air conditioner at different wind speeds.
Background
The refrigerating capacity is an important index of the air conditioner, is a reference standard for measuring the function and the effect of the air conditioner, and is the only important 'size' index in fact except the appearance size. The refrigerating capacity refers to the sum of heat removed from a closed space, a room or an area in unit time when the air conditioner performs refrigerating operation, and the legal measurement unit is W (watt).
After each air conditioner leaves the factory, a manufacturer can set a corresponding nameplate according to the national standard to calibrate the refrigerating capacity of the air conditioner, however, in the actual use process, along with the change of the environment and the working state of the air conditioner, the actual refrigerating capacity is not equal to the refrigerating capacity marked on the nameplate, and more serious deviation can be generated.
In the current technical means, a method capable of calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds does not exist, and people do not have related calculation methods for the refrigerating capacity deviation at different wind speeds, so that the invention provides a method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds.
Disclosure of Invention
The invention aims to provide a method for calculating the rated refrigerating capacity deviation of an air conditioner at different wind speeds so as to solve the problems in the background technology.
In order to solve the technical problems, the invention provides the following technical scheme: a method for calculating rated refrigerating capacity deviation of an air conditioner under different wind speeds comprises the following steps:
s1, testing the refrigerating and heating capacities of the air conditioner by using an air enthalpy method, measuring the air supply parameter, the air return parameter and the circulating air quantity of the air conditioner, and obtaining a result;
s2, calculating by using a sensitivity coefficient to obtain uncertainty components, and evaluating the influence degree of each component on the experimental result of the step S1;
s3, selecting the uncertainty component with the largest influence according to the uncertainty component obtained in the step S2, taking a window type air conditioner standard machine as an experimental object, and carrying out test simulation by using a rated refrigeration T1 working condition specified in national standard as a test working condition;
s4, according to the analysis data of the uncertainty component with the largest influence in the step S3, calculating the influence on the uncertainty component under different wind speed conditions by using a control variable method, and calculating the influence degree on the refrigerating capacity of the measured air conditioner according to the influence;
and S5, selecting reference wind speed according to the related files, and determining the deviation of the rated refrigerating capacity of the air conditioner under different wind speeds by using the data in the steps 1-4.
According to the technical scheme, in the step S1, the air supply parameter, the return air parameter and the circulating air quantity of the air conditioner are measured by the following formulas respectively, and the capacity of the air conditioner is determined by the product of the measured air quantity and the enthalpy difference between the air supply and the return air;
ha1＝1.01t1+W1(2500+1.84t1) (2)
ha2＝1.01t2+W2(2500+1.84t2) (4)
wherein phi istcThe refrigerating capacity of the air conditioner is unit W; q. q.smiIs the indoor air quantity of the air conditioner in unit m3/s； ha1The enthalpy value (dry air) of return air at the inner side of the air conditioner is J/kg; h isa2The enthalpy value (dry air) of the outlet air at the inner side of the air conditioner is expressed in J/kg; v'nSpecific volume of humid air at the measuring point in m3/kg；WnAir humidity at the measurement point in kg/kg (dry air); w1The air moisture content of the indoor side air return inlet is unit kg/kg (dry air); dsw1The moisture content of saturated air at an indoor side air return inlet is kg/kg (dry air); w2The air moisture content of an air outlet at the indoor side is kg/kg (dry air); dsw2The humidity content of saturated air at an air outlet at the indoor side is kg/kg (dry air); t is t1The temperature of the indoor return air dry bulb is unit ℃; t is tw1The indoor return air wet bulb temperature is unit ℃; t is t2The temperature of the air-out dry bulb at the indoor side is unit ℃; t is tw2Is the indoor side outlet wet bulb temperature in units of ℃.
According to the above technical solution, in step S2, the factor for introducing the uncertainty component includes the indoor return air dry bulb temperature t1(ii) a Indoor side return air wet bulb temperature tw1(ii) a Indoor side air-out dry bulb temperature t2(ii) a Indoor side air-out wet bulb temperature tw2(ii) a Dry bulb temperature t before nozzle3(ii) a Atmospheric pressure pb(ii) a Static pressure p before nozzle2(ii) a Differential pressure Δ p across the nozzle; the nozzle diameter D.
