A method and system for improving a vapor compression refrigeration cycle

Abstract

This invention relates to a method and system for improving the performance of a vapor compression refrigeration cycle. It utilizes two cycles: Cycle A gains heat from a heat source, releases heat to a heat sink, and stores heat using a heat carrier; Cycle B does not gain heat from a heat source but gains heat through the cooling of the heat carrier and releases heat to the heat sink. By introducing a dual-cycle architecture and utilizing a heat carrier, this invention not only solves the problems of efficiency reduction and heating interruption caused by frosting but also achieves efficient cascaded energy utilization and continuous, stable system operation. This technology can be widely applied in air conditioning, heat pumps, refrigeration, and other fields, and is particularly suitable for high-energy-consuming scenarios such as high-temperature heat pumps and cryogenic systems with large temperature differences between the heat source and heat sink, demonstrating significant energy-saving potential and broad application prospects.

Description

Technical Field

[0001] This invention relates to a method and system for improving a vapor compression refrigeration cycle, and more particularly to a method and system for improving a vapor compression refrigeration cycle by adding a cycle that does not extract heat from an external heat source, but instead utilizes the area of ​​the condenser and evaporator as a heat source. Background Technology

[0002] A conventional vapor compression refrigeration cycle has three regions: a low-temperature region, a high-temperature region, and a sub-high-temperature region, such as... Figure 1 As shown, the low-temperature and high-temperature regions are essential for the normal operation of the cycle to ensure that the heat pump extracts heat from the heat source and releases heat through the heat sink. That is, the evaporation temperature must be low, such as... Figure 1 The 12℃ shown indicates a higher condensation temperature, such as... Figure 1 The temperature of 85°C shown in the figure is not necessary for the cycle, but its existence not only fails to make effective use of the temperature, but also leads to energy loss and reduced efficiency. Summary of the Invention

[0003] This invention provides a method for improving the performance of a vapor compression refrigeration cycle. The method utilizes two cycles: Cycle A gains heat from a heat source, releases heat to a heat sink, and stores heat using a heat carrier; Cycle B does not gain heat from a heat source but gains heat by cooling a heat carrier and releases heat to a heat sink. The heat carrier is the refrigerant between the condenser and the expansion valve in Cycle A, as well as components in contact with the refrigerant, including containers, pipes, and their accessories.

[0004] It should be noted that in the field of thermodynamics and refrigeration engineering, a "cycle" refers to a complete workflow in which a working fluid (such as a refrigerant) undergoes a series of continuous thermodynamic processes (including compression, condensation, throttling, evaporation, etc.) and finally returns to its initial state, achieving energy conversion or heat transfer in the process. In this invention, both cycle A and cycle B represent such closed thermodynamic paths. In this invention, for clarity and distinction, the loop formed by the components performing the compression, condensation, throttling, and evaporation processes of cycle A is described as cycle A loop, including a compressor, condenser, throttling valve, evaporator, pipes, etc.; furthermore, as is common knowledge in the art, a gas-liquid separator is conventionally installed before the compressor, and a throttling valve is conventionally installed before the evaporator; while the loop formed by the components performing cycle B is described as cycle B loop, which is connected to the aforementioned heat carrier.

[0005] The vapor compression refrigeration cycle of the present invention, such as Figure 2As shown in Figure 3, a dual-cycle system is employed. Cycle A extracts heat from an external heat source, while Cycle B uses heat from a slightly higher temperature source. This increases the heat extraction capacity of Cycle A from the external heat source and allows it to operate at a temperature higher than the evaporation temperature of Cycle A, exceeding it by 12°C (shown in the figure as 12°C-40°C). Consequently, its heating and cooling capacity and energy efficiency are significantly higher than those of conventional heat pumps. Figure 2 The dual-cycle system is an alternating cycle, using one set of equipment to alternately switch between two cycles. Figure 3 The system employs two parallel cycles and two sets of equipment, operating simultaneously.

[0006] The core of this invention lies in employing two cooperating thermodynamic cycles—Cycle A and Cycle B. Cycle A is the main cooling or heating cycle, absorbing heat from an external heat source (such as outdoor air), compressing it, and releasing the heat to a heat sink (such as indoor space) to achieve normal cooling or heating functions. The section of Cycle A between the condenser and the expansion valve acts as a heat carrier, storing the heat of the high-temperature, high-pressure liquid refrigerant, which serves as the heat source for Cycle B. Cycle B is an auxiliary cycle; it does not directly absorb heat from the external environment but uses the heat stored in the heat carrier of Cycle A as its heat source, continuing to release heat to the heat sink. In other words, Cycle B operates using the heat extracted from the outside and stored internally by the system, thus eliminating the need for additional energy consumption from the outside. The key advantage of this design is that Cycle B significantly increases the evaporation temperature of the cooling cycle while resolving the issue of heat cancellation in Cycle A, thereby greatly improving the efficiency of cooling or heating. Furthermore, even under harsh external heat source conditions (such as low temperature and high humidity leading to frost), the system can still continuously supply heat, significantly improving overall energy efficiency and heating continuity.

[0007] The so-called "heat carrier" refers to the high-temperature, high-pressure liquid refrigerant and its contact containers and pipes in the section between condensation and throttling in cycle A. This portion of the refrigerant has a high temperature, and its heat can be stored in the heat carrier. By controlling valve switching, this heat can be used as a heat source for cycle B, achieving cascaded energy utilization and improving system thermal efficiency.

[0008] In air source heat pump applications, when the ambient temperature is below 5°C and humidity is high, frost easily forms on the evaporator surface, leading to decreased heat transfer efficiency and a continuous drop in evaporation temperature, ultimately affecting heating capacity and energy efficiency. Traditional heat pumps must periodically stop heating and reverse operation for defrosting. This process not only interrupts heating but also absorbs heat from the indoor environment and discharges it outdoors, resulting in energy waste. This invention, however, actively switches to cycle B before the frost layer severely affects heat transfer, preventing the continuous deterioration of the evaporation temperature and maintaining the stable evaporation temperature of cycle A (e.g., constant at -10°C), thereby maintaining high-efficiency heat absorption capacity.

[0009] During the operation of Cycle B, the evaporator, which is normally used for heat absorption, does not absorb heat from the outside air. Instead, it can be heated by introducing high-temperature refrigerant to achieve defrosting on the evaporator surface. This process is not accomplished by consuming electrical energy or reversing the system, but by utilizing the system's existing high-temperature waste heat. Simultaneously, the heat carrier itself continues to supply heat to the room during the defrosting process, rather than cooling it. This achieves a continuous operation mode of "defrosting while providing heat," completely solving the problems of heating interruption and sudden drop in energy efficiency during defrosting in traditional heat pumps. Only a small portion of the heat energy is consumed when frost falls off; most of the heat can still be used as a heat source for Cycle B.

[0010] Air-source heat pumps that use a vapor compression refrigeration cycle will experience frost formation at low ambient temperatures, such as below 5°C. This frost problem severely impacts heat pump performance, including heating capacity and energy efficiency. Figure 4 As shown, conventional heat pumps must stop heating and defrost when they reach a certain level of frost. The defrosting process corresponds to cycle B of a dual-cycle heat pump. However, the defrosting process not only does not generate heat, but also cools down, resulting in heat loss. The heating process of a conventional heat pump at low ambient temperatures... Figure 4 In cycle A, due to frost formation during the heating process, the evaporation temperature will continuously decrease as the frost layer thickens from no frost. Figure 4 The temperature displayed on the screen dropped from -10℃ to -20℃, until it finally deteriorated to the point where it could no longer heat and began to defrost. Figure 4 In the defrosting process of cycle B, the heat pump switches via a four-way valve, swapping the evaporator and condenser. During this time, the heat pump not only fails to provide heat to the heat sink, but also extracts heat from it. However, in the steam-cooling compression cycle heat pump of this invention, the heating process seamlessly switches and smoothly transitions between cycles A and B throughout the entire operation, avoiding the pressure shocks and temperature fluctuations caused by the four-way valve switching in traditional heat pumps. Since defrosting is no longer a "reverse cooling process" but a combined action of "using waste heat for heating + defrosting," the overall heating capacity and coefficient of performance (COP) of the system are significantly improved. Figure 5 The intermediate circulation A has a constant evaporation temperature (-10℃), meaning the evaporation temperature does not decrease. This is significantly lower than the average evaporation temperature of conventional heat pump heating compared to this invention. Figure 5 The evaporation temperature of the intermediate cycle A is such that the defrosting process of this invention does not stop heating, and it can also heat at higher evaporation temperatures (-10°C to 15°C). Figure 5 Middle loop B.

