Refrigeration system and control method thereof

Abstract

The present invention provides a refrigeration system and a control method thereof, wherein the refrigeration system includes: a compressor, a vortex tube, a condenser reheater, and an evaporator, wherein the vortex tube includes an inlet end, a hot end, and a cold end, wherein the outlet temperature of the hot end is higher than the outlet temperature of the cold end, the inlet end of the vortex tube is connected to the outlet end of the compressor, the hot end of the vortex tube is connected to one end of the condenser reheater, the other end of the condenser reheater can be connected to one end of the evaporator, and the other end of the evaporator can be connected to the intake end of the compressor; the evaporator and the condenser reheater constitute at least part of the structure of a constant temperature and humidity component. According to the present invention, the condenser reheater can be used to reheat the air passing through the constant temperature and humidity component, effectively utilizing the condensation heat for reheating, and the heat exchange capacity at the condenser reheater can be improved by setting the vortex tube.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration, and in particular to a refrigeration system and a control method thereof. Background Art

[0002] With the advancement of technology, people are increasingly yearning for a higher quality of life, and air conditioning is playing an increasingly important role in people's lives. Currently, building energy consumption has become a major energy consumer, with the HVAC industry accounting for the majority of energy consumption. The development of green and energy-saving products is urgent.

[0003] For some special occasions, it is required to control the temperature and humidity in the room to be constant. The traditional approach is to use electric heating to control the temperature. For the entire refrigeration system, the condensation heat generated by refrigeration is not fully utilized, which results in energy waste.

[0004] Since the prior art constant temperature and humidity refrigeration system with dehumidification function has technical problems such as inability to effectively recover condensation heat, resulting in low overall energy efficiency, the present invention studies and designs a refrigeration system and a control method thereof. Summary of the Invention

[0005] Therefore, the technical problem to be solved by the present invention is to overcome the defect of the constant temperature and humidity refrigeration system in the prior art that the condensation heat cannot be effectively recovered, resulting in low overall energy efficiency, thereby providing a refrigeration system and a control method thereof.

[0006] In order to solve the above problems, the present invention provides a refrigeration system, comprising:

[0007] A compressor, a vortex tube, a condenser reheater and an evaporator, the vortex tube comprising an inlet end, a hot end and a cold end, the outlet temperature of the hot end being higher than the outlet temperature of the cold end, the inlet end of the vortex tube being connected to the outlet end of the compressor, the hot end of the vortex tube being connected to one end of the condenser reheater, the other end of the condenser reheater being able to be connected to one end of the evaporator, and the other end of the evaporator being able to be connected to the suction end of the compressor; the evaporator and the condenser reheater constitute at least a partial structure of a constant temperature and humidity component.

[0008] In some embodiments, a first fan is further included, the constant temperature and humidity component includes the first fan, the evaporator, the condenser reheater and the first fan are in the same dehumidification air duct, and the first fan can drive air to pass through the evaporator and the condenser reheater in sequence for heat exchange; the hot end and the cold end of the vortex tube are both provided with an electric proportional control valve.

[0009] In some embodiments, a condenser is further included, one end of the condenser is connected to the cold end of the vortex tube, and the other end of the condenser can be connected to one end of the evaporator. The condenser can increase the supercooling degree of the refrigerant entering the evaporator.

[0010] In some embodiments, an economizer is further included. The economizer is disposed between the condenser and the evaporator. The economizer can further increase the subcooling degree of the refrigerant entering the evaporator, and the economizer can replenish air to the compressor.

[0011] In some embodiments, it includes a first pipeline, a second pipeline, a third pipeline, a fourth pipeline and a first throttling device, one end of the first pipeline is connected to the outlet end of the compressor, and the other end is connected to the inlet end of the vortex tube, one end of the second pipeline is connected to the hot end of the vortex tube, and the other end is connected to one end of the condenser reheater, one end of the third pipeline is connected to the other end of the condenser reheater, and the other end of the third pipeline is connected to one end of the evaporator, one end of the fourth pipeline is connected to the other end of the evaporator, and the other end of the fourth pipeline is connected to the suction end of the compressor, and the first throttling device is arranged on the third pipeline.

[0012] In some embodiments, when a condenser and an economizer are also included, the refrigeration system further includes a fifth pipeline, a sixth pipeline, a seventh pipeline and a second throttling device, one end of the fifth pipeline is connected to the cold end of the vortex tube, and the other end is connected to one end of the condenser, one end of the sixth pipeline is connected to the other end of the condenser, and the other end of the sixth pipeline is connected to the first end of the economizer, one end of the seventh pipeline is connected to the second end of the economizer, and the other end is connected to a position on the third pipeline between the first throttling device and the evaporator, the first end and the second end are connected inside the economizer, and the second throttling device is arranged on the seventh pipeline.

