Refrigeration system, expansion valve assembly, and refrigeration system control method

Abstract

The present invention relates to a refrigeration system, an expansion valve assembly and a control method for the refrigeration system, the refrigeration system including a bypass passage, a second temperature sensor and a controller, the bypass passage communicating with a first passage and a second passage, the bypass passage having a throttle portion located between an inlet and an outlet of the bypass passage, the sensing head of the second temperature sensor is disposed in the bypass passage, located between the throttle portion and the outlet of the bypass passage and disposed adjacent to the outlet, when the system is operated, the working medium in the bypass passage where the sensing head of the second temperature sensor is located is in a saturated state, the controller obtains the detection results of the first temperature sensor and the second temperature sensor, determines a difference between the detection results, and determines a superheat degree at the inlet of the compressor according to the difference, the present invention solves the problem that the refrigeration system needs to rely on a pressure sensor to determine the superheat degree at the inlet of the compressor, which is advantageous to reduce the manufacturing cost.

Description

[Technical Field]

[0001] This application claims priority to a Chinese patent application filed with the China Patent Office on May 14, 2021, bearing application number 202110530306.8 and entitled "Refrigeration system, expansion valve assembly and refrigeration system control method," the entire contents of which are incorporated herein by reference.

[0002] The present invention relates to the technical field of air conditioning, and more particularly to a refrigeration system, an expansion valve assembly and a method for controlling a refrigeration system. [Background technology]

[0003] In the prior art, a refrigeration system needs to be provided with a temperature sensor capable of detecting temperature data and a pressure sensor capable of detecting pressure data. The refrigeration system determines and controls the superheat degree at the inlet of the compressor based on temperature data and pressure data to ensure that liquid refrigerant does not enter the compressor and prevent the compressor from being damaged by the liquid refrigerant, but the cost of the pressure sensor is high.

[0004] In the prior art, the refrigeration system has to rely on a pressure sensor to determine the superheat at the compressor inlet, which increases the manufacturing cost, and no effective solution has been proposed yet to solve this problem. Summary of the Invention [Problem to be solved by the invention]

[0005] An object of the present invention is to provide a refrigeration system, an expansion valve assembly, and a refrigeration system control method that are advantageous in reducing manufacturing costs. [Means for solving the problem]

[0006] In order to achieve the above object, the present invention is as follows: A refrigeration system includes a compressor, a condenser, an expansion valve, an evaporator, a first passage, a first temperature sensor, and a second passage, the first passage communicating between the evaporator and the compressor, a sensing head of the first temperature sensor being provided in the first passage, the second passage being located between the condenser and the evaporator, and the expansion valve being capable of forming a throttle point in the second passage; a bypass passage having an outlet communicating with the first passage and an inlet communicating with the second passage, the bypass passage having a throttle portion located between the inlet and the outlet; a second temperature sensor having a sensing head disposed within the bypass passage and positioned between the restriction and an outlet of the bypass passage and adjacent to the outlet; Further includes:

[0007] Furthermore, the present invention discloses a refrigeration system control method applied to the refrigeration system, The refrigeration system control method includes: obtaining detection results of a first temperature sensor and a second temperature sensor in the refrigeration system; determining a difference between the sensing results of the first temperature sensor and the second temperature sensor; determining superheat at an inlet of a compressor of the refrigeration system based on the difference; Includes.

[0008] An embodiment of the present invention provides a refrigeration system including a bypass passage, a second temperature sensor, and a controller, the bypass passage communicating with a first passage and a second passage, the bypass passage communicating with the first passage through an outlet, and the bypass passage communicating with the second passage through an inlet, the bypass passage having a throttle portion located between the inlet and the outlet of the bypass passage, and the sensing head of the second temperature sensor being located in the bypass passage and between the throttle portion and the outlet of the bypass passage and adjacent to the outlet, so that using two temperature sensors to obtain the superheat degree is advantageous in terms of reducing manufacturing costs compared to using a temperature pressure sensor to obtain the superheat degree. [Brief explanation of the drawings]

[0009] The drawings described herein provide a further understanding of the present invention and constitute a part of the present invention, and the description of the present invention is intended to interpret the present invention and is not to be construed as an undue limitation of the present invention. The drawings are as follows:

[0010] [Figure 1] 1 is a configuration block diagram of a refrigeration system according to a first embodiment of the present invention. [Figure 2] FIG. 4 is a configuration block diagram of a refrigeration system according to a second embodiment of the present invention. [Figure 3] FIG. 2 is a pressure-enthalpy schematic diagram of a refrigeration system according to an embodiment of the present invention. [Figure 4] FIG. 10 is a configuration block diagram of a refrigeration system according to a third embodiment of the present invention. [Figure 5] FIG. 10 is a configuration block diagram of a refrigeration system according to a fourth embodiment of the present invention. [Figure 6] FIG. 10 is a configuration block diagram of a refrigeration system according to a fifth embodiment of the present invention. [Figure 7] FIG. 10 is a configuration block diagram of a refrigeration system according to a sixth embodiment of the present invention. [Figure 8] FIG. 10 is a schematic diagram showing the configuration of a bypass passage according to a seventh embodiment of the present invention. [Figure 9] FIG. 13 is a schematic diagram showing the configuration of a bypass passage according to an eighth embodiment of the present invention. [Figure 10] FIG. 13 is a schematic diagram showing the configuration of a bypass passage according to a ninth embodiment of the present invention. [Figure 11] FIG. 19 is a schematic diagram of the flow direction of the working medium in a refrigeration system according to a tenth embodiment of the present invention. [Figure 12] FIG. 11 is a schematic diagram of the flow direction of the working medium in a refrigeration system according to an eleventh embodiment of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0011] FIG. 1 is a block diagram of a refrigeration system according to a first embodiment of the present invention. As shown in FIG. 1, the refrigeration system includes four basic devices: a compressor 10, a condenser 20, an expansion valve 30, and an evaporator 40. Furthermore, the compressor 10 is the power source of the refrigeration cycle, and the compressor 10 can extract the working medium (for example, the working medium is a refrigerant or a coolant) in the evaporator 40 at the appropriate time by constantly rotating the electric motor. Furthermore, the compressor 10 also increases the pressure and temperature of the working medium through its compression action, and the condenser 20 is a heat exchange device that uses an external environment medium (for example, air or water) to cool the high-temperature, high-pressure working medium from the compressor 10. After the working medium passes through the condenser 20, it is condensed into a high-pressure, room-temperature working medium. The high-pressure, room-temperature working medium cannot be directly sent to the low-pressure, low-temperature evaporator 40. According to the principle of one-to-one correspondence between saturation pressure and saturation temperature, lowering the pressure of the working medium will also lower the saturation temperature of the working medium. Therefore, the high-pressure, room-temperature working medium is throttled and decompressed by the expansion valve 30 to obtain a low-temperature, low-pressure working medium, which is then sent to the evaporator 40 to absorb heat and evaporate. The evaporator 40 is also a heat exchange device, and the low-temperature, low-pressure working medium after throttling evaporates into steam within the evaporator 40, absorbing the heat of the object to be cooled and lowering the temperature of the object, thereby achieving purposes such as cooling, freezing, and refrigeration. The refrigeration system includes four basic devices: a compressor 10, a condenser 20, an expansion valve 30, and an evaporator 40, as well as a first passage 50, a first temperature sensor 60, and a second passage . The first passage 50 communicates between the evaporator 40 and the compressor 10, and the first temperature sensor 60 can detect the temperature in the first passage 50, thereby providing part of the detection data for measuring and controlling the superheat degree of the compressor 10, ensuring that the working medium in a liquid state does not flow into the inlet of the compressor 10, and avoiding liquid hammer damage to the compressor 10. The second passage 70 is located between the condenser 20 and the evaporator 40 , and the expansion valve 30 includes a valve body 31 and a valve element 32 . The valve element 32 and the second passage 70 form a throttling area within the second passage 70, and specifically, the valve element 32 moves up and down to adjust the flow area of ​​the second passage 70 and achieve the purpose of throttling. In this embodiment, at least a portion of the second passage 70 is molded in the expansion valve 30 , and specifically, can be located in the valve body 31 of the expansion valve 30 .