[0011] When water is used as a heat source, such as in an ice maker, the alternating operation of circulation A and circulation B can also achieve simple and efficient de-icing, and its mechanism is similar to the defrosting process of the air source heat pump mentioned above.

[0012] To further optimize heat carrier management, the system can be configured with multiple heat carriers (sets) for alternating storage of high-temperature liquid refrigerant. These heat carriers alternately connect to cycle A for heating and energy storage, or to cycle B for releasing heat, forming a periodic, alternating operating mode. This design makes heat storage and release more controllable, enhancing the system's flexibility and responsiveness.

[0013] Furthermore, the system can incorporate a secondary compressor and combine it with evaporative cooling to further improve heat pump performance. As is common knowledge in the field, "evaporative cooling" refers to the process by which a liquid absorbs heat from its surroundings or its own system during a phase change (from liquid to gas). This invention provides two implementation methods:

[0014] Flash evaporator or economizer cooling: During cycle A, a portion of the high-temperature liquid refrigerant is throttled into the flash evaporator or economizer. Due to the pressure reduction, some of the liquid evaporates, absorbing heat from the remaining liquid and causing its temperature to drop. The cooled liquid can serve as a heat source for subsequent cycles as a "heat carrier," while the generated vapor enters the secondary compressor located after the main compressor, and after compression, it enters the condenser to release heat.

[0015] Alternatively, the superheated gaseous refrigerant produced by the compressor can be cooled by the evaporation of liquid refrigerant. During cycle A, the compressor exhaust (superheated gas) exchanges heat with the liquid refrigerant, and the liquid evaporates and cools, reducing its superheat. The gas then enters a secondary compressor located after the main compressor, where it is compressed and then enters the condenser to release heat. This optimizes the compression process, reduces compression work, and improves the system's COP (Coefficient of Performance).

[0016] The compressor and the secondary compressor can also be integrated into a single two-stage compressor with intermediate gas injection function.

[0017] The system architecture includes:

[0018] The condenser, expansion valve, evaporator, gas-liquid separator, compressor, pipes, and refrigerant in the pipes are used to form loop A; the condenser, expansion valve, evaporator, gas-liquid separator, and compressor are connected in sequence through pipes to form a loop; the refrigerant between the condenser and the expansion valve and the components in contact with the refrigerant are configured as heat carriers;

[0019] A component connected to a heat carrier to form a loop B; using the heat from the heat carrier as a heat source, the heat is output to the heat sink through a refrigeration cycle. Those skilled in the art can design various structural forms based on this.

[0020] In addition, the valves control circulation A and circulation B to operate in accordance with the aforementioned method.

[0021] Furthermore, the present invention supports two implementations: one is as follows Figure 2 The alternating cycle mode shown uses a single main set of equipment (the core of which is two cycles using a condenser to release heat from the heat sink), switching between cycle A and cycle B via valves; another mode is as follows... Figure 3 The parallel circulation mode shown features two independent but collaborative circulation systems that can operate simultaneously without interference. The former has a simple structure and low cost, making it suitable for residential or small-to-medium-sized commercial systems; the latter operates stably and provides continuous heating, making it more suitable for large-scale industrial applications or scenarios with high stability requirements.

[0022] In the first configuration, the component is connected to a condenser to perform cycle B, which releases heat to the heat sink through the condenser.

[0023] The component includes a secondary pipe, one end of which is connected to the pipe between the condenser and the throttle valve, and the other end is connected to the inlet side of the gas-liquid separator. During operation of cycle B, the heat carrier between the condenser and the throttle valve enters the gas-liquid separator through the secondary pipe, and then enters the compressor. The compressed high-pressure gas enters the condenser for condensation and heat release.

[0024] The evaporator can also be connected in series on the secondary pipe. During cycle B, the heat carrier enters the evaporator through the secondary pipe to defrost the evaporator.

[0025] Furthermore, it also includes a storage tank, which is connected to the condenser and the throttle valve via a pipeline; one end of the auxiliary pipeline is connected to the storage tank, and the other end is connected to the inlet side of the gas-liquid separator.

[0026] Furthermore, it also includes a secondary compressor connected in series after the compressor; during the operation of cycle A, the liquid refrigerant, which acts as a heat carrier, evaporates and cools down to produce gaseous refrigerant, which mixes with the superheated gaseous refrigerant after being compressed by the compressor, and is then compressed again by the secondary compressor before entering the condenser to condense and release heat; the liquid refrigerant evaporates and cools down in the following ways: a portion of the liquid refrigerant cools down while the other portion evaporates; or the heat from the superheated gaseous refrigerant generated by the compressor is used to cause a portion of the liquid refrigerant to evaporate.

[0027] The situation where a portion of the liquid refrigerant is cooled, causing another portion of the liquid refrigerant to evaporate, can be achieved in a flash evaporator or an economizer. Those skilled in the art should know that a throttling valve should be installed before the flash evaporator or economizer, which is described in this invention as a secondary throttling valve.

[0028] In the second form, the components include a secondary condenser, a secondary gas-liquid separator, a secondary compressor, and a secondary pipeline; during operation of cycle B, the heat carrier between the condenser and the throttle valve enters the secondary gas-liquid separator through the secondary pipeline, and then enters the secondary compressor. The compressed high-pressure gas enters the secondary condenser for condensation and heat release.

[0029] In summary, this invention utilizes a heat carrier and introduces a dual-cycle architecture to increase the average evaporation temperature of the cycle, while reducing heat loss and improving thermodynamic efficiency, resulting in a significant increase in overall energy efficiency (COP). It also overcomes the performance limitations of traditional vapor compression cycle air source heat pumps in low-temperature and high-humidity environments. It not only solves the problems of efficiency loss and heating interruption caused by frosting, but also achieves efficient cascaded energy utilization and continuous, stable system operation. Furthermore, this invention provides a simple, reliable, efficient, and economical solution for traditional ice makers, which suffer from difficulties in de-icing and low energy efficiency.

[0030] This technology can be widely applied in air conditioning, heat pumps, refrigeration, and other fields, and is especially suitable for high-energy-consuming scenarios such as high-temperature heat pumps and cryogenic systems with large temperature differences between the heat source and heat sink, showing significant energy-saving potential and broad application prospects. The dual-cycle system of this invention not only improves efficiency but also increases heating capacity and improves heating effect, such as heating continuity.

[0031] This invention is applicable not only to large industrial systems and small and medium-sized commercial systems, but also to micro-systems, including household air conditioning systems.

[0032] Given the widespread existence and application of vapor compression refrigeration cycles, including in industrial, agricultural, commercial, transportation, energy, and construction fields, the methods and systems of this invention have broad application potential and techno-economic value. At the same time, they are of great significance and impact in addressing the climate crisis and reducing carbon emissions.

[0033] The importance and significance of this invention will be fully demonstrated in the following detailed description. Attached Figure Description

[0034] Figure 1 A schematic diagram of a conventional vapor compression refrigeration cycle to show the temperature distribution;

[0035] Figure 2 This is a schematic diagram of the principle of the alternating vapor compression refrigeration cycle of the present invention;

[0036] Figure 3 This is a schematic diagram of the vapor compression refrigeration cycle containing parallel circulation of the present invention.