According to the technical scheme, the sensitivity coefficient c of each factor of the uncertainty component is introducediWherein i represents each factor, the calculation formula is as follows:
according to the sensitivity coefficient ciStandard uncertainty u of each factoriUsing | ciuiI determine the factor that plays an absolute dominant role in the nine influences as the wet bulb temperature tw1And tw2。
According to the technical scheme, in the step S3, the rated refrigeration T1 working condition specified in the national standard is indoor dry bulb: 27.00 ℃; indoor wet bulb: 19.00 ℃; outdoor side dry bulb: 35.00 ℃; outdoor wet bulb: 24.00 ℃.
According to the technical scheme, in the step S3, in the test simulation process, a window type air conditioner standard machine is selected, and the bs value of the indoor side wet bulb temperature sensor is adjusted to be corrected by utilizing the indication error of the wet bulb temperature sensor, so that the condition that the temperature of a wet bulb is not measured accurately and the ambient humidity is deviated is simulated.
According to the technical scheme, the wet bulb temperature sensor is wrapped by gauze with good matching degree, the gauze which is arranged on the part of the sensor in an excess manner is connected with the water container, the moisture evaporation on the gauze can take away the heat on the wet bulb, so that the temperature of the wet bulb is lower than the temperature of a dry bulb, the moisture evaporation efficiency on the wet bulb gauze directly influences the temperature of the wet bulb, and the moisture evaporation efficiency and the wind speed form a functional relation with the moisture content in the ambient air.
According to the above technical solution, in step S4, a method for controlling variables is used, where the different wind speeds are different wind speeds in the wet and dry bulb temperature sampler at the air return opening, and the calculation formula is as follows:
wherein U is the ambient relative humidity, in% RH; t is the dry bulb temperature in units; t is twWet bulb temperature in units; e.g. of the typewSaturated water vapor pressure at wet bulb temperature in Pa; e.g. of the typesIs the saturated vapor pressure at dry bulb temperature, in Pa; a is the dry-wet bulb coefficient; p is atmospheric pressure in Pa; v is wind speed in m/s;
under the condition that other conditions are not changed and only the wind speed is changed, the theoretical value of the relative humidity under different wind speeds is calculated.
According to the above technical solution, in step S5, the document in question is GB/T7725-2004 Room air conditioner C.1.3, which requires that "the air flow velocity at which the wet bulb thermometer flows is not less than 5 m/S".
According to the technical scheme, in the step S5, the data and the conclusion obtained in the steps S1-S4 are utilized to carry out analysis, the relation between the change of the refrigerating capacity of the tested air conditioner and the change of the refrigerating capacity of the tested air conditioner is obtained, and then a formula for calculating the deviation of the rated refrigerating capacity of the air conditioner at different wind speeds is obtained;
when the wind speed is lower than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝3.5907x4-52.606x3+284.34x2-681.11x+629.18；
when the wind speed is higher than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝0.0004x4-0.0159x3-0.0012x2+4.6443x-20.73。
compared with the prior art, the invention has the following beneficial effects:
the invention uses the air enthalpy method to measure the air supply parameter, the return air parameter and the circulating air quantity of the air conditioner, determines the capacity of the air conditioner by the product of the measured air quantity and the enthalpy difference between the air supply and the return air, then obtains the uncertainty component by calculating the sensitivity coefficient in the uncertainty evaluation of the measurement of the air conditioner in the air enthalpy method, can visually show the influence degree of each component on the experimental result, selects the influence factors playing the absolute dominant role to further analyze, uses the method of controlling the variable to discuss the accuracy analysis of the influence factors under different wind speeds, further obtains the deviation formula for calculating the rated refrigerating capacity of the air conditioner under different wind speeds, provides a new calculation mode according to a large amount of data and accurate experiments, can realize the calculation of the deviation of the rated refrigerating capacity of the air conditioner under different wind speeds, fills the blank of the field.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:
FIG. 1 is a layout diagram of a testing apparatus for a method of calculating deviation of rated cooling capacity of an air conditioner at different wind speeds according to the present invention;
FIG. 2 is a graph of variation trend of relative humidity with wind speed according to the method for calculating deviation of rated refrigerating capacity of an air conditioner at different wind speeds;
FIG. 3 is a schematic diagram of the variation of the rated refrigerating capacity deviation with the wind speed (wind speed < 5m/s) according to the method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds;
FIG. 4 is a schematic diagram of the variation of the rated refrigerating capacity deviation with the wind speed (wind speed > 5m/s) according to the method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds;
FIG. 5 is a schematic diagram illustrating the steps of a method for calculating the deviation of the rated cooling capacity of the air conditioner at different wind speeds according to the present invention;
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1-4, the present invention provides the following technical solutions: a method for calculating rated refrigerating capacity deviation of an air conditioner under different wind speeds comprises the following steps:
s1, testing the refrigerating and heating capacities of the air conditioner by using an air enthalpy method, measuring the air supply parameter, the air return parameter and the circulating air quantity of the air conditioner, and obtaining a result;
s2, calculating by using a sensitivity coefficient to obtain uncertainty components, and evaluating the influence degree of each component on the experimental result of the step S1;
s3, selecting the uncertainty component with the largest influence according to the uncertainty component obtained in the step S2, taking a window type air conditioner standard machine as an experimental object, and carrying out test simulation by using a rated refrigeration T1 working condition specified in national standard as a test working condition;
s4, according to the analysis data of the uncertainty component with the largest influence in the step S3, calculating the influence on the uncertainty component under different wind speed conditions by using a control variable method, and calculating the influence degree on the refrigerating capacity of the measured air conditioner according to the influence;
and S5, selecting reference wind speed according to the related files, and determining the deviation of the rated refrigerating capacity of the air conditioner under different wind speeds by using the data in the steps 1-4.
