CN201003930Y - Cooling water tower - Google Patents

Abstract

The utility model discloses a cooling tower, it includes the cooling tower main part, and the hygrometer can variable frequency control's water pump, a plurality of temperature measurers and the controller of utensil operation function. The necessary data such as the maximum allowable operation range of the cooling tower, the heat transfer performance of the cooling tower, the relation between the wet bulb temperature and the proximity of the outside air, etc. are calculated by a numerical method and are built in the controller. When the cooling water tower is running, the program is transmitted to the controller by the measurement of the temperature measuring device, and the actual data and the pre-calculated data are compared in the controller to obtain the most suitable cooling water flow and cooling air flow. The controller controls the cooling water pump and the cooling fan in the cooling water tower respectively to achieve the most suitable flow rate. The utility model discloses but not only automatic adjustment cooling air flow, more adjustable cooling water flow to save the energy that cooling tower used by a wide margin.

Description

a cooling tower

technical field

The utility model relates to an air conditioning system, in particular to a cooling water tower used in the air conditioning system which can automatically adjust the flow of cooling water and the flow of cooling air as the load changes.

Background technique

As the domestic people's livelihood becomes richer, the usage of central air-conditioning systems has also increased, making the power consumption of air-conditioning one of the main reasons for the high peak power consumption in summer. How to improve the efficiency of air-conditioning energy use to reduce peak power consumption in summer has become one of the important topics of domestic energy conservation policies.

The configuration and operating principle of the main components of the known central air-conditioning system are shown in Figure 1, which basically includes five heat exchange circulation systems, from the indoor air-conditioning load on the left to the outside one by one, both the indoor air and the cooling coil 4 do heat Exchange; heat exchange between ice water and refrigerant in evaporator 3; then heat exchange between refrigerant and cooling water in condenser 2 of ice water host; finally, heat exchange between cooling water and outdoor air in cooling water tower 1.

The power consumption of the above-mentioned last heat exchange procedure "cooling water and outdoor air are engaged in heat exchange process in the cooling water tower" is still relatively high, and there is room for further improvement. This utility model is aimed at the above-mentioned last heat exchange procedure. .

Utility model content

The technical problem to be solved by the utility model is to provide a cooling water tower that can automatically adjust the cooling water flow and cooling air flow as the load changes, so as to improve and overcome the defects of the above-mentioned known technologies and reduce the power consumption of the central air-conditioning system.

The technical solution of the utility model is: a cooling water tower that can automatically adjust the flow of cooling water and cooling air as the load changes, wherein the cooling water tower includes the main body of the cooling water tower, a hygrometer, a water pump that can be controlled by frequency conversion, multiple temperature A measuring device and a controller with computing functions. The main body of the cooling water tower is used in parallel in one or more groups to inhale cooling air to cool the inflowing cooling water. The hygrometer is installed in the cooling water tower to measure the inhaled cooling air The wet bulb temperature change value, the cooling water pump that can be controlled by frequency conversion is installed in the cooling water flow channel to control the cooling water flow, and multiple temperature measuring devices are respectively installed at the inlet and outlet of the cooling air and cooling water to measure Measure the change value of each temperature and connect with the controller. In addition, at least one controller is used to calculate the wet bulb temperature of the cooling air and the temperature difference when the cooling water enters and exits the cooling water tower. The maximum allowable operating conditions are preset in the controller and the built-in and external The data of the proximity corresponding to the wet bulb temperature of the gas is used to process the data obtained by the aforementioned controller to determine the optimal cooling water flow and cooling air flow data.