[0037] Figure 4 This is a schematic diagram of a conventional air-source vapor compression refrigeration cycle that includes defrosting.

[0038] Figure 5 This is a schematic diagram of the vapor compression refrigeration cycle with alternating cycles that has a defrosting function according to the present invention.

[0039] Figure 6 This is System 1 of the present invention;

[0040] Figure 7For loop A of system one;

[0041] Figure 8 For loop B of system one;

[0042] Figure 9 This is system two of the present invention;

[0043] Figure 10 For loop A of system two;

[0044] Figure 11 For loop B of system two;

[0045] Figure 12 This is system three of the present invention;

[0046] Figure 13 For loop A of system three;

[0047] Figure 14 For loop B of system three;

[0048] Figure 15 This is system four of the present invention;

[0049] Figure 16 For loop A of system four;

[0050] Figure 17 For loop B of system four;

[0051] Figure 18 This is system five of the present invention;

[0052] Figure 19 For loop A of system five;

[0053] Figure 20 For loop B of system five;

[0054] Figure 21 This is System Six of the present invention;

[0055] Figure 22 For loop A of system six;

[0056] Figure 23 For loop B of system six;

[0057] Figure 24 This is system seven of the present invention;

[0058] Figure 25 For loop A of system seven;

[0059] Figure 26 For loop B of system seven;

[0060] Figure 27 This is system eight of the present invention;

[0061] Figure 28 For loop A of system eight;

[0062] Figure 29 For loop B of system eight;

[0063] Figure 30 This is System Nine of the present invention;

[0064] Figure 31 For loop A of system nine;

[0065] Figure 32 For loop B of system nine;

[0066] Figure 33 This is a variation of system nine of the present invention;

[0067] Figure 34 This is a variation of system nine of the present invention. Detailed Implementation

[0068] To further illustrate the technical means and effects of the present invention in achieving its intended purpose, the following detailed description of the specific implementation methods, structures, features, and effects of the present invention, in conjunction with the accompanying drawings and preferred embodiments, is provided below.

[0069] In the description of this invention, it should be understood that the terms "first," "second," "secondary," and "subsidiary" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first," "second," "secondary," or "subsidiary" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise expressly defined.

[0070] The terms “up,” “down,” “front,” “back,” “left,” “right,” “vertical,” and “horizontal” indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the present invention.

[0071] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0072] Figure 6 A system according to the method of the present invention is shown, the system comprising a condenser 101, an evaporator 102, a compressor 103, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a first storage tank 1071, a second storage tank 1072, a first valve 1081, a second valve 1082, a third valve 1083, a fourth valve 1084, and a fifth valve 1085. The refrigerant pipeline 105 connects the above components to form the system, that is, the outlet of the compressor 103 is connected to the condenser 1041. The refrigerant inlet of condenser 101 is connected to the refrigerant side inlet. The outlet of condenser 101 is connected to the first inlet of first storage tank 1071. The first outlet of first storage tank 1071 is connected to the inlet of first throttle valve 1041 via a pipe equipped with third valve 1083. The outlet of first throttle valve 1041 is connected to the refrigerant side inlet of evaporator 102. The outlet of evaporator 102 is connected to the inlet of gas-liquid separator 106 via a pipe equipped with fifth valve 1085. The outlet of gas-liquid separator 106 is connected to the inlet of compressor 103. The second outlet of first storage tank 1071 is connected to the inlet of second throttle valve 1042 via a pipe equipped with first valve 1081. The outlet of second throttle valve 1042 is connected to the first inlet of second storage tank 1072. The second outlet of second storage tank 1072 is connected to the pipe between fifth valve 1085 and gas-liquid separator 106 via a pipe equipped with fourth valve 1084. The second outlet of the second storage tank 1072 is connected to the second inlet of the first storage tank 1071. In this system, the condenser 101, evaporator 102, compressor 103, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and first storage tank 1071 correspond to the condenser, evaporator, compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of loop A, respectively. The second storage tank 1072, as a supplement to the first storage tank 1071, can help control and reduce the pressure of the first storage tank. The second storage tank 1072-fourth valve 1084 and its extended pipeline correspond to the auxiliary pipeline of loop B, and are connected to the condenser of loop A to form a loop.

[0073] The first type of system switches between two loops, such as Figure 7 , Figure 8 As shown.

[0074] Cycle A: Valve 1081 is closed, valve 1082 is open, valve 1083 is open, valve 1084 is closed, and valve 1085 is open; simplified version as follows... Figure 7As shown in the diagram, only open valves are shown; closed valves and disconnected pipes are omitted. Low-pressure refrigerant absorbs heat from an external heat source in evaporator 102, producing low-pressure gaseous refrigerant. This gaseous refrigerant enters gas-liquid separator 106, then enters compressor 103 where it is compressed and its pressure increased before being discharged. It then enters condenser 101, where it cools and releases heat to the heat sink, becoming liquid. This high-temperature, high-pressure liquid refrigerant enters the first storage tank 1071. Liquid refrigerant in the second storage tank 1072 returns to the first storage tank 1071 by gravity. The second storage tank 1072 is installed higher than the first storage tank 1071. The liquid in the first storage tank 1071 enters evaporator 102 after passing through the first throttle valve 1041.

[0075] Cycle B does not extract heat from the outside; instead, it obtains heat by lowering the temperature of the first storage tank 1071. The first valve 1081 and the fourth valve 1084 are open, while the second valve 1082, the third valve 1083, and the fifth valve 1085 are closed. (Simplified version follows...) Figure 8 As shown in the diagram, only the open valves are shown; closed valves and disconnected pipes are omitted. At this point, the high-temperature, high-pressure refrigerant in the first storage tank 1071 enters the second storage tank 1072 through the second throttle valve 1042. A portion of the refrigerant absorbs heat from the external heat source in the evaporator 102 and vaporizes. It then passes through the fourth valve 1084 into the gas-liquid separator 106, and then into the compressor 103. The compressed high-pressure gas enters the condenser 101, where it condenses and releases heat, before returning to the first storage tank 1071. The second storage tank 1072 still contains some unvaporized but cooled liquid refrigerant. However, after switching to cycle A, the second valve 1082 opens, and the liquid refrigerant returns to the first storage tank 1071. After cycle B is completed, the system switches back to cycle A.

[0076] The two cycles alternate operation. Clearly, the evaporation temperature of cycle B is higher than that of cycle A. Compared to a conventional cycle, or a system with only cycle A, its efficiency is improved. The temperature change of cycle B is as follows: Figure 2 , Figure 3 As shown, when switching between cycle A and cycle B, in order to achieve a smooth switch, the temperature of cycle B is lower and close to that of cycle A. The intermediate process is from low to high and then from high to low.

[0077] Figure 9This invention discloses a second system comprising a condenser 101, an evaporator 102, a compressor 103, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a storage tank 107 containing a heat storage body 1073, a first valve 1081, a second valve 1082, a third valve 1083, and a fourth valve 1084. The refrigerant pipeline 105 connects the above components to form the system. Specifically, the outlet of the compressor 103 is connected to the refrigerant-side inlet of the condenser 101, and the outlet of the condenser 101 is connected to the inlet of the second throttle valve 1042. The outlet of 1042 is connected to the inlet of storage tank 107. The second throttle valve 1042 is also connected in parallel with a bypass valve, namely the first valve 1081. The inlet and outlet of the first valve 1081 are connected to the inlet and outlet of the second throttle valve 1042. The first outlet of storage tank 107 is connected to the inlet of the second throttle valve 1042 via a pipe equipped with the second valve 1082. The outlet of the second throttle valve 1042 is connected to the refrigerant-side inlet of evaporator 102. The outlet of evaporator 102 is connected to the inlet of gas-liquid separator 106 via a pipe equipped with the fourth valve 1084. The outlet of gas-liquid separator 106 is connected to the inlet of compressor 103. The second outlet of storage tank 107 is connected to the pipe between the fourth valve 1084 and gas-liquid separator 106 via a pipe equipped with the third valve 1083. In this system, condenser 101, evaporator 102, compressor 103, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and first storage tank 107 correspond to the condenser, evaporator, compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively; the first storage tank 107-third valve 1083 and its extension pipeline correspond to the auxiliary pipeline of cycle B, and are connected to the condenser of cycle A to form a loop.