[0013] In some embodiments, an eighth pipeline and a ninth pipeline are further included, wherein one end of the eighth pipeline is connected to the pipe section of the seventh pipeline located between the second end and the second throttling device, and the other end is connected to the third end of the economizer; one end of the ninth pipeline is connected to the fourth end of the economizer, and the other end is connected to the air supply end of the compressor, and the third end is connected to the fourth end inside the economizer.

[0014] In some embodiments, a third throttling device is further included, and the third throttling device is disposed on the eighth pipeline, and the third end and the fourth end are communicated with each other inside the economizer.

[0015] In some embodiments, the first end and the second end are connected inside the economizer through a first heat exchange section, and the third end and the fourth end are connected inside the economizer through a second heat exchange section, and heat exchange can be performed between the first heat exchange section and the second heat exchange section.

[0016] In some embodiments, a second fan is further included, which is arranged opposite to the condenser and can drive the airflow to exchange heat with the refrigerant in the condenser.

[0017] The present invention further provides a method for controlling a refrigeration system as described in any of the preceding items, comprising:

[0018] a detection step of detecting the moisture content of the air after heat exchange through the evaporator;

[0019] a determination step of determining a magnitude relationship between the air moisture content and a preset moisture content;

[0020] The control step increases the operating frequency of the compressor when the air humidity is greater than a preset humidity, and decreases the operating frequency of the compressor when the air humidity is less than the preset humidity.

[0021] In some embodiments, when the refrigeration system further includes a condenser and a second fan:

[0022] The detecting step further detects the subcooling degree of the refrigerant at the outlet of the condenser;

[0023] The judging step comprises judging the magnitude relationship between the refrigerant subcooling degree and a preset subcooling degree;

[0024] The control step is to control the operating frequency of the second fan matched with the condenser to decrease when the refrigerant subcooling degree is greater than the preset subcooling degree; and to control the operating frequency of the second fan matched with the condenser to increase when the refrigerant subcooling degree is less than the preset subcooling degree.

[0025] In some embodiments, the detecting step further detects the supply air temperature at the outlet of the condenser reheater;

[0026] The determining step is to determine the magnitude relationship between the air supply temperature and the preset temperature;

[0027] The control step controls the proportional regulating valve at the hot end of the vortex tube to decrease its opening when the supply air temperature is greater than the preset temperature; and controls the proportional regulating valve at the hot end of the vortex tube to increase its opening when the supply air temperature is less than the preset temperature.

[0028] The refrigeration system and control method provided by the present invention have the following beneficial effects:

[0029] 1. The present invention provides a vortex tube structure and a condenser reheater in the refrigeration system, and connects the hot end of the vortex tube with the condenser reheater, so that the high-pressure and high-temperature gas at the outlet of the compressor can be further heated through the vortex tube for heat exchange at the condenser reheater, and the constant temperature and humidity component composed of the condenser reheater and the evaporator of the present invention can utilize the condenser reheater to reheat the air passing through the constant temperature and humidity component, effectively utilizing the condensation heat to reheat the dehumidified low-temperature air, and the temperature entering the condenser reheater of the present invention is higher than the temperature at the outlet of the compressor due to the action of the vortex tube, thereby further improving the heat exchange capacity at the condenser reheater, thereby improving the reheating effect of the constant temperature and humidity component, and can simultaneously improve the energy efficiency of the entire refrigeration system and improve the reheating effect of the dehumidification and reheating components.

[0030] 2. The present invention also connects the cold end of the vortex tube to the condenser, and the outlet end of the condenser can be connected to the evaporator. The temperature of the refrigerant entering the condenser can be reduced through the cold end of the vortex tube, and the outlet temperature of the condenser can be further reduced, thereby increasing the supercooling of the refrigerant before entering the evaporator, and then improving the evaporation efficiency of the evaporator and the evaporation effect; and the present invention also uses the arrangement of the economizer to perform superheating and supercooling heat exchange inside the economizer, thereby further increasing the supercooling of the refrigerant before entering the evaporator, further improving the evaporation efficiency of the evaporator and the evaporation effect; the present invention also connects the air supply channel of the economizer with the air supply port of the compressor, and can increase the system refrigerant circulation volume under the same heat exchange area, forming two-stage (or quasi-two-stage) compression, increasing the heat exchange capacity of the system, and improving the operating energy efficiency ratio. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 is a system structure diagram of the refrigeration system of the present invention;

[0032] Figure 2 Schematic diagram of the structure of the vortex tube in the refrigeration system of the present invention;

[0033] Figure 3 is a schematic structural diagram of an economizer of a refrigeration system of the present invention;

[0034] Figure 4 It is a control flow chart of the refrigeration system of the present invention.

