CN210718297U

CN210718297U - Cooling circulation system

Info

Publication number: CN210718297U
Application number: CN201920969115.XU
Authority: CN
Inventors: 黄进; 黄绍新
Original assignee: Beijing Xinyuan Ruip Technology Development Co ltd
Current assignee: Beijing Xinyuan Ruip Technology Development Co ltd
Priority date: 2019-06-25
Filing date: 2019-06-25
Publication date: 2020-06-09
Anticipated expiration: 2029-06-25

Abstract

A cooling circulation system comprises a refrigerant box, a closed heat dissipation device and a refrigerator, wherein the cooling circulation system is communicated with a refrigerant inlet and a refrigerant outlet of a process device; the system also comprises a first temperature sensor, a second temperature sensor and a third temperature sensor, wherein the first temperature sensor is used for monitoring the refrigerant temperature of the refrigerant box, the second temperature sensor is used for monitoring the cold inlet temperature in the refrigerant outlet, and the third temperature sensor is used for monitoring the cold outlet temperature in the refrigerant outlet; the controller is suitable for controlling the refrigerant discharged from the refrigerant outlet to be introduced into the closed heat dissipation device, the refrigerant discharged from the closed heat dissipation device to be introduced into the evaporator of the refrigerating machine and the refrigerant discharged from the evaporator to be introduced into the refrigerant inlet under the first condition that the inlet cooling temperature is lower than the refrigerant temperature and the refrigerant temperature is lower than the outlet cooling temperature. The utility model provides a cooling circulation system can reduce the system energy consumption.

Description

Cooling circulation system

Technical Field

The utility model relates to a cooling circulation technical field, concretely relates to cooling circulation system.

Background

In industrial and information industry processes, in order to maintain the process flow continuously, a cooling circulation system is required to take out and take away the "waste heat" generated in the industrial and information industry manufacturing equipment (process side).

The cooling circulation system generally comprises a natural cooling tower and a refrigerating machine, the existing control scheme is a cutting method, simple judgment is carried out according to the environment temperature, when the environment temperature is low, the natural cooling tower is directly used for selling and receiving the waste heat of the process side, when the environment temperature is high, the refrigerating machine is used for processing the waste heat of the process side, the control method is too coarse, and more energy is wasted.

Therefore, how to provide a solution to overcome the above-mentioned drawbacks remains a technical problem to be solved by those skilled in the art.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a cooling circulation system can the lowering system energy consumption to can overcome the decay of refrigerator performance to a great extent, in order to guarantee the refrigeration efficiency of refrigerator.

In order to solve the technical problem, the utility model provides a cooling circulation system, which comprises a cryogen tank, a closed heat dissipation device and a refrigerator, wherein the cooling circulation system is communicated with a cryogen inlet and a cryogen outlet of a process device; the temperature monitoring device is characterized by further comprising a first temperature sensor, a second temperature sensor and a third temperature sensor, wherein the first temperature sensor is used for monitoring the refrigerant temperature of the refrigerant box, the second temperature sensor is arranged at the refrigerant inlet and used for monitoring the cooling temperature in the refrigerant outlet, and the third temperature sensor is arranged at the refrigerant outlet and used for monitoring the cooling temperature in the refrigerant outlet; the controller is in signal connection with the first temperature sensor and the second temperature sensor, and is suitable for controlling the refrigerant discharged from the refrigerant outlet to be introduced into the closed heat dissipation device, the refrigerant discharged from the closed heat dissipation device to be introduced into the evaporator of the refrigerator and the refrigerant discharged from the evaporator to be introduced into the refrigerant inlet under a first condition that the cooling inlet temperature is lower than the refrigerant temperature and the refrigerant temperature is lower than the cooling outlet temperature.

The utility model provides a cooling circulation system, its controller is less than under the first condition that cryogen temperature and cryogen temperature are less than the play cold temperature advancing cold temperature, can establish ties closed heat abstractor and refrigerator mutually, carry out the cooling to the technology side with the mode that adopts joint cooling, thus, because closed heat abstractor has also exerted partly refrigeration effect, can more fully utilize the natural cooling resource, and then can alleviate the work burden of refrigerator, the refrigerator can be in and work under the lower load state, make the refrigerator keep at comparatively efficient operating condition for a long time, and simultaneously, the work of refrigerator can compensate natural cooling's not enough again, in order to satisfy the cooling requirement of technology side.

Compare in the cooling system who cuts among the prior art, the utility model provides a cooling circulation system more can adapt to under the great environment of temperature variation, controls more meticulously, more is favorable to the energy saving.

In addition, the utility model provides a cooling cycle system is based on closed heat abstractor, compares in traditional open cooling tower, and the cryogen among the closed heat abstractor does not contact with the air, does not have aeration, external impurity to get into the scheduling problem, can reduce the production of impurity such as incrustation scale among the cryogen circulation process, and then can overcome the decay of refrigerator performance to a great extent to guarantee the work efficiency of refrigerator, and this is also the reason that natural cooling device can carry out the series connection with the refrigerator in this embodiment; meanwhile, the generation of scale is less, so that the acid washing frequency can be reduced, and the energy consumption caused by the washing machine can be reduced.

Optionally, the refrigerant tank comprises a first cold tank and a second cold tank, and the first temperature sensor is arranged at the discharge port of the first cold tank and used for monitoring the temperature of the refrigerant of the first cold tank; the first port and the second port of the four-way valve are respectively connected with the refrigerant outlet and the inlet of a condenser of the refrigerator, the outlet of the condenser is communicated with the second cold box, and the second cold box is communicated with the closed heat dissipation device through a second driving pump; the controller is in signal connection with the four-way valve and is suitable for controlling a first port and a second port of the four-way valve to be communicated under the first condition.

