A refrigerant mixing method in heat exchange equipment

Abstract

The present application relates to a method for mixing refrigerants in a heat exchange device, which belongs to the technical field of distributors. The heat exchange device includes a heat exchanger and a distributor. The heat exchanger is provided with multiple flow paths. The distributor is provided with an inner cavity. The inner cavity is provided with a rotatable stirring member. The multiple flow paths are connected to the inner cavity respectively. The refrigerant mixing method includes the following steps: collecting the temperature of the refrigerant at the outlet of each flow path; obtaining the superheat of the refrigerant at the outlet of each flow path based on the temperature of the refrigerant at the outlet of each flow path; obtaining the superheat discreteness σ of the refrigerant at the outlet of each flow path based on the superheat of the refrigerant; and controlling the rotation speed of the stirring member based on the superheat discreteness σ. The mixing method in this embodiment can adjust the rotation speed of the stirring member in real time, so that the refrigerant can be evenly mixed and separated when the heat exchange device is in different working conditions. The stirring member does not need to maintain a stable high rotation speed all the time to cause energy waste, thereby reducing energy consumption and achieving the purpose of energy saving.

Description

Technical Field

[0001] The present application relates to the technical field of distributors, and in particular to a refrigerant mixing method in a heat exchange device. Background Art

[0002] Distributors are typically installed at the inlet of an air conditioner heat exchanger to evenly distribute the medium throughout the heat exchanger's various flow paths. Liquid distribution within the heat exchanger significantly impacts its performance, which in turn significantly impacts the performance of the refrigeration system. This is especially true when the heat exchanger is an evaporator and the evaporator inlet is a two-phase medium. The uniform distribution of the two-phase medium into each flow path is crucial.

[0003] A distributor generally consists of a manifold and multiple distribution pipes. The manifold is connected to the refrigeration system's expansion valve, while the distribution pipes connect to various flow paths in the heat exchanger. Because the medium after passing through the expansion valve is a two-phase gas-liquid medium, in practical applications, uneven distribution of the gas-liquid medium among the distribution pipes often leads to varying heat exchange efficiencies in different flow paths of the heat exchanger, resulting in poor overall heat exchange capacity. Therefore, uniform distribution of liquid in the distributor is particularly critical in refrigeration systems.

[0004] The dispersion σ of the refrigerant superheat at the heat exchanger outlet is used to characterize the degree of superheat nonuniformity at the outlets of each heat exchanger flow path. The smaller the dispersion σ, the more uniform the superheat at each flow path outlet, and the lower the mixing intensity required in the distributor. When the dispersion is zero, the superheat at each flow path outlet is equal, and the liquid distribution is most uniform. The larger the dispersion σ, the more discrete and less concentrated the superheat at each flow path. In this case, the liquid distribution nonuniformity increases, and the mixing intensity required in the distributor is higher. Therefore, how to adopt different mixing intensities for different operating conditions is an urgent problem in this field. Summary of the Invention

[0005] Based on this, it is necessary to provide a refrigerant mixing method in a heat exchange device that can simultaneously meet the requirements of uniform refrigerant mixing and reduced energy consumption.

[0006] A method for mixing refrigerants in a heat exchange device, the heat exchange device comprising a heat exchanger and a distributor, the heat exchanger being provided with a plurality of flow paths, the distributor being provided with an inner cavity, the inner cavity being provided with a rotatable stirring member, the plurality of flow paths being respectively connected to the inner cavity; the refrigerant mixing method comprising the following steps:

[0007] Collect the temperature of the refrigerant at the outlet of each flow path;

[0008] According to the temperature of the refrigerant at the outlet of each flow path, the superheat degree of the refrigerant at the outlet of each flow path is obtained;

[0009] Obtain the superheat dispersion σ according to the superheat of the refrigerant at the outlet of each flow path;

[0010] Based on the dispersion σ of the superheat degree, the rotation speed of the stirring member is controlled.

