A dual-cold source refrigerant liquid separation device

Abstract

The embodiment of the present application provides a dual-cold source refrigerant liquid separation device, which relates to the technical field of air-conditioning equipment. The dual-cold source refrigerant liquid separation device includes a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative cooling heat exchanger, and a heat exchanger; the compressor is used to compress the refrigerant gas; the regulating valve includes a first interface, a second interface, and a third interface, the first interface of the regulating valve is connected to the compressor, and the regulating valve is used to adjust the refrigerant flow according to the ambient temperature and operating power consumption; the air-cooled heat exchanger is connected to the second interface of the regulating valve; the evaporative cooling heat exchanger is connected to the third interface of the regulating valve; the heat exchanger is respectively connected to the compressor, the air-cooled heat exchanger, and the evaporative cooling heat exchanger to form a refrigerant circulation loop. The dual-cold source refrigerant liquid separation device can reduce the overall power consumption of the unit, improve the performance coefficient and reliability, and achieve the technical effect of energy saving and efficiency improvement.

Description

Technical Field

[0001] The present application relates to the technical field of air-conditioning equipment, and in particular to a dual-cold-source refrigerant liquid separation device. Background Art

[0002] Currently, evaporative cooling is significantly more efficient than air cooling, and evaporative chillers boast a higher COP (coefficient of performance, measured in W / W) than air-cooled chillers. However, when it comes to heating, evaporative heat pump water heaters are limited by the freezing of low-temperature water, restricting their use in certain environments. Air-cooled heat pump water heaters, on the other hand, can operate in sub-zero temperatures in winter, meeting heating needs.

[0003] Dual-cooling heat pump units are currently available on the market. These units consist of an air-cooled fin heat exchanger and an evaporative heat exchanger. Connecting the two heat exchangers in series can limit the heat transfer capacity of one heat exchanger. Connecting them in parallel can also lead to liquid separation issues. Without a specific liquid separation approach, the two heat exchangers may not achieve optimal performance, resulting in high energy consumption and a failure to achieve energy savings. Summary of the Invention

[0004] The purpose of the embodiments of the present application is to provide a dual-cold source refrigerant liquid separation device, which can reduce the overall power consumption of the unit, improve the performance coefficient and reliability, and achieve the technical effect of energy saving and efficiency improvement.

[0005] The embodiment of the present application provides a dual-cold source refrigerant liquid separation device, including a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative cooling heat exchanger, and a heat exchanger;

[0006] The compressor is used to compress refrigerant gas;

[0007] The regulating valve comprises a first interface, a second interface and a third interface, the first interface of the regulating valve is connected to the compressor, and the regulating valve is used to adjust the refrigerant flow path according to the ambient temperature and operating power consumption;

[0008] The air-cooled heat exchanger is connected to the second interface of the regulating valve;

[0009] The evaporative cooling heat exchanger is connected to the third interface of the regulating valve;

[0010] The heat exchanger is connected to the compressor, the air-cooled heat exchanger and the evaporative cooling heat exchanger respectively to form a refrigerant circulation loop.

[0011] In the above implementation process, the dual-cold source refrigerant liquid separation device can be transformed into cooling mode or heating mode by converting the flow direction of the refrigerant between the compressor, air-cooled heat exchanger, evaporative heat exchanger and heat exchanger, and the heat exchanger provides cooling or heat; a regulating valve is set between the compressor, air-cooled heat exchanger and evaporative heat exchanger to adjust the refrigerant path according to the ambient temperature and operating power consumption, so that the refrigerant flow entering the air-cooled heat exchanger and evaporative heat exchanger is adjusted through the regulating valve, so that the air-cooled heat exchanger and evaporative heat exchanger can always be in the best heat exchange performance, which can reduce the overall power consumption of the unit, improve the performance coefficient and reliability, and achieve the technical effect of energy saving and efficiency improvement.

[0012] Furthermore, the device also includes a reversing valve, which is provided with four interfaces, respectively connected to the inlet of the compressor, the outlet of the compressor, the first interface of the regulating valve and the heat exchanger, and the reversing valve is used to adjust the flow direction of the refrigerant.

[0013] In the above implementation process, the reversing valve is provided with four interfaces, which can switch the passages between each other to achieve the reversal of the refrigerant flow direction, thereby realizing the switching of the dual-cold-source refrigerant liquid separation device between the cooling mode and the heating mode. For example, in the cooling mode, the refrigerant flow cycle of the dual-cold-source refrigerant liquid separation device is: compressor → regulating valve → air-cooled heat exchanger and evaporative heat exchanger → heat exchanger → compressor; in the heating mode, the refrigerant flow cycle of the dual-cold-source refrigerant liquid separation device is: compressor → heat exchanger → air-cooled heat exchanger and evaporative heat exchanger → regulating valve → compressor.

