CN217559993U - Indirect evaporative cooling system - Google Patents

Abstract

The application provides an indirect evaporative cooling system for the computer lab heat dissipation. The indirect evaporative cooling system comprises a cooling loop, a heat exchange unit and a mechanical evaporative cooling unit, wherein the heat exchange unit and the mechanical evaporative cooling unit are arranged on the cooling loop; the heat exchange unit is provided with a first air channel and a second air channel, the first air channel is used for first air circulation, and the second air channel is used for second air circulation outside the machine room; the temperature of the second air is lower than that of the first air, and the second air is used for heat exchange with the first air; the mechanical evaporative cooling unit comprises an evaporator and a condenser, the evaporator is arranged on the air outlet side of the first air channel, the condenser is communicated with the evaporator, and the condenser avoids the air outlet side of the second air channel. The application provides a mechanical evaporation cooling unit can not increase the windage of system, can assist heat transfer unit to carry out good heat dissipation to first air for entire system has higher radiating efficiency.

Description

Indirect evaporative cooling system

Technical Field

The application relates to the technical field of sensors, in particular to an indirect evaporative cooling system.

Background

Indirect evaporative cooling refers to a process of transferring the cold energy of wet air (secondary air) obtained by direct evaporative cooling to air to be treated (primary air) through a non-direct contact heat exchanger to cool the air to be treated. Because the air is not in direct contact with water, the moisture content of the air is kept unchanged, and the primary air change process is an equal-humidity cooling process.

At present, an indirect evaporation refrigeration system mostly adopts mechanical refrigeration auxiliary refrigeration, wherein a mechanical refrigeration part is generally not arranged on a fresh air outlet side of a heat exchange core, so that the wind resistance of the system is increased, the mechanical refrigeration energy efficiency is lower, and the cooling effect is limited.

SUMMERY OF THE UTILITY MODEL

The application provides an indirect evaporative cooling system can provide good heat dissipation for the computer lab, has higher radiating efficiency.

In a first aspect, the present application provides an indirect evaporative cooling system that may be used to dissipate heat for a machine room. The indirect evaporative cooling system comprises a cooling loop, and a heat exchange unit and a mechanical evaporative cooling unit which are arranged on the cooling loop; the cooling circuit is used for being communicated with the machine room so as to circulate first air in the machine room, and the first air in the machine room can return to the machine room after being cooled by the cooling circuit. Specifically, the heat exchange unit is used for performing gas-gas heat exchange on first air of the machine room. The heat exchange unit is provided with a first air channel and a second air channel, the first air channel is used for first air circulation, and the second air channel is used for second air circulation outside the machine room. Wherein the second air has a temperature lower than that of the first air, the second air being for heat exchange with the first air. When the second air circulates in the second air channel, the first air circulates in the first air channel, and the second air can take away the heat of the first air through the heat exchange unit, so that the first air is cooled. The mechanical evaporative cooling unit comprises an evaporator and a condenser, wherein the evaporator is arranged on the air outlet side of the first air channel, the heat of the first air can be absorbed by the evaporator to gasify the refrigerant in the evaporator, the gasified refrigerant is transmitted to the condenser to be cooled and liquefied, and the liquefied refrigerant can return to the evaporator again to realize the circulation of the refrigerant. The condenser avoids the air outlet side of the second air channel, namely the circulation paths of the condenser and the second air are not interfered with each other, the condenser cannot increase the wind resistance of a system, the circulation of the second air cannot be interfered, and good heat exchange can be realized with the first air.

It can be seen that the mechanical evaporative cooling unit that this application provided can not increase the windage of system, can assist heat exchange unit to carry out good heat dissipation to first air for entire system has higher radiating efficiency.

The indirect evaporative cooling system also comprises a liquid storage tank communicated with the second air channel, and cooling liquid is stored in the liquid storage tank; the liquid storage tank is provided with an air outlet for exhausting the second air, and the condensing unit is arranged in the liquid storage tank. The cooling liquid in the liquid storage tank is beneficial to heat dissipation of the condenser, and is also beneficial to the circulation efficiency of the refrigerant between the evaporator and the condenser, and the first air is well dissipated.

In particular, the condenser may be a plate-type evaporative condenser or a tube-type evaporative condenser, in which case the condenser may be disposed above the coolant of the reservoir. Alternatively, the condenser may be a submerged condenser, in which case the condenser is submerged in the cooling liquid of the liquid storage tank.

In some possible implementations, a compressor is disposed between the outlet of the evaporator and the inlet of the condenser, and a first circulation pump is disposed between the inlet of the evaporator and the outlet of the condenser. Wherein, the fluorine pump can be selected as the first circulating pump specifically to reduce system energy consumption.