Optionally, the refrigerant tank further comprises a third cold tank, an outlet of the closed heat dissipation device is communicated with the first cold tank, and an outlet of the first cold tank is further connected with a first drive pump; the first port and the second port of the first three-way valve are respectively connected with the outlet of the first driving pump and the inlet of the evaporator; the controller is in signal connection with the first three-way valve and is adapted to control the first port and the second port of the first three-way valve to communicate under the first condition.

Optionally, the outlet of the evaporator is communicated with the third cold box, and the third cold box is further communicated with the refrigerant inlet through a third driving pump; the controller is also in signal connection with the third driving pump and is suitable for adjusting the flow of the third driving pump according to the cooling temperature.

Optionally, a descaling device is arranged between the second cold box and the closed heat sink, and between the third cold box and the refrigerant inlet.

Optionally, the third port of the four-way valve is further connected to the inlet of the evaporator, and the controller is further adapted to control the first port and the third port of the four-way valve to communicate with each other under a second condition that the refrigerant temperature is greater than or equal to the cooling temperature.

Optionally, the third port of the first three-way valve is further connected to the inlet of the condenser, and the controller is further adapted to control the first port and the third port of the first three-way valve to communicate under the second condition.

Optionally, the fourth port of the four-way valve is further connected to the third cold box, and the controller is further adapted to control the first port of the four-way valve to communicate with the fourth port under a third condition that the refrigerant temperature is equal to the cooling-in temperature; in the third condition, the controller is further adapted to adjust the flow rate of the second drive pump based on ambient temperature.

Optionally, the closed heat dissipation device further comprises a second three-way valve, among three ports of the second three-way valve, a first port is connected with the first cold box, a second port is connected with the second cold box, a third port is communicated with the closed heat dissipation device, and the controller is in signal connection with the second three-way valve.

Optionally, the closed heat dissipation device further comprises a water replenishing pipeline, the water replenishing pipeline is provided with a water softening device, a fourth driving pump and a third three-way valve, one of two output ports of the third three-way valve is connected with the second cooling box, the other one of the two output ports of the third three-way valve is connected with a spraying part in the closed heat dissipation device, and the controller is in signal connection with the third three-way valve.

Drawings

Fig. 1 is a schematic flow chart of a control method of a cooling cycle system provided by the present invention under a first condition;

fig. 2 is a schematic flow chart of a control method of a cooling cycle system according to the present invention under a second condition;

fig. 3 is a schematic flow chart of a control method of a cooling cycle system according to the present invention under a third condition;

fig. 4 is a schematic diagram of a refrigerant cycle when the cooling cycle system of the present invention is operating under a first condition;

fig. 5 is a schematic diagram of a refrigerant cycle when the cooling cycle system of the present invention is operating in a second condition;

fig. 6 is a schematic diagram of a refrigerant cycle when the cooling cycle system of the present invention is operating under a third condition;

fig. 7 is a schematic diagram of the refrigerant cycle when the cooling cycle system provided by the present invention operates under the third condition and stops spraying;

fig. 8 is a schematic diagram of the refrigerant cycle when the cooling cycle system provided by the present invention operates under the third condition, stops spraying, and reduces the flow rate of the second driving pump;

fig. 9 is a schematic diagram of the refrigerant cycle when the cooling cycle system provided by the present invention operates under the third condition and a closed heat sink is turned off;

fig. 10 is a schematic diagram of a refrigerant cycle of the cooling cycle system according to the present invention during filling, exhausting and cleaning of the process apparatus;

fig. 11 is a schematic diagram of a refrigerant cycle of the cooling cycle system according to the present invention during filling, exhausting and cleaning the closed heat dissipation device;

fig. 12 is a schematic diagram of a refrigerant cycle of the cooling cycle system according to the present invention during filling, exhausting and cleaning of the condenser of the refrigerator;

fig. 13 is a schematic diagram of the refrigerant cycle when the cooling cycle system of the present invention injects liquid, exhausts gas, and cleans the evaporator of the refrigerator.

The reference numerals in fig. 1-13 are illustrated as follows:

1 refrigerant box, 11 first cold box, 111 first driving pump, 12 second cold box, 121 second driving pump, 13 third cold box and 131 third driving pump;

2 closed heat sink, 21 spray part;

3 refrigerator, 31 evaporator, 32 condenser;

4, a process device, a 41 refrigerant inlet and a 42 refrigerant outlet;

5 water supply pipeline, 51 water softening device and 52 fourth driving pump;

6, a descaling device;

an SV0 four-way valve, an SV1 first three-way valve, an SV2 second three-way valve, an SV3 third three-way valve, an SV4 cleaning valve and an SV5 antifreezing valve;

T₁temperature, T, of refrigerant₂Cooling temperature, T₃And (4) cooling temperature.

Detailed Description

In order to make those skilled in the art better understand the technical solution of the present invention, the present invention will be further described in detail with reference to the accompanying drawings and specific embodiments.

The terms "first", "second", and the like, as used herein are used for convenience only to describe two or more structures or components that are the same or similar in structure, and do not denote any particular limitation on the order.