[0011] The beneficial effects of adopting this solution:

[0012] Compared to existing technologies, this solution incorporates a stirring element within the inner cavity of the distributor body. The rotation of the stirring element stirs the refrigerant within the inner cavity, allowing the various phases of the refrigerant to be evenly mixed and fully atomized, enhancing the heat exchange efficiency of the heat exchanger. Furthermore, the rotation of the stirring element facilitates heat dissipation from the refrigerant, lowering its temperature and further improving heat exchange efficiency.

[0013] By adopting the mixing method in this embodiment, the rotation speed of the stirring element can be adjusted in real time according to the discrete degree σ of the superheat of the refrigerant at the outlet of the heat exchanger, so that the rotation speed of the stirring element matches the discrete degree σ of the refrigerant, so that the refrigerant can be evenly mixed and separated when the heat exchange equipment is in different working conditions, and the stirring element does not need to maintain a stable high rotation speed all the time to cause energy waste. Therefore, the mixing method of this scheme can reduce energy consumption while ensuring uniform mixing of the refrigerant, thereby achieving the purpose of energy saving.

[0014] In one embodiment, the rotation speed n of the stirring member at time T is T The calculation formula is as follows:

[0015]

[0016] Among them, σ T is the dispersion of superheat at time T, σ1 is the maximum dispersion of superheat, σ0 is the minimum dispersion of superheat, n1 is the maximum speed of the stirring element, and n0 is the minimum speed of the stirring element.

[0017] In one embodiment, the maximum dispersion σ1 and the minimum dispersion σ0 of the superheat are obtained by the following method:

[0018] When debugging the heat exchanger, debug the heat exchanger under different working conditions. When the dispersion of the superheat of the refrigerant at the outlet of multiple flow paths is the largest, calculate the dispersion and record it as the maximum dispersion of the superheat σ1;

[0019] When the dispersion of the superheat degree of the refrigerant at the outlets of the multiple flow paths is the smallest, the dispersion is calculated and recorded as the minimum dispersion of the superheat degree σ0.

[0020] In one embodiment, it is assumed that the heat exchanger includes N flow paths, and the superheat of the refrigerant at the outlet of the i-th flow path is SHi.

[0021] The calculation formula of superheat dispersion σ is as follows:

[0022]

[0023] Here, u is the average value of the superheat of the refrigerant in N flow paths.

[0024] In one embodiment, the calculation formula for the average value u of the superheat of the refrigerant at the outlets of N flow paths is as follows:

[0025]

[0026] In one embodiment, assuming that the heat exchanger includes N flow paths, the superheat of the refrigerant in the i-th flow path is SHi, and the calculation formula of SHi is as follows:

[0027] SHi=ti-tz,

[0028] Wherein, ti is the temperature of the refrigerant at the outlet of the i-th flow path, and tz is the evaporation temperature of the heat exchanger.

[0029] In one embodiment, the evaporation temperature tz of the heat exchanger is calculated from the evaporation pressure of the heat exchanger.

[0030] In one embodiment, the heat exchange device further comprises a driving member, wherein the driving member is capable of driving the agitator to rotate; wherein the method for controlling the rotation of the agitator comprises:

[0031] The driving member is controlled to rotate according to the dispersion σ to control the rotation speed of the stirring member.

[0032] In one embodiment, the stirring member includes an impeller, the driving member includes a motor, and the impeller is rotationally connected to the motor.

[0033] In one embodiment, a transmission rod is connected to the motor, and an end of the transmission rod away from the driving member extends into the inner cavity and is connected to the impeller. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the conventional technology, the following briefly introduces the drawings required for use in the embodiments or the conventional technology descriptions. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0035] Figure 1 This is a schematic diagram of the distributor structure provided in this application.

[0036] Figure 2Cross-sectional view of the dispenser provided for this application.