[0014] Furthermore, the device also includes a gas-liquid separator, which is connected to the reversing valve and the inlet of the compressor respectively.

[0015] In the above implementation process, the gas-liquid separator can be installed at the inlet of the gas compressor to separate the gas and liquid, treat the refrigerant containing a small amount of condensate, and realize the recovery of the refrigerant.

[0016] Furthermore, the device further includes a liquid reservoir, the air-cooled heat exchanger and the evaporative cooling heat exchanger are provided with a confluence port, and the liquid reservoir is connected to the confluence port and the heat exchanger respectively.

[0017] In the above implementation process, the liquid accumulator can temporarily store the refrigerant and play the role of transferring the refrigerant.

[0018] Furthermore, the device also includes a throttling mechanism, which is respectively connected to the liquid reservoir, the confluence port, and the heat exchanger.

[0019] In the above implementation process, the refrigerant flows from the liquid accumulator to the throttling mechanism, and the refrigerant passes through the throttling mechanism, undergoes throttling and pressure reduction, and becomes a gas-liquid two-phase refrigerant.

[0020] Furthermore, the device includes at least one one-way valve, which is arranged on a connecting pipe of the liquid reservoir.

[0021] In the above implementation process, the one-way valve is arranged on the connecting pipe of the liquid accumulator. The one-way valve has the characteristic of one-way passage of liquid, so that the flow direction of the refrigerant in the dual-cold source refrigerant liquid separation device can always be maintained as liquid accumulator → throttling mechanism regardless of whether it is in heating mode or cooling mode.

[0022] Furthermore, the device includes a first one-way valve and a second one-way valve, the first one-way valve is arranged on the connecting pipe between the confluence and the liquid reservoir, and the second one-way valve is arranged on the connecting pipe between the throttling mechanism and the heat exchanger, so that the refrigerant flows through the confluence, the liquid reservoir, the throttling mechanism and the heat exchanger in sequence.

[0023] In the above implementation process, the first one-way valve and the second one-way valve can enable the dual-cold-source refrigerant liquid separation device to flow the refrigerant in the following direction in the cooling mode: confluence port → liquid reservoir → throttling mechanism → heat exchanger.

[0024] Furthermore, the device includes a third one-way valve and a fourth one-way valve, the third one-way valve is arranged on the connecting pipe between the heat exchanger and the liquid reservoir, and the fourth one-way valve is arranged on the connecting pipe between the throttling mechanism and the confluence, so that the refrigerant flows through the heat exchanger, the liquid reservoir, the throttling mechanism and the confluence in sequence.

[0025] In the above implementation process, the third one-way valve and the fourth one-way valve can make the refrigerant flow direction of the dual-cold source refrigerant liquid separation device in the heating mode: heat exchanger → liquid reservoir → throttling mechanism → confluence port.

[0026] Furthermore, the air-cooled heat exchanger includes a fan and a fin heat exchange mechanism, the fin heat exchange mechanism is respectively connected to the second interface of the regulating valve and the heat exchanger, and the fan is arranged above the fin heat exchange mechanism.

[0027] Furthermore, the evaporative heat exchanger includes a spray mechanism, a plate and tube heat exchange mechanism, a water pump, a water tank and an exhaust fan. The spray mechanism, the plate and tube heat exchange mechanism and the water tank are stacked in sequence from top to bottom. The water pump is respectively connected to the spray mechanism and the water tank, and the exhaust fan is arranged above the spray mechanism.

[0028] Other features and advantages of the present disclosure will be set forth in the following description, or some features and advantages may be inferred or unambiguously determined from the description, or may be learned by practicing the above-mentioned technology of the present disclosure.

[0029] In order to make the above-mentioned objects, features and advantages of the present application more obvious and easy to understand, preferred embodiments are given below and described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following is a brief introduction to the drawings required for use in the embodiments of the present application. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without creative work.

[0031] Figure 1 A schematic structural diagram of a dual-cold-source refrigerant liquid separation device provided in an embodiment of the present application;

[0032] Figure 2 A schematic structural diagram of another dual-cold-source refrigerant liquid separation device provided in an embodiment of the present application;

[0033] Figure 3 A schematic structural diagram of an air-cooled heat exchanger provided in an embodiment of the present application;

[0034] Figure 4 A schematic structural diagram of an evaporative cooling heat exchanger provided in an embodiment of the present application. DETAILED DESCRIPTION

[0035] The technical solutions in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all of the embodiments. The components of the embodiments of the present application generally described and shown in the drawings here can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present application provided in the drawings is not intended to limit the scope of the application for protection, but merely represents the selected embodiments of the present application. Based on the embodiments of the present application, all other embodiments obtained by those skilled in the art without making creative work are within the scope of protection of this application.