As shown in fig. 1, the layout diagram of the testing apparatus in step S1 is shown, the air volume measuring device is installed at the indoor side, the outdoor unit is connected to the indoor unit, the outlet of the indoor unit is connected to the air volume measuring device through the mixer, wherein the dry-wet bulb temperature sampler is installed at both sides of the mixer, the pressure gauge is installed above the outlet, after leaving the air volume measuring device, the air directly enters the air handling unit, the set working condition is obtained by processing, according to the "air enthalpy method", the air supply parameter, the return air parameter and the circulating air volume of the air conditioner are measured by the following formulas, and the capacity of the air conditioner is determined by the product of the measured air volume and the air supply and return enthalpy difference;
ha1＝1.01t1+W1(2500+1.84t1) (2)
ha2＝1.01t2+W2(2500+1.84t2) (4)
wherein phi istcThe refrigerating capacity of the air conditioner is unit W; q. q.smiIs the indoor air quantity of the air conditioner in unit m3/s； ha1The enthalpy value (dry air) of return air at the inner side of the air conditioner is J/kg; h isa2For air-out of the air conditioner at the inner sideEnthalpy (dry air) in J/kg; v'nSpecific volume of humid air at the measuring point in m3/kg；WnAir humidity at the measurement point in kg/kg (dry air); w1The air moisture content of the indoor side air return inlet is unit kg/kg (dry air); dsw1The moisture content of saturated air at an indoor side air return inlet is kg/kg (dry air); w2The air moisture content of an air outlet at the indoor side is kg/kg (dry air); dsw2The humidity content of saturated air at an air outlet at the indoor side is kg/kg (dry air); t is t1The temperature of the indoor return air dry bulb is unit ℃; t is tw1The indoor return air wet bulb temperature is unit ℃; t is t2The temperature of the air-out dry bulb at the indoor side is unit ℃; t is tw2Is the indoor side outlet wet bulb temperature in units of ℃.