[0037] Reference numerals:

[0038] 100. Distributor; 110. Distributor body; 111. Inner cavity; 1111. First cavity section; 1112. Second cavity section; 1113. Third cavity section; 112. Inlet section; 113. Throttle ring; 120. Connecting pipe; 130. Stirring assembly; 131. Impeller; 132. Motor; 133. Drive rod. DETAILED DESCRIPTION

[0039] To make the above-mentioned objects, features, and advantages of the present application more clearly understood, the specific embodiments of the present application are described in detail below with reference to the accompanying drawings. The following description sets forth many specific details to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways than those described herein, and those skilled in the art can make similar improvements without violating the scope of the present application. Therefore, the present application is not limited to the specific embodiments disclosed below.

[0040] It should be noted that when a component is referred to as being "fixed to" or "disposed on" another component, it may be directly on the other component or there may be a central component. When a component is considered to be "connected to" another component, it may be directly connected to the other component or there may be a central component at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in the specification of this application are for illustrative purposes only and do not represent the only implementation method.

[0041] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of such features. Throughout the description of this application, "plurality" means at least two, for example, two, three, etc., unless otherwise specifically defined.

[0042] In this application, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it can mean that the first feature is directly in contact with the second feature, or the first feature and the second feature are indirectly in contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it can mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is higher in level than the second feature. When a first feature is "below," "below," or "below" a second feature, it can mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is lower in level than the second feature.

[0043] Unless otherwise defined, all technical and scientific terms used in the specification of this application have the same meaning as commonly understood by those skilled in the art to which this application belongs. The terms used in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application. The term "and / or" used in the specification of this application includes any and all combinations of one or more of the relevant listed items.

[0044] The following further describes in detail the distributor 100, the heat exchange device, and the refrigerant mixing method in the heat exchange device of the present invention in conjunction with the accompanying drawings and specific embodiments:

[0045] The present invention is described below using a heat exchanger as an example, and a gas-liquid two-phase flow refrigerant as an example of the medium. However, those skilled in the art will appreciate that the present invention can be applied to other heat exchange equipment, and the medium can also be other multiphase fluid media.

[0046] A heat exchanger is installed in the refrigeration system of an air conditioner to provide heat exchange function for the air conditioner. In order to evenly distribute the refrigerant to each flow path of the heat exchanger, the heat exchanger includes a plurality of heat exchange tubes. The pipes of the plurality of heat exchange tubes form a plurality of flow paths. The air exchanger is connected to a distributor 100, which distributes the refrigerant to each flow path of the heat exchanger through the distributor 100. Figure 1 and Figure 2 As shown, the distributor 100 includes a distributor body 110 and a plurality of connecting pipes 120. The distributor body 110 is connected to the expansion valve of the refrigeration system. An inner cavity 111 is provided in the distributor body 110. The connecting pipe 120 is provided on the distributor body 110 and is connected to the inner cavity 111 at one end. The connecting pipe 120 is connected to the heat exchange pipe at the other end so that the refrigerant in the inner cavity 111 of the distributor 100 flows into the heat exchange pipe through the connecting pipe 120, thereby realizing heat exchange of the heat exchanger.

[0047] The distributor body 110 also includes an inlet section 112 for the refrigerant to flow in. Preferably, multiple connecting pipes 120 and the inlet section 112 are located on both sides of the inner cavity 111. The multiple connecting pipes 120 are arranged in a radial shape, and the center lines of the multiple connecting pipes 120, the center line of the inlet section 112 and the center line of the inner cavity 111 are located on the same straight line.

[0048] The refrigerant in the refrigeration system flows through the expansion valve into the inner cavity 111 of the distributor body 110. From there, it is distributed to the various connecting pipes 120 and flows through these pipes into the various flow paths of the heat exchanger. Because the refrigerant after passing through the expansion valve is in a two-phase gas-liquid state, uneven distribution of the gas-liquid phase within the distribution pipes often results in varying heat exchange efficiencies in different flow paths of the heat exchanger, leading to poor overall heat exchange capacity.