[0035] The reference numerals indicate:

[0036] 1. Compressor; 11. Air outlet; 12. Air intake; 13. Air supply; 2. Vortex tube; 21. Inlet; 22. Hot end; 23. Cold end; 3. Condenser; 4. Second fan; 5. Second throttling device; 6. Third throttling device; 7. First throttling device; 8. Economizer; 81. First end; 82. Second end; 83. Third end; 84. Fourth end; 9. Evaporator; 10. Condenser reheater; 14. First fan; 101. First pipeline; 102. Second pipeline; 103. Third pipeline; 104. Fourth pipeline; 105. Fifth pipeline; 106. Sixth pipeline; 107. Seventh pipeline; 108. Eighth pipeline; 109. Ninth pipeline. DETAILED DESCRIPTION

[0037] like Figure 1-4 As shown, the present invention provides a refrigeration system, which includes:

[0038] A compressor 1, a vortex tube 2, a condenser reheater 10 and an evaporator 9, wherein the vortex tube 2 includes an inlet end 21, a hot end 22 and a cold end 23, the outlet temperature of the hot end 22 is higher than the outlet temperature of the cold end 23, the inlet end 21 of the vortex tube 2 is connected to the outlet end 11 of the compressor 1, the hot end 22 of the vortex tube 2 is connected to one end of the condenser reheater 10, the other end of the condenser reheater 10 can be connected to one end of the evaporator 9, and the other end of the evaporator 9 can be connected to the intake end 12 of the compressor 1; the evaporator 9 and the condenser reheater 10 constitute at least part of the structure of a constant temperature and humidity component.

[0039] The vortex tube of the present invention is an energy separation device, generally comprising a vortex chamber, an injection channel, a hot-end tube, a cold orifice plate, a hot-end regulating valve, and a cold-end regulating valve. After entering the vortex tube, high-pressure fluid rotates at high speed within the vortex chamber, becoming a low-temperature fluid at the cold end of the vortex tube and a high-temperature fluid at the hot end.

[0040] The present invention provides a vortex tube and a condenser reheater in the refrigeration system and connects the hot end of the vortex tube with the condenser reheater, so that the high-pressure and high-temperature gas at the outlet end of the compressor can be further heated through the vortex tube for heat exchange at the condenser reheater. The constant temperature and humidity component composed of the condenser reheater and the evaporator of the present invention can utilize the condenser reheater to reheat the air passing through the constant temperature and humidity component, effectively utilizing the condensation heat to reheat the dehumidified low-temperature air. In addition, the temperature entering the condenser reheater of the present invention is higher than the temperature at the outlet end of the compressor due to the action of the vortex tube, thereby further improving the heat exchange capacity at the condenser reheater, thereby improving the reheating effect of the constant temperature and humidity component, and can simultaneously improve the energy efficiency of the entire refrigeration system and improve the reheating effect of the dehumidification and reheating components.

[0041] The present invention designs a quasi-two-stage compression constant temperature and humidity refrigeration system with a vortex tube to recover condensation heat, reduce energy consumption, and improve the overall energy efficiency of the system. Under the same heat exchange area, the system refrigerant circulation volume is increased, and the quasi-two-stage compression is adopted to increase the system's heat exchange and improve the operating energy efficiency ratio. The vortex tube is adopted and the vortex effect of the vortex tube is utilized to increase the refrigerant temperature entering the condenser reheater, thereby improving the reheating efficiency. The refrigerant temperature entering the condenser is reduced, which can increase the subcooling degree.

[0042] The invention lies in: 1. Designing a direct expansion constant temperature and humidity refrigeration system so that air directly exchanges heat with the refrigerant, avoiding the energy loss of secondary heat exchange; the vortex tube has a simple structure, low cost, and no moving parts, and can divide the constant pressure fluid into two fluids, one cold and one hot. When used in a refrigeration system, it can further increase the temperature of the refrigerant entering the condenser reheater and further reduce the temperature of the refrigerant entering the condenser, thereby increasing the supercooling of the refrigerant entering the evaporator.

[0043] 2. Using a quasi-two-stage compression system with an intermediate air-supply compressor, under the same heat exchange area, the quasi-two-stage compression is used to increase the heat exchange capacity of the system and improve the operating energy efficiency ratio.