In this embodiment, window air conditioner standard machines with cooling capacities of 2700W, 4470W and 5122W are selected as experimental subjects, the test conditions adopt rated cooling T1 conditions (indoor dry bulb: 27.00 ℃; indoor wet bulb: 19.00 ℃; outdoor dry bulb: 35.00 ℃; outdoor wet bulb: 24.00 ℃) specified in national standards, and according to step S2, uncertainty components obtained by calculation of "sensitivity coefficients" in uncertainty evaluation of air conditioner measurement by air enthalpy method are analyzed as follows:
1) indoor side return air dry bulb temperature t1The sensitivity coefficient is calculated by the introduced uncertainty component
And (3) obtaining the standard uncertainty of the return air dry bulb temperature according to a calibration certificate and related technical data: u (t)1) 0.03 ℃ to obtain
2) Indoor side return air wet bulb temperature tw1Introduced (a)Uncertainty component, calculating sensitivity coefficient
And (3) obtaining the standard uncertainty of the return air wet bulb temperature according to a calibration certificate and related technical data: u (t)w1) 0.05 ℃ to yield
3) Indoor side air-out dry bulb temperature t2The sensitivity coefficient is calculated by the introduced uncertainty component
According to the calibration certificate and the related technical data, the standard uncertainty of the temperature of the air outlet dry bulb is as follows:
u(t2) 0.03 ℃ to obtain
4) Indoor side air-out wet bulb temperature tw2The sensitivity coefficient is calculated by the introduced uncertainty component
And obtaining the standard uncertainty of the air outlet wet bulb temperature according to the calibration certificate and the related technical data:
u(tw2) 0.05 ℃ to yield
5) Dry bulb temperature t before nozzle3The sensitivity coefficient is calculated by the introduced uncertainty component
Standard uncertainty of dry bulb temperature before nozzle, based on calibration certificates and related technical data:
u(t3) 0.03 ℃ to obtain
6) Atmospheric pressure pbThe sensitivity coefficient c is calculated by the introduced uncertainty componentpb；
According to the calibration certificate and the related technical data, the standard uncertainty of the atmospheric pressure gauge is 0.5 percent FS, the measurement range is 80-110 kpa, and the standard uncertainty u (p) of the atmospheric pressure isb) Obtained at 0.55kPa
7) Static pressure p before nozzle2Introducing uncertainty component, and calculating to obtain sensitivity coefficient
According toThe accuracy grade of the static pressure p before the nozzle is 0.5 grade, the measuring range of the digital pressure gauge is 50 Pa-500 Pa, and the standard uncertainty is 2.5Pa due to p2＝pbP, according to the uncertainty synthesis theorem, obtaining a standard uncertainty u (p)2) Obtained at 0.5kPa
8) Calculating the uncertainty component introduced by the pressure difference delta p before and after the nozzle to obtain the sensitivity coefficient c△p；
According to the calibration certificate and the related technical data, the accuracy grade of the pressure difference between the front and the rear of the nozzle is 0.2 grade, the measuring range of the digital pressure gauge is 0 Pa-1000 Pa, the standard uncertainty u (delta p) is 2.0Pa, and c is obtainedΔpu(Δp)＝8.22W；
9) The diameter D of the nozzle introduces an uncertainty component, and a sensitivity coefficient c is obtained by calculationD；
The vernier caliper meets the requirements of JJG 30-2012, the indication error is 0.02mm, and the standard uncertainty u (D) is 0.00002m to obtain cDu(D)＝1.69W；
A summary of the above data is given in Table 1 below,
TABLE 1 summary of measured uncertainty components
According to | c of Table 1iuiIt can be seen that there are many factors affecting the cooling capacity, and the influence of the wet bulb temperatures tw1 and tw2 is particularly prominent among the nine influencesAnd at the maximum, plays an absolute dominant role. Under the condition that other conditions are not changed, the indication error of the wet bulb sensor is assumed to be 0.03 ℃ or-0.03 ℃, and the bs value of the indoor side wet bulb sensor is adjusted to be corrected so as to simulate the condition that the environment humidity generates deviation when the wet bulb temperature measurement is inaccurate. According to experimental data, when the wet bulb temperature deviates by 0.03 ℃, the relative humidity of the environment changes by about 0.2% RH, and the refrigerating capacity of the corresponding air conditioner to be tested changes by about 17W, so that the influence of the accuracy of the wet bulb temperature on the air conditioning capacity test by the enthalpy difference method is very obvious, and the specific data are shown in table 2.
TABLE 2 test data of rated refrigerating capacity of wet bulb under different bs value settings
By the uncertainty analysis and the experimental data, it can be seen how to accurately measure the wet bulb temperature and ensure the accuracy and stability of the relative humidity of the environment. At present, most laboratories using air enthalpy methods control the ambient temperature and relative humidity by using a dry-wet-bulb method, which is a method of calculating or looking up a table to obtain the relative humidity by using dry-wet-bulb temperature sensors under the same wind speed condition according to the temperature difference. Wet bulb temperature sensor uses the gauze parcel that the matching degree is good, the gauze that exceeds the sensor part links to each other with the water container, the last heat on the wet bulb can be taken away in the evaporation of water on the gauze, make its temperature be less than dry bulb temperature, wet bulb temperature will directly be influenced to the height of the evaporation efficiency of water on the wet bulb gauze, look up relevant data and learn, it becomes certain functional relation with the moisture content in wind speed and the ambient air, in step S4, utilize the method of controlled variable, the computational formula is as follows:
wherein U is the ambient relative humidity, in% RH; t is the dry bulb temperature in units; t is twWet bulb temperature in units; e.g. of the typewSaturated water vapor pressure at wet bulb temperature in Pa; e.g. of the typesIs the saturated vapor pressure at dry bulb temperature, in Pa; a is the dry-wet bulb coefficient; p is atmospheric pressure in Pa; v is wind speed in m/s;
calculating to obtain the theoretical values of the relative humidity under different wind speeds in the table 3
TABLE 3 theoretical values of relative humidity at different wind speeds
From the above data, the trend chart of relative humidity with wind speed is shown in fig. 2.