[0078] The second type of system switches between two loops, such as Figure 10 , Figure 11 As shown.

[0079] In cycle A, valve 1081 is open, valve 1082 is open, valve 1084 is open, and valve 1083 is closed. Low-pressure refrigerant absorbs heat from the external heat source in evaporator 102, generating low-pressure gaseous refrigerant. The gaseous refrigerant enters gas-liquid separator 106, then enters compressor 103, is compressed and its pressure is increased before being discharged. It then enters condenser 101, where it is cooled and releases heat to the heat sink, turning into liquid. The high-temperature, high-pressure liquid refrigerant enters storage tank 107, and the liquid in storage tank 107 enters evaporator 102 after passing through first throttle valve 1041.

[0080] Cycle B does not extract heat from the outside; instead, it obtains heat through the temperature reduction of storage tank 107. This includes the temperature of storage tank 107 itself, the temperature of the heat storage body 1073 within storage tank 107, and the temperature of the refrigerant within storage tank 107. First valve 1081, second valve 1082, and fourth valve 1084 are closed, while third valve 1083 is open. (Simplified version follows...) Figure 11 As shown in the diagram, only the open valves are shown; closed valves and their disconnected pipes are omitted. Refrigerant from condenser 101 enters storage tank 107 through the second throttle valve 1042. The refrigerant absorbs heat from storage tank 107, evaporates into a gaseous state, and then enters gas-liquid separator 106. It then enters compressor 103, where it is compressed and its pressure increased before being discharged. Finally, it enters condenser 101, where it is cooled and releases heat to the heat sink, becoming liquid.

[0081] Figure 12This invention presents a third system with defrosting and de-icing functions, applicable to applications such as air-source heat pumps and ice-making systems. The third system includes a condenser 101, an evaporator 102, a compressor 103, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a first storage tank 1071, a second storage tank 1072, a first valve 1081, a second valve 1082, a third valve 1083, a fourth valve 1084, and a fifth valve 1085. The refrigerant pipeline 105 connects these components to form the system; that is, the outlet of the compressor 103 is connected to the outlet of the condenser 101. The refrigerant side inlet is connected, the outlet of condenser 101 is connected to the first inlet of first storage tank 1071, the outlet of first storage tank 1071 is connected to the inlet of first throttle valve 1041, the outlet of first throttle valve 1041 is connected to the refrigerant side inlet of evaporator 102, the outlet of evaporator 102 is connected to the inlet of gas-liquid separator 106 through a pipe equipped with third valve 1083, the first throttle valve 1041 is also equipped with a bypass valve, namely second valve 1082, the inlet and outlet of second valve 1082 are connected to the inlet and outlet of first throttle valve 1041; the outlet of gas-liquid separator 106 is connected to the inlet of compressor 103. The second inlet of the first storage tank 1071 is connected to the second outlet of the second storage tank 1072 via a pipe equipped with the first valve 1081. The inlet of the second storage tank 1072 is connected to the pipe between the third valve 1083 and the outlet of the evaporator 102 via a pipe equipped with the fourth valve 1084 and the second throttle valve 1042. The first outlet of the second storage tank 1072 is connected to the pipe between the third valve 1083 and the gas-liquid separator 106 via a pipe equipped with the fifth valve 1085. In this system, the condenser 101, evaporator 102, compressor 103, first throttle valve 1041, refrigerant pipe 105, gas-liquid separator 106, and first storage tank 1071 correspond to the condenser, evaporator, compressor, throttle valve, pipe, gas-liquid separator, and storage tank of cycle A, respectively. The second storage tank 1072, as a supplement to the first storage tank 1071, can help control and reduce the pressure of the first storage tank. The second storage tank 1072, the fourth valve 1084 and their extended pipes correspond to the secondary pipes of circulation B, and the evaporator is connected in series to the secondary pipes, which are connected to the condenser of circulation A to form a loop.

[0082] The third type of system switches between two loops, such as Figure 13 , Figure 14 As shown.

[0083] Figure 13 In the intermediate circulation A, valve 1081 is open, valve 1082 is closed, valve 1083 is open, and valves 1084 and 1085 are closed. (Simplified version follows) Figure 13As shown in the diagram, only open valves are shown; closed valves and disconnected pipes are omitted. Low-pressure refrigerant absorbs heat from an external heat source in evaporator 102, producing low-pressure gaseous refrigerant. This gaseous refrigerant then enters gas-liquid separator 106, and then enters compressor 103 where it is compressed and its pressure increased before being discharged. It then enters condenser 101, where it cools and releases heat to the heat sink, becoming liquid. The high-temperature, high-pressure liquid refrigerant enters the first storage tank 1071. The liquid in the first storage tank 1071 passes through the first throttle valve 1041 and enters evaporator 102. The liquid in the second storage tank 1072 returns to the first storage tank 1071. After frost or ice formation in evaporator 102, the cycle switches to cycle B.

[0084] Figure 14 In cycle B, heat is not drawn from the outside. Instead, heat is obtained by lowering the temperature of the first storage tank 1071. The first valve 1081 is closed, the second valve 1082 and the fourth valve 1084 are open, the third valve 1083 is closed, and the fifth valve 1085 is open. At this time, refrigerant from the condenser 101 enters the first storage tank 1071, then the evaporator 102. The evaporator defrosts or removes ice, and then the refrigerant passes through the second throttle valve 1042 into the second storage tank 1072. The refrigerant cools down, and some of it evaporates into a gaseous state before entering the gas-liquid separator 106. It then enters the compressor 103, where it is compressed and its pressure increased before being discharged. Finally, it enters the condenser 101, where it cools and releases heat to the heat sink, becoming liquid. The liquid in the second storage tank 1072 returns to the first storage tank 1071 during cycle A.

[0085] Figure 15This invention discloses a fourth system with defrosting and de-icing functions, applicable to systems such as air-source heat pumps and ice-making systems. The fourth system includes a condenser 101, an evaporator 102, a compressor 103, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a first storage tank 1071, a second storage tank 1072, a first valve 1081, a second valve 1082, a third valve 1083, a fourth valve 1084, and a fifth valve 1085. The sixth valve 1086, the seventh valve 1087, the eighth valve 1088, and the refrigerant pipe 105 connect the above components to form a system. That is, the outlet of the compressor 103 is connected to the refrigerant side inlet of the condenser 101. The outlet of the condenser 101 is divided into two paths. One path is connected to the first inlet of the first storage tank 1071 through a pipe equipped with the second valve 1082. The other path is connected to the intermediate pipe between the refrigerant side outlet of the evaporator 102 and the seventh valve 1087 through a pipe equipped with the first valve 1081. The outlet of the first storage tank 1071 splits into two paths. One path (indicated by the green line) connects to the inlet of the first throttle valve 1041 via a pipe equipped with the third valve 1083. The outlet of the first throttle valve 1041 is connected to the refrigerant inlet of the evaporator 102. The refrigeration side outlet of the evaporator 102 is connected to the gas-liquid separator 106 via a pipe equipped with the seventh valve 1087. The other path (indicated by the red line) connects to the inlet of the second throttle valve 1042 via the fourth valve 1084. The outlet of the second throttle valve 1042 is connected to the second storage tank 1072. The inlet of the first storage tank 1071 is connected to the inlet of the compressor 103. The first outlet of the second storage tank 1072 is connected to the pipe between the seventh valve 1087 and the gas-liquid separator 106 through a pipe equipped with the sixth valve 1086. The outlet of the gas-liquid separator 106 is connected to the inlet of the compressor 103. The outlet of the second valve 1082 is also connected to the pipe between the first throttle valve 1041 and the evaporator 102 through a pipe equipped with the fifth valve 1085. The second inlet of the first storage tank 1071 and the second outlet of the second storage tank 1072 are connected through the eighth valve 1088.