[0036] In this application, terms such as "upper," "lower," "left," "right," "front," "back," "top," "bottom," "inner," "outer," "center," "vertical," "horizontal," "transverse," and "longitudinal" indicate positions or locations based on the positions or locations shown in the accompanying drawings. These terms are primarily intended to better describe this application and its embodiments and are not intended to limit the devices, elements, or components indicated to having a specific orientation, or to being constructed or operated in a specific orientation.

[0037] Furthermore, some of the above terms may be used to express other meanings besides indicating a position or location. For example, the term "on" may also be used to indicate a dependency or connection in certain circumstances. Those skilled in the art will understand the specific meanings of these terms in this application based on the specific circumstances.

[0038] Furthermore, the terms "installed," "disposed," "provided with," "connected," and "connected" should be interpreted broadly. For example, they can refer to fixed connections, removable connections, or integral structures; mechanical connections or point connections; direct connections, indirect connections through an intermediary, or internal communication between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in this application based on the specific circumstances.

[0039] Furthermore, the terms "first," "second," and the like are primarily used to distinguish different devices, elements, or components (which may or may not be the same in type and configuration) and are not intended to indicate or imply the relative importance or quantity of the devices, elements, or components indicated. Unless otherwise specified, "plurality" means two or more.

[0040] The embodiment of the present application provides a dual-cold source refrigerant liquid separation device, which can be used in the field of air conditioning for cooling or heating; the dual-cold source refrigerant liquid separation device can be converted into a cooling mode or a heating mode by converting the flow direction of the refrigerant between the compressor, the air-cooled heat exchanger, the evaporative heat exchanger and the heat exchanger, and the heat exchanger provides cooling or heat; a regulating valve is set between the compressor, the air-cooled heat exchanger and the evaporative heat exchanger, and the refrigerant path is adjusted according to the ambient temperature and operating power consumption, so that the refrigerant flow entering the air-cooled heat exchanger and the evaporative heat exchanger is adjusted through the regulating valve, so that the air-cooled heat exchanger and the evaporative heat exchanger can always be in the best heat exchange performance, which can reduce the overall power consumption of the unit, improve the performance coefficient and reliability, and achieve the technical effect of energy saving and efficiency improvement.

[0041] See Figure 1 , Figure 1 Schematic diagram of the structure of a dual-cold-source refrigerant liquid separation device provided in an embodiment of the present application, the dual-cold-source refrigerant liquid separation device includes a compressor 10, a regulating valve 20, an air-cooled heat exchanger 30, an evaporative cooling heat exchanger 40, and a heat exchanger 50;

[0042] Illustratively, the compressor 10 is used to compress refrigerant gas.

[0043] For example, compressor 10 is a driven fluid machine that boosts low-pressure gas to high-pressure gas. It is the heart of the refrigeration system. It draws low-temperature, low-pressure refrigerant gas from the intake pipe, compresses it through a motor-driven piston, and discharges high-temperature, high-pressure refrigerant gas to the exhaust pipe, powering the refrigeration cycle. This completes the refrigeration cycle of compression → condensation (heat release) → expansion → evaporation (heat absorption).

[0044] Exemplarily, the regulating valve 20 includes a first port 21 , a second port 22 and a third port 23 . The first port 21 of the regulating valve is connected to the compressor 10 . The regulating valve 20 is used to adjust the refrigerant flow path according to the ambient temperature and operating power consumption.

[0045] In some embodiments, the ambient temperature includes the ambient dry-bulb temperature and the ambient wet-bulb temperature; the above-mentioned operating power consumption and the overall operating power consumption of the dual-cold-source refrigerant separation device.

[0046] Illustratively, the ambient dry bulb temperature is the value read from a dry bulb thermometer that is exposed to air but not directly exposed to the sun.

[0047] For example, the ambient wet bulb temperature refers to the temperature of a system when, under adiabatic conditions, a large amount of water is in contact with a limited amount of moist air, and the latent heat required for evaporation of the water comes entirely from the sensible heat released by the decrease in the temperature of the moist air. The system reaches a saturated state and thermal equilibrium.

[0048] In some embodiments, the dual-cold-source refrigerant liquid separation device further includes an ambient dry-bulb temperature sensor and an ambient wet-bulb temperature sensor, which are used to detect the ambient dry-bulb temperature and the ambient wet-bulb temperature, respectively.

[0049] In some embodiments, the regulating valve 20 is an electric three-way regulating valve.

[0050] Exemplarily, the air-cooled heat exchanger 30 is connected to the second port 22 of the regulating valve 20 .

[0051] Illustratively, the air-cooled heat exchanger 30 accelerates the flow of air to exchange heat with the refrigerant.