[0049] Regarding the above issues, refer to Figure 1 and Figure 2 According to one embodiment of the present invention, the distributor 100 further includes a stirring assembly 130 , which includes a driving member and a stirring member. The stirring member is disposed in the inner cavity 111 , and the driving member drives the stirring member to rotate so that the refrigerant is evenly mixed in the inner cavity 111 and distributed to each connecting pipe 120 .

[0050] This solution provides a drive member and a stirring member on the distributor 100. The stirring member rotates within the inner cavity 111 of the distributor body 110 to stir the refrigerant in the inner cavity 111. Because the stirring member is driven by the drive member, it rotates at a relatively high speed, allowing the various phases of the refrigerant to be evenly mixed and fully atomized. The refrigerant is then evenly distributed to the various pipes 120 and flows through each pipe 120 into the various flow paths of the heat exchanger. As a result, the various phases of the refrigerant are evenly distributed in each pipe 120, and the composition of the refrigerant in each pipe 120 is the same, achieving the purpose of uniform liquid distribution of the distributor 100. At the same time, the refrigerant in each flow path of the heat exchanger is the same, and the heat exchange efficiency is also the same, enhancing the heat exchange effect of the entire heat exchanger.

[0051] Furthermore, in this embodiment, the rotation of the stirring member in the inner cavity 111 is driven by an external driving member, the rotation speed is fast, and the stirring amplitude is large, which is more conducive to the heat dissipation of the refrigerant. The refrigerant temperature is further reduced, and after entering the heat exchanger flow path, the heat exchange effect is further improved.

[0052] In this embodiment, the rotation plane of the agitator is perpendicular to the flow direction of the refrigerant, that is, the rotation plane of the agitator is perpendicular to the center line of the multiple connecting pipes 120, and the rotation plane of the agitator is roughly parallel to the plane where the inlets of the multiple connecting pipes 120 are located, so that the refrigerant entering the distributor body 110 presents a spiral flow, the refrigerant can be fully stirred and evenly mixed, and then evenly distributed to each connecting pipe 120.

[0053] In this embodiment, the stirring component 130 is preferably a mechanical stirring component, such as Figure 2 As shown, the stirring member is preferably an impeller 131, and the driving member is preferably a motor 132. The motor 132 is located outside the distributor body 110. A transmission rod 133 is also provided between the motor 132 and the impeller 131. One end of the transmission rod 133 is connected to the motor 132, and the other end of the transmission rod 133 penetrates into the distributor body 110 and is connected to the impeller 131. The motor 132 drives the impeller 131 to rotate via the transmission rod 133, thereby stirring the refrigerant. The use of the above-mentioned mechanical stirring assembly 130 has a high degree of connection stability between the components, so that the impeller 131 can be stably maintained in the set position and direction during rotation, ensuring the stirring effect.

[0054] Of course, in other embodiments, the stirring assembly 130 is not limited to a mechanical stirring assembly 130 and can also be a magnetic stirring assembly 130. In this case, the stirring member is a magnet and the driving member is a coil. By changing the direction of the current in the coil, the direction of the magnetic field is changed, thereby driving the magnet to rotate. With this structure, there is no need for a separate transmission part between the stirring member and the driving member. Accordingly, there is no need to provide a separate through-hole in the dispenser body 110 for installing the transmission part, which reduces the manufacturing difficulty and ensures the strength and sealing of the dispenser body 110.

[0055] A throttling ring 113 is provided between the inlet section 112 and the inner cavity 111 of the distributor body 110. The refrigerant flowing into the distributor 100 is further cooled and decompressed through the throttling ring 113. After the cooled and decompressed refrigerant flows into the heat exchanger, the heat exchange effect is further enhanced.

[0056] To further mix the refrigerant, refer to Figure 2 According to one embodiment of the present invention, the inner cavity 111 of the distributor body 110 is formed by at least two cavity segments connected in sequence, wherein the inner diameters of any two adjacent cavity segments are different, so as to form turbulence in the inner cavity 111 and further improve the heat exchange effect.