An auxiliary cooling unit is also arranged in the liquid storage tank and is positioned between the air outlet of the liquid storage tank and the cooling liquid. When the cooling liquid is heated and gasified, the cooling liquid rises to the auxiliary cooling unit, the auxiliary cooling unit can absorb the heat of the gaseous cooling liquid, the gaseous cooling liquid is liquefied, and the liquefied cooling liquid falls back to the bottom of the liquid storage tank. The auxiliary cooling unit may particularly comprise an evaporative cooling filling and/or a membrane heat exchanger core.

In addition, the liquid storage box is also provided with an air inlet, and air flow can be formed between the air inlet and the air outlet, so that the air flow is favorable for cooling the air in the liquid storage box. In order to regulate and control the air inlet quantity, an air inlet valve is arranged at the air inlet. The air inlet valve can adjust the air inlet quantity, and then the air circulation rate in the liquid storage tank is adjusted.

The air inlet side of the second air channel is also provided with a spraying unit which can perform spraying heat dissipation for second air entering the second air channel. The spraying unit is communicated with the liquid storage tank, and cooling liquid in the liquid storage tank can supply liquid to the spraying unit.

In some possible implementation modes, the heat exchange unit is of a telescopic structure, so that the volume of the heat exchange unit can be extended or shortened, and when the volume of the heat exchange unit is shortened, the wind resistance of the system can be reduced. The volume of the heat exchange unit can be changed, and the ventilation quantity of the first air duct and/or the second air duct can be adjusted. The ventilation quantity of at least one of the first air channel and the second air channel is adjusted to change the heat exchange efficiency of the first air and the second air. The telescopic structure of the heat exchange unit can reduce the size of the heat exchange unit and reduce the ventilation quantity of the first air channel and/or the second air channel when the heat exchange unit does not need to work at full power, and further reduces the heat exchange efficiency of the first air and the second air.

In order to adapt to more application scenarios, the evaporator may be disposed in the machine room in the form of a wind wall, a room-level air conditioner, an administrative air conditioner, a back panel, an overhead air conditioner, or the like, so as to implement a separate architecture of the mechanical evaporative cooling unit.

Drawings

FIG. 1 is a schematic diagram of an indirect evaporative cooling system of the prior art;

fig. 2a and fig. 2b are schematic structural diagrams of an indirect evaporative cooling system provided in an embodiment of the present application;

FIG. 3a is a schematic structural diagram of a heat exchange unit in an indirect evaporative cooling system according to an embodiment of the present disclosure;

FIG. 3b is a perspective view of the heat exchange unit of FIG. 3 a;

FIG. 4 is a schematic structural diagram of a heat exchange unit in an indirect evaporative cooling system according to an embodiment of the present disclosure;

FIG. 5 is a schematic diagram of a first core structure of a heat exchange unit in an indirect evaporative cooling system according to an embodiment of the present application;

FIG. 6 is a schematic structural diagram of a second core of a heat exchange unit in an indirect evaporative cooling system according to an embodiment of the present disclosure;

fig. 7a to 7c are schematic diagrams illustrating the state of change of the expansion and contraction of the heat exchange unit in the indirect evaporative cooling system according to the embodiment of the present application;

FIGS. 8a and 8b are schematic structural diagrams of an indirect evaporative cooling system provided in an embodiment of the present application;

FIG. 9 is a schematic structural diagram of an indirect evaporative cooling system according to an embodiment of the present disclosure;

FIG. 10 is a schematic structural diagram of an indirect evaporative cooling system according to an embodiment of the present disclosure;

FIG. 11 is a schematic structural diagram of an indirect evaporative cooling system according to an embodiment of the present disclosure;

FIG. 12 is a schematic diagram of a heat exchange unit in an indirect evaporative cooling system according to an embodiment of the present disclosure.

Reference numerals are as follows: 1-a heat exchange unit; 11-a first core; 111-port section; 112-a first telescoping section; 12-a second core; 121-side plate; 122-a second telescoping section; 2-a mechanical evaporative cooling unit; 21-an evaporator; 22-a condenser; 3-a compressor; 4-a first circulation pump; 5-a liquid storage tank; 51-an air inlet valve; 61-a first fan; 62-a second fan; 7-an auxiliary cooling unit; 8-a spraying unit; 81-second circulation pump.