The features and advantages of the utility model are: in the past, in order to save the energy consumption of the cooling water tower, the main method is to automatically adjust the cooling air flow in and out of the cooling water tower with the change of the heat load of the ice water host, so as to achieve the purpose of energy saving. In order to make more effective use of energy, the utility model proposes a new cooling tower control system, which can not only automatically adjust the cooling air flow rate but also the cooling water flow rate according to the change of the thermal load of the ice water main engine, which can greatly save the cooling water tower. energy. The utility model comprises a main body of a cooling water tower, a hygrometer, a water pump capable of frequency conversion control, a plurality of temperature measuring devices and a controller with a computing function. Necessary data, such as the maximum allowable operating range of the cooling tower, the heat transfer performance of the cooling tower, the relationship between the wet bulb temperature and the proximity of the outside air, etc., are calculated using numerical methods and built into the controller. When the cooling water tower is running, the temperature measuring device is used to measure, and the program is sent to the controller, and the actual data and the pre-calculated data are compared in the controller to obtain the most suitable cooling water flow and cooling air flow value, and then The controller separately controls the cooling water pump and the cooling fan in the cooling water tower to achieve the most suitable flow. The utility model overcomes the defects of the prior art and proposes a brand-new method for saving energy, which can reduce the power consumption of the central air-conditioning system and reduce the pressure of peak power consumption.

Description of drawings

Fig. 1 is a known central air-conditioning system diagram.

Figure 2 is a detailed view of the operation of the condenser and the cooling water tower of the present invention.

Figure 3 is a heat balance diagram for a small distance.

Figure 4 is a system control architecture diagram.

Figure 5 is a graph showing the relationship between the outside wet bulb temperature WB and the proximity AP.

Explanation of reference numbers:

1. Cooling tower 11. Fan

12. Cooling plate 13. Sink

14. Temperature measuring device (measured T _G1 ) 15. Temperature measuring device (measured T _G2 )

16. Hygrometer 2. Condenser

21. Temperature measuring device (T _L1 is measured) 22. Temperature measuring device (T _L2 is measured)

23. Cooling water pump 24. Controller

25. Controller 26. Controller

3. Evaporator 4. Indoor fan cooling coil

5. Compressor 6. Ice water pump

7. Expansion valve

Detailed ways

FIG. 2 is a detailed view of the operation between the condenser 2 and the cooling tower 1 . M _L is the cooling water flow rate, which is used to cool the working fluid (refrigerant) in the condenser, and the temperature of the cooling water rises to T _L1 to flow out of the condenser. Then it is transported to the inlet of the cooling water tower 1. Generally, through the action of gravity, the cooling water of high temperature T _L1 flows from the inlet of the cooling tower through the cooling plate 12 in the cooling tower, and then flows down to the water tank 13 at the bottom of the cooling tower. The exhaust fan 11 _above the _cooling water tower draws the low-temperature cooling air from the lower entrance of the cooling water tower 1. Connect the hygrometer 16 to measure the wet-bulb temperature change value of the inhaled cooling air, wherein the cooling air absorbs the cooling water with a higher temperature, so when it leaves the cooling water tower 1 above, the temperature rises to T _G2 , strictly speaking, Cooling air will increase the flow rate due to the addition of evaporated water vapor, but it is generally considered to be constant _{approximately} . On the contrary, the cooling water is cooled from the higher temperature of T _L1 to T _L2 , although the flow rate is slightly reduced due to the evaporation of water, but generally M _L is still regarded as a constant value. The cooling water whose temperature is T _L2 then enters the condenser 2 to perform a new loop function. In FIG. 2 , the controller 24 can adjust and set the temperature of the cooling water flowing out of the cooling water tower, and transmit the temperature signal of T _L2 to the controller 26 . The controller 25 can calculate and adjust the temperature difference ΔT(T _L1 −T _L2 ) of the set cooling water, and send the signal of the temperature difference to the controller 26 . The controller 26 integrates various signals, and sends instructions to adjust and set the speed and flow of the cooling tower fan 11 and the cooling water pump 23 .

Due to the relationship of energy conservation, the total heat transferred from the cooling water flowing in from the top of the cooling water tower and flowing out from the bottom must be equal to the total heat obtained by the cooling air flowing in from the bottom of the cooling water tower and flowing out above. From a microscopic point of view, the heat exchange between cooling water and cooling air can be shown in Figure 3. The outgoing heat of the cooling water between this trace distance dx

dQ _L ＝-M _L ×C _L ×(ΔT _L ) (Formula 1)

In (Equation 1), ΔT _L is the temperature difference in this interval, and C _L is the specific heat of cooling water. Assuming that it does not change with temperature, it can be regarded as a fixed value. The negative sign in the formula indicates the heat transfer.