According to step S5, GB/T7725-2004 Room air Conditioning device C.1.3 requires that "the air flow velocity flowing through the wet bulb thermometer is not less than 5 m/S", so, with the wind velocity of 5m/S as the reference point, the corresponding relative humidity reference point is 46.5% RH as can be seen from Table 3, and according to the experimental data: "the relative humidity of the environment will change by about 0.2% RH and the corresponding measured refrigerating capacity of the air conditioner will change by about 17W", and the corresponding relationship of the difference between the wind speed values and the corresponding reference points in Table 4 is established.
TABLE 4 Difference correspondence between wind speed values and corresponding reference points
According to table 4, a deviation formula for calculating the rated cooling capacity of the air conditioner at different wind speeds is obtained, as shown in fig. 3 and 4. The deviation formula is as follows:
when the wind speed is lower than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝3.5907x4-52.606x3+284.34x2-681.11x+629.18；
when the wind speed is higher than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝0.0004x4-0.0159x3-0.0012x2+4.6443x-20.73。
the working principle of the invention is as follows: the invention utilizes an air enthalpy method to measure the air supply parameters, the return air parameters and the circulating air quantity of the air conditioner, determines the capacity of the air conditioner by the product of the measured air quantity and the enthalpy difference between the air supply and the return air, obtains uncertainty components by 'sensitivity coefficient' calculation, selects the influence factors which play an absolute dominant role to further analyze, discusses the accuracy analysis of the influence factors under different wind speeds by using a method for controlling variables, further obtains a deviation formula for calculating the rated refrigerating capacity of the air conditioner under different wind speeds, provides a new calculation mode according to a large amount of data and accurate experiments, can realize the calculation of the deviation of the rated refrigerating capacity of the air conditioner under different wind speeds, and fills the blank in the field.
It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
Finally, it should be noted that: although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that changes may be made in the embodiments and/or equivalents thereof without departing from the spirit and scope of the invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (9)
1. A method for calculating rated refrigerating capacity deviation of an air conditioner under different wind speeds is characterized by comprising the following steps: the method comprises the following steps:
s1, testing the refrigerating and heating capacities of the air conditioner by using an air enthalpy method, measuring the air supply parameter, the air return parameter and the circulating air quantity of the air conditioner, and obtaining a result;
s2, calculating by using a sensitivity coefficient to obtain uncertainty components, and evaluating the influence degree of each component on the experimental result of the step S1;
s3, selecting the uncertainty component with the largest influence according to the uncertainty component obtained in the step S2, and performing test simulation by using a rated refrigeration T1 working condition specified in national standards as a test working condition;
s4, according to the analysis data of the uncertainty component with the largest influence in the step S3, calculating the influence on the uncertainty component under different wind speed conditions by using a control variable method, and calculating the influence degree on the refrigerating capacity of the measured air conditioner according to the influence;
s5, selecting a reference wind speed according to the related files, and determining a formula to calculate the rated refrigerating capacity deviation of the air conditioner at different wind speeds by using the data in the steps S1-S4;
in step S5, analyzing by using the data and the conclusion obtained in the steps S1-S4 to obtain the relation between the change of the refrigerating capacity of the tested air conditioner and the change of the refrigerating capacity of the tested air conditioner, and further obtaining a formula for calculating the deviation of the rated refrigerating capacity of the air conditioner at different wind speeds; the requirement "the speed of air flow at which the wet bulb thermometer flows is not less than 5 m/s" in article C.1.3 of GB/T7725-2004 Room air Conditioning apparatus;
when the wind speed is lower than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝3.5907x4-52.606x3+284.34x2-681.11x+629.18；
when the wind speed is higher than 5m/s, the formula for calculating the deviation of the rated refrigerating capacity is as follows:
y＝0.0004x4-0.0159x3-0.0012x2+4.6443x-20.73。