Detailed Description

An indirect evaporative cooling system is a commonly used heat dissipation system at present, and particularly, an air cooling mode is mostly adopted in a mechanical refrigeration part of the system. Fig. 1 shows a schematic diagram of an indirect evaporative cooling system having a cooling circuit A1 for cooling the primary air in the machine room. Two ends of the cooling loop A1 are communicated with the machine room, and the cooling loop A1 is sequentially provided with a heat exchange core 1 'and an evaporator 2'. In order to radiate heat to the evaporator 2', an air-cooled condenser 3' is also arranged, and gas-liquid circulation is realized between the evaporator 2' and the air-cooled condenser 3' through a compressor 4 '. The system also has a fresh air circuit A2 passing through the heat exchange core 1', and the fresh air circuit A2 is used for circulating secondary air with lower temperature. A spraying assembly 5' for spraying and radiating secondary air is arranged at the secondary air inlet of the heat exchange core 1', a water tank 6' for supplying water is arranged for the spraying assembly 5', and water in the water tank 6' is circularly supplied to the spraying assembly 5' through a water pump 7 '. The heat exchange core 1 'can simultaneously supply the primary air in the cooling loop A1 and the secondary air in the fresh air loop A2 to circulate, and the primary air and the secondary air exchange heat at the heat exchange core 1' so that the temperature of the primary air is reduced and the primary air returns to the machine room again to complete the cooling circulation of the air in the machine room. In the system, the air-cooled condenser 3' is arranged on the secondary air outlet side of the heat exchange core 1', so that the air-cooled condenser 3' can increase the air resistance of secondary air circulation, the mechanical refrigeration energy efficiency is low, and the cooling effect is not ideal.

Based on this, the embodiment of the application provides an indirect evaporative cooling system that can be applied to heat dissipation of a machine room, so as to solve the above problems. In order to make the objects, technical solutions and advantages of the present application more clear, the present application will be further described in detail with reference to the accompanying drawings.

The terminology used in the following examples is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in the specification of this application and the appended claims, the singular forms "a", "an", "the" and "the" are intended to include the plural forms as well, such as "one or more", unless the context clearly indicates otherwise.

Reference throughout this specification to "one embodiment" or "some embodiments," or the like, means that a particular feature, structure, or characteristic described in connection with the embodiment is included in one or more embodiments of the present application. Thus, appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," or the like, in various places throughout this specification are not necessarily all referring to the same embodiment, but rather mean "one or more but not all embodiments" unless specifically stated otherwise. The terms "comprising," "including," "having," and variations thereof mean "including, but not limited to," unless expressly specified otherwise.

As shown in FIG. 2a, this application embodiment provides an indirect evaporative cooling system, and this indirect evaporative cooling system is used for supporting computer lab for the computer lab cooling, specifically gets back to the computer lab again after cooling the higher first air cooling of temperature in the computer lab, can realize the cooling of computer lab indoor air. As shown in fig. 2a, the machine room has an air outlet K1 and an air return opening K2, the air outlet K1 is used for discharging the first air in the machine room, and the air return opening K2 is used for returning the first air after temperature reduction to the machine room. The indirect evaporative cooling system is provided with a cooling loop B1 for first air circulation, namely, the first air is exhausted from an air outlet K1 of the machine room and then returns to an air return port K2 through the cooling loop B1. In order to cool the first air, the indirect evaporative cooling system is also provided with a fresh air loop. The fresh air loop is used for second air circulation, the second air is located outside the machine room, and the temperature of the second air is lower than that of the first air. This new trend return circuit B2 intersects with cooling circuit B1, and first air and second air can carry out cold and hot exchange at new trend return circuit B2 and cooling circuit B1's intersection, specifically are the heat that the first air was taken away to the second air, realize the cooling of first air.

With continued reference to fig. 2a, the indirect evaporative cooling system includes a heat exchange unit 1 and a mechanical evaporative cooling unit 2. The heat exchange unit 1 is specifically arranged at the intersection of the fresh air loop B2 and the cooling loop B1. In order to facilitate the air-air cooling heat exchange between the first air and the second air, the heat exchange unit 1 may be used for the first air circulation and the second air circulation, and the first air circulation is isolated from the second air circulation, so that only heat transfer is achieved. Specifically, when first air and second air circulate in heat exchange unit 1 simultaneously, the heat of first air can transmit the second air, and the heat of first air is taken away to the second air and is realized the cooling to first air. The mechanical evaporative cooling unit 2 specifically includes an evaporator 21 and a condenser 22, and the evaporator 21 is disposed on the air outlet side of the first air to absorb heat of the first air. The liquid refrigerant in the evaporator 21 absorbs the heat of the first air, and then is gasified into a gaseous refrigerant and transferred to the condenser 22, and the condenser 22 is used for condensing the gaseous refrigerant into a liquid refrigerant and returning the liquid refrigerant to the evaporator 21 again, and absorbs the heat of the first air through gas-liquid state conversion. Wherein, new trend return circuit B2 is through the lower second air of temperature and the higher first air heat exchange of temperature to first air cooling, and the windage size of second air at the circulation in-process has influenced new trend return circuit B2's refrigeration efficiency. The condenser 22 is evacuated from the fresh air circuit B2, i.e., the condenser 22 does not interfere with the flow of the second air.