Similarly, the heat dQ _G available to cool the air is

dQ _G ＝M _G ×(ΔH) (Formula 2)

In (Formula 2), ΔH is the enthalpy difference of the cooling air in this area, which is calculated by the following formula

ΔH＝H _(TG+dTG) -H _(TG) (Formula 3)

H _(TG) and H _(TG+dTG) are the enthalpy values of the air entering and leaving the trace space respectively, (Formula 1) and (Formula 2) must be equal so

dQ _G ＝M _G ×(ΔH)＝-M _L ×C _L ×(ΔT _L )＝dQ _L (Formula 4)

Generally, in engineering applications, dQ _G can also be approximated by the following formula

$d{Q}_G=\frac{f}{k}(h_{\mathrm{the\; s}}-h)D$ (Formula 5)

f in (Formula 5) is the convection heat coefficient, and k is determined by the physical properties of the cooling liquid and cooling gas used, and its value is approximately constant. H is the enthalpy value of unsaturated air (unsaturated air) in this interval, and H _s is the enthalpy value of saturated air (saturated air) corresponding to the surface temperature of cooling water (approximately with the temperature of cooling water) in this interval. Both H and H _S are temperature functions, (H _S -H) means that heat flows from the air on the surface of the cooling water to the surrounding cooling air, and dA is the heat transfer area of this interval.

If the micro-distance is extended to the integral cooling tower, the following formula holds.

$-{\∫}_{T_{L3}}^{T_{L2}}{m}_L\×C_L\mathrm{dT}={\∫}_0^A\frac{f}{k}(\mathrm{Hs}-h)D$ (Formula 6)

In the formula, A represents the total heat transfer area of the cooling plate (12) in the cooling tower. (Formula 6) can be rewritten as the following formula.

${\&Integral;}_0^A\frac{f}{k}D=\frac{f}{k}=-{\&Integral;}_{\mathrm{<figure-callout\; id="1"\; label="TL"\; filenames="Y20062013293900141.png,Y20062013293900151.png"\; state="\{\{state\}\}">TL</figure-callout>}1}^{\mathrm{TL}2}\frac{m_L\&times;C_L}{(h_{\mathrm{the\; s}}-h)}d{T}_L$ (Formula 7)

The actual calculation uses the following formula

$\frac{f}{k}=-m_L\&times;C_L\&times;\mathrm{\&Delta;T\&Sigma;}\frac{1}{(h_{\mathrm{the\; s}}-h)}$ (Formula 8)

边的值。当

的值为已知时，则可求得等号右边各参数的值。where ( _HS -H) represents the average enthalpy difference within the volume increment. ΔT is the temperature difference of the volume increment, when the value on the right side of the equal sign in (Equation 8) is known, the numerical method can be used to obtain the equal sign

edge value. when

When the value of is known, the value of each parameter on the right side of the equal sign can be obtained.

Generally, when a manufacturer sells a cooling tower, it will provide the cooling water flow M _L , the cooling air flow M _G , the range RT, and the approach AP of the cooling water tower when the heat load is 100%. The upper temperature limit T _L2 of the cooling water when entering the condenser, the upper limit T _L1 of the cooling water temperature when leaving the condenser, and the wet bulb temperature WB of the outside air.

The meaning of proximity AP refers to the difference between the temperature (T _L2 ) when the cooling water leaves the cooling tower and the wet bulb temperature (wet bulb temperature) WB when the cooling air enters the cooling tower, that is

T _L2 ＝WB+AP (Formula 9)

The meaning of the range degree RT refers to the temperature difference between the cooling water entering and leaving the cooling tower, that is

RT＝T _L1 -T _L2 (Formula 10)

And the load Q _L of condenser 2 can be obtained by the following formula

Q _L ＝M _L ×C _L ×(T _L1 -T _L2 ) (Formula 11)

available after substitution

Q _L ＝M _L ×C _L ×RT (Formula 12)

The total heat Q _G of the cooling air is expressed by the following formula

Q _G ＝M _G ×(H _TG2 -H _TG1 )＝Q _L (Formula 13)