[0052] For example, the evaporative cooling heat exchanger 40 is connected to the third port 23 of the regulating valve 20 .

[0053] For example, the evaporative heat exchanger 40 is a spray-type heat exchanger. This type of heat exchanger features rows of heat exchange tubes fixed to a steel frame. Hot fluid flows through the tubes, while cooling water sprays from above. A highly turbulent liquid film forms on the outside of the tubes. Furthermore, this type of heat exchanger can be placed in an area with good air circulation. The evaporation of the cooling water also removes some heat, lowering the cooling water temperature and increasing the driving force for heat transfer.

[0054] Illustratively, the heat exchanger 50 is connected to the compressor 10 , the air-cooling heat exchanger 30 , and the evaporative cooling heat exchanger 40 , respectively, to form a refrigerant circulation loop.

[0055] For example, the heat exchanger 50 may be a shell and tube heat exchanger or a fin heat exchanger. It should be understood that the heat exchanger 50 is merely an example and not a limitation, and the heat exchanger 50 may also be a heat exchanger of other forms as needed.

[0056] In some implementation scenarios, the regulating valve 20 is an electric three-way regulating valve having three interfaces, namely a first interface 21, a second interface 22 and a third interface 23; in the refrigeration mode, after the refrigerant gas is compressed by the compressor 10, the refrigerant enters the first interface 21, and the regulating valve 20 controls and adjusts the diameter between the first interface 21 and the second interface 22, and the first interface 21 and the third interface 23 according to the ambient dry-bulb temperature, the ambient wet-bulb temperature and the operating power consumption, thereby changing the refrigerant flow rate flowing to the air-cooled heat exchanger 30 and the evaporative heat exchanger 40.

[0057] In some implementation scenarios, the ambient dry-bulb temperature is expressed as TD and the ambient wet-bulb temperature is expressed as TW; according to the different changes in the ambient dry-bulb temperature TD and the wet-bulb temperature TW, the refrigerant flow entering the air-cooled heat exchanger 30 and the evaporative heat exchanger 40 is adjusted through the calculation regulating valve 20, so that the air-cooled heat exchanger 30 and the evaporative heat exchanger 40 are always in the best heat exchange performance, reducing the overall power consumption of the unit, improving the performance coefficient and reliability, and achieving the technical effect of energy saving and efficiency improvement.

[0058] In some embodiments, the dual-cold source refrigerant liquid separation device also includes a reversing valve 60, which is provided with four interfaces, namely a first reversing interface 61, a second reversing interface 62, a third reversing interface 63 and a fourth reversing interface 64, which are respectively connected to the inlet of the compressor, the outlet of the compressor, the first interface of the regulating valve and the heat exchanger. The reversing valve is used to adjust the flow direction of the refrigerant.

[0059] Exemplarily, the reversing valve is provided with four interfaces, which can switch passages between each other to achieve reversal of the refrigerant flow direction, thereby enabling the dual-cold-source refrigerant liquid separation device to switch between cooling mode and heating mode. Exemplarily, in cooling mode, the refrigerant flow cycle of the dual-cold-source refrigerant liquid separation device is: compressor 10 → regulating valve 20 → air-cooled heat exchanger 30 and evaporative heat exchanger 40 → heat exchanger 50 → compressor 10; in heating mode, the refrigerant flow cycle of the dual-cold-source refrigerant liquid separation device is: compressor 10 → heat exchanger 50 → air-cooled heat exchanger 30 and evaporative heat exchanger 40 → regulating valve 20 → compressor 10.

[0060] See Figure 2 , Figure 2 A schematic structural diagram of another dual-cold source refrigerant liquid separation device provided in an embodiment of the present application, the dual-cold source refrigerant liquid separation device includes a compressor 10, a regulating valve 20, an air-cooled heat exchanger 30, an evaporative heat exchanger 40, a heat exchanger 50, a reversing valve 60, a gas-liquid separator 70, a liquid reservoir 80, a throttling mechanism 90 and at least one one-way valve 100.

[0061] Exemplarily, the gas-liquid separator 70 is connected to the reversing valve 60 and the inlet of the compressor 10 , respectively; optionally, the gas-liquid separator 70 is connected to the second reversing port 62 of the reversing valve 60 and the inlet of the compressor 10 , respectively.

[0062] For example, the gas-liquid separator 70 may be installed at the inlet of the gas compressor for gas-liquid separation, processing refrigerant containing a small amount of condensate, and realizing refrigerant recovery.

[0063] Exemplarily, the air-cooled heat exchanger 30 and the evaporative cooling heat exchanger 40 are provided with a confluence port 34 , and the liquid reservoir 80 is connected to the confluence port 34 and the heat exchanger 50 , respectively.

[0064] For example, the accumulator can temporarily store the refrigerant and serve as a transfer refrigerant.