It can be seen that the condenser 22 in the embodiment of the present application does not interfere with the fresh air circuit B2, and does not increase the wind resistance of the fresh air circuit B2, which is beneficial to the second air to cool the first air. Simultaneously, the second air in new trend return circuit B2 lies in first air heat exchange back temperature rising, and condenser 22 can give off the heat to the condensation of gas, and condenser 22 in this application embodiment does not interfere with new trend return circuit B2, and the second air that has absorbed the heat of first air can not become the liquid with the gas condensation to condenser 22 and cause adverse effect for evaporimeter 21 and condenser 22 can be to the circulative cooling of first air.

Referring to fig. 2a, in order to realize gas-liquid communication between the evaporator 21 and the condenser 22, the compressor 3 is provided on a path through which the evaporator 21 feeds the gaseous refrigerant to the condenser 22. Specifically, the compressor 3 is disposed between an outlet of the evaporator 21 and an inlet of the condenser 22. The compressor 3 sucks the gaseous refrigerant in the evaporator 21, compresses the gaseous refrigerant, increases the pressure of the gas, and sends the compressed gaseous refrigerant to the condenser 22. The compressor 3 here may in particular be a gas suspension compressor or a normal compressor, capable of providing a compression function for the gaseous refrigerant in the mechanical evaporative cooling unit 2. Wherein the compressor 3 can be an oil-free compressor, which can improve the reliability of the system.

As shown in fig. 2b, the condenser 22 condenses the gaseous refrigerant into liquid refrigerant and sends it back to the evaporator 21 again. The first circulation pump 4 is provided on a path through which the condenser 22 sends the liquid refrigerant to the evaporator 21. Specifically, the first circulation pump 4 is disposed between the inlet of the evaporator 21 and the outlet of the condenser 22. The first circulation pump 4 is a fluorine pump, and may be a liquid floating fluorine pump or a common fluorine pump without oil lubrication. First circulating pump 4 chooses for use the fluorine pump, can reduce entire system's energy consumption, and then can promote mechanical evaporation cooling unit 2's full operating mode energy efficiency. With continued reference to the indirect evaporative cooling system shown in fig. 2b, a first fan 61 for driving the first air flow is disposed on the air outlet side of the evaporator 21.

In specific use, the boiling point of the refrigerant can be set to be close to the dew point temperature, so that the condensation temperature of the mechanical evaporative cooling unit 2 can be further reduced, and a more efficient evaporative cooling effect is achieved. Alternatively, the cold water close to the evaporation cooling temperature may be directly sent to the evaporator 21 to cool the first air.

The structure of the heat exchange unit 1 can be exemplified with reference to fig. 3 a. In fig. 3a, the heat exchanging unit 1 has a first air channel D1 and a second air channel D2, the first air channel D1 is used for the first air circulation, and the second air channel D2 is used for the second air circulation. The number of the first air ducts D1 is plural, the plural first air ducts D1 are arranged in parallel along a first direction, and the first direction is perpendicular to the circulation direction of the first air in the first air ducts D1. The number of the second air ducts D2 is plural, the plural second air ducts D2 are arranged in parallel along a second direction, and the second direction is perpendicular to the circulation direction of the second air in the second air ducts D2. In the embodiment of the application, the first direction is perpendicular to the second direction.

Referring to the perspective view of the heat exchange unit 1 illustrated in fig. 3b, it can be seen that the first air duct D1 and the second air duct D2 are isolated from each other, and the plurality of first air ducts D1 and the plurality of second air ducts D2 are located on different structural layers, that is, the first air ducts D1 and the second air ducts D2 are located at different height positions of the heat exchange unit 1. In operation, the first air circulates in the first air duct D1, the second air circulates in the second air duct D2, and heat of the first air can be transferred to the second air through the heat exchange unit 1, so that the second air can absorb and take away heat of the first air, and air-air cooling heat exchange is realized. Here, the material of the heat exchange unit 1 may be a material with good heat conductivity, such as aluminum or aluminum alloy. The condenser 22 specifically avoids the air outlet side of the second air duct D2, namely, the condenser 22 does not interfere with the air outlet side of the second air duct D2, so that the wind resistance of the heat exchange unit 1 cannot be increased by the condenser 22, the circulation of the second air in the second air duct D2 is affected, and the heat exchange efficiency of the second air and the first air is further improved.