[0044] Solved the following technical problems:

[0045] 1. Use condensation heat instead of electric heating to reduce energy waste;

[0046] 2. Under the same heat exchange area, the use of quasi-two-stage compression can increase the system refrigerant circulation volume, thereby increasing the system's heat exchange capacity and improving the operating energy efficiency ratio, thus solving the problem of low energy efficiency;

[0047] 3. The use of vortex tubes increases the refrigerant temperature entering the condenser reheater, improving reheat efficiency; lowering the refrigerant temperature entering the condenser can increase subcooling, solving the problem of low dehumidification and reheating effect and the problem of low evaporation efficiency caused by low subcooling.

[0048] In some embodiments, a first fan 14 is further included. The constant temperature and humidity assembly includes the first fan 14. The evaporator 9, the condenser reheater 10, and the first fan 14 are located in the same dehumidification duct. The first fan 14 can drive air to sequentially pass through the evaporator 9 and the condenser reheater 10 for heat exchange. The hot end 22 and the cold end 23 of the vortex tube 2 are both provided with electric proportional control valves. This is a further preferred structural form of the refrigeration system of the present invention. That is, the first fan, the evaporator, and the condenser reheater are located in the dehumidification duct. The first fan can drive air to flow through the evaporator and the condenser reheater in sequence, so that the air is first cooled and dehumidified by the evaporator, and then the cooled air is heated and raised by the condenser reheater to achieve a constant temperature dehumidification effect. In addition, due to the use of a vortex tube in the present invention, the hot end of the vortex tube is connected to the condenser reheater, which can increase the temperature of the refrigerant entering the condenser reheater, improve the heat exchange effect of the condenser reheater, and thus improve the reheating capacity. The hot end 22 and the cold end 23 of the vortex tube 2 of the present invention are both provided with electric proportional control valves, which can adjust the refrigerant flow at the cold end outlet and the hot end outlet, thereby adjusting parameters such as the indoor air supply temperature as needed to improve indoor comfort.

[0049] The present invention designs a quasi-two-stage compression constant temperature and humidity refrigeration system with a vortex tube, which recovers condensation heat, reduces energy consumption, and improves the overall energy efficiency of the system. Under the same heat exchange area, the quasi-two-stage compression is adopted to increase the system refrigerant circulation volume, increase the system heat exchange rate, and improve the operating energy efficiency ratio. The vortex tube is adopted and the vortex effect of the vortex tube is utilized to increase the refrigerant temperature entering the condenser reheater, thereby improving the reheating efficiency. The refrigerant temperature entering the condenser is reduced, which can increase the subcooling degree.

[0050] The compressor 1, condensing fan (second fan 4), and blower (first fan 14) of the present invention are preferably driven by variable-frequency motors. The vortex tube 2 of the present invention has electric proportional control valves at both the hot end 22 and the cold end 23 outlets. These valves are integrated with the vortex tube, allowing the opening of the electric proportional control valves to be adjusted, thereby regulating the flow of refrigerant through the hot end 22 and cold end 23 outlets.

[0051] In some embodiments, a condenser 3 is further included, one end of which is connected to the cold end 23 of the vortex tube 2, and the other end of which can be connected to one end of the evaporator 9. The condenser 3 can increase the subcooling of the refrigerant entering the evaporator 9. The present invention also provides a condenser, and by connecting the cold end of the vortex tube to the condenser, the outlet end of the condenser can be connected to the evaporator. The cold end of the vortex tube can be connected to the condenser, and the outlet temperature of the condenser can be further reduced, thereby increasing the subcooling of the refrigerant before entering the evaporator, thereby improving the evaporation efficiency of the evaporator and improving the evaporation effect.

[0052] In some embodiments, an economizer 8 is further included, disposed between the condenser 3 and the evaporator 9. The economizer 8 can further increase the subcooling of the refrigerant entering the evaporator 9 and can also provide air supply to the compressor 1. The present invention also utilizes the economizer to perform heat exchange between superheat and subcooling, thereby further increasing the subcooling of the refrigerant before entering the evaporator, further improving the evaporation efficiency of the evaporator and enhancing the evaporation effect. Furthermore, the present invention connects the economizer's air supply channel to the compressor's air supply port, increasing the system's refrigerant circulation volume under the same heat exchange area, forming a two-stage (or quasi-two-stage) compression system, increasing the system's heat exchange capacity, and improving the operating energy efficiency ratio.