[0012] FIG. 2 is a block diagram of a refrigeration system according to a second embodiment of the present invention. As shown in FIG. 2, the first passage 50 can be formed in the expansion valve 30 for industrial use, and the refrigeration system provided by the embodiment of the present invention further includes a bypass passage 80 and a second temperature sensor 90. In this embodiment, at least a portion of the first passage 50 and at least a portion of the second passage 70 are both molded in the expansion valve 30 , specifically, in the valve body 31 of the expansion valve 30 . The second passage 70 is located between the condenser 20 and the evaporator 40, the first passage 50 is located between the evaporator 40 and the compressor 10, the sensing head of the first temperature sensor 60 is located in the first passage 50, and the bypass passage 80 connects the first passage 50 and the second passage 70. The sensing head of the second temperature sensor 90 is located within the bypass passage 80 and on the side of the bypass passage 80 that is adjacent to the first passage 50 . The bypass passage 80 may be a minute passage having a circular cross section or any other shape. If the sensing head portion of the second temperature sensor 90 protrudes from the wall surface of the first passage 50, it will be affected by the superheated gas C at the outlet of the evaporator 40, making the detected temperature inaccurate. If the sensing head of the second temperature sensor 90 is too far from the wall surface of the first passage 50, the pressure here will not be equal to the pressure inside the first passage 50, which will affect the final determination of the degree of superheat. Therefore, the second temperature sensor 90 can be provided at the end of the bypass passage 80 and close to the wall surface of the first passage 50 so as not to be affected by the superheated gas C at the outlet of the evaporator 40.

[0013] It should be noted that the size of the nominal diameter of the bypass passage 80 must be appropriately selected. Specifically, the size of the nominal diameter of the bypass passage 80 must satisfy the following. That is, when the refrigeration system is operating, the working medium in the bypass passage 80 where the sensing head of the second temperature sensor 90 is located is saturated. If the nominal diameter of the bypass passage 80 is too small, the bypass flow rate will be too small, and the working medium will be heated or cooled by the expansion valve 30 and the environment before reaching the second temperature sensor 90, becoming a superheated gas or a subcooled liquid. The temperature of the working medium detected by the second temperature sensor 90 is not the saturation temperature of the gas-liquid two-phase fluid. If the nominal diameter of the bypass passage 80 is too large, the bypass flow rate will be too large, and excessive gas-liquid two-phase working medium will pass through the bypass passage 80 and enter the first passage 50. In order to ensure a constant degree of superheat in the first passage 50, the gas at the outlet of the evaporator 40 will require a greater degree of superheat, which will reduce the operating efficiency of the evaporator 40.

[0014] Furthermore, the nominal diameter of the bypass passage 80 can be determined by the following means so that the working medium at the second temperature sensor 90 is saturated when the refrigeration system is operating: in the process, at the position of the sensing head of the second temperature sensor 90 in the bypass passage 80, a pressure sensor and a temperature sensor are used to detect the pressure and temperature of the working medium at this position, and the pressure and temperature values ​​are compared with the values ​​in the temperature and pressure correspondence table for the saturated state. If the measured pressure and temperature values ​​are the same as or essentially the same as the pair of pressure and temperature values ​​in this relationship table, the bypass passage 80 can be processed according to the nominal diameter of the bypass passage 80 in this case.

[0015] In addition, the refrigeration system further includes a controller that acquires the detection results of the first temperature sensor 60 and the second temperature sensor 90, determines a difference between the detection results of the first temperature sensor 60 and the second temperature sensor 90, and determines a superheat controller (not shown) at the inlet of the compressor 10 based on the difference.

[0016] The embodiment of the present invention also provides an operating principle that allows the controller to determine the superheat degree at the inlet of the compressor 10 based on the difference, and this operating principle is only a general explanation and is not a limiting explanation. The operating principle is as follows: As shown in FIG. 2, the compressor 10 compresses a gaseous, low-temperature, low-pressure working medium gas into a high-temperature, high-pressure gas and discharges it. The high-temperature, high-pressure gaseous working medium is liquefied as it passes through the condenser 20, and its heat is absorbed by the air outside the vehicle. Then, the high-pressure liquid working medium A is reduced in pressure by the throttling action of the expansion valve 30 to become a low-pressure gas-liquid two-phase fluid B, and the low-pressure gas-liquid two-phase fluid in one branch path absorbs heat in the evaporator 40 to become superheated gas C, and the low-pressure gas-liquid two-phase fluid B in the other branch path enters the bypass passage 80, where it is throttled and its pressure further decreases to become a gas-liquid two-phase fluid D. The gas-liquid two-phase fluid D in the bypass passage 80 and the superheated gas C at the outlet of the evaporator 40 join together in the first passage 50 to form gas E. The bypass passage 80 is connected to the first passage 50, and the pressure of the gas-liquid two-phase fluid D is approximately equal to the pressure of the gas E. Therefore, the saturation temperature of the gas E is the same as the saturation temperature of the gas-liquid two-phase fluid D. When the bypass passage 80 was manufactured, the nominal diameter was controlled so that the gas-liquid two-phase fluid D was saturated. Therefore, the saturation temperature of the gas-liquid two-phase fluid D is the temperature of the gas-liquid two-phase fluid D. Therefore, the degree of superheat in the first passage 50 can be the difference between the temperature of the gas E and the temperature of the gas-liquid two-phase fluid D. Since the first temperature sensor 60 detects the temperature of the surrounding gas E and the second temperature sensor 90 detects the temperature of the surrounding gas-liquid two-phase fluid D, the degree of superheat in the first passage 50 can be the difference between the detection results of the first temperature sensor 60 and the second temperature sensor 90. The first passage 50 is connected to the inlet of the compressor 10, and when the distance and pressure drop from the first passage 50 to the compressor 10 are ignored, the degree of superheat in the first passage 50 can approach the degree of superheat at the inlet of the compressor 10.