[0086] The fourth system switches between loop A and loop B, such as... Figure 16 , Figure 17 As shown.

[0087] During cycle A, valves 1087 (seventh), 1088 (eighth), 1083 (third), and 1082 (second) are open, while valves 1081 (first), 1084 (fourth), 1085 (fifth), and 1086 (sixth) are closed. (Simplified version follows...) Figure 16As shown in the diagram, only open valves are shown; closed valves and disconnected pipes are omitted. Low-pressure refrigerant absorbs heat from an external heat source in evaporator 102, producing low-pressure gaseous refrigerant. This gaseous refrigerant then enters gas-liquid separator 106, and then enters compressor 103 where it is compressed and its pressure increased before being discharged. It then enters condenser 101, where it cools and releases heat to the heat sink, becoming liquid. The high-temperature, high-pressure liquid refrigerant enters the first storage tank 1071. The liquid in the first storage tank 1071 passes through the first throttle valve 1041 and enters evaporator 102. The liquid in the second storage tank 1072 returns to the first storage tank 1071. After frost or ice formation in evaporator 102, the cycle switches to cycle B. In this system, condenser 101, evaporator 102, compressor 103, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and first storage tank 1071 correspond to the condenser, evaporator, compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively. Second storage tank 1072 supplements first storage tank 1071 and helps control and reduce the pressure of first storage tank. Second storage tank 1072, fourth valve 1084, and its extended pipeline correspond to the secondary pipeline of cycle B, and the evaporator is connected in series to the secondary pipeline, forming a loop with the condenser and other components of cycle A.

[0088] During cycle B, valves 1087 (seventh valve), 1088 (eighth valve), 1083 (third valve), and 1082 (second valve) are closed, while valves 1081 (first valve), 1084 (fourth valve), 1085 (fifth valve), and 1086 (sixth valve) are open. (Simplified version follows...) Figure 17 As shown in the diagram, only the open valves are shown; closed valves and disconnected pipes are omitted. Cycle B does not extract heat from the outside; it obtains heat through the temperature reduction of the first storage tank 1071. At this time, the refrigerant from the condenser 101 enters the evaporator 102, where it defrosts or defrosts. The refrigerant then enters the first storage tank 1071, passes through the second throttle valve 1042, and enters the second storage tank 1072. The refrigerant cools down, and some of it evaporates into a gaseous state before entering the gas-liquid separator 106. It then enters the compressor 103, where it is compressed and its pressure increased before being discharged. Finally, it enters the condenser 101, where it cools and releases heat to the heat sink, becoming liquid. The liquid in the second storage tank 1072 returns to the first storage tank 1071 during cycle A.

[0089] Figure 18The fifth system includes a condenser 101, an evaporator 102, a compressor 103, a two-way throttle valve 1043, a refrigerant pipeline 105, a storage tank 107, a heat storage body 1073 inside the storage tank 107, and a four-way valve 1089. The refrigerant pipeline 105 connects the above components to form a system. Specifically, the outlet of the compressor 103 is connected to the refrigerant-side inlet of the condenser 101, the refrigerant-side outlet of the condenser 101 is connected to the first port of the four-way valve 1089, the second port of the four-way valve 1089 is connected to the inlet of the compressor 103, the third port of the four-way valve 1089 is connected to the first port of the storage tank 107, the second port of the storage tank 107 is connected to the first port of the two-way throttle valve 1043, the second port of the two-way throttle valve 1043 is connected to the first port of the evaporator 102, and the second port of the evaporator 102 is connected to the fourth port of the four-way valve 1089. In this system, condenser 101, evaporator 102, compressor 103, two-way throttle valve 1043, refrigerant pipeline 105, gas-liquid separator 106, and storage tank 107 correspond to the condenser, evaporator, compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively; the system ingeniously utilizes two-way throttle valve 1043 and four-way valve 1089 to realize the operation of cycle B.

[0090] The system switches between cycle A and cycle B by switching via the four-way valve 1089.

[0091] Loop A, such as Figure 19 As shown, the low-pressure refrigerant absorbs heat from the external heat source in the evaporator 102, producing low-pressure gaseous refrigerant. This gaseous refrigerant then enters the fourth port of the four-way valve 1089, exits from the second port, enters the compressor 103 where it is compressed and its pressure increased before exiting. It then enters the condenser 101, where it cools and releases heat to the heat sink, becoming liquid. The high-temperature, high-pressure liquid refrigerant then enters the first port of the four-way valve 1089, exits from the third port, enters the storage tank 107, and then passes through the bidirectional throttling valve 1043 before entering the evaporator 102. After frost or ice forms in the evaporator 102, the cycle switches to cycle B.

[0092] Figure 20 Cycle B, as shown, does not extract heat from the outside; instead, it obtains heat through the temperature reduction of the storage tank. Refrigerant from condenser 101 enters the first port of four-way valve 1089, exits from the fourth port, and then enters evaporator 102. In evaporator 102, it defrosts or defrosts. Then, it passes through two-way throttling valve 1043 into storage tank 107. In storage tank 107, the heat storage body 1073, the refrigerant, and the tank itself all cool down. The refrigerant evaporates into a gaseous state and enters compressor 103, where it is compressed and its pressure increased before being discharged. It then enters condenser 101, where it cools and releases heat to the heat sink, becoming liquid. After defrosting or defrosting is complete, the system switches back to cycle A.

[0093] Figure 21The sixth system is shown, which includes a first condenser 101A, a second condenser 101B, an evaporator 102, a first-stage compressor 103A, a second-stage compressor 103B, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a first gas-liquid separator 106A, a second gas-liquid separator 106B, a first storage tank 1071, a second storage tank 1072, a first valve 1081, a second valve 1082, a third valve 1083, a fourth valve 1084, a fifth valve 1085, a sixth valve 1086, a seventh valve 1087, and an eighth valve 1088. The refrigerant pipeline 105 connects the above components to form two sets of left and right circulation systems.

[0094] In the right-side circulation system, the outlet of the first compressor 103A is connected to the refrigerant-side inlet of the first condenser 101A. The refrigerant-side outlet of the first condenser 101A is connected to the first port of the first storage tank 1071 through the second valve 1082. The second port of the first storage tank 1071 is connected to the inlet of the first throttle valve 1041 through the third valve 1083. The outlet of the first throttle valve 1041 is connected to the refrigerant-side inlet of the evaporator 102. The refrigerant-side outlet of the evaporator 102 is connected to the inlet of the first gas-liquid separator 106. The outlet of the first gas-liquid separator 106 is connected to the inlet of the first-stage compressor 103A.

[0095] In the left-side circulation system, the outlet of the secondary compressor 103B is connected to the refrigerant-side inlet of the second condenser 101B, and its outlet is connected to the inlet of the second throttle valve 1042. The outlet of the second throttle valve 1042 is connected to the second port of the second storage tank 1072 through the seventh valve 1087. The first port of the second storage tank 1072 is also connected to the inlet of the second gas-liquid separator 106B through the sixth valve. The outlet of the second gas-liquid separator 106B is connected to the inlet of the secondary compressor 103B.

[0096] The following connection is established between the two loop systems:

[0097] The outlet on the refrigerant side of the first condenser 101 A is connected to the first interface of the second storage tank 1072 through the first valve 1081;

[0098] The second port of the second storage tank 1072 is connected to the inlet of the first throttle valve 1041 through the fourth valve 1084;

[0099] The outlet of the second throttle valve 1042 is connected to the second port of the first storage tank 1071 through the eighth valve 1088;

[0100] The first port of the first storage tank 1071 is connected to the inlet of the second gas-liquid separator 106B via the fifth valve 1085.