Referring to fig. 1-13, fig. 1 is a schematic flow chart of a control method of a cooling circulation system provided by the present invention under a first condition, fig. 2 is a schematic flow chart of a control method of a cooling circulation system provided by the present invention under a second condition, fig. 3 is a schematic flow chart of a control method of a cooling circulation system provided by the present invention under a third condition, fig. 4 is a schematic flow chart of a refrigerant circulation when the cooling circulation system provided by the present invention operates under the first condition, fig. 5 is a schematic flow chart of a refrigerant circulation when the cooling circulation system provided by the present invention operates under the second condition, fig. 6 is a schematic flow chart of a refrigerant circulation when the cooling circulation system provided by the present invention operates under the third condition, fig. 7 is a schematic flow chart of a refrigerant circulation when the cooling circulation system provided by the present invention operates under the third condition and stops spraying, fig. 8 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention running under the third condition, stopping spraying, and when the second driving pump reduces the flow rate, fig. 9 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention running under the third condition, and shutting down a closed heat dissipation device, fig. 10 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention during filling, exhausting and cleaning the process device, fig. 11 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention during filling, exhausting and cleaning the closed heat dissipation device, fig. 12 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention during filling, exhausting and cleaning the condenser of the refrigerator, fig. 13 is the coolant circulation schematic diagram of the cooling circulation system provided by the present invention during filling, exhausting and cleaning the evaporator of the refrigerator again, The refrigerant circulation is schematic diagram during cleaning.

Example one

For the process side, once the process unit 4 determines the inlet cooling temperature T of its refrigerant inlet 41₂The cooling temperature T of the refrigerant outlet 42₃Are all deterministic, and in one exemplary scenario, T₂May be at 12 ℃ T₃Can be 18 ℃, if the ambient temperature is lower, the cooling requirement can be met only by adopting a natural cooling scheme, but if the ambient temperature is higher, the refrigerating machine 3 is required to carry out high-efficiency refrigeration.

In traditional scheme, once natural cooling can not satisfy the requirement, just begin to adopt refrigerator 3 to carry out the cooling comprehensively, however, ambient temperature is not fixed unchangeable, in the very big area of china, the difference in temperature round the clock, the difference in temperature of morning, noon and evening is all very big, probably morning, evening temperature is only several degrees, and noon's temperature can nevertheless reach twenty thirty degrees, if the one-tenth switches over the cold source (natural cold source, refrigerator 3), then will lead to the utilization of natural cold source not thorough certainly, and also probably can not satisfy the cooling requirement of technology side.

For this purpose, the present embodiment provides a control method of a cooling cycle system, which may be referred to fig. 4, and includes a refrigerant tank 1, a closed heat sink 2, and a refrigerator 3, where the refrigerant tank 1 is used to store a refrigerant, the refrigerant may be cooling medium such as cooling water, the closed heat sink 2 is a natural cooling device, and the cooling cycle system is communicated with a refrigerant inlet 41 and a refrigerant outlet 42 of the process device 4.

With reference to fig. 1, the control method includes: step S1, obtaining the refrigerant temperature T in the refrigerant tank 1₁The cooling temperature T at the refrigerant inlet 41₂And the cooling temperature T at the refrigerant outlet 42₃(ii) a Step S2, comparing the refrigerant temperature T₁Cold inlet temperature T₂And the cold discharge temperature T₃If the temperature T is cold₂<Temperature T of refrigerant₁<Cold exit temperature T₃Step S3 is executed; step S3, controlling the refrigerant discharged from the refrigerant outlet 42 to flow into the closed heat sink 2; step S4, controlling the refrigerant discharged by the closed heat radiator 2 to be introduced into the refrigerant box 1; step S5, controlling the refrigerant in the refrigerant box 1 to be introduced into the evaporator 31 of the refrigerator 3; in step S6, the refrigerant discharged from the evaporator 31 is controlled to be introduced into the refrigerant inlet 41.

The utility model provides a control method, at the temperature T of entering cold₂<Temperature T of refrigerant₁<Cold exit temperature T₃Under the first condition, the closed heat radiator 2 and the refrigerator 3 can be connected in series to supply cold to the process side in a combined cooling mode, so that the closed heat radiator 2 can exert a part of refrigeration effect and canThe natural cooling resources are utilized more fully, the workload of the refrigerator 3 can be further reduced, the refrigerator 3 can work in a lower load state, the refrigerator 3 is kept in a relatively efficient working state for a long time, and meanwhile, the defect of natural cooling can be overcome by the operation of the refrigerator 3, so that the cooling requirement of a process side is met.

Compare in prior art the control scheme that a sword was cut, the utility model provides a control method more can adapt to under the great environment of temperature variation, control more meticulously, more is favorable to the energy saving.

In addition, the utility model provides a control method is based on closed heat abstractor 2, compares in traditional open cooling tower, and the cryogen in closed heat abstractor 2 does not contact with the air, does not have aeration, external impurity to get into the scheduling problem, can reduce the production of impurity such as incrustation scale in the cryogen circulation process, and then can overcome the decay of refrigerator performance to a great extent to guarantee the work efficiency of refrigerator 3, and this is also the reason that natural cooling device can carry out the series connection with refrigerator 3 in this embodiment; meanwhile, the generation of scale is less, so that the acid washing frequency can be reduced, and the energy consumption caused by the washing machine can be reduced.