[0065] Exemplarily, the throttling mechanism 90 is connected to the liquid reservoir 80 , the confluence port 34 , and the heat exchanger 50 , respectively.

[0066] Illustratively, the refrigerant flows from the liquid accumulator 80 to the throttling mechanism 90 , and the refrigerant passes through the throttling mechanism 90 , where it is throttled and depressurized, and becomes a gas-liquid two-phase refrigerant.

[0067] Exemplarily, the one-way valve 100 is provided on a connecting pipe of the liquid reservoir 80 .

[0068] For example, the one-way valve 100 is arranged on the connecting pipe of the liquid reservoir 80. The one-way valve 100 has the characteristic of one-way passage of liquid, so that the flow direction of the refrigerant in the dual-cold source refrigerant separation device can always be maintained as liquid reservoir 80 → throttling mechanism 90 regardless of whether it is in heating mode or cooling mode.

[0069] In some embodiments, the dual-cold source refrigerant liquid separation device includes a first one-way valve 101 and a second one-way valve 102. The first one-way valve 101 is arranged on the connecting pipe between the confluence 34 and the liquid reservoir 80, and the second one-way valve 102 is arranged on the connecting pipe between the throttling mechanism 90 and the heat exchanger 50, so that the refrigerant flows through the confluence 34, the liquid reservoir 80, the throttling mechanism 90 and the heat exchanger 50 in sequence.

[0070] For example, the first one-way valve 101 and the second one-way valve 102 can make the refrigerant flow direction of the dual-cold-source refrigerant liquid separation device in the cooling mode: confluence port 34 → liquid reservoir 80 → throttling mechanism 90 → heat exchanger 50 .

[0071] In some embodiments, the dual-cold source refrigerant liquid separation device includes a third one-way valve 103 and a fourth one-way valve 104. The third one-way valve 103 is arranged on the connecting pipe between the heat exchanger 50 and the liquid reservoir 80, and the fourth one-way valve 104 is arranged on the connecting pipe between the throttling mechanism 90 and the confluence 34, so that the refrigerant flows through the heat exchanger 50, the liquid reservoir 80, the throttling mechanism 90 and the confluence 34 in sequence.

[0072] In the above implementation process, the third one-way valve 103 and the fourth one-way valve 104 can make the refrigerant flow direction of the dual-cold source refrigerant liquid separation device in the heating mode: heat exchanger 50 → liquid reservoir 80 → throttling mechanism 90 → confluence port 34.

[0073] In some embodiments, the air-cooled heat exchanger 30 includes a fan 31 and a fin heat exchange mechanism 32 . The fin heat exchange mechanism 32 is respectively connected to the second interface 22 of the regulating valve 20 and the heat exchanger 50 . The fan 31 is arranged above the fin heat exchange mechanism 32 .

[0074] See Figure 3 , Figure 3 A schematic structural diagram of an air-cooled heat exchanger provided in an embodiment of the present application.

[0075] Exemplarily, the fin heat exchange mechanism 32 can be composed of three rows of parallel spiral fin tube bundles between the air flow directions. The fin heat exchange mechanism 32 can adopt mechanical winding, the contact surface between the heat dissipating fins and the heat dissipating tubes is large and tight, the heat transfer performance is good and stable, the air passing resistance is small, the refrigerant flows through the steel pipe, and the heat is transferred to the air passing through the fins through the fins tightly wound on the steel pipe, thereby achieving the effect of heating and cooling the air.

[0076] In some embodiments, the evaporative heat exchanger 40 includes a spray mechanism 41, a plate and tube heat exchange mechanism 42, a water pump 43, a water tank 44 and an exhaust fan 45. The spray mechanism 41, the plate and tube heat exchange mechanism 42 and the water tank 44 are stacked in sequence from top to bottom. The water pump 43 is respectively connected to the spray mechanism 41 and the water tank 44, and the exhaust fan 45 is arranged above the spray mechanism 41.

[0077] See Figure 4 , Figure 4 A schematic structural diagram of an evaporative cooling heat exchanger provided in an embodiment of the present application.

[0078] Illustratively, the evaporative heat exchanger 40 realizes water circulation through the spray mechanism 41, the plate and tube heat exchange mechanism 42 and the water tank 44, and removes the condensation heat by utilizing water evaporation and forced air circulation to cool the high-temperature and high-pressure refrigerant discharged from the compressor 10 and condense it into liquid.