的值可视为一种非常有意义的冷却塔性能系数，当M_L、MLG和WB值保持一定时，此冷却水塔性能系数

亦需维持定值，利用此关系则可由数值计算反算当冷凝器2的热负载改变时(亦即RT值改变)的T_L2、T_L1和AP的变化。得知T_L2和T_L1的变化后，可通过数值计算并调整冷却水M_L和MLG比值，而使T_L2和T_L1达到最佳状态，此调整过程可有效的达到节约能源的目的。本实用新型的主要内容在下列所示实施例中做具体说明。In the actual application of cooling tower performance calculation, use the hygrometer 16 measuring instrument to measure the wet bulb temperature WB and cooling water volume M _L of the cooling air entering the cooling tower, as well as the set ratio MLG, and then obtain T _L2 and T _L1 in turn . Substituting into (Equation 8), we can get value. From the physical meanings of f, A and k,

The value of can be regarded as a very meaningful coefficient of performance of the cooling tower. When the values of _ML , MLG and WB are kept constant, the coefficient of performance of the cooling tower

It is also necessary to maintain a constant value. By using this relationship, the changes of T _L2 , T _L1 and AP can be back-calculated when the heat load of the condenser 2 changes (that is, the RT value changes). After knowing the changes of T _L2 and T _L1 , the ratio of cooling water _ML and MLG can be calculated and adjusted numerically, so that T _L2 and T _L1 can reach the best state. This adjustment process can effectively achieve the purpose of saving energy. The main contents of the utility model are described in detail in the following examples.

Embodiment 1: Taking a certain factory as an example, the calculation metadata provided by the manufacturer are as follows;

Cooling water flow M _L ＝30GPM (30 gallons per minute)

Cooling air flow M _G = 25GPM (25 gallons per minute (= 256 pounds))

Mass flow ratio of cooling water and cooling air

MLG(M _L /M _G ) = 1.2

Range RT＝10

Proximity AP=7

The wet bulb temperature of the cooling air flowing into the cooling tower WB＝83

The temperature upper limit T _L2 of the cooling water flowing out of the condenser is

T _L2 ＝WB+AP＝83+7＝90

T _L1 ＝T _L2 +RT＝90+10＝100

This set of data (T _L2 =90, T _L1 =100) is the upper temperature limit of the cooling water entering and leaving the condenser at WB=83, that is, the set maximum allowable operating condition.

At this time, the heat load Q _C of the condenser can be obtained by the following formula,

Q _C ＝M _L ×C _L ×(T _L1 -T _L2 )15000Btu/hr

C _L =1Btu/lb-

的值由(式8)可求得

The value of can be obtained from (Equation 8)

$\frac{\mathrm{<span\; class="notranslate">\; f</span>}}{\mathrm{<span\; class="notranslate">\; k</span>}}<span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; 0.976</span>}$

Example 2: Changes of T _L1 and T _L2 when the heat load of the condenser decreases.

When the operating conditions M _L , M _G and WB are the same as in Example 1, and the heat load of the condenser is reduced, the temperature measuring devices 21 and 22 of the condenser can know the changes of the inlet and outlet temperatures T _L1 and T _L2 of the cooling water . The changed values are respectively T _L1 =95°F and T _L2 =88°F.

From the above (Equation 11), the thermal load Q _C can be calculated

Q _C ＝M _L ×C _L ×(T _L1 -T _L2 )10500Btu/hr

的值也必须和例1相同，

为0.976。利用此 $\frac{\mathrm{fA}}{k}=0.976$ 的条件，代入(式8)，亦可求得一组对应的T_L1和T_L2。通过数值计算，可知T_L1＝95.24，T_L2＝88.24，由温度量测器(21)和(22)所得量测值约为T_L1＝95，T_L2＝88，两者可近似视为相等。以下的节能的实施例以70％的热负载为依据。Compared with the Q _C of Example 1, it is about 70% (=10500/15000), that is, a decrease of 30%. Since the operating conditions M _L , M _G and WB at this time are the same as in Example 1, so

The value of must also be the same as Example 1,

is 0.976. use this $\frac{f}{k}=0.976$ Conditions, substituting (Equation 8), can also obtain a set of corresponding T _L1 and T _L2 . Through numerical calculation, it can be known that T _L1 = 95.24, T _L2 = 88.24, the measured values obtained by the temperature measuring devices (21) and (22) are about T _L1 = 95, T _L2 = 88, both can be Approximately considered equal. The following energy saving examples are based on a 70% heat load.