Here, the embodiment of the present invention does not limit the types of the closed heat dissipation device 2 and the refrigerator 3, and in implementation, a person skilled in the art can select the heat dissipation device according to actual needs; preferably, the closed heat dissipation device 2 can adopt an isenthalpic humidifying air cooler, the refrigerating machine 3 can adopt a magnetic suspension centrifugal refrigerating machine, and the refrigerating machine 3 in the form is particularly suitable for variable-working-condition operation and can ensure higher working efficiency.

The step S3 may specifically include: step S31, controlling the refrigerant discharged from the refrigerant outlet 42 to be introduced into the condenser 32 of the refrigerator 3; in step S32, the refrigerant discharged from the condenser 32 is controlled to be introduced into the closed heat sink 2.

That is, under the first condition, the refrigerant discharged from the refrigerant outlet 42 may also flow through the condenser 32 of the refrigerator 3 to absorb heat of the condenser 32 before entering the closed heat sink 2. So set up, on the one hand, can assist the internal cycle who accomplishes refrigerator 3, on the other hand, the cryogen is after having absorbed the produced heat of condenser 32, and the temperature of cryogen can improve, and the difference in temperature between cryogen and the nature cold source can be bigger, and this also can promote closed heat abstractor 2 to play a role better to more fully utilize the nature cold source.

The refrigerant tank 1 may include a first cold tank 11 and a second cold tank 12, and the refrigerant temperature T in the refrigerant tank 1 is acquired in step S1₁Actually, the temperature of the refrigerant in the first cold box 11 is obtained, and the step S5 may specifically be controlling the refrigerant discharged from the first cold box 11 to pass through the evaporator 31 of the refrigerator 3; step S32 may include: step S321, controlling the refrigerant discharged from the condenser 32 to be introduced into the second cold box 12; in step S322, the refrigerant discharged from the second cold box 12 is controlled to be introduced into the closed heat sink 2. The driving pressure of the refrigerant driving pump (the first driving pump 111) between the outlet of the closed heat sink 2 and the inlet of the evaporator 31, and the driving pressure of the refrigerant driving pump (the second driving pump 121) between the outlet of the condenser 32 and the inlet of the closed heat sink 2 can be reduced by using the first cold box 11 as the buffer between the closed heat sink 2 and the evaporator 31, and using the second cold box 12 as the buffer between the condenser 32 and the closed heat sink 2.

The refrigerant tank 1 may further include a third cold tank 13, and the step S6 may include: step S61, controlling the refrigerant discharged from the evaporator 31 to be introduced into the third cold box 13; in step S62, the refrigerant discharged from the third cold box 13 is controlled to be introduced into the refrigerant inlet 41. Similarly, the third cold box 13 serves as a buffer between the outlet of the evaporator 31 and the refrigerant inlet 41, and thus the driving pressure of the refrigerant-driven pump (i.e., the third driving pump 131) between the outlet of the evaporator 31 and the inlet of the process unit 4 can be reduced.

In order to further overcome the problems of scale accumulation in the system, scale adhesion on the surface of the pipeline, and performance degradation of the refrigerator 3 and increase of pipeline flow resistance caused by the scale accumulation and adhesion, in the step S22, the refrigerant discharged from the second cold box 12 may be subjected to a scale removal treatment before being introduced into the closed heat sink 2; in step S44, the refrigerant discharged from the third cold box 13 may be subjected to a descaling process before being introduced into the refrigerant inlet 41. The descaling process mentioned here can be carried out in particular in special descaling units, for example electronic descalers or the like, which in particular practice are connected to the lines of the refrigerant circuit.

The circulation flow path of the refrigerant in the combined refrigeration (i.e. under the first condition) of the closed heat sink 2 and the refrigerator 3 can be referred to fig. 4, wherein the temperature T of the refrigerant in the first cold box 11 is₁The temperature T of the refrigerant is determined by the closed heat sink 2₁The cooling temperature of the closed heat sink 2 and the cooling temperature T of the refrigerant inlet 41 of the process unit 4 are actually the cooling temperatures₂The cooling temperature T of the refrigerant outlet 42 of the process unit 4 is determined by the evaporator 31₃It is determined by the third driving pump 131.

In the actual operation process, the cooling temperature T can be ensured as much as possible by adjusting the cooling efficiency of the closed type heat sink 2, the cooling efficiency of the evaporator 31, and the flow rate of the third driving pump 131₂Cold outlet temperature T₃Is constant; and along with the change and the duration of the environmental temperature, the energy consumption and the cooling temperature of the closed heat dissipation device 2 can be actively adjusted, through a smaller energy cost, the evaporator 31 of the refrigerator 3 can be kept to operate in the states of constant flow, constant water outlet temperature and variable water inlet temperature as far as possible, and the evaporator 31 can operate in a variable load working state under the condition that the condenser 32 can keep a lower condensation temperature, so that the working condition change state of the refrigerator 3 with safety, high energy efficiency ratio and minimum water inlet and outlet temperature difference of the condenser 32 is achieved, and the energy efficiency coefficient of the whole system is further improved.

With reference to fig. 2, in this embodiment, step S2 may further include: at the temperature T of the refrigerant₁Not less than the cold tapping temperature T₃Under the second condition of (4), step S7 is executed; in step S7, the refrigerant discharged from the refrigerant outlet 42 is controlled to be introduced into the evaporator 31 of the refrigerator 3, and then step S6 is performed.

As the ambient temperature increases, the cooling temperature T of the closed heat sink 2₂Greater than or equal to the cold exit temperature T₃The closed heat sink 2 can not directly participate in the process-side cooling, and the refrigerant discharged from the refrigerant outlet 42 can be directly introduced into the evaporator 31 of the refrigerator 3 to be evaporated completelyThe device 31 assumes the task of cooling.