[0101] In this system, condenser 101, evaporator 102, compressor 103, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and first storage tank 1071 / second storage tank 1072 correspond to the condenser, evaporator, compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively; second condenser 101B, second gas-liquid separator 106B, and second-stage compressor 103B correspond to the auxiliary condenser, auxiliary gas-liquid separator, and auxiliary compressor of cycle B, respectively. Second condenser 101B, second gas-liquid separator 106B, and second-stage compressor 103B are connected to first storage tank 1071 / second storage tank 1072 through auxiliary pipelines and multiple valves.

[0102] The sixth system has two loops (loop A and loop B) running in parallel. There are two possible scenarios:

[0103] Scenario 1: The first storage tank 1071 is heated, and the second storage tank 1072 is cooled;

[0104] The second scenario: the first storage tank 1071 cools down, and the second storage tank 1072 heats up;

[0105] In the first scenario, valves 1082, 1083, 1087, and 1086 are opened, while valves 1081, 1084, 1085, and 1088 are closed. The left and right circulation systems operate independently, as shown in the simplified diagram below. Figure 22 As shown in the diagram, only the open valves are shown, while the closed valves and disconnected pipes are omitted. In the right-side circulation system (circulation A), the low-pressure refrigerant absorbs heat from the external heat source in the evaporator 102, generating low-pressure gaseous refrigerant. The gaseous refrigerant enters the first gas-liquid separator 106A, then enters the first-stage compressor 103A, where it is compressed and its pressure is increased before being discharged. It then enters the first condenser 101A, where it is cooled and releases heat to the heat sink, turning into a liquid. At this time, the high-temperature, high-pressure liquid refrigerant enters the first storage tank 1071, squeezing out the subcooled liquid in the first storage tank 1071, thus raising the temperature of the first storage tank 1071. The subcooled liquid then enters the evaporator 102 after passing through the first throttle valve 1041. In the left-hand circulation system (circulation B), heat is not extracted from the outside; instead, heat is obtained through the temperature reduction of the second storage tank 1072. Part of the refrigerant in the second storage tank 1072 evaporates, producing low-pressure gaseous refrigerant, which subcools the unevaporated liquid refrigerant. The low-pressure gaseous refrigerant then enters the second-stage compressor 103B via the second gas-liquid separator 106B. After being compressed and its pressure increased, it is discharged into the second condenser 101B, where it is cooled and releases heat to the heat sink, turning into a liquid state. It then returns to the second storage tank 1072, where the liquid refrigerant is gradually cooled. The system's evaporation temperature also continuously decreases, but the evaporation temperature of circulation B remains higher than that of circulation A.

[0106] In the second scenario, valves 1082, 1083, 1087, and 1086 are closed, while valves 1081, 1084, 1085, and 1088 are open. Figure 23 As shown, the first storage tank 1071 is connected to the circulation loop B, and the second storage tank 1072 is connected to the circulation loop A. The subcooled liquid refrigerant in the second storage tank 1072 is discharged and replaced by high-temperature liquid refrigerant. The second storage tank 1072 heats up, and the high-temperature liquid refrigerant in the first storage tank 1071 becomes low-temperature liquid refrigerant. The medium-temperature liquid refrigerant in the first storage tank 1071 is gradually cooled.

[0107] Thus, the first storage tank 1071 is alternately connected to the circulation loop A and the circulation loop B, and correspondingly, the second storage tank 1072 is alternately connected to the circulation loop B and the circulation loop A.

[0108] Figure 24The seventh system is shown, which includes a condenser 101, an evaporator 102, a primary compressor 103A, a secondary compressor 103B, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a storage tank 107 containing a heat storage body 1073, a first valve 1081, a second valve 1082, a third valve 1083, a fourth valve 1084, a fifth valve 1085, and a sixth valve 1086. The refrigerant pipeline 105 connects the above components to form the system. Specifically, the outlet of the secondary compressor 103B is connected to the refrigerant-side inlet of the condenser 101, and the refrigerant-side outlet of the condenser 101 is divided into two paths. One path is connected to the refrigeration-side outlet of the evaporator 102 via a pipeline equipped with the second valve 1082, and the other path is connected to the third valve 1083. Between the pipes, another path is connected to the inlet of the first throttle valve 1041 via a pipe equipped with a first valve 1081. The outlet of the first throttle valve 1041 is connected to the first inlet of the storage tank 107. The first outlet of the storage tank 107 is connected to the inlet of the secondary compressor 103B. The second outlet of the storage tank 107 is connected to the inlet of the second throttle valve 1042. The outlet of the second throttle valve 1042 is connected to the inlet of the refrigeration side of the evaporator 102 via a pipe equipped with a fifth valve 1085. The outlet of the refrigeration side of the evaporator 102 is connected to the gas-liquid separator 106 via a pipe equipped with a third valve 1083. The outlet of the gas-liquid separator 106 is connected to the inlet of the primary compressor 103A. The outlet of the primary compressor 103A is connected to the second inlet of the storage tank 107 via a pipe equipped with a fourth valve 1084. A connecting pipe is provided between the pipes between the first valve 1081 and the first throttle valve 1041, and between the fifth valve 1085 and the evaporator 102. A sixth valve 1086 is installed on the connecting pipe. In this system, condenser 101, evaporator 102, primary compressor 103A, secondary compressor 103B, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and storage tank 107 correspond to the condenser, evaporator, compressor, secondary compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of loop A, respectively; the pipeline where the sixth valve 1086 is located constitutes the secondary pipeline of loop B, and the evaporator is connected in series to the secondary pipeline, connecting with the condenser of loop A to form a loop.

[0109] Figure 25 and Figure 26 The display system has two cycles, which switch between each other.

[0110] In cycle A, the system extracts heat from the outside. Valve 1081, 1083, 1084, and 1085 are open, while valves 1082 and 1086 are closed. Low-pressure liquid refrigerant evaporates in evaporator 102, then enters gas-liquid separator 106, and then enters first compressor 1031 where it is compressed and pressurized. The compressed medium-pressure superheated gaseous refrigerant enters the second inlet of storage tank 107, where it exchanges heat with the gas-liquid two-phase refrigerant at the first inlet, causing a portion of the refrigerant to... Liquid refrigerant evaporates, superheated gaseous refrigerant cools down, and gaseous refrigerant generated in storage tank 107 is discharged from the first outlet of the storage tank or enters the secondary compressor 103B to be further pressurized, and then enters the condenser 101 to condense and release heat. The condensed high-temperature and high-pressure liquid refrigerant passes through the first throttle valve 104A and enters the storage tank through the first inlet. The unevaporated liquid refrigerant in the storage tank is discharged through the second outlet of the storage tank, and enters the evaporator 102 after passing through the second throttle valve 1042. It should be noted that the heat storage body 1073 in the storage tank has a low temperature at the beginning of cycle A, and is heated to increase its temperature during cycle A. During cycle A, the evaporator 102 frosts or freezes. If the heat source is air, frost will form; if the heat source is water, freezing will occur. After frost or freezing reaches a certain level, cycle B can be switched to defrost or remove ice.

[0111] In cycle B, heat is not extracted from the outside. Instead, heat is obtained through the heat storage body 1073 in the storage tank 107, the refrigerant, and the cooling of the storage tank itself. At this time, the first valve 1081, the third valve 1083, the fourth valve 1084, and the fifth valve 1085 are closed, while the second valve 1082 and the sixth valve 1086 are open. At this time, the first-stage compressor 103A and the gas-liquid separator 106 are not connected to the system and their operation stops. The cycle is as follows: High-temperature, high-pressure liquid refrigerant from condenser 101 enters evaporator 102, where it defrosts or defrosts. The liquid refrigerant discharged from evaporator 102 passes through sixth valve 1086 and first throttle valve 1041, then enters storage tank 107 through the first inlet. It absorbs heat from the storage tank and evaporates to produce gaseous refrigerant, which then enters the second compressor 103 through the first outlet of the storage tank. After being pressurized in compressor 103, the high-temperature, high-pressure gaseous refrigerant enters condenser 101, condenses, and releases heat. It then enters evaporator 102 for defrosting or defrosting. Once defrosting or defrosting is complete, the cycle switches to cycle A.