[0079] In some implementation scenarios, the dual-cold-source refrigerant liquid separation device operates in a cooling mode. In this case, the workflow is as follows:

[0080] Compressor 10 compresses low-temperature, low-pressure refrigerant gas into high-temperature, high-pressure refrigerant gas. The refrigerant gas flows through first reversing port 61 of reversing valve 60 to third reversing port 63, and then to first port 21 of regulating valve 20. Regulating valve 20 calculates the flow diameters of second port 22 and third port 23 based on the ambient dry-bulb temperature TD and wet-bulb temperature TW using thermodynamic formulas. Refrigerant flows from second port 22 to air-cooled heat exchanger 30 for condensation, and from third port 23 to evaporative heat exchanger 40 for condensation. After condensation, the two high-temperature and high-pressure refrigerant liquids merge and flow through the first one-way valve 101 and the liquid accumulator 80, to the throttling mechanism 90 for throttling and pressure reduction, turning into gas-liquid two-phase refrigerant, and then to the heat exchanger 50 for evaporative cooling, turning into low-temperature and low-pressure refrigerant gas, and then pass through the fourth reversing interface 64 of the reversing valve 60 to the second reversing interface 62 and the gas-liquid separator 70, and return to the inlet of the compressor 10; the above process is repeated, which is the refrigeration cycle of the dual-cold source refrigerant liquid separation device.

[0081] During the condensation process in air-cooled heat exchanger 30, fan 31 uses the ambient dry-bulb temperature TD to force air through fin heat exchange mechanism 32, removing heat from the refrigerant. During the condensation process in evaporative heat exchanger 40, the ambient wet-bulb temperature TW is used to lower the circulating water temperature. The cooled circulating water is pumped from water tank 44 to spray mechanism 41 via water pump 43, and then evenly distributed across the surface of plate-and-tube heat exchange mechanism 42. Heat is transferred to the water film, which evaporates and is then discharged by exhaust fan 45. Heat exchanger 50, which can be a shell-and-tube heat exchanger, fin heat exchanger, or other device, can provide cooling to users.

[0082] In some implementation scenarios, the dual-cold-source refrigerant liquid separation device operates in heating mode. In this case, the workflow example is as follows:

[0083] Compressor 10 compresses low-temperature, low-pressure refrigerant gas into high-temperature, high-pressure refrigerant gas. The refrigerant gas passes through the first reversing port 61 of the reversing valve 60 to the fourth reversing port 64, then to the heat exchanger 50, where it condenses and becomes a high-temperature, high-pressure refrigerant liquid. It then passes through the third one-way valve 103 and the accumulator 80, before being throttled and reduced in pressure by the throttling mechanism 90, becoming a gas-liquid two-phase refrigerant. This refrigerant is then split into two streams. One stream is evaporated by the air-cooled heat exchanger 30 and flows to the second port 22 of the regulating valve 20, while the other stream is condensed by the evaporative cooling heat exchanger 40 and flows to the third port 23 of the regulating valve 20. The two streams then converge at the first port 21 of the regulating valve, pass through the third reversing port 63 of the reversing valve 60, to the second reversing port 62, and finally to the gas-liquid separator 70, returning to the inlet of the compressor 10. This reciprocating process constitutes the heating cycle of the dual-cold-source refrigerant liquid separation device.

[0084] During the condensation process in air-cooled heat exchanger 30, fan 31 uses the ambient dry-bulb temperature TD to force air through fin heat exchange mechanism 32, removing the refrigerant's cold energy. During the condensation process in evaporative heat exchanger 40, the ambient wet-bulb temperature TW is used to lower the circulating water temperature. The cooled circulating water is pumped from water tank 44 to spray mechanism 41 by water pump 43, and then evenly distributed across the surface of plate-and-tube heat exchange mechanism 42. The cold energy is transferred to the water film, which evaporates and is then discharged by exhaust fan 45. Heat exchanger 50, which can be a shell-and-tube heat exchanger, fin heat exchanger, or other device, can provide heat to users.

[0085] In some embodiments, a pressure sensor is installed on the air-cooled heat exchanger 30 to detect the real-time pressure P1 of the air-cooled heat exchanger 30, and the corresponding saturation temperature T1 can be calculated using thermodynamic formulas. A pressure sensor is installed on the evaporative heat exchanger 40 to detect the real-time pressure P2 of the evaporative heat exchanger 40, and the corresponding saturation temperature T2 can be calculated using thermodynamic formulas. A pressure sensor is installed on the heat exchanger 50 to detect the real-time pressure P3 of the heat exchanger 50, and the corresponding saturation temperature T3 can be calculated using thermodynamic formulas.