On the basis, the method can further comprise the steps of S8, S9 and S8, controlling the refrigerant discharged from the first cold box 11 to be introduced into the condenser 32 of the refrigerator 3, and controlling the refrigerant discharged from the condenser 32 to be introduced into the closed heat sink 2 and then to flow back to the first cold box 11, wherein the step S9 is carried out. Although the refrigerant in the first cooling box 11 cannot directly participate in cooling, the refrigerant is introduced into the condenser 32 to absorb the heat released by the condenser 32, so as to form a refrigerant with a higher temperature, and then the refrigerant is introduced into the closed heat dissipation device 2, so that natural cooling resources can be utilized, a cooling loop capable of taking away the heat of the condenser 32 is formed, and the natural cooling resources can be utilized under the condition of high ambient temperature, so as to further save energy consumption.

The step S9 may include: step S91, controlling the refrigerant discharged from the condenser 32 to be introduced into the second cold box 12; step S92, controlling the refrigerant discharged from the second cold box 12 to be introduced into the closed heat sink 2; and step S93, controlling the refrigerant discharged by the closed heat sink 2 to flow into the first cold box 11. In this way, the driving pressure of the refrigerant drive pumps (the first drive pump 111 and the second drive pump 121) in the cooling circuit can be significantly reduced by the buffering of the first cooling tank 11 and the second cooling tank 12.

The circulation flow path of the refrigerant when the refrigerator 3 performs the cooling alone (i.e., in the second condition) can be referred to fig. 5, in which the temperature T of the refrigerant in the first cooling tank 11 is set₁The cooling temperature T of the refrigerant inlet 41 of the process unit 4 is determined by the closed heat sink 2₂The cooling temperature T of the refrigerant outlet 42 of the process unit 4 is determined by the evaporator 31₃It is determined by the third driving pump 131.

In the actual operation process, the closed heat radiator 2 can actively adjust the energy consumption and the water supply temperature T₂And the condensing temperature of the refrigerating machine 3 is reduced to a safe and high-energy-efficiency-ratio variable working condition state through a smaller energy and water cost, so that the energy efficiency coefficient of the whole system is improved.

With reference to fig. 3, in this embodiment, step S2 may further include: at the temperature T of the refrigerant₁Cold entering temperature T₂Under the third condition of (2), the first and second,step S10 is executed; in step S10, the refrigerant discharged from the refrigerant outlet 42 is controlled to flow into the closed heat sink 2 and then into the refrigerant inlet 41.

When the temperature T of the refrigerant is reduced along with the reduction of the ambient temperature₁And the cooling temperature T₂When the difference is equal, the closed heat sink 2 can provide cold energy completely, and the refrigerator 3 can be shut down to further save energy.

The step S10 may specifically include: step S101, controlling the refrigerant discharged from the refrigerant outlet 42 to be introduced into the second cold box 12; step S102, controlling the refrigerant discharged from the second cold box 12 to be introduced into the closed heat dissipation device 2; step S103, controlling the refrigerant discharged by the closed heat dissipation device 2 to be introduced into the first cold box 11; and step S104, controlling the refrigerant discharged from the third cold box 13 to be introduced into the refrigerant inlet 41. The driving pressure of the refrigerant driving pumps (the second driving pump 121 and the third driving pump 131) between the closed heat dissipation device 2 and the process device 4 can be reduced through the buffering of the first cooling box 11, the second cooling box 12 and the third cooling box 13; meanwhile, through the buffering of the refrigerant box 1, the amount of refrigerant supplied to the closed heat dissipation device 2 can be conveniently controlled so as to adapt to the change of the ambient temperature, in detail, when the ambient temperature is continuously lowered, the refrigerant in the second cold box 12 can not be completely sent to the closed heat dissipation device 2, that is, the second driving pump 121 can operate for reducing the flow rate, then the naturally cooled refrigerant discharged from the closed heat dissipation device 2 is mixed with the refrigerant left in the refrigerant box 1, and the cold inlet temperature T can be obtained₂Equal refrigerant to meet the requirement of cooling.

Reference may be made to fig. 6 to 9 for a refrigerant circulation flow path when the closed heat sink 2 performs cooling alone (i.e., under a third condition), where fig. 6 shows a circulation flow path diagram when the closed heat sink 2 performs normal cooling under the third condition, a water supply pipeline 5 supplies spray water to a spray part 21 in the closed heat sink 2 and supplies refrigerant into the refrigerant tank 1, and a spray amount of the spray part 21 is controlled by the closed heat sink 2; fig. 7 shows a circulation flow chart under a third condition, in which the ambient temperature is lower and spraying is not required, and the shower water can flow back into the first cold box 11 due to continuous temperature reduction, stop of spraying, and backflow of the shower water; fig. 8 is a flow chart showing the circulation flow of fig. 7 when the second driving pump 121 is operated at a reduced flow rate, in which case the driving pressure of the second driving pump 121 is greatly reduced, which can save driving energy; fig. 9 shows a circulation flow diagram of a closed heat sink 2 in a third condition, where the closed heat sink 2 is shut down due to a decreasing temperature, and it should be noted that there are generally a plurality of closed heat sinks 2 in a cooling circulation system, and when the ambient temperature is further decreased, some of the closed heat sinks 2 can be shut down.