[0053] The refrigerant exiting the exhaust port of compressor 1 enters the inlet port 21 of vortex tube 2. A portion flows through the hot end 22 of vortex tube 2 into the condenser reheater 10, then passes through the electronic expansion valve (first throttling device 7) to enter the evaporator 9. The remaining portion flows through the cold end 23 of vortex tube 2 to enter the condenser 3 for heat dissipation. The low-temperature refrigerant exiting condenser 3 enters the first end 81 of economizer 8. After passing through the second end 82 of economizer 8, the refrigerant is split into two parts. The main refrigerant passes through the electronic expansion valve (second throttling device 5) and merges with the refrigerant that has passed through the first throttling device 7. Together, they enter the evaporator 9 for evaporation and heat exchange. After heat exchange in the evaporator, the refrigerant enters compressor 1, completing the main compression and refrigeration cycle. The auxiliary refrigerant passes through the third throttling device 6 and enters the third end 83 of the economizer. After exiting the fourth end 84 of the economizer, it enters the air supply port 13 of compressor 1, completing the auxiliary compression and refrigeration cycle.

[0054] Compared with the vortex tube without vortex, due to the vortex effect of the vortex tube 2, on the one hand, the temperature of the refrigerant entering the condenser reheater is higher, so that relatively less refrigerant can be used to increase the required reheat temperature. On the other hand, the temperature of the refrigerant entering the condenser 3 is lower, which is equivalent to increasing the subcooling degree entering the evaporator and improving the refrigeration effect.

[0055] In some embodiments, it includes a first pipeline 101, a second pipeline 102, a third pipeline 103, a fourth pipeline 104 and a first throttling device 7, one end of the first pipeline 101 is connected to the outlet end 11 of the compressor 1, and the other end is connected to the inlet end 21 of the vortex tube 2, one end of the second pipeline 102 is connected to the hot end 22 of the vortex tube 2, and the other end is connected to one end of the condenser reheater 10, one end of the third pipeline 103 is connected to the other end of the condenser reheater 10, the other end of the third pipeline 103 is connected to one end of the evaporator 9, one end of the fourth pipeline 104 is connected to the other end of the evaporator 9, and the other end of the fourth pipeline 104 is connected to the suction end 12 of the compressor 1, and the first throttling device 7 is arranged on the third pipeline 103.

[0056] This is the pipeline connection method of the present invention, that is, the first pipeline connects the compressor outlet end and the vortex tube inlet end, the second pipeline connects the hot end outlet of the vortex tube and the condenser reheater, the third pipeline connects the condenser reheater and the evaporator, and the fourth pipeline connects the evaporator and the compressor suction end, thereby forming a complete refrigeration and dehumidification refrigerant cycle, improving the condensation heat recovery capacity, improving energy efficiency, and improving the dehumidification and reheating effect.

[0057] In some embodiments, when the condenser 3 and the economizer 8 are also included, the refrigeration system further includes a fifth pipeline 105, a sixth pipeline 106, a seventh pipeline 107 and a second throttling device 5, one end of the fifth pipeline 105 is connected to the cold end 23 of the vortex tube 2, and the other end is connected to one end of the condenser 3, one end of the sixth pipeline 106 is connected to the other end of the condenser 3, and the other end of the sixth pipeline 106 is connected to the first end 81 of the economizer 8, one end of the seventh pipeline 107 is connected to the second end 82 of the economizer 8, and the other end is connected to a position on the third pipeline 103 between the first throttling device 7 and the evaporator 9, the first end 81 and the second end 82 are connected inside the economizer 8, and the second throttling device 5 is arranged on the seventh pipeline 107.

[0058] The economizer is a heat exchanger that absorbs heat through the throttling and evaporation of the refrigerant itself, thereby supercooling another part of the refrigerant.

[0059] This is a further pipeline connection method of the present invention. The cold end of the vortex tube and the condenser can be connected through the fifth pipeline, the sixth pipeline connects the condenser and the first end of the economizer, and the seventh pipeline connects the second end of the economizer and the evaporator, thereby effectively connecting the condenser and the economizer between the cold end of the vortex tube and the evaporator. The gas temperature of the cold end of the vortex tube can be lower than that of the compressor outlet end, so that the supercooling degree of the condenser outlet end is higher, which can increase the supercooling degree before entering the evaporator and improve the evaporation heat exchange efficiency; by entering the economizer, the temperature of the refrigerant flowing out of the second end of the economizer and before entering the evaporator can be further reduced (the supercooling degree is further improved), which can further improve the evaporation heat exchange efficiency.