[0086] For example, the corresponding power consumption, cooling capacity, and mass flow rate of the dual-cold-source refrigerant liquid separation device can be calculated using the preset coefficients (C0 to C9) of the compressor 10 and the formula. The calculation formula is as follows:

[0087] Y = C0 + C1*Te + C2*Tc + C3*Te^2 + C4*Te*Tc + C5*Tc^2 + C6*Te^3 + C7*Tc*Te^2 + C8*Te*Tc^2 + C9*Tc^3;

[0088] Among them, when the dual-cold source refrigerant liquid separation device is cooling, Y1 corresponds to Te=T3, Tc=T1, and Y2 corresponds to Te=T3, Tc=T2; when the dual-cold source refrigerant liquid separation device is heating, Y1 corresponds to Te=T1, Tc=T3, and Y2 corresponds to Te=T2, Tc=T3.

[0089] The preset coefficients C0-C9 are determined based on the specific parameter values ​​of different types of compressors 10, power consumption, cooling capacity, and mass flow rate.

[0090] In some implementation scenarios, when the dual-cold-source refrigerant separation device is cooling, the regulating valve 20 is adjusted as follows: After the dual-cold-source refrigerant separation device is turned on, the second port 22 and the third port 23 of the regulating valve 20 evenly distribute the refrigerant flow. The refrigerant flow distribution is then adjusted based on changes in the ambient dry-bulb temperature TD and the ambient wet-bulb temperature TW, with priority given to the evaporative heat exchanger 40. The overall power consumption of the dual-cold-source refrigerant separation device is calculated. If the power consumption calculated in the current cycle is greater than that in the previous cycle, the adjustment is performed in the opposite direction of the previous cycle; if the power consumption calculated in the current cycle is less than that in the previous cycle, the action of the previous cycle is continued. A fluctuation range is set as a stable interval. Optionally, the action amplitude of each cycle can be the same or different.

[0091] In some implementations, when the dual-cold-source refrigerant separation device is heating, the regulating valve 20 is adjusted as follows: After the dual-cold-source refrigerant separation device is powered on, the ambient dry-bulb temperature TD and the ambient wet-bulb temperature TW are detected. When the dry-bulb temperature TD is below 0°C, the regulating valve 20 is directly adjusted to flow from the first port 21 to the second port 22, with the remaining openings closed. When the wet-bulb temperature TW is below 8°C or a set value, and the dry-bulb temperature TD is greater than 0°C, the regulating valve 20 is adjusted to prioritize the flow from the first port 21 to the second port 22, and the opening from the first port 21 to the third port 23 is appropriately adjusted. When the wet-bulb temperature TW is greater than 8°C or a set value, the overall power consumption of the dual-cold-source refrigerant separation device is calculated. If the power consumption calculated in the current cycle is greater than that in the previous cycle, the adjustment is reversed from the previous cycle; if the power consumption calculated in the current cycle is less than that in the previous cycle, the previous cycle's adjustment is continued. A fluctuation range is set as a stable interval. Optionally, the amplitude of the adjustment can be the same or different in each cycle.

[0092] In all embodiments of the present application, "big" and "small" are relative, "more" and "less" are relative, and "up" and "down" are relative. The expressions of such relative terms will not be elaborated in the embodiments of the present application.

[0093] It should be understood that the phrases “in this embodiment,” “in an embodiment of the present application,” or “as an optional implementation” mentioned throughout the specification mean that specific features, structures, or characteristics related to the embodiment are included in at least one embodiment of the present application. Therefore, “in this embodiment,” “in an embodiment of the present application,” or “as an optional implementation” appearing throughout the specification do not necessarily refer to the same embodiment. In addition, these specific features, structures, or characteristics may be combined in one or more embodiments in any suitable manner. Those skilled in the art should also be aware that the embodiments described in the specification are all optional embodiments, and the actions and modules involved are not necessarily required for the present application.

[0094] In the various embodiments of the present application, it should be understood that the size of the serial numbers of the above-mentioned processes does not necessarily mean the order of execution. The order of execution of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present application.

[0095] The above description is merely a specific embodiment of the present application, but the scope of protection of the present application is not limited thereto. Any modifications or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present application should be included within the scope of protection of the present application. Therefore, the scope of protection of the present application should be based on the scope of protection of the claims.