2. the method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 1, wherein the method comprises the following steps: in step S1, the air supply parameter, the return air parameter and the circulating air quantity of the air conditioner are measured by the following formulas, and the capacity of the air conditioner is determined by the product of the measured air quantity and the enthalpy difference between the supply air and the return air;
ha1＝1.01t1+W1(2500+1.84t1) (2)
ha2＝1.01t2+W2(2500+1.84t2) (4)
wherein phi istciThe refrigerating capacity of the air conditioner is unit W; q. q.smiIs the indoor air quantity of the air conditioner in unit m3/s；ha1The enthalpy value of return air at the inner side of the air conditioner is equal to the enthalpy value of dry air, and the unit of J/kg is equal to the unit of J/kg; h isa2For air conditioner indoorSide air outlet enthalpy, dry air, unit J/kg; v'nSpecific volume of humid air at the measuring point in m3/kg；WnThe air humidity at a measuring point is expressed as unit kg/kg, and air is dried; w1The air moisture content of an indoor side air return inlet is unit kg/kg, and the air is dry; dsw1The saturated air moisture content of an indoor side air return inlet is unit kg/kg, and the air is dry; w2The air moisture content of an air outlet at the indoor side is unit kg/kg, and the air is dry; dsw2The humidity content of saturated air at an air outlet at the indoor side is unit kg/kg, and the air is dry; t is t1The temperature of the indoor return air dry bulb is unit ℃; t is tw1The indoor return air wet bulb temperature is unit ℃; t is t2The temperature of the air-out dry bulb at the indoor side is unit ℃; t is tw2Is the indoor side outlet wet bulb temperature in units of ℃.
3. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 1, wherein the method comprises the following steps: in step S2, the factor that introduces the uncertainty component includes the indoor return air dry bulb temperature t1(ii) a Indoor side return air wet bulb temperature tw1(ii) a Indoor side air-out dry bulb temperature t2(ii) a Indoor side air-out wet bulb temperature tw2(ii) a Dry bulb temperature t before nozzle3(ii) a Atmospheric pressure pb(ii) a Static pressure p before nozzle2(ii) a Differential pressure Δ p across the nozzle; the nozzle diameter D.
4. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 3, wherein the method comprises the following steps: sensitivity coefficient c of each factor introducing uncertainty componentiWherein i represents each factor, the calculation formula is as follows:
and calculating to obtain the sensitivity coefficient.
5. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 4, wherein the method comprises the following steps: according to the sensitivity coefficient ciStandard uncertainty u of each factoriUsing | ciuiI determine the factor that plays an absolute dominant role in the nine influences as the wet bulb temperature tw1And tw2。
6. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 1, wherein the method comprises the following steps: in step S3, in the test simulation process, a window air conditioner standard machine is selected, and the bs value of the indoor side wet bulb temperature sensor is adjusted to correct the indication error of the wet bulb temperature sensor, so as to simulate the situation that the deviation of the ambient humidity is caused due to the inaccurate wet bulb temperature measurement.
7. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 6, wherein the method comprises the following steps: the wet bulb temperature sensor is wrapped by gauze with good matching degree, the gauze which is arranged on the sensor part is connected with the water container, the heat on the wet bulb can be taken away by the evaporation of the water on the gauze, the temperature of the wet bulb is lower than the temperature of a dry bulb, the temperature of the wet bulb is directly influenced by the evaporation efficiency of the water on the gauze, and the temperature of the wet bulb is in a functional relation with the wind speed and the water content in the surrounding air.
8. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 1, wherein the method comprises the following steps: in step S4, using the method of controlling variables, the calculation formula is as follows:
wherein U is the relative humidity of the environmentIn units% RH; t is the dry bulb temperature in units; t is twWet bulb temperature in units; e.g. of the typewSaturated water vapor pressure at wet bulb temperature in Pa; e.g. of the typesIs the saturated vapor pressure at dry bulb temperature, in Pa; a is the dry-wet bulb coefficient; p is atmospheric pressure in Pa; v is wind speed in m/s;
under the condition that other conditions are not changed and only the wind speed is changed, the theoretical value of the relative humidity under different wind speeds is calculated.
9. The method for calculating the rated refrigerating capacity deviation of the air conditioner at different wind speeds as claimed in claim 1, wherein the method comprises the following steps: in step S4, the different wind speeds are different wind speeds in the wet and dry bulb temperature sampler at the return air inlet.
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