Example 3:

Countermeasures when the heat load of the condenser is reduced. Decrease the cooling air flow rate M _G so that the temperature T _L2 of the cooling water entering the condenser rises from 88°F in Example 2 to the upper limit temperature of 90°F in Example 1 to save power energy.

It is known from Example 2 that when the thermal load of the condenser is reduced by 70% of Example 1, the temperature T _L2 of the cooling water entering the condenser becomes 88 . In order to save electric energy, the flow M _G of the cooling air is reduced at this time , the cooling capacity of the cooling water tower is thus reduced, causing the temperature of the cooling water to rise. Since the upper limit of the temperature of the cooling water entering the condenser is 90 , the purpose can be achieved through the control of the temperature measuring device of the cooling water at 22°C, and the power energy is saved at the same time. This energy-saving method has been widely used at present, and the former patent of Taiwan Patent Publication No. " 305447 " and the name "cooling water tower whose energy can be automatically adjusted and changed with load changes" also adopts this method. It can be known from the aforementioned numerical calculation method; the state at this time is as follows

T _L1 = 97, T _L2 = 90, $\frac{f}{k}=2.802$

The cooling air flow has been changed, of course The value of will also change accordingly, and the thermal load Q _C of the condenser can be obtained by the following formula.

Q _C ＝M _L ×C _L ×(T _L1 -T _L2 )10500Btu/hr

Still 70% of Example 1.

Example 4:

When the thermal load of the condenser is reduced, the utility model provides a countermeasure. Reduce cooling water M _L and cooling air M _G flow at the same time, make the temperature of cooling water entering and leaving the condenser from T _L1 = 95 , T _L2 = 88  of Example 2; rise to the maximum allowable operating condition T _L1 = as mentioned above 100°F, T _L2 =90°F.

This method first reduces the cooling water flow M _L , and then lowers the cooling air flow M _G . Compared with the method proposed in the previous patent of example 3, the power energy is greatly reduced, and a more effective energy saving effect is achieved. This method is the utility model main content of .

From example 3, we know that reducing the amount of cooling air can increase the temperature of the water entering and leaving the condenser to T _L1 = 97 , T _L2 = 90 . However, the upper limit temperature of the condenser is T _L1 = 100 , T _L2 = 90 , and it is known from the data that T _L1 still has a utilization range of 3  (= 100 -97 ). Therefore, under the condition of maintaining Q _C at 10500Btu/hr, using the aforementioned numerical calculation method, it can be obtained that when the cooling water volume M _L =21GPM, the cooling air flow M _L =18GPM, and MLG=1.167, T _L1 =100 , T _L2 ＝90 reaches the upper limit temperature, at this time The value of becomes 0.960, and the heat load Q _C of the condenser can be obtained by the following formula

Q _C ＝M _L ×C _L ×(T _L1 -T _L2 )＝21×CL×(100-90)10500Btu/hr

It can be seen that it is still 10500Btu/hr. As a result, it is known that the cooling water flow rate and the cooling air flow rate can be reduced, and the operating range of Example 1 can still be maintained.

It can be verified from the calculation results that when the heat load becomes 70%, the cooling water flow rate is about 70% (=21GPM/30GPM) of the original (Example 1) cooling water flow rate. From this conclusion, the control method applied to the cooling water flow is as follows;

From the temperature measuring devices 21 and 22 of the cooling water, it is known that the temperature T _L1 = 95  and T _L2 = 88  after the heat load of the condenser is reduced, and the temperature difference ΔT = 7  is obtained. The temperature difference ΔT between the upper limit temperatures set by the condensers _TL1 and _TL2 is 10°F (=100°F-90°F), and the ratio between them is 0.7 (=7/10). The cooling water flow is then adjusted to 21GPM (=30GPM×0.7) from the original 30GPM in the upper limit temperature state by 30%, and then the cooling air flow M _G is adjusted so that the readings from the temperature measuring devices 21 and 22 are respectively T _L1 =100, T _L2 =90. Since the energy required for cooling water transportation is much greater than that of cooling air, reducing the flow rate of cooling water will greatly save the energy consumption of the water pump 23. Therefore, the energy saving method of this case is not only far better than the energy saving method of the previous case in Example 3, and the numerical value The calculation derivation and the verification of the actual measurement are indeed correct and feasible. The overall control is shown in Figure 4. The content contained in the dotted line in the figure can be integrated by the programmable logic controller in actual application.