[0017] In order to avoid liquid hammer damage to the compressor 10, it is necessary to ensure that the difference between the detection results of the first temperature sensor 60 and the second temperature sensor 90 is greater than the set value. Figure 3 is a pressure-enthalpy schematic diagram of a refrigeration system according to an embodiment of the present invention. As shown in FIG. 3, in order to avoid liquid hammer damage to the compressor 10, the location of the gas E in the pressure-enthalpy diagram should be in the area to the right of the solid line in the pressure-enthalpy diagram. In addition, the working medium A cooled in the condenser is throttled and expanded in the second passage, becoming a low-temperature two-phase fluid B. In one passage, it passes through the evaporator to absorb heat and becomes a superheated gas C. The working medium is in a two-phase fluid state at point B, and its temperature at point B is the saturation temperature of point B. However, due to pressure loss caused by the evaporator 40, the saturation temperature corresponding to point C is lower than that of point B. Therefore, the temperature at point B cannot be made the saturation temperature of point C. The small flow rate of the working medium in the other passage is further decompressed to D in the bypass passage 80. The working medium corresponding to point D is still in a two-phase state, and its temperature is the saturation temperature. Furthermore, the pressure at point D is equal to the pressure at point C, and the working medium corresponding to point E, which is a mixture of the working medium corresponding to point C and the working medium corresponding to point D, is maintained such that the pressures at point D and point C are essentially unchanged. Furthermore, since the working medium corresponding to point E is cooled by the two-phase fluid at point D, the temperature at point E is slightly lower than that at point C. The temperature difference between points E and D is the superheat at the inlet of the compressor 10. What is most important for the compressor 10 is not the superheat at point C, but the superheat at point E.

[0018] Because the cost of a pressure sensor is higher than the cost of a temperature sensor, the present invention determines the superheat degree at the inlet of the compressor 10 by obtaining the detection results of the first temperature sensor 60 and the second temperature sensor 90, which is more advantageous in reducing manufacturing costs than the prior art method of determining the superheat degree at the inlet of the compressor 10 by obtaining the detection results of the first temperature sensor 60 and the second pressure sensor 90. At the same time, when the temperature is below zero, the accuracy of the temperature sensor is higher than the accuracy of the pressure sensor, and when the temperature is below zero, the superheat degree determined by the embodiment of the present invention is more accurate.

[0019] In this embodiment, as shown in FIG. 2, the bypass passage 80 is opened in the valve body 31 of the expansion valve 30. In some other embodiments, as shown in FIG. 1, the bypass passage 80 may be partially opened in the valve body 31 of the expansion valve 30 and partially form a piping structure; in some other embodiments, as shown in FIG. 4, which is a structural block diagram of a refrigeration system according to a third embodiment of the present invention, the bypass passage 80 may be formed in the evaporator 40, and an insulating section is provided between the bypass passage 80 and the main body of the evaporator 40 to prevent the temperature in the evaporator 40 from affecting the temperature of the working medium in the bypass passage 80. In some other embodiments, FIG. 5 is a structural block diagram of a refrigeration system according to a fourth embodiment of the present invention. As shown in FIG. 5, a bypass passage 80 may be provided between the expansion valve 30 and the evaporator 40, forming an independent pipe structure.