[0060] In some embodiments, an eighth pipeline 108 and a ninth pipeline 109 are further included. One end of the eighth pipeline 108 is connected to the section of the seventh pipeline 107 between the second end 82 and the second throttling device 5, and the other end is connected to the third end 83 of the economizer 8. One end of the ninth pipeline 109 is connected to the fourth end 84 of the economizer 8, and the other end is connected to the air supply port 13 of the compressor 1. The third end 83 and the fourth end 84 are connected within the economizer. The present invention also allows the refrigerant in the seventh pipeline to be drawn out through the eighth pipeline and enter the economizer through the third end. The section between the third end 83 and the fourth end 84 exchanges heat with the section between the first end 81 and the second end 82, further reducing the temperature of the refrigerant in the section between the first end and the second end, thereby further subcooling the refrigerant entering the seventh pipeline and enhancing the heat exchange efficiency of the evaporator. The present invention also allows the refrigerant (i.e., the intermediate-pressure refrigerant) after heat exchange to be introduced into the air supply port of the compressor through the ninth pipeline, achieving the air supply effect.

[0061] In some embodiments, a third throttling device 6 is further included. The third throttling device 6 is disposed on the eighth pipeline 108, and the third end 83 and the fourth end 84 are in communication with each other inside the economizer 8. The third throttling device disposed on the eighth pipeline can throttle and reduce the pressure of the refrigerant entering the pipeline, thereby absorbing heat in the first heat exchange section between the third end 83 and the fourth end 84, thereby further reducing the refrigerant temperature in the first heat exchange section.

[0062] In some embodiments, the first end 81 and the second end 82 are connected within the economizer 8 via a first heat exchange section, and the third end 83 and the fourth end 84 are connected within the economizer 8 via a second heat exchange section, enabling heat exchange between the first and second heat exchange sections. The present invention utilizes the first and second heat exchange sections within the economizer to respectively connect the first and second ends, and the third and fourth ends, and to effectively exchange heat between the first and second heat exchange sections. One section generates intermediate pressure to replenish air to the compressor, while the other section achieves further subcooling, thereby enhancing the refrigeration efficiency of the evaporator.

[0063] In some embodiments, a second fan 4 is further included, which is disposed opposite to the condenser 3 and can drive airflow to exchange heat with the refrigerant in the condenser 3. The present invention can also drive and control the heat exchange of the condenser through the second fan.

[0064] The present invention adopts a direct expansion refrigeration system with a condenser reheater, which can meet the temperature and humidity requirements of special occasions; the system adopts quasi-two-stage compression to increase the system refrigerant circulation volume; at the same time, the system adds a vortex tube, and uses the cooling effect of the vortex tube to maximize the use of the cold and hot energy of the refrigeration system.

[0065] The present invention further provides a method for controlling a refrigeration system as described in any of the preceding items, comprising:

[0066] a detection step of detecting the moisture content of the air after heat exchange through the evaporator 9;

[0067] a determination step of determining a magnitude relationship between the air moisture content and a preset moisture content;

[0068] The control step is to increase the operating frequency of the compressor 1 when the air humidity is greater than the preset humidity, and to decrease the operating frequency of the compressor 1 when the air humidity is less than the preset humidity.

[0069] The present invention detects the absolute moisture content after the evaporator and compares it with the target value, and adjusts the operating frequency of the compressor according to the detection result. When the measured moisture content is greater than the target moisture content + deviation value, the compressor increases the frequency; when the target moisture content - deviation value is less than the measured moisture content and less than the target moisture content + deviation value, the compressor maintains the current operating frequency; when the measured moisture content is less than the target moisture content - deviation value, the compressor decreases the frequency. When the actual moisture content is high, the present invention can provide a larger flow of exhaust refrigerant by increasing the compressor frequency, thereby increasing the amount of refrigerant in the evaporator 9, thereby improving the dehumidification effect and reducing the moisture content of the air. When the moisture content is low, the compressor frequency is reduced to reduce the cooling capacity in the evaporator 9, thereby reducing the dehumidification effect and increasing the moisture content. The humidity in the room or designated space can be controlled within an appropriate range to meet the requirements of human comfort or process requirements under more working conditions.

[0070] In some embodiments, when the refrigeration system further includes a condenser 3 and a second fan 4:

[0071] The detection step also detects the subcooling degree of the refrigerant at the outlet of the condenser 3;

[0072] The judging step comprises judging the magnitude relationship between the refrigerant subcooling degree and a preset subcooling degree;

[0073] The control step is as follows: when the refrigerant subcooling degree is greater than the preset subcooling degree, the operating frequency of the second fan 4 matched with the condenser 3 is controlled to decrease; when the refrigerant subcooling degree is less than the preset subcooling degree, the operating frequency of the second fan 4 matched with the condenser 3 is controlled to increase.