Claims

1. A control method for a dual-cold-source refrigerant liquid separation device, characterized in that: The dual-cold source refrigerant liquid separation device includes a compressor, a regulating valve, an air-cooled heat exchanger, an evaporative cooling heat exchanger, and a heat exchanger; The compressor is used to compress refrigerant gas; The regulating valve includes a first interface, a second interface, and a third interface. The first interface of the regulating valve is connected to the compressor. When the dual-cold-source refrigerant liquid separation device is cooling or heating, the regulating valve is used to adjust the flow distribution of the refrigerant according to the ambient dry-bulb temperature, the ambient wet-bulb temperature, and the overall power consumption. The air-cooled heat exchanger is connected to the second interface of the regulating valve; The evaporative cooling heat exchanger is connected to the third interface of the regulating valve; The heat exchanger is respectively connected to the compressor, the air-cooled heat exchanger and the evaporative cooling heat exchanger to form a refrigerant circulation loop; The control method of the dual-cold-source refrigerant liquid separation device includes: When the dual-cold-source refrigerant liquid separation device is cooling, the regulating valve is adjusted as follows: after the dual-cold-source refrigerant liquid separation device is turned on, the second interface and the third interface of the regulating valve evenly distribute the refrigerant flow, and the refrigerant flow distribution is adjusted according to the ambient dry-bulb temperature and the ambient wet-bulb temperature; the overall power consumption of the dual-cold-source refrigerant liquid separation device is calculated, and if the power consumption detected and calculated in the current cycle is greater than that in the previous cycle, the regulation is reversed to that in the previous cycle; if the power consumption detected and calculated in the current cycle is less than that in the previous cycle, the operation of the previous cycle is continued; When the dual-cold-source refrigerant liquid separation device is heating, the regulating valve is adjusted as follows: after the dual-cold-source refrigerant liquid separation device is turned on, the ambient dry-bulb temperature and the ambient wet-bulb temperature are detected. When the ambient dry-bulb temperature is lower than 0°C, the passage of the regulating valve is adjusted from the first interface to the second interface, and the rest is closed; when the ambient wet-bulb temperature is lower than the set value and the ambient dry-bulb temperature is greater than 0°C, the regulating valve is adjusted to give priority to the passage from the first interface to the second interface, and the opening from the first interface to the third interface is appropriately adjusted; when the ambient wet-bulb temperature is greater than the set value, the overall power consumption of the dual-cold-source refrigerant liquid separation device is calculated. If the power consumption detected and calculated in the current cycle is greater than that in the previous cycle, the adjustment is opposite to that of the previous cycle; if the power consumption detected and calculated in the current cycle is less than that in the previous cycle, the action of the previous cycle is continued.

2. The control method of the dual-cold-source refrigerant liquid separation device according to claim 1, characterized in that: The device also includes a reversing valve, which is provided with four interfaces respectively connected to the inlet of the compressor, the outlet of the compressor, the first interface of the regulating valve and the heat exchanger. The reversing valve is used to adjust the flow direction of the refrigerant.

3. The control method of the dual-cold-source refrigerant liquid separation device according to claim 2, characterized in that: The device further comprises a gas-liquid separator, which is connected to the reversing valve and the inlet of the compressor respectively.

4. The control method of the dual-cold-source refrigerant liquid separation device according to claim 1, characterized in that: The device further includes a liquid reservoir, the air-cooled heat exchanger and the evaporative cooling heat exchanger are provided with a confluence port, and the liquid reservoir is connected to the confluence port and the heat exchanger respectively.

5. The control method of the dual-cold-source refrigerant liquid separation device according to claim 4, characterized in that: The device further comprises a throttling mechanism, which is respectively connected to the liquid reservoir, the confluence port and the heat exchanger.

6. The control method of the dual-cold-source refrigerant liquid separation device according to claim 5, characterized in that: The device comprises at least one one-way valve, which is arranged on a connecting pipe of the liquid reservoir.

7. The control method of the dual-cold-source refrigerant liquid separation device according to claim 6, characterized in that: The device includes a first one-way valve and a second one-way valve, the first one-way valve is arranged on the connecting pipe between the confluence port and the liquid accumulator, and the second one-way valve is arranged on the connecting pipe between the throttling mechanism and the heat exchanger, so that the refrigerant flows through the confluence port, the liquid accumulator, the throttling mechanism and the heat exchanger in sequence.

8. The control method of the dual-cold-source refrigerant liquid separation device according to claim 6, characterized in that: The device includes a third one-way valve and a fourth one-way valve. The third one-way valve is arranged on the connecting pipe between the heat exchanger and the liquid accumulator, and the fourth one-way valve is arranged on the connecting pipe between the throttling mechanism and the confluence, so that the refrigerant flows through the heat exchanger, the liquid accumulator, the throttling mechanism and the confluence in sequence.

9. The control method of the dual-cold-source refrigerant liquid separation device according to claim 1, characterized in that: The air-cooled heat exchanger includes a fan and a fin heat exchange mechanism, the fin heat exchange mechanism is connected to the second interface of the regulating valve and the heat exchanger respectively, and the fan is arranged above the fin heat exchange mechanism.

10. The control method of the dual-cold-source refrigerant liquid separation device according to claim 1, characterized in that: The evaporative heat exchanger includes a spray mechanism, a plate-tube heat exchange mechanism, a water pump, a water tank and an exhaust fan. The spray mechanism, the plate-tube heat exchange mechanism and the water tank are stacked in sequence from top to bottom. The water pump is respectively connected to the spray mechanism and the water tank, and the exhaust fan is arranged above the spray mechanism.

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