It should be understood that the structure of the heat exchange unit 1 illustrated in fig. 3a and 3b is only an example, and in practical applications, there are other possible ways to implement the structure of the heat exchange unit 1, as long as the first air in the first air duct D1 and the air in the second air duct D2 can achieve heat and cold exchange.

In the embodiment of the present application, the heat exchange unit 1 is used for the heat exchange between the first air and the second air to cool the first air. Meanwhile, the mechanical evaporative cooling unit 2 can also cool the first air through gas-liquid conversion of the refrigerant. Possibly, in some application scenarios, the first air of the heat exchange unit 1 is not required to be cooled, or the heat exchange unit 1 is not required to run at the highest power. Based on the requirement, when the first air of the heat exchange unit 1 is not needed to be cooled or the heat exchange unit 1 does not need to operate at the highest power, only one or several second air ducts D2 in the heat exchange unit 1 illustrated in fig. 3a or fig. 3b may be used, which is equivalent to reducing the ventilation volume of the second air ducts D2, so that the energy consumption may be reduced.

Specifically, the heat exchange unit 1 may be a retractable structure, so that the size of the whole heat exchange unit 1 may be extended or contracted, thereby changing the volume of the heat exchange unit 1. The volume of the heat exchange unit 1 is reduced, the wind resistance of the system can be reduced, the ventilation quantity of the first air channel D1 and/or the second air channel D2 can also be reduced, and then the heat exchange efficiency of the first air and the second air is reduced. When the demand for cooling in the machine room is lower or other more suitable cooling modes exist, the power consumption of the heat exchange unit can be reduced by reducing the size of the heat exchange unit 1.

In some embodiments, as shown in fig. 4, another heat exchange unit 1 in the embodiment of the present application may specifically include a first core 11 and a second core 12, where the first core 11 is formed with a first air duct D1, and the second core 12 is formed with a second air duct D2. As shown in fig. 5, the structure of the first core 11 includes two port portions 111 and a first stretchable portion 112 connected between the two port portions 111. The first extendable portion 112 has a cylindrical shape and can form the first air passage D1. The first stretchable and contractible portion 112 may be stretched or contracted in the second direction. When the first telescopic part 112 is extended, the two port parts 111 approach to each other, and the length of the first air duct D1 is shortened; when the first extendable portion 112 is extended, the two port portions 111 are separated, and the length of the first air path D1 is increased. Correspondingly, the structure of the second core 12 can be seen with reference to fig. 6. The second core 12 includes two side plates 121 and two second stretchable parts 122 connected between the two side plates 121, and the two second stretchable parts 122 and the two side plates 121 may enclose a second air duct D2. The two second extendable portions 122 may be extended or shortened in the second direction as shown. When the second extendable portion 122 extends, the inner diameter of the second air path D2 increases, and the ventilation volume of the second air path D2 increases. When the second extendable portion 122 is shortened, the inner diameter of the second air passage D2 is reduced, and the ventilation volume of the second air passage D2 is reduced. As shown in fig. 5 and 6, when the first stretchable and contractible portion 112 and the second stretchable and contractible portion 122 are simultaneously stretched or shrunk in the second direction, the size of the heat exchange unit 1 in the second direction may be increased or decreased. The first telescopic part 112 and the second telescopic part 122 are equivalent to realize that the structural size of the heat exchange unit 1 is adjustable.

The heat exchange efficiency of the first air passing through the first air duct D1 and the second air passing through the second air duct D2 in the heat exchange unit 1 is positively correlated to the size of the heat exchange unit 1. When the size of the heat exchange unit 1 is reduced, the heat exchange efficiency of the first air and the second air is reduced. When the heat exchange unit 1 is not required to cool down the first air or when the heat exchange unit 1 is not required to operate at the highest power, the size of the heat exchange unit 1 can be reduced by adjusting the first stretchable part 112 and the second stretchable part 122. The size of the heat exchange unit 1 is reduced, which is equivalent to the reduction of the size of the heat exchange unit 1, so that the wind resistance of the whole system is reduced, and the system cooling efficiency is improved.