[0074] The present invention detects the refrigerant subcooling at the condenser outlet and compares it with a target value, adjusting the condensing fan operating frequency according to the detection result. When the measured subcooling is greater than the target subcooling + deviation value, the condensing fan operating frequency is reduced; when the target subcooling - deviation value is less than the measured subcooling and less than the target subcooling + deviation value, the condensing fan operating frequency is maintained at the current operating frequency; when the measured subcooling is less than the target subcooling - deviation value, the condensing fan operating frequency is increased. Wherein: subcooling = saturation temperature corresponding to saturation pressure - measured refrigerant temperature. For example, when the subcooling is high, the present invention controls the second fan frequency to decrease to reduce heat exchange at condenser 3, thereby reducing subcooling. It can also reduce the fan operating frequency while meeting the subcooling requirement, thereby saving energy and improving system energy efficiency. When the subcooling is low, the second fan frequency is controlled to increase to increase heat exchange at condenser 3, thereby increasing subcooling. The subcooling of the evaporator can be controlled within an appropriate range to meet the requirements of human comfort or process requirements under more working conditions.

[0075] In some embodiments, the detecting step further detects the supply air temperature at the outlet of the condenser reheater 10;

[0076] The determining step is to determine the magnitude relationship between the air supply temperature and the preset temperature;

[0077] The control step controls the proportional regulating valve at the hot end of the vortex tube 2 to decrease its opening when the supply air temperature is greater than the preset temperature; and controls the proportional regulating valve at the hot end of the vortex tube 2 to increase its opening when the supply air temperature is less than the preset temperature.

[0078] The present invention detects the supply air temperature after the condenser reheater and compares it with a target value, then adjusts the flow rate at the outlet of the hot end 22 of the vortex tube based on the detection result. When the measured supply air temperature exceeds the target supply air temperature + a deviation value, the proportional control valve at the hot end 22 of the vortex tube is closed; when the measured supply air temperature is less than the target supply air temperature - the deviation value, the proportional control valve at the hot end 22 of the vortex tube is opened; and when the target supply air temperature - the deviation value is less than the measured supply air temperature < the target supply air temperature + the deviation value, the proportional control valve at the hot end 22 of the vortex tube maintains its current opening. For example, when the supply air temperature is high, the refrigerant flow entering the condenser reheater is high, so the vortex tube needs to be controlled to reduce the flow rate entering the condenser reheater. When the supply air temperature is low, the refrigerant flow entering the condenser reheater is low, so the vortex tube needs to be controlled to increase the flow rate entering the condenser reheater. This allows the indoor supply air temperature to be controlled within an appropriate range, meeting human comfort requirements or process requirements.

[0079] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention. The above description is merely a preferred embodiment of the present invention. It should be noted that those skilled in the art can make various improvements and variations without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. A refrigeration system, characterized in that: include: A compressor (1), a vortex tube (2), a condenser reheater (10) and an evaporator (9), wherein the vortex tube (2) includes an inlet end (21), a hot end (22) and a cold end (23), the outlet temperature of the hot end (22) is higher than the outlet temperature of the cold end (23), the inlet end (21) of the vortex tube (2) is connected to the outlet end (11) of the compressor (1), the hot end (22) of the vortex tube (2) is connected to one end of the condenser reheater (10), the other end of the condenser reheater (10) can be connected to one end of the evaporator (9), and the other end of the evaporator (9) can be connected to the suction end (12) of the compressor (1); the evaporator (9) and the condenser reheater (10) constitute at least part of the structure of a constant temperature and humidity component.

2. The refrigeration system according to claim 1, characterized in that: The constant temperature and humidity component further comprises a first fan (14), the evaporator (9), the condenser reheater (10) and the first fan (14) are located in the same dehumidification air duct, and the first fan (14) can drive air to pass through the evaporator (9) and the condenser reheater (10) in sequence for heat exchange; the hot end (22) and the cold end (23) of the vortex tube (2) are both provided with electric proportional control valves.

3. The refrigeration system according to claim 1 or 2, characterized in that: It also includes a condenser (3), one end of the condenser (3) is connected to the cold end (23) of the vortex tube (2), and the other end of the condenser (3) can be connected to one end of the evaporator (9), and the condenser (3) can increase the supercooling degree of the refrigerant entering the evaporator (9).

4. The refrigeration system according to claim 3, wherein: The economizer (8) is also included. The economizer (8) is arranged between the condenser (3) and the evaporator (9). The economizer (8) can further increase the supercooling degree of the refrigerant entering the evaporator (9), and the economizer (8) can replenish air to the compressor (1).