Step S1 may be preceded by: and step S0, controlling the closed heat dissipation device 2, the refrigerator 3 and the process device 4 to perform liquid injection, gas exhaust and cleaning.

Step S0 is actually a preparation step before the system is operated, and can be specifically seen in fig. 10 to 13: fig. 10 is a view showing a circulation flow path for filling, discharging and cleaning the process equipment 4, in which the coolant is supplied to the coolant tank 1 through the water supply line 5, and the coolant in the coolant tank 1 is circulated in the process equipment 4 by the third drive pump 131 to discharge the gas in the process equipment 4 and clean the cooling circulation line in the process equipment 4; fig. 11 is a flow chart showing a circulation flow path for filling, exhausting and cleaning the closed heat sink 2, in which the refrigerant tank 1 is replenished with the refrigerant through the water replenishing pipe 5, and the second driving pump 121 drives the refrigerant in the refrigerant tank 1 to the closed heat sink 2 to discharge the gas in the closed heat sink 2 and clean the cooling circulation pipe in the closed heat sink 2; fig. 12 is a view showing a circulation flow path for filling, discharging and cleaning the condenser 32 of the refrigerator 3, in which the refrigerant tank 1 is replenished with the refrigerant through the water replenishment line 5, and the first drive pump 111 drives the refrigerant in the refrigerant tank 1 to circulate through the condenser 32 to discharge the gas in the condenser 32 and clean the cooling circulation line in the condenser 32; fig. 13 is a diagram showing a circulation flow path when the evaporator 31 of the refrigerator 3 is charged, discharged, and cleaned, in which the refrigerant tank 1 is replenished with the refrigerant through the water replenishment line 5, and the first drive pump 111 drives the refrigerant in the refrigerant tank 1 to circulate in the evaporator 31, discharges the gas in the evaporator 31, and cleans the cooling circulation line in the evaporator 31.

As can be seen from the above, the control method of the cooling cycle system provided in this embodiment mainly includes, in addition to the preparation step, control steps under the combined refrigeration condition of the closed heat dissipation device 2 and the refrigerator 3, under the individual refrigeration condition of the refrigerator 3, and under the individual refrigeration condition of the closed heat dissipation device 2, and through calculation, compared with the conventional control method using the open cooling tower, the energy saving rate of the control method provided in this embodiment can be increased by 29.2% under the condition of a new water machine (new equipment), and the energy saving rate of the control method provided in this embodiment can be increased by 46.9% under the condition of water injection of an old machine (after a specific operation time), so that the energy saving rate is greatly increased.

Example two

The embodiment also provides a cooling circulation system, which comprises a refrigerant box 1, a closed heat dissipation device 2 and a refrigerator 3, wherein the cooling circulation system is communicated with a refrigerant inlet 41 and a refrigerant outlet 42 of the process device 4; the system also comprises a first temperature sensor, a second temperature sensor and a third temperature sensor, wherein the first temperature sensor is used for monitoring the refrigerant temperature T of the refrigerant box 1₁A second temperature sensor is provided at the refrigerant inlet 41 for monitoring the cooling temperature T in the refrigerant outlet 42₂And a third temperature sensor is provided at the refrigerant outlet 42 for monitoring the cooling temperature T in the refrigerant outlet 42₃(ii) a The cold air conditioner further comprises a controller (not shown in the figure), wherein the controller is in signal connection with the first temperature sensor and the second temperature sensor, and the controller is suitable for controlling the cold air conditioner to be at the cold inlet temperature T₂<Temperature T of refrigerant₁<Cold exit temperature T₃Under the first condition, the refrigerant discharged from the refrigerant outlet 42 is controlled to be introduced into the closed heat sink 2, the refrigerant discharged from the closed heat sink 2 is controlled to be introduced into the refrigerant tank 1, the refrigerant discharged from the refrigerant tank 1 is controlled to be introduced into the evaporator 31 of the refrigerator 3, and the refrigerant discharged from the evaporator 31 is controlled to be introduced into the refrigerant inlet 41.

The cooling circulation system provided by the present invention corresponds to the control method in the first embodiment, and since the first embodiment already has the above technical effects, the cooling circulation system corresponding to the first embodiment also has similar technical effects, and therefore the description thereof is omitted here.

As shown in FIG. 4, the refrigerant tank 1 may include a first cold box 11 and a second cold box 12, and the first temperature sensor may be provided at an outlet of the first cold box 11 for useFor monitoring the temperature of the refrigerant in the first cold box 11, i.e. the aforementioned refrigerant temperature T₁In fact the temperature of the refrigerant inside the first cold box 11, and this temperature is characteristic of the cooling temperature of the closed cooling device 2; a four-way valve SV0 may be further included, the four-way valve SV0 having four ports, wherein a first port SV0-a and a second port SV0-b may be connected to the refrigerant outlet 42 and the inlet of the condenser 32 of the refrigerator 3, respectively, the outlet of the condenser 32 may be communicated with the second cold box 12, and the outlet of the second cold box 12 may be communicated with the closed heat sink 2 through the second driving pump 121.

The controller is also in signal connection with a four-way valve SV0 and is adapted to control a first port SV0-a and a second port SV0-b of a four-way valve SV0 to communicate under a first condition to communicate the refrigerant outlet 42 with the condenser 32 to pass the refrigerant discharged from the process unit 4 into the condenser 32 for temperature rise.