[0057] Preferably, the inner cavity 111 includes a first cavity section 1111, a second cavity section 1112 and a third cavity section 1113 which are connected in sequence, the first cavity section 1111 is connected to the inlet section 112, the third cavity section 1113 is connected to multiple connecting pipes 120, the agitator is located in the second cavity section 1112, and the inner diameters of the first cavity section 1111 and the third cavity section 1113 are both smaller than the inner diameter of the second cavity section 1112.

[0058] The first cavity section 1111 is connected to the inlet section 112 via a throttling ring 113, so the inner diameter of the first cavity section 1111 is relatively small. The refrigerant is stirred and mixed in the second cavity section 1112, which requires a larger space. Therefore, the inner diameter of the second cavity section 1112 is relatively large. The mixed refrigerant is distributed to each connecting pipe 120 through the third cavity section 1113. Therefore, the inner diameter of the third cavity section 1113 is relatively small, so that the refrigerant is concentrated before being distributed, which speeds up the distribution speed, reduces the distribution difficulty, and enhances the distribution effect. At the same time, the multiple cavity sections with different inner diameters in the inner cavity 111 form multiple turbulences to enhance the mixing effect of the refrigerant. Therefore, the multi-section structure of the inner cavity 111 is multi-purpose and ensures the mixing and distribution effect.

[0059] According to one embodiment of the present invention, a method for mixing refrigerant in a heat exchanger is further provided, wherein the rotation speed of the stirring element is adjusted according to the dispersion of the refrigerant superheat at the heat exchanger outlet. The refrigerant mixing method includes the following steps:

[0060] Collect the temperature of the refrigerant at the outlet of each flow path;

[0061] According to the temperature of the refrigerant at the outlet of each flow path, the superheat degree of the refrigerant at the outlet of each flow path is obtained;

[0062] Obtain the superheat dispersion σ according to the superheat of the refrigerant at the outlet of each flow path;

[0063] Based on the dispersion σ of the superheat, the rotation speed of the agitator is controlled.

[0064] The dispersion σ of the refrigerant superheat at the heat exchanger outlet is used to characterize the degree of superheat nonuniformity at the outlets of each flow path of the heat exchanger. A smaller dispersion σ indicates a more uniform superheat at each outlet, requiring less mixing and less agitation. When the dispersion is zero, the superheat at each outlet is equal, resulting in the most uniform liquid separation. A larger dispersion σ indicates a more dispersed and less concentrated superheat at each flow path. This leads to greater nonuniform liquid separation, a higher degree of mixing, and a greater agitation. Consequently, a smaller dispersion σ requires a slower agitator rotational speed, while a larger dispersion σ requires a faster agitator rotational speed.

[0065] The rotation of the stirring element requires a driver. Regardless of whether the driver is the motor 132 or the coil, its operation consumes energy. If the stirring element maintains a constant rotational speed, in order to achieve uniform mixing of refrigerants in all conditions, the stirring element must always maintain a maximum rotational speed, resulting in energy waste. However, in this embodiment, the rotational speed of the stirring element is adjusted in real time based on the actual operating conditions of the refrigerant in the heat exchanger, so that the rotational speed of the stirring element matches the dispersion σ of the refrigerant. This ensures uniform mixing of the refrigerant while reducing energy consumption, thereby achieving energy conservation.

[0066] Since the agitator rotates passively and requires a driving member to drive its rotation, the method for controlling the rotation of the agitator includes controlling the rotation of the driving member according to the discreteness σ to control the rotation speed of the agitator. This reduces the energy consumption of the driving member by adjusting the rotation speed in real time.

[0067] The stirring assembly 130 in this embodiment is preferably a mechanical stirring assembly, wherein the stirring member is an impeller 131 and the driving member is a motor 132. The motor 132 and the impeller 131 are connected to each other via a transmission rod 133. Under the drive of the transmission rod 133, the impeller 131 and the motor 132 rotate synchronously, and the speed of the motor 132 is equal to the speed of the impeller 131.