Referring to fig. 5 and 6, the process of adjusting the size of the heat exchange unit 1 according to different cooling requirements can be illustrated in fig. 7a to 7c, and for convenience of observing the size change of the heat exchange unit 1, two heat exchange units 1 are provided, which are referred to herein as the evaporator 21. In fig. 7a, the heat exchange unit 1 is in a maximum size state, at which time the heat exchange unit 1 can operate at maximum power, and the first air in the first air duct D1 and the second air in the second air duct D2 can exchange heat and cold with maximum efficiency. In fig. 7b, the size of the heat exchange unit 1 along the second direction is reduced, and compared to the state shown in fig. 7a, at this time, the heat exchange efficiency between the first air in the first air duct D1 and the second air in the second air duct D2 is lower. In fig. 7c, the heat exchange unit 1 continues to shrink to the minimum size along the second direction, and compared to the state shown in fig. 7b, the first air in the first air duct D1 and the second air in the second air duct D2 do not exchange heat. In the state of the heat exchange unit 1 shown in fig. 7c, the ventilation volume of the second air duct D2 is the smallest, and it can be considered that at this time, substantially no second air can pass through the second air duct D2.

With reference to the heat exchange unit 1 shown in fig. 5 to 7c, in the heat exchange unit 1 provided in the embodiment of the present application, the structure of the second core 12 may be adjusted along the second direction, so that the wind resistance of the heat exchange unit 1 to the circulation of the second air may be reduced, and the energy efficiency of the unit is improved; meanwhile, the size of the heat exchange unit 1 is adjusted according to different cooling requirements, so that the energy consumption of the unit can be reduced. It should be understood that the structure of the heat exchange unit 1 shown in fig. 5 and 6 is only an example, and the first core 11 and the second core 12 may also be elongated or shortened in the first direction at the same time. The heat exchange unit 1 may also have other structures with adjustable sizes, and the final purpose is to reduce the heat exchange efficiency between the first air in the first air duct D1 and the heat in the second air duct D2, as long as the purpose can be achieved.

The indirect evaporative cooling system that this application embodiment provided still is provided with liquid reserve tank 5, as shown in fig. 8a, liquid reserve tank 5 sets up in heat exchange unit 1 second wind channel D2's air-out side, is stored with the coolant liquid in the liquid reserve tank 5. The liquid storage tank 5 is communicated with the second air channel D2, and an air outlet P is formed in the liquid storage tank 5 in order to lead out second air discharged from the second air channel D2. In fig. 8a, the air outlet P is arranged at the top of the reservoir 5. The second air passes through the second air duct D2 of the heat exchange unit 1, enters the liquid storage tank 5, and is discharged from the air outlet P of the liquid storage tank 5. Wherein, a second fan 62 for driving the second air to flow is provided at the air outlet P of the liquid storage tank 5. With continued reference to fig. 8a, the indirect evaporative cooling system is shown wherein the condenser 22 is selected to be a submerged condenser, which is submerged in the cooling liquid in the liquid storage tank 5. The cooling fluid can absorb the heat emitted from the condenser 22 to meet the condensing requirements of the condenser 22.

In some embodiments, as shown in fig. 8b, the reservoir 5 is further provided with an air inlet Q. Air in the external environment can enter the liquid storage box 5 through the air inlet Q, and the air in the liquid storage box 5 is discharged from the air outlet P under the driving of the second fan 62. The air inlet Q and the air outlet P can form air flow in the liquid storage tank 5 to take away heat of the cooling liquid, and are also beneficial to the heat dissipation of the cooling liquid to the condenser 22. In order to control the air intake, an intake valve 51 is provided at the intake Q.

Alternatively, as shown in fig. 9, the condenser 22 may be a plate-type evaporative condenser or a tube-type evaporative condenser, and in this case, the condenser 22 is provided in the liquid storage tank 5 so as not to contact the coolant. The air inlet Q and the air outlet P can form air flow in the liquid storage tank 5 and can also perform air cooling function on the condenser 22 to absorb heat emitted by the condenser 22.

In order to improve the heat radiation effect to the condenser 22, for example, a submerged condenser, as shown in fig. 10, an auxiliary cooling unit 7 may be further provided in the liquid storage tank 5. Auxiliary cooling unit 7 is located between coolant liquid and the air exit P, and the coolant liquid absorbs gasification evaporation behind the radiating heat of condenser 22, and gaseous coolant liquid rises to auxiliary cooling unit 7, and auxiliary cooling unit 7 can carry out cooling to gaseous coolant liquid for gaseous coolant liquid liquefaction, and liquid coolant liquid falls back to the bottom of liquid reserve tank 5 under the action of gravity, realizes the evaporation cooling cycle of coolant liquid.