[0112] Figure 27The eighth system is shown, which includes a condenser 101, an evaporator 102, a first compressor 1031, a second compressor 1032, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a storage tank 107, a heat storage body 1073, a four-way valve 1089, a first valve 1081, and a one-way valve DV. Refrigerant piping 105 connects the aforementioned components to form a system. Specifically, the outlet of the second compressor 1032 is connected to the refrigerant-side inlet of the condenser 101, and its outlet is connected to the first port of the four-way valve 1089. The second port of the four-way valve 1089 is connected to the inlet of the gas-liquid separator 106. The third port of the four-way valve 1089 is connected to the first throttle valve 1041. The first throttle valve 1041 is connected to the first port of the storage tank 107. The second liquid port of the storage tank 107 is connected to the second throttle valve 1042. The second throttle valve 1042 is connected to the first port of the evaporator 102. The second port of the evaporator 102 is connected to the fourth port of the four-way valve 1089. The third port of the storage tank 107 is connected to the piping between the first compressor 1031 and the second compressor 1032 via the first valve 1081. A heat storage body 1073 is provided inside the storage tank 107. The first throttle valve 1041 is provided with a bypass, and a one-way valve DV is provided on the bypass. In this system, condenser 101, evaporator 102, primary compressor 103A, secondary compressor 103B, second throttle valve 1042, refrigerant pipeline 105, gas-liquid separator 106, and storage tank 107 correspond to the condenser, evaporator, compressor, secondary compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively; while the first throttle valve 1041 is set up for evaporative cooling of storage tank 107. The system cleverly utilizes a four-way valve 1089 and a one-way valve to realize the operation of cycle B.

[0113] Figure 28 and Figure 29 The display system has two cycles, which switch between each other.

[0114] Figure 28For cycle A, the system extracts heat from the outside. At this time, the first valve 1081 opens, and the low-pressure liquid refrigerant evaporates in the evaporator 102 to produce gaseous refrigerant. This gaseous refrigerant enters the four-way valve 1089 through its fourth port and exits from its second port, entering the gas-liquid separator 106. It then enters the first compressor 1031 to be compressed and pressurized. The compressed, medium-pressure superheated gaseous refrigerant mixes with the gaseous refrigerant from the storage tank 107 and enters the second compressor 1032 for further pressure increase. Finally, it enters the condenser 101 to condense and release heat. After heat dissipation and condensation, the high-temperature and high-pressure liquid refrigerant enters the first port of the four-way valve 1089, exits from the third port of the four-way valve 1089, passes through the first throttle valve 1041, and enters the storage tank 107 through the first port of the storage tank 107. In the storage tank 107, it flashes to generate gaseous refrigerant, which exits from the third port. After mixing with the gas at the outlet of the first compressor 1031, it enters the second compressor 1032. At the same time, the liquid is cooled by the heat storage body 1073, exits through the second port of the storage tank 107, and then enters the evaporator 102 through the second throttle valve 1042.

[0115] It should be noted that the liquid refrigerant and heat storage body 1073 in storage tank 107 are at a low temperature at the beginning of cycle A, and are heated to increase temperature during cycle A. During cycle A, evaporator 102 will frost or freeze. Frosting will occur if the heat source is air, and freezing will occur if the heat source is water. After frost or freezing reaches a certain level, cycle B can be switched to defrost or melt the ice.

[0116] Loop B, such as Figure 29 As shown, heat is not extracted from the outside; instead, it is obtained through the heat storage body 1073, the refrigerant, and the cooling of the tank 107 itself. At this time, the first valve 1081 is closed. The liquid refrigerant evaporates in the tank 107 to produce gaseous refrigerant, causing the entire tank 107 to cool down. The gaseous refrigerant is discharged from the first port of the tank 107 and passes through the one-way valve DV. The refrigerant enters through the third port of the four-way valve 1089 and exits through the second port of the four-way valve 1089, then enters the gas-liquid separator 106, then the first compressor 1031, and then the second compressor 1032. The gas discharged from the second compressor 1032 enters the condenser 101 to release heat to the heat sink. The liquid high-pressure refrigerant discharged from the condenser 101 enters the four-way valve 1089 through the first port of the four-way valve 1089 and exits through the fourth port of the four-way valve 1089. It flows into the second port of the evaporator 102 to defrost or de-ice the evaporator 102, and then exits from the first port of the evaporator 102. It then flows into the storage tank 107 through the second throttle valve 1042 and the second port of the storage tank 107. The refrigerant evaporates in the storage tank 107, and the temperature of the storage tank 107 decreases.

[0117] Figure 30The ninth system is shown, comprising a condenser 101, an evaporator 102, a first compressor 1031, a second compressor 1032, a first throttle valve 1041, a second throttle valve 1042, a refrigerant pipeline 105, a gas-liquid separator 106, a storage tank 107, a four-way valve 1089, a flash evaporator 109, a first valve 1081, a first one-way valve DV1, a second one-way valve DV2, and a third one-way valve DV3. The refrigerant pipeline 105 connects these components to form the system. Specifically, the outlet of the second compressor 1032 is connected to the refrigerant-side inlet of the condenser 101, the refrigerant-side outlet of the condenser 101 is connected to the inlet of the second throttle valve 1042, the outlet of the second throttle valve is connected to the inlet of the flash evaporator 109, and the gas outlet of the flash evaporator 109 is divided into two paths: one path connects to the pipeline connecting the outlet of the first compressor 1031 and the inlet of the second compressor 1032, and the other path connects to the pipeline connecting the outlet of the first compressor 1031 and the inlet of the second compressor 1032. One path is connected to the pipeline between the first check valve DV1 and the outlet of the evaporator 102 via the first valve 1081. The liquid outlet of the flash evaporator 109 is connected to the first port of the four-way valve 1089. The second port of the four-way valve 1089 is connected to the inlet of the gas-liquid separator 106. The third port of the four-way valve 1089 is connected to the inlet of the storage tank 107. The outlet of the storage tank 107 is connected to the inlet of the first throttle valve 1041. The outlet of the first throttle valve 1041 is connected to the inlet of the evaporator 102. The outlet of the evaporator 102 is connected to the inlet of the first check valve DV1. The outlet of the first check valve DV1 is split into two paths: one path is connected to the fourth port of the four-way valve 1089, and the other path is connected to the inlet of the second check valve DV2. The outlet of the second check valve DV2 is connected to the inlet of the third check valve DV3. The outlet of the third check valve DV3 is connected to the pipeline between the first throttle valve 1041 and the inlet of the evaporator 102. In this system, condenser 101, evaporator 102, primary compressor 103A, secondary compressor 103B, first throttle valve 1041, refrigerant pipeline 105, gas-liquid separator 106, and storage tank 107 correspond to the condenser, evaporator, compressor, secondary compressor, throttle valve, pipeline, gas-liquid separator, and storage tank of cycle A, respectively. The second throttle valve 1042 is designed for evaporation and cooling of flash evaporator 109. The system cleverly utilizes a four-way valve 1089 and a one-way valve, and further includes a secondary pipeline containing the first valve 1081. The evaporator is connected in series to this secondary pipeline, forming a loop with the condenser and other components.

[0118] Figure 31 and Figure 32 The display system has two cycles, which switch between each other.