[0068] In this embodiment, it is assumed that the heat exchanger includes N flow paths, and the superheat of the refrigerant at the outlet of the i-th flow path is SHi.

[0069] The calculation formula of SHi is as follows:

[0070] SHi=ti-tz,

[0071] Where ti is the refrigerant temperature at the outlet of the i-th flow path, and tz is the heat exchanger evaporation temperature, which is calculated from the evaporation pressure of the heat exchanger. The evaporation pressure of the heat exchanger is a predetermined value that has been designed before its production.

[0072] According to the superheat degree of the refrigerant at the outlet of each flow path, the average value u of the superheat degree of the refrigerant at the outlet of N flow paths can be obtained. The calculation formula is as follows:

[0073]

[0074] According to the superheat of the refrigerant at the outlet of each flow path and the average value u of the superheat of the refrigerant at the outlet of N flow paths, the dispersion σ of the superheat can be obtained. The calculation formula is as follows:

[0075]

[0076] If you want to get the dispersion σ of superheat at time T T , then SHi in the above formula is the superheat of the refrigerant at the outlet of the i-th flow path at time T, and u is the average superheat of the refrigerant at the outlet of N flow paths at time T.

[0077] The dispersion of superheat at time T σ T , we can get the rotation speed nT of the stirring member at time T, and the calculation formula is as follows:

[0078]

[0079] In the calculation formula, σ T is the dispersion of superheat at time T, σ1 is the maximum dispersion of superheat, σ0 is the minimum dispersion of superheat, n1 is the maximum speed of the stirring element, and n0 is the minimum speed of the stirring element.

[0080] Among them, the maximum dispersion σ1 and the minimum dispersion σ0 of superheat are obtained by the following method:

[0081] When debugging the heat exchanger, debug the heat exchanger under different working conditions. When the dispersion of the superheat of the refrigerant at the outlet of multiple flow paths is the largest, calculate the dispersion and record it as the maximum dispersion of the superheat σ1;

[0082] When the dispersion of the superheat degree of the refrigerant at the outlets of the multiple flow paths is the smallest, the dispersion is calculated and recorded as the minimum dispersion of the superheat degree σ0.

[0083] The maximum speed n1 and the minimum speed n0 of the impeller 131 in the formula are mainly determined by the performance of the motor 132, and the maximum speed and the minimum speed of the motor 132 are determined by its own structure and are predetermined values.

[0084] From the rotation speed n of the stirring element at time T T It can be seen from the calculation formula that the rotation speed of the motor 132 and the impeller 131 is controlled by the dispersion of the superheat at the outlet of the heat exchanger. Specifically, the rotation speed of the motor 132 and the impeller 131 is positively correlated with the dispersion of the superheat at the outlet of the heat exchanger. When the dispersion is greater than zero, it means that the refrigerants in each flow path are different and the refrigerant distribution is uneven. The motor 132 is started to rotate so that the impeller 131 stirs the refrigerant to mix; the greater the dispersion of the superheat, the greater the required rotation speed of the stirring element; as the mixing proceeds, the dispersion of the superheat decreases and the required rotation speed of the stirring element also decreases; when the dispersion is zero, it means that the refrigerant has been evenly distributed in each flow path and the motor 132 is turned off.

[0085] The above formulas can be used to determine the required rotational speed of impeller 131 at each moment, i.e., the required rotational speed of motor 132 at each moment, based on the refrigerant temperature values ​​collected at each flow path outlet. This allows for real-time adjustment of the rotational speed of motor 132, thereby reducing the energy consumption of motor 132 while ensuring sufficient mixing, atomization, and uniform liquid separation of the refrigerant. This ensures uniform liquid separation under different operating conditions and refrigerant flow rates in the refrigeration system, while minimizing the energy consumption of motor 132 during its operating cycle.