5. The refrigeration system according to any one of claims 1 to 4, characterized in that: The utility model comprises a first pipeline (101), a second pipeline (102), a third pipeline (103), a fourth pipeline (104) and a first throttling device (7), wherein one end of the first pipeline (101) is connected to the outlet end (11) of the compressor (1), and the other end is connected to the inlet end (21) of the vortex tube (2), one end of the second pipeline (102) is connected to the hot end (22) of the vortex tube (2), and the other end is connected to one end of the condenser reheater (10), one end of the third pipeline (103) is connected to the other end of the condenser reheater (10), and the other end of the third pipeline (103) is connected to one end of the evaporator (9), one end of the fourth pipeline (104) is connected to the other end of the evaporator (9), and the other end of the fourth pipeline (104) is connected to the suction end (12) of the compressor (1), and the first throttling device (7) is arranged on the third pipeline (103).

6. The refrigeration system according to claim 5, characterized in that: When the refrigeration system further includes a condenser (3) and an economizer (8), the refrigeration system further includes a fifth pipeline (105), a sixth pipeline (106), a seventh pipeline (107) and a second throttling device (5), one end of the fifth pipeline (105) is connected to the cold end (23) of the vortex tube (2), and the other end is connected to one end of the condenser (3), one end of the sixth pipeline (106) is connected to the other end of the condenser (3), and the other end of the sixth pipeline (106) is connected to the first end (81) of the economizer (8), one end of the seventh pipeline (107) is connected to the second end (82) of the economizer (8), and the other end is connected to a position on the third pipeline (103) between the first throttling device (7) and the evaporator (9), the first end (81) and the second end (82) are connected inside the economizer (8), and the second throttling device (5) is arranged on the seventh pipeline (107).

7. The refrigeration system according to claim 6, characterized in that: The system further comprises an eighth pipeline (108) and a ninth pipeline (109), wherein one end of the eighth pipeline (108) is connected to the pipe section of the seventh pipeline (107) between the second end (82) and the second throttling device (5), and the other end is connected to the third end (83) of the economizer (8); one end of the ninth pipeline (109) is connected to the fourth end (84) of the economizer (8), and the other end is connected to the air supply end (13) of the compressor (1); and the third end (83) and the fourth end (84) are connected inside the economizer.

8. The refrigeration system according to claim 7, characterized in that: It also includes a third throttling device (6), which is arranged on the eighth pipeline (108), and the third end (83) and the fourth end (84) are connected inside the economizer (8).

9. The refrigeration system according to claim 7 or 8, characterized in that: The first end (81) and the second end (82) are connected inside the economizer (8) through a first heat exchange section, and the third end (83) and the fourth end (84) are connected inside the economizer (8) through a second heat exchange section, and heat exchange can be performed between the first heat exchange section and the second heat exchange section.

10. The refrigeration system according to claim 3 or 4, characterized in that: It also includes a second fan (4), which is arranged opposite to the condenser (3), and the second fan (4) can drive the airflow to exchange heat with the refrigerant in the condenser (3).

11. A method for controlling a refrigeration system according to any one of claims 1 to 10, characterized in that: include: a detection step of detecting the moisture content of the air after heat exchange through the evaporator (9); a determination step of determining a magnitude relationship between the air moisture content and a preset moisture content; The control step is to increase the operating frequency of the compressor (1) when the air humidity is greater than a preset humidity, and to decrease the operating frequency of the compressor (1) when the air humidity is less than the preset humidity.

12. The control method according to claim 11, characterized in that: When the refrigeration system further includes a condenser (3) and a second fan (4): The detection step also detects the subcooling degree of the refrigerant at the outlet of the condenser (3); The judging step comprises judging the magnitude relationship between the refrigerant subcooling degree and a preset subcooling degree; The control step controls the operating frequency of the second fan (4) matched with the condenser (3) to decrease when the refrigerant subcooling degree is greater than the preset subcooling degree; and controls the operating frequency of the second fan (4) matched with the condenser (3) to increase when the refrigerant subcooling degree is less than the preset subcooling degree.

13. The control method according to claim 11, characterized in that: The detection step further detects the supply air temperature at the outlet of the condenser reheater (10); The determining step is to determine the magnitude relationship between the air supply temperature and the preset temperature; The control step controls the proportional regulating valve at the hot end of the vortex tube (2) to decrease its opening when the air supply temperature is greater than the preset temperature; and controls the proportional regulating valve at the hot end of the vortex tube (2) to increase its opening when the air supply temperature is less than the preset temperature.

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