The refrigerant box 1 can also comprise a third cold box 13, the outlet of the closed heat sink 2 can be communicated with the first cold box 11, and the outlet of the first cold box 11 can also be connected with a first drive pump 111; a first three-way valve SV1 may also be included, the first three-way valve SV1 having three ports, wherein a first port SV1-a and a second port SV1-b may be connected to the outlet of the first drive pump 111 and the inlet of the evaporator 31, respectively.

The controller can also be in signal connection with the first three-way valve SV1 and is suitable for controlling the first port SV1-a and the second port SV1-b of the first three-way valve SV1 to be communicated under a first condition so as to conduct the first cold box 11 and the evaporator 31 to lead the refrigerant discharged from the first cold box 11 into the evaporator 31 for cooling.

The outlet of the evaporator 31 can be communicated with the third cold box 13, the outlet of the third cold box 13 can be communicated with the refrigerant inlet 41 through the third driving pump 131, the controller can be in signal connection with the third driving pump 131, and the controller is also suitable for being used for controlling the refrigerant according to the cooling temperature T₃The flow rate of the third driving pump 131 is adjusted to adjust the cooling temperature T₃Is maintained at a substantially constant value.

The descaling device 6 can be arranged between the second cooling box 12 and the closed heat dissipation device 2 and between the third cooling box 13 and the refrigerant inlet 41, and the descaling device 6 can be specifically an electronic descaling instrument to remove scale possibly generated in a pipeline, so that the problems of pipeline blockage, performance attenuation of the refrigerator 3 and the like caused by the scale can be overcome to a greater extent.

The four-way valve SV0 further has a third port SV0-c, which third port SV0-c may be connected to the inlet of the evaporator 31, as shown in FIG. 5, the controller being adapted to control the refrigerant temperature T₁Not less than the cold tapping temperature T₃Under the second condition, the first port SV0-a and the third port SV0-c of the four-way valve SV0 are controlled to communicate with each other to conduct the refrigerant outlet 42 to the inlet of the evaporator 31, whereby the refrigerant discharged from the process unit 4 is directly introduced into the evaporator 31 for powerful temperature reduction.

The first three-way valve SV1 also has a third port SV1-c, the third port SV1-c can be connected with the inlet of the condenser 32, and the controller is suitable for controlling the first port SV1-a and the third port SV1-c of the first three-way valve SV1 to be communicated under the second condition so as to conduct the first cold box 11 and the condenser 32, so that the refrigerant in the first cold box 11 can be guided into the condenser 32 to be heated under the action of the first driving pump 111, and the heat of the condenser 32 can be absorbed.

The four-way valve SV0 further has a fourth port SV0-d, which fourth port SV0-d may be connected to the third cold box 13, the controller being adapted to control the refrigerant temperature T₁Equal to the cooling temperature T₂Under the third condition, the first port SV0-a of the four-way valve SV0 is controlled to communicate with the fourth port SV0-d to conduct the process unit 4 and the second cold box 12, so that the refrigerant discharged from the refrigerant outlet 42 of the process unit 4 can be introduced into the second cold box 12.

In a third condition, the controller is further adapted to adjust the flow rate of the second driving pump 121 according to the ambient temperature to control the amount of the refrigerant entering the closed heat sink 2, which has been described in the first embodiment and to which reference should be made.

Further, a second three-way valve SV2 may be further included, the second three-way valve SV2 having three ports, wherein the first port SV2-a may be connected to the first cold box 11, the second port SV2-b may be connected to the second cold box 12, and the third port SV2-c may be communicated with the closed heat sink 2; the controller may also be in signal connection with the second three-way valve SV2, as shown in fig. 3-8, to connect the second port SV2-b of the second three-way valve SV2 to the third port SV2-c when the closed cooling device 2 needs to be operated, and to shut down the second three-way valve SV2 when the closed cooling device 2 does not need to be operated, as shown in fig. 10, 12, 13.

Under the first condition, as shown in fig. 4, the refrigerant circulates in the third driving pump 131 → the scale removing device 6 → the process device 4 → the four-way valve SV0(a → b) → the condenser 32 → the second cold box 12 to constitute a hot side, and the refrigerant circulates in the second cold box 12 → the second driving pump 121 → the scale removing device 6 → the second three-way valve SV2(b → c) → the closed heat radiating device 2 → the first cold box 11 → the first driving pump 111 → the first three-way valve SV1(a → b) → the evaporator 31 → the third water box 13 to constitute a cold side.

Under the second condition, as shown in fig. 5, the refrigerant circulates in the third drive pump 131 → the descaling device 6 → the process device 4 → the four-way valve SV0(a → c) → the evaporator 31 → the third cold box 13 to constitute a refrigeration circuit, and the refrigerant circulates in the first drive pump 111 → the first three-way valve SV1(a → c) → the condenser 32 → the second cold box 12 → the second drive pump 121 → the descaling device 6 → the second three-way valve SV2(b → c) → the closed heat sink 2 → the first cold box 11 to constitute a cooling circuit.

Under a third condition, referring to fig. 6, the refrigerant circulates in the third driving pump 131 → the scale removing device 6 → the process device 4 → SV0(a → d) → the second cold box 12 to constitute a hot side, and the refrigerant circulates in the second driving pump 121 → the scale removing device 6 → the second three-way valve SV2(b → c) → the closed heat sink 2 → the first cold box 11 to constitute a cold side.