Example 5: When the heat load of the condenser is still 100% and the external environment becomes colder, so that the wet bulb temperature WB of the external air is reduced from 83  (Example 1) to 81 , how to adjust the cooling water inlet and outlet temperature The values of T _L1 and T _L2 .

值仍为0.976，范围度RT维持在10，而此时外界的WB值降为81时，以上述条件利用前述的数值计算方法可求得符合此状态的冷却水进出口温度T_L1＝98.5、T_L2＝88.5。此时接近度AP由原来(例1)的7.0改变为7.47，在冷凝器100％热负载下。接近度AP和冷却空气进入冷却塔时的湿球温度WB之间的关系，可用前述数值计算方法求得，其关系如图5。当WB为81时，AP约为7.5。冷却水的T_L2＝WB+AP为最佳值，所以T_L2＝81+7.5＝88.5Since the heat load of the condenser is still 100%, the cooling water and cooling air flows are still M _L =30 GPM, M _G =25 GPM, respectively. MLG is still 1.2 (=30/25) the heat load Q _C of 100% of condenser is known to be 15000Btu/hr by example 1, so the cooling water tower

The value is still 0.976, the range degree RT is maintained at 10 , and at this time the external WB value drops to 81 , the cooling water inlet and outlet temperature T _L1 corresponding to this state can be obtained by using the above-mentioned numerical calculation method. 98.5°F, T _L2 =88.5°F. At this time, the proximity AP is changed from 7.0 to 7.47 in the original (Example 1), under 100% heat load of the condenser. The relationship between the proximity AP and the wet bulb temperature WB when the cooling air enters the cooling tower can be obtained by the aforementioned numerical calculation method, and the relationship is shown in Figure 5. When WB is 81, AP is about 7.5. T _L2 =WB+AP of cooling water is the best value, so T _L2 =81+7.5=88.5

值变为0.974。If you want to save energy at this time, as in the previous case in Example 3, reduce the cooling air volume M _G alone, so that MLG becomes 1.65, which can save the power energy of the cooling tower fan, and make T _L1 = 100, T _L2 = 90 ,

The value becomes 0.974.

In a general system, the energy of the chiller doing work (mainly by the compressor 5) is about 15 times the energy of the cooling tower doing work (mainly by the fan 11). When the cooling air flow rate is reduced, T _L2 rises from 88.5 to 90, which saves the power energy of the fan, but the accompanying result makes T _L1 rise from 98.5 to 100, which increases the work of the chiller and consumes more Energy, generally speaking, can't achieve the effect of saving because of small losses. Therefore, in the previous proposal of example 3, the effect of saving cannot be achieved by setting a fixed T _L2 from 90  (this data is provided by the manufacturer, under the conditions of full load and external WB of 83 ).

In contrast to the method of the present utility model, from the results in Fig. 5, T _L2 can be adjusted to be 88.5 , and T _L1 can be obtained as 98.5  under the conditions that the cooling water and cooling air flow rates are still M _L = 30GPM and M _G = 25GPM respectively. The temperature of the water entering and leaving the condenser has dropped, which means that the work done by the chiller has decreased, thus achieving the purpose of energy saving. Attempts to increase the flow of cooling air to keep T _L2 below 88.5°F at this point would be futile only to increase energy use, because from Figure 5, WB plus AP would be the minimum for T _L2 value. When the heat load of the condenser decreases at this time, it can be adjusted according to the method mentioned in Example 4 in this case, which can save more energy. Therefore when the temperature measuring device 14 of the cooling air measures and knows that the wet bulb temperature (WB) of the outside air drops, the upper limit temperature of the cooling water entering the condenser is set according to the result of FIG. That is to achieve the most efficient energy use conditions.