In particular, the auxiliary cooling unit 7 may particularly comprise an evaporative cooling filling and/or a thin-film heat exchanger core. That is, the auxiliary cooling unit 7 may include only the evaporative cooling filler, only the film heat exchange core, or both the evaporative cooling filler and the film heat exchange core. When the coolant absorbs the heat dissipated by the condenser 22 and evaporates, the gaseous coolant rises to the auxiliary cooling unit 7. The evaporative cooling filling material can absorb the heat of the gaseous cooling liquid, and the film heat exchange core can enable the gaseous cooling liquid to exchange heat with the airflow between the air inlet Q and the air outlet P. Finally, the temperature of the gaseous cooling liquid is reduced and liquefied, and the liquid cooling liquid falls back, so that the evaporative cooling circulation of the cooling liquid is realized.

As shown in fig. 11, the indirect evaporative cooling system provided in the embodiment of the present application is further provided with a spraying unit 8, and the spraying unit 8 is specifically disposed on the air inlet side of the second air duct D2 of the heat exchange unit 1. The spraying unit 8 is communicated with the liquid storage tank 5, and the liquid storage tank 5 can supply liquid for the spraying unit 8. A second circulating pump 81 is arranged between the liquid inlet of the spraying unit 8 and the liquid outlet of the liquid storage tank 5. The spraying unit 8 can spray and cool the second air before entering the second air duct D2, which is beneficial to improving the cold-heat exchange effect between the second air and the first air. The second circulation pump 81 here can be selected to be oil-free, which is beneficial to improving the reliability of the system.

In the indirect evaporative cooling system provided in the embodiment of the present application, the evaporator 21 in the mechanical evaporative cooling unit 2 may also be disposed in the machine room. As shown in fig. 12, the evaporator 21 may be provided in the machine room in the form of a wind wall, a room-level air conditioner, an administrative air conditioner, a back panel, an overhead air conditioner, or the like. In this case, the evaporator 21 corresponds to an indoor unit, and the condenser 22 corresponds to an outdoor unit. The distribution mode can further reduce the wind resistance of the system, thereby improving the energy efficiency. In particular, in implementation, the evaporator 21 can be selectively installed outdoors or indoors as required to meet different usage scenarios. In addition, the various forms of the evaporator 21 may select the end of the refrigerant inside, may select the end of the cooling water inside, or may be compatible with both refrigerant and cooling water end air conditioning.

The operation principle of the indirect evaporative cooling system provided by the embodiment of the present application will be described based on the indirect evaporative cooling system shown in fig. 12. In practical application, the strategy of cooling the first air in the machine room needs to be reasonably selected according to the difference of the outdoor temperature.

The indirect evaporative cooling system implements a first strategy when the outdoor temperature (equivalent to the second air) is lower than the first temperature. The first temperature here is below ambient temperature, for example 15 ℃. The first strategy is specifically an Air Handling Unit (AHU) mode, and under the first strategy, a fresh air loop is started to extract the second air to the heat exchange unit 1, and the second air circulates in the second air duct D2 of the heat exchange unit 1. The second air in the second air duct D2 and the first air in the first air duct D1 generate air-air cooling heat exchange in the heat exchange unit 1, so as to cool the first air. Under this strategy, the first air of the machine room is equivalent to passing through the heat exchange unit 1 and the evaporator 21 at the same time, but only exchanging heat at the heat exchange unit 1 for cooling. Here, the heat exchange unit 1 has the largest size (see fig. 7 a), which is equivalent to that the heat exchange unit 1 operates at the maximum power, and the second air in the second air duct D2 and the first air in the first air duct D1 can achieve the highest heat exchange efficiency.

The indirect evaporative cooling system implements a second strategy when the outdoor temperature is greater than the first temperature and less than a second temperature. The second temperature here is higher than the first temperature, for example 19 ℃. The second strategy is specifically a combined air conditioning box mode + evaporative condensing mode. Under this second strategy, start the new trend return circuit, extract heat exchange unit 1 with the second air, the second air circulates in heat exchange unit 1's second wind channel D2. The second air in the second air duct D2 and the first air in the first air duct D1 generate air-air cooling heat exchange in the heat exchange unit 1, so as to cool the first air. Meanwhile, the evaporator 21 and the condenser 22 are started, the evaporator 21 absorbs heat of the first air to gasify the refrigerant and transfer the refrigerant to the condenser 22 to release heat and condense the refrigerant into a liquid state, and cooling of the first air is achieved. Under this strategy, the first air of the machine room equivalently passes through the heat exchange unit 1 and the evaporator 21 at the same time, and the heat exchange unit 1 is subjected to heat exchange and temperature reduction and the evaporator 21 is subjected to heat dissipation and temperature reduction at the same time. It should be noted that under this strategy, heat exchange unit 1 can be operated at a power level greater than minimum power and less than maximum power (as shown in FIG. 7b, heat exchange unit 1 is reduced in size).