[0086] The technical features of the above-mentioned embodiments can be combined arbitrarily. In order to make the description concise, not all possible combinations of the technical features in the above-mentioned embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0087] The above-described embodiments merely represent several implementation methods of the present application. While the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that a person of ordinary skill in the art may make various modifications and improvements without departing from the spirit of the present application, all of which fall within the scope of protection of the present application. Therefore, the scope of patent protection for the present application shall be determined by the appended claims.

Claims

1. A method for mixing refrigerants in a heat exchange device, the heat exchange device comprising a heat exchanger and a distributor, the heat exchanger being provided with a plurality of flow paths, the distributor being provided with an inner cavity, the inner cavity being provided with a rotatable stirring member, the plurality of flow paths being respectively connected to the inner cavity; characterized in that: The refrigerant mixing method comprises the following steps: Collect the temperature of the refrigerant at the outlet of each flow path; According to the temperature of the refrigerant at the outlet of each flow path, the superheat degree of the refrigerant at the outlet of each flow path is obtained; Obtain the superheat dispersion σ according to the superheat of the refrigerant at the outlet of each flow path; controlling the rotation speed of the stirring member based on the dispersion σ of the superheat; The rotation speed n of the stirring member at time T is T The calculation formula is as follows: Among them, σ T is the dispersion of superheat at time T, σ1 is the maximum dispersion of superheat, σ0 is the minimum dispersion of superheat, n1 is the maximum speed of the stirring element, and n0 is the minimum speed of the stirring element.

2. The refrigerant mixing method in a heat exchange device according to claim 1, characterized in that: The maximum dispersion σ1 and the minimum dispersion σ0 of superheat are obtained by the following method: When debugging the heat exchanger, debug the heat exchanger under different working conditions. When the dispersion of the superheat of the refrigerant at the outlet of multiple flow paths is the largest, calculate the dispersion and record it as the maximum dispersion of the superheat σ1; When the dispersion of the superheat degree of the refrigerant at the outlets of the multiple flow paths is the smallest, the dispersion is calculated and recorded as the minimum dispersion of the superheat degree σ0.

3. The refrigerant mixing method in a heat exchange device according to claim 1, characterized in that: Assume that the heat exchanger includes N flow paths, and the superheat of the refrigerant at the outlet of the i-th flow path is SHi, The calculation formula of superheat dispersion σ is as follows: Here, u is the average value of the superheat of the refrigerant in N flow paths.

4. The refrigerant mixing method in a heat exchange device according to claim 3, characterized in that: The calculation formula for the average value u of the refrigerant superheat at the outlet of N flow paths is as follows:

5. The refrigerant mixing method in a heat exchange device according to claim 1, characterized in that: Assuming that the heat exchanger includes N flow paths, the superheat of the refrigerant in the i-th flow path is SHi, then the calculation formula of SHi is as follows: SHi=ti-tz, Wherein, ti is the temperature of the refrigerant at the outlet of the i-th flow path, and tz is the evaporation temperature of the heat exchanger.

6. The refrigerant mixing method in a heat exchange device according to claim 5, characterized in that: The evaporation temperature tz of the heat exchanger is calculated from the evaporation pressure of the heat exchanger.

7. The refrigerant mixing method in a heat exchange device according to claim 1, characterized in that: The heat exchange device further includes a driving member capable of driving the stirring member to rotate; wherein the method for controlling the rotation of the stirring member includes: The driving member is controlled to rotate according to the dispersion σ to control the rotation speed of the stirring member.

8. The refrigerant mixing method in a heat exchange device according to claim 7, characterized in that: The stirring member includes an impeller, the driving member includes a motor, and the impeller is rotationally connected to the motor.

9. The refrigerant mixing method in a heat exchange device according to claim 8, characterized in that: A transmission rod is connected to the motor, and one end of the transmission rod away from the driving member extends into the inner cavity and is connected to the impeller.

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