Claims (12)

1. A cooling water tower that can automatically adjust the flow of cooling water and cooling air as the load changes, wherein the cooling water tower includes a main body of the cooling water tower, a hygrometer, a water pump that can be controlled by frequency conversion, multiple temperature measuring devices, and has computing functions The controller is characterized in that: the main body of the cooling water tower is used in parallel with one or more groups to inhale cooling air to cool the inflowing cooling water, the hygrometer is installed in the cooling water tower, and the cooling water pump that can be controlled by frequency conversion is installed In the cooling water flow channel, and a plurality of temperature measuring devices are installed at the inlet and outlet of cooling air and cooling water, and connected to the controller, including at least one used to calculate the wet bulb temperature of the cooling air and the cooling water entering and leaving the cooling The temperature difference controller of the water tower, wherein the controller is pre-set with the maximum allowable operating conditions and the data of the proximity corresponding to the wet bulb temperature of the built-in external air. 2. The cooling water tower capable of automatically adjusting the cooling water flow and the cooling air flow as the load changes according to claim 1, wherein the main body of the cooling water tower includes a cooling fan, a cooling plate and a water tank that can be controlled by frequency conversion. 3. The cooling water tower capable of automatically adjusting the cooling water flow and the cooling air flow as the load changes according to claim 2, wherein the cooling fan that can be controlled by frequency conversion is controlled by a controller to control the amount of cooling air flow . 4. The cooling water tower capable of automatically adjusting cooling water flow and cooling air flow as the load changes according to claim 1, characterized in that the cooling water pump that can be controlled by frequency conversion is controlled by a controller to control the amount of cooling water flow. 5. The cooling water tower capable of automatically adjusting cooling water flow and cooling air flow according to claim 1, wherein the cooling water tower includes four thermometers and three controllers. 6. The cooling water tower capable of automatically adjusting the flow of cooling water and the flow of cooling air as claimed in claim 5, characterized in that two of the four temperature measuring devices are respectively installed in and out of the condensing The cooling water channel of the condenser is used to measure the water temperature when the cooling water enters and exits the condenser respectively, and is connected with the controller. 7. The cooling water tower capable of automatically adjusting the cooling water flow and the cooling air flow as the load changes according to claim 5, characterized in that two of the four temperature measuring devices are installed at the inlet and outlet cooling towers respectively. The cooling air inlet and outlet of the water tower are used to measure the temperature of the cooling air when it enters and exits the cooling water tower, and connect it with the controller. 8. The cooling water tower capable of automatically adjusting cooling water flow and cooling air flow as the load changes as claimed in claim 5, characterized in that, the first controller in the three controllers contains a calculation program and receives humidity The first controller is connected with another second controller based on the data collected by the meter and the temperature measuring device installed at the cooling air inlet of the cooling water tower. 9. The cooling water tower capable of automatically adjusting cooling water flow and cooling air flow as claimed in claim 8, characterized in that, the third controller among the three controllers is connected to the condenser installed in and out of the cooling tower. The two temperature measuring devices of the cooling water channel are connected. 10. The cooling water tower capable of automatically adjusting the cooling water flow and the cooling air flow as the load changes according to claim 8, characterized in that the second controller among the three controllers is set with a maximum allowable operation Conditions, and connected with the first and third controllers, and it retrieves the measured external air wet bulb temperature and cooling water inlet and outlet temperature difference data, and compares with the maximum allowable operating conditions to determine the best cooling Water flow and cooling air flow, and send signals to a cooling water pump that can be controlled by frequency conversion and a cooling air fan that can be controlled by frequency conversion. 11. The cooling water tower capable of automatically adjusting cooling water flow and cooling air flow as load changes according to claim 1, characterized in that the data of the corresponding proximity of the wet bulb temperature of the outside air is built in the controller. 12. The cooling water tower that can automatically adjust the cooling water flow and cooling air flow as the load changes according to claim 1, characterized in that the controller simultaneously controls and uses multiple cooling water towers of the same type in parallel.

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