When the outdoor temperature is higher than the second temperature, the indirect evaporative cooling system implements a third strategy, which is specifically an evaporative condensation mode. Under the third strategy, the fresh air loop is closed, and the state of the heat exchange unit 1 can be as shown in fig. 7c (the heat exchange unit 1 has the smallest size, and the second air in the second air channel D2 hardly exchanges heat with the first air in the first air channel D1). The evaporator 21 and the condenser 22 are started, the evaporator 21 absorbs the heat of the first air to gasify the refrigerant and transfers the refrigerant to the condenser 22 to release heat and condense the refrigerant into a liquid state, and cooling of the first air is achieved. Under this strategy, the first air of the room is equivalent to passing only the evaporator 21 and exchanging heat at the evaporator 21.

According to experimental data, in the same external environment, if a traditional system is adopted for heat dissipation in a machine room of a data center, a Cooling Load Factor (CLF) can reach 0.088. By adopting the indirect evaporative cooling system provided by the embodiment of the application, the cooling load factor can reach 0.063, and the energy efficiency can be improved by 28%.

To sum up, the indirect evaporative cooling system provided by the embodiment of the application can be applied to heat dissipation of machine rooms with more scenes, can cool down the first air in the machine room through the heat exchange unit 1, and provides cold supplement or cold required by all the machine rooms through the mechanical evaporative cooling unit 2. The evaporator 21 of the mechanical evaporative cooling unit 2 may be a submerged condenser, a plate-type evaporative condenser, or a tube-type evaporative condenser, and is capable of absorbing heat absorbed by the evaporator 21. A gas suspension compressor or a common compressor may be used between the evaporator 21 and the condenser 22 to provide a refrigerant vapor compression function of the refrigeration cycle. The first circulation pump 4 and the second circulation pump 81 which are lubricated without oil can be adopted in the system, and the reliability of the system can be improved. When the first circulation pump 4 is an oil-free fluorine pump, the energy consumption of the system can be reduced. In addition, the system is provided with an air inlet valve 51 at the air inlet Q of the liquid storage box 5, so that the air quantity at the outdoor side can be adjusted according to the heat dissipation requirement, and the control is carried out by matching with the heat dissipation requirement of the whole unit.

The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present application, and shall be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.

Claims (11)

1. An indirect evaporative cooling system, comprising a cooling loop, and a heat exchange unit and a mechanical evaporative cooling unit disposed on the cooling loop; the cooling circuit is used for being communicated with a machine room for first air circulation in the machine room;

the heat exchange unit is provided with a first air duct and a second air duct, the first air duct is used for first air circulation, and the second air duct is used for second air circulation outside the machine room; the temperature of the second air is lower than that of the first air, and the second air is used for heat exchange with the first air;

mechanical evaporation cooling unit includes evaporimeter and condenser, the evaporimeter set up in the air-out side in first wind channel, the condenser with the evaporimeter intercommunication, just the condenser dodges the air-out side in second wind channel.

2. The indirect evaporative cooling system of claim 1, further comprising a reservoir in communication with the second air duct, the reservoir storing a cooling fluid therein, the condenser being disposed within the reservoir;

the liquid storage tank is provided with an air outlet, and the second air is discharged from the air outlet.

3. The indirect evaporative cooling system of claim 2, further comprising an auxiliary cooling unit disposed within the reservoir and between the air exit of the reservoir and the cooling liquid.

4. The indirect evaporative cooling system of claim 3, wherein the secondary cooling unit comprises an evaporative cooling fill and/or a thin film heat exchanger core.

5. The indirect evaporative cooling system of claim 2, wherein the liquid storage tank further has an air inlet, and an air inlet valve is disposed at the air inlet.

6. The indirect evaporative cooling system of claim 2, wherein the condenser is a submerged condenser, the submerged condenser being submerged within the cooling liquid.

7. The indirect evaporative cooling system of claim 2, further comprising a spray unit disposed on an air intake side of the second air duct, the liquid storage tank being in communication with the spray unit to supply liquid to the spray unit.

8. The indirect evaporative cooling system of claim 1, wherein the heat exchange unit is a retractable structure for adjusting the ventilation of the first air duct and/or the second air duct.

9. The indirect evaporative cooling system of claim 1, wherein a compressor is disposed between the outlet of the evaporator and the inlet of the condenser, and a first circulation pump is disposed between the inlet of the evaporator and the outlet of the condenser.

10. The indirect evaporative cooling system of claim 9, wherein the first circulation pump is a fluorine pump.

11. The indirect evaporative cooling system of any of claims 1-10, wherein the evaporator is disposed within the machine room.

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