[0119] Figure 31For cycle A, the system extracts heat from the outside. At this time, the first valve 1081 is closed, and the low-pressure liquid refrigerant evaporates in the evaporator 102 to produce gaseous refrigerant. This gaseous refrigerant then passes through the first one-way valve DV1, enters the four-way valve 1089 through its fourth port, and exits from the second port of the four-way valve 1089. It then enters the gas-liquid separator 106, and then enters the first compressor 1031 where it is compressed and pressurized. The compressed medium-pressure superheated gaseous refrigerant mixes with the gaseous refrigerant from the flash evaporator 109 and enters the second compressor 1032 where its pressure is further increased. Finally, it enters the condenser 10... 1. The condensation process releases heat and dissipates heat. The high-temperature, high-pressure liquid refrigerant after condensation enters the flash evaporator 109 through the inlet of the first throttle valve. The gas generated by the flash evaporator 109 mixes with the gas from the outlet of the first compressor 1031 and enters the second compressor 1032. The liquid enters the four-way valve 1089 through the first port of the four-way valve 1089 through the liquid outlet of the flash evaporator 109, and then enters the storage tank 107 through the third port of the four-way valve 1089. The cold liquid refrigerant in the storage tank 107 is discharged and replaced by hot liquid refrigerant. The discharged cold liquid refrigerant enters the evaporator 102 through the first throttle valve 1041, and the evaporator 102 generates gaseous refrigerant.

[0120] It should be noted that the liquid refrigerant in storage tank 107 has a low temperature at the beginning of cycle A, and its temperature is raised during cycle A. During cycle A, evaporator 102 will frost or freeze. Frosting will occur if the heat source is air, and freezing will occur if the heat source is water. After frost or freezing reaches a certain level, cycle B can be switched to defrost or remove ice.

[0121] Loop B, such as Figure 32 As shown, heat is not extracted from the outside, but is obtained through the refrigerant in the storage tank 107 and the cooling of the storage tank 107 itself. At this time, the first valve 1081 is opened.

[0122] Liquid refrigerant evaporates in storage tank 107 to produce gaseous refrigerant, which cools storage tank 107. The gaseous refrigerant enters four-way valve 1089 through the third port, and then exits through the second port into a gas-liquid separator. It then enters the first compressor 1031. The gas discharged from the first compressor 1031 mixes with the gas from flash evaporator 109 and enters the second compressor 1032. The gas discharged from the second compressor 1032 enters condenser 101, releasing heat to the heat sink. Liquid high-pressure refrigerant discharged from condenser 101 passes through the second throttle valve into flash evaporator 109. The liquid is discharged from the liquid outlet of flash evaporator 109. Then, it enters the four-way valve 1089 through the first port and exits from the fourth port of the four-way valve 1089. Then, it flows into the evaporator outlet through the second and third check valves and mixes with the refrigerant discharged from the evaporator outlet. Then, it enters the storage tank 107 through the first throttle valve 1041. Part of the gas coming out of the flash evaporator gas outlet mixes with the exhaust gas of the first compressor 1031 and flows into the second compressor 1032. The other part flows into the evaporator through the first valve 1081 to defrost the evaporator. After condensing in the evaporator, it is discharged from the evaporator and mixes with the liquid at the outlet of the third check valve. Then, it flows into the storage tank 107 through the first throttle valve 1041.

[0123] Switch to cycle A after defrosting or de-icing is complete.

[0124] The reason why the liquid in flash evaporator 109 is short-circuited and does not flow into the evaporator is that the temperature of the liquid flowing out of flash evaporator 109 is already low, and there is not much sensible heat available. The latent heat of the gas discharged from flash evaporator 109 is mainly used for defrosting or de-icing.

[0125] However, when rapid defrosting is required, it is also possible to consider using the compressor's exhaust gas directly for defrosting, such as... Figure 33 As shown, Figure 33 The system is Figure 30 The system's variation also has two loops, loop A and loop B. Figure 31 Completely identical, loop B and Figure 32 The only difference is that the gas entering the evaporator is exhaust from the compressor.

[0126] Rapid defrosting can also be achieved using the high-temperature, high-pressure liquid after condenser 101, such as... Figure 34 As shown, Figure 34 The system is Figure 30 Another variation of the system also has two loops, loop A and loop B. Figure 31 Completely identical, loop B and Figure 32 The only difference is that the refrigerant entering the evaporator is the high-temperature refrigerant from condenser 101.

[0127] The two-stage compression in System 8 or System 9 can be achieved by two independent compressors or by a single compressor with a two-stage compression mechanism and supplementary gas supply.

Claims

1. A method for improving the performance of a vapor compression refrigeration cycle, characterized in that, It contains two cycles: Cycle A obtains heat from a heat source, releases heat to a heat sink, and stores heat using a heat carrier; Cycle B does not obtain heat from a heat source, but obtains heat by cooling the heat carrier and releases heat to the heat sink; the heat carrier is the refrigerant between the condenser and the expansion valve in Cycle A and the components in contact with the refrigerant; the components are the storage tank connected between the condenser and the expansion valve. In cycle A, the refrigerant between the condenser and the expansion valve, and the components in contact with the refrigerant, are configured as heat carriers; the heat carriers are connected in cycle B.

2. The method according to claim 1, characterized in that, The heat source for cycle A is air or water. After the evaporator of cycle A frosts, it switches to cycle B to defrost or remove ice from the evaporator. Cycle B releases heat to the heat sink. After defrosting or removing ice is completed, it switches back to cycle A.

3. The method according to claim 1, characterized in that, There are at least two heat carriers, which are alternately connected to cycle A for heating or to cycle B for cooling.

4. A system, characterized in that, include: The condenser, expansion valve, evaporator, gas-liquid separator, compressor, piping, and refrigerant in the piping used to form loop A; The condenser, expansion valve, evaporator, gas-liquid separator, and compressor are connected in sequence through pipes to form a loop; the refrigerant between the condenser and the expansion valve, and the components in contact with the refrigerant, are configured as heat carriers; A component that connects to the heat carrier and forms a circulating loop B; And the valves controlling cycle A and cycle B shall operate in accordance with the method described in any one of claims 1 to 3; The component is connected to the condenser to perform cycle B, which releases heat to the heat sink through the condenser. The component includes a secondary pipe, one end of which is connected to the pipe between the condenser and the throttle valve, and the other end is connected to the inlet side of the gas-liquid separator. During operation of cycle B, the heat carrier between the condenser and the throttle valve enters the gas-liquid separator through the secondary pipe, and then enters the compressor. The compressed high-pressure gas enters the condenser for condensation and heat release. It also includes a storage tank, which is connected to the condenser and the throttle valve via a pipeline; one end of the auxiliary pipeline is connected to the storage tank and the other end is connected to the inlet side of the gas-liquid separator.

5. The system according to claim 4, characterized in that, The evaporator is connected in series on the secondary pipe. During cycle B, the heat carrier enters the evaporator through the secondary pipe to defrost the evaporator.

6. The system according to claim 4, characterized in that, It also includes a secondary compressor connected in series after the compressor; during operation of cycle A, the liquid refrigerant, which acts as a heat carrier, evaporates and cools down to produce gaseous refrigerant, which mixes with the superheated gaseous refrigerant compressed by the compressor, and is then compressed again by the secondary compressor before entering the condenser to condense and release heat; the liquid refrigerant evaporation and cooling includes: the liquid refrigerant itself cooling down, causing a portion of the liquid refrigerant to cool down, and another portion of the liquid refrigerant evaporating; or cooling down the superheated gaseous refrigerant produced by the compressor through the evaporation of the liquid refrigerant.

7. The system according to claim 4, characterized in that, The components include a secondary condenser, a secondary gas-liquid separator, a secondary compressor, and a secondary pipeline. During operation of cycle B, the heat carrier between the condenser and the throttle valve enters the secondary gas-liquid separator through the secondary pipeline, and then enters the secondary compressor. The compressed high-pressure gas enters the secondary condenser for condensation and heat release.

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