[0020] In this embodiment, as shown in FIG. 2, the bypass passage 80 is straight, and in some other embodiments, as shown in FIG. 6, which is a structural block diagram of a refrigeration system according to a fifth embodiment of the present invention, the bypass passage 80 may be bent.

[0021] Specifically, when at least a portion of the bypass passage 80 is provided inside the expansion valve 30, the bypass passage 80 may be provided on either side of the second passage 70 in the axial direction. That is, the bypass passage 80 may be provided before or after the throttle portion of the second passage 70 . FIG. 7 is a structural block diagram of a refrigeration system according to a sixth embodiment of the present invention. As shown in FIG. 7, a bypass passage 80 may be provided on the inlet side of the second passage 70. Since the working medium starts to enter the bypass passage 80 from state A instead of state B, the pressure difference across the bypass passage 80 is greater, so that the bypass passage 80 can be made longer and narrower when provided on the inlet side of the second passage 70.

[0022] Furthermore, in order to make the gas-liquid two-phase fluid D more likely to reach the required saturated state, a throttle section 81 can be provided in the bypass passage 80 to significantly reduce the pressure in the bypass passage 80, and this throttle section 81 is provided on the side of the second temperature sensor 90 away from the first passage 50. This second temperature sensor 90 is located within a wider area than the throttling portion 81 to avoid a large pressure drop at the detection position of the second temperature sensor 90. Figure 8 is a schematic diagram of the configuration of a bypass passage 80 according to a seventh embodiment of the present invention, Figure 9 is a schematic diagram of the configuration of a bypass passage 80 according to an eighth embodiment of the present invention, and Figure 10 is a schematic diagram of the configuration of a bypass passage 80 according to a ninth embodiment of the present invention. As shown in Figures 8 to 10, the constriction 81 may be of any shape, and optionally, for ease of processing, the constriction 81 may be set to a regular shape.

[0023] FIG. 11 is a schematic diagram of the flow direction of the working medium in a refrigeration system according to a tenth embodiment of the present invention, and FIG. 12 is a schematic diagram of the flow direction of the working medium in a refrigeration system according to an eleventh embodiment of the present invention. As shown in Figures 11 and 12, when the bypass passage 80 is provided outside the expansion valve 30, the bypass passage 80 may be provided upstream of the second passage 70 of the expansion valve 30, or the bypass passage 80 may be provided downstream of the second passage 70 of the expansion valve 30.

[0024] The technical features of the embodiments described above can be combined in any combination, and for the sake of brevity, not all possible combinations of the technical features in the above embodiments are described, but as long as there is no contradiction in the combination of these technical features, they are within the scope described in this specification.

[0025] The above-described examples merely represent some embodiments of the present invention, and although the descriptions are more specific and detailed, they cannot be understood as limitations on the scope of the invention patent. Further modifications and improvements are possible without departing from the concept of the present invention, and all of these fall within the scope of protection of this application. Therefore, the scope of protection of this patent shall be determined according to the appended claims. [Explanation of symbols]

[0026] 10 ···Compressor; 20 ···Condenser; 30 ···Expansion valve; 31 ···Valve body; 311 ···First Hole; 312 ···valve orifice; 313 ···Second Hole; 32 ···Valve body; 40 ···Evaporator; 50 ···First passage; 60 ···First temperature sensor; 70 ···Second passage; 80 ···bypass passage; 81 ···Throat section; 90 ···Second temperature sensor.

Claims

1. A refrigeration system comprising a compressor (10), a condenser (20), an expansion valve (30), an evaporator (40), a first passage (50), a first temperature sensor (60), and a second passage (70), wherein the first passage (50) connects the evaporator (40) and the compressor (10), a sensing head of the first temperature sensor (60) is provided in the first passage (50), the second passage (70) is located between the condenser (20) and the evaporator (40), and the expansion valve (30) is capable of forming a throttling point in the second passage (70), a bypass passage (80) having an outlet communicating with the first passage (50) and an inlet communicating with the second passage (70) and located downstream of the expansion valve (30) when the refrigeration system performs a cooling operation, the bypass passage (80) having a throttle portion (81) located between the inlet and the outlet; a second temperature sensor (90) whose sensing head is provided in the bypass passage (80) and which is located between the throttle portion (81) and the outlet of the bypass passage (80) and is provided close to the outlet; The refrigeration system further comprising:

2. 2. The refrigeration system of claim 1, further comprising a controller capable of determining a degree of superheat at the inlet of the compressor based on the detection results of the first temperature sensor and the second temperature sensor.