The cooling circulation system provided by the embodiment can further comprise a water supplementing pipeline 5, the water supplementing pipeline 5 can be provided with a water softening device 51, a fourth driving pump 52 and a third three-way valve SV3, the water softening device 51 can reduce the hardness of supplemented water so as to reduce the possibility of scale generation when water is circulated in the pipeline as refrigerant, the fourth driving pump 52 is used for providing driving force for the water supplementing pipeline 5, the third three-way valve SV3 is provided with an input port SV3-a and two output ports SV3-b and SV3-c, the input port SV3-a is used for being connected with the water supplementing pipeline 5, one output port SV3-b can be connected with the spray part 21 in the closed heat dissipation device 2, and the other output port SV3-c can be connected with the second cold box 12.

The controller may also be in signal connection with the third three-way valve SV3, the controller being adapted to control the first port SV3-a and the third port SV3-c of the third three-way valve SV3 to communicate when the refrigerant tank 1 requires make-up water, and the controller being further adapted to control the first port SV3-a and the second port SV3-b of the third three-way valve SV3 to communicate when the closed heat sink 2 requires to perform a spray operation, although these three ports may also be communicated simultaneously as required.

As shown in fig. 9, an antifreeze valve SV5 connected to the closed heat sink 2 may be provided, the antifreeze valve SV5 being opened when the closed heat sink 2 is shut down, and the antifreeze return water being constituted with the closed heat sink 2, the first cold box 11, and the second three-way valve SV2(a → c). As shown in fig. 10, a purge valve SV4 for connecting the refrigerant outlet 42 and the third cold box 13 may be provided for starting the process equipment 4 at the time of water filling, gas discharging, and purging.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of improvements and decorations can be made without departing from the principle of the present invention, and these improvements and decorations should also be regarded as the protection scope of the present invention.

Claims

1. A cooling circulation system is characterized by comprising a refrigerant box (1), a closed heat dissipation device (2) and a refrigerator (3), wherein the cooling circulation system is communicated with a refrigerant inlet (41) and a refrigerant outlet (42) of a process device (4);

the cold storage tank further comprises a first temperature sensor, a second temperature sensor and a third temperature sensor, wherein the second temperature sensor is arranged at the refrigerant inlet (41) and used for monitoring the cold inlet temperature (T) in the refrigerant outlet (42)₂) The third temperature sensor is arranged at the refrigerant outlet (42) and is used for monitoring the cooling temperature (T) in the refrigerant outlet (42)₃）；

The refrigerant box (1) comprises a first cold box (11) and a second cold box (12), and the first temperature sensor is arranged on the first cold boxA discharge port of the first cold box (11) for monitoring a refrigerant temperature (T) of the first cold box (11)₁) The outlet of the closed heat dissipation device (2) is communicated with the first cold box (11), and the outlet of the first cold box (11) is also connected with a first driving pump (111);

the closed heat dissipation device further comprises a first three-way valve (SV 1) and a four-way valve (SV 0), wherein a first port and a second port of the four-way valve (SV 0) are respectively connected with the refrigerant outlet (42) and an inlet of a condenser (32) of the refrigerator (3), an outlet of the condenser (32) is communicated with the second cold box (12), the second cold box (12) is communicated with the closed heat dissipation device (2) through a second driving pump (121), and a first port and a second port of the first three-way valve (SV 1) are respectively connected with an outlet of the first driving pump (111) and an inlet of an evaporator (31) of the refrigerator (3);

still include the controller, the controller with first temperature sensor, second temperature sensor, third temperature sensor, first three-way valve (SV 1), four-way valve (SV 0) are all signal connection, the controller can control first port and the second port of first three-way valve (SV 1) are in the connected state, control first port and the second port of four-way valve (SV 0) are in the connected state.

2. The cooling cycle system according to claim 1, wherein the refrigerant tank (1) further comprises a third cold tank (13), the outlet of the evaporator (31) communicates with the third cold tank (13), and the third cold tank (13) further communicates with the refrigerant inlet (41) through a third drive pump (131).

3. The cooling cycle system according to claim 2, characterized in that a descaling device (6) is arranged between the second cold box (12) and the closed heat sink (2) and between the third cold box (13) and the refrigerant inlet (41).

4. The cooling cycle system as set forth in claim 2, wherein a third port of the four-way valve (SV 0) is further connected to the inlet of the evaporator (31), and the controller is further configured to control the first port and the third port of the four-way valve (SV 0) to be in a communicating state.

5. The cooling circulation system of claim 4, wherein the third port of the first three-way valve (SV 1) is further connected to the inlet of the condenser (32), and wherein the controller is further configured to control the first port and the third port of the first three-way valve (SV 1) to be in communication.

6. The cooling cycle system as set forth in claim 2, wherein a fourth port of said four-way valve (SV 0) is further connected to said third cold box (13), and said controller is further configured to control said first port and said fourth port of said four-way valve (SV 0) to be in communication.

7. The cooling circulation system as set forth in claim 2, further comprising a second three-way valve (SV 2), a first port of the three ports of the second three-way valve (SV 2) being connected to the first cold box (11), a second port of the three ports being connected to the second cold box (12), a third port of the three ports being in communication with the closed heat sink (2), the controller being in signal connection with the second three-way valve (SV 2).

8. The cooling circulation system according to claim 2, further comprising a water supply line (5), wherein the water supply line (5) is provided with a water softening device (51), a fourth driving pump (52) and a third three-way valve (SV 3), one of two output ports of the third three-way valve (SV 3) is connected with the second cold box (12), the other one is connected with a spray component (21) in the closed heat sink (2), and the controller is in signal connection with the third three-way valve (SV 3).