3. 3. The refrigeration system of claim 2, wherein the controller is capable of determining the degree of superheat at the inlet of the compressor based on a difference between the detection results of the first temperature sensor and the second temperature sensor.

4. The expansion valve (30) includes a valve body (31) and a valve element (32), The valve body (31) has a first passage (311) having a valve port (312), The valve body (32) is movable relative to the valve port (312), The valve body (32) is capable of adjusting the flow area of ​​the first hole (311), The refrigeration system according to any one of claims 1 to 3, wherein the first passage (311) is a part of the second passage (70).

5. The valve body (31) has a second hole (313), The second passage (313) is a part of the first passage (50), 5. The refrigeration system of claim 4, wherein the first temperature sensor (60) is fixedly connected to the valve body (31).

6. At least a portion of the bypass passage (80) is provided within the expansion valve (30), or The refrigeration system according to any one of claims 1 to 3, characterized in that at least a part of the bypass passage (80) is provided between the expansion valve (30) and the evaporator (40), or at least a part of the bypass passage (80) is provided inside the evaporator (40), and a heat insulating section is provided between the bypass passage (80) and a main body of the evaporator (40).

7. At least a portion of the bypass passage (80) is provided within the expansion valve (30); 7. The refrigeration system according to claim 6, wherein an inlet of the bypass passage (80) is closer to the inlet of the second passage (70) than a throttling point of the second passage (70), or the inlet of the bypass passage (80) is closer to an outlet of the second passage (70) than a throttling point of the second passage.

8. 5. The refrigeration system according to claim 4, wherein one end of the bypass passage (80) communicating with the first passage (50) is located in the valve body (31).

9. 2. The refrigeration system according to claim 1, wherein the diameter of the bypass passage (80) is designed so that, when the refrigeration system is operating, the working medium in the bypass passage (80) is saturated at a location where the sensing head of the second temperature sensor (90) is located.

10. 1. An expansion valve assembly for use in a refrigeration system, comprising: an expansion valve (30), a first temperature sensor (60), a bypass passage (80), a second temperature sensor (90), and a controller; The expansion valve (30) includes a valve body (31) and a valve element (32), The valve body (31) has a first hole (311) and a second hole (313), The sensing head of the first temperature sensor (60) is provided in the second hole (313); The valve body (32) and the first hole (311) can cooperate to form a restriction, the bypass passage (80) communicates the first hole (311) and the second hole (313), and when the refrigeration system performs cooling operation, the bypass passage (80) has an inlet communicating with the first hole (311) and an outlet communicating with the second hole (313), and the inlet of the bypass passage (80) is located downstream of a throttle point formed by the valve body (32) and the first hole (311); The sensing head of the second temperature sensor (90) is provided in the bypass passage (80), Located on the side of the bypass passage (80) close to the second hole (313), The expansion valve assembly is characterized in that the bypass passage (80) includes a throttle portion (81) provided on a side of the second temperature sensor (90) away from the second hole (313).

11. Based on the detection results of the first temperature sensor (60) and the second temperature sensor (90), 11. The refrigeration system of claim 10, further comprising a controller capable of determining the degree of superheat at the outlet of the second passage (313).

12. 12. The refrigeration system of claim 11, wherein the controller is capable of determining the degree of superheat at the outlet of the second passage (313) based on a difference between the detection results of the first temperature sensor (60) and the second temperature sensor (90).

13. 11. The expansion valve assembly according to claim 10, wherein the second temperature sensor (90) is provided at the end of the bypass passage (80) and is close to the wall surface of the second passage (313).

14. 11. The refrigeration system control method of claim 10, wherein the diameter of the bypass passage (80) is designed so that the working medium in the bypass passage (80) is saturated at a location where the sensing head of the second temperature sensor (90) is located when the refrigeration system is operating.

15. A refrigeration system control method applied to the refrigeration system according to claim 1, comprising: Obtaining sensing results of a first temperature sensor (60) and a second temperature sensor (90) in the refrigeration system; determining a difference between the sensing results of the first temperature sensor (60) and the second temperature sensor (90); determining a degree of superheat at an inlet to a compressor (10) of the refrigeration system based on the difference; 10. A method for controlling a refrigeration system, comprising:

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