Non-azeotropic mixed working medium heat pump system

Abstract

The utility model relates to the technical field of heat pumps, and discloses a non-azeotropic mixed working medium heat pump system which comprises a compressor and a refrigerant circulation loop connected with the compressor to form a loop, and a condenser, a first throttling device, a heat exchange assembly and a second throttling device are sequentially arranged on the refrigerant circulation loop in the refrigerant flow direction. The heat exchange assembly is provided with a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet and a second refrigerant outlet, the first refrigerant inlet is connected with the first throttling device, the first refrigerant outlet is connected with an inlet of the second throttling device, the second refrigerant inlet is connected with an outlet of the second throttling device, and the second refrigerant outlet is connected with an air return opening of the compressor. According to the non-azeotropic mixed working medium heat pump system, the non-azeotropic mixed working medium is sequentially subjected to secondary throttling and heat regeneration from the condenser outlet to the second refrigerant inlet, so that the throttling temperature difference from the condenser to the heat exchange assembly is reduced compared with a traditional heat pump system, and finally the throttling loss is reduced, so that the heating performance of the non-azeotropic mixed working medium heat pump system is improved.

Description

Technical Field

[0001] This utility model relates to the field of heat pump technology, and in particular to a non-azeotropic mixed working fluid heat pump system. Background Technology

[0002] With the development of science and technology and the improvement of people's living standards, heat pump technology is increasingly widely used in residential and industrial fields. Because the temperature range between the heat source and heat sink in a heat pump system is large, traditional single working fluids are no longer sufficient to meet the requirements, such as ultra-low ambient temperature heating in buildings and ultra-high water temperature heating in industry. Non-azeotropic mixtures can flexibly select the components and proportions of the working fluid according to the application, increasing the temperature difference between the heat source and heat sink, thereby adapting to the large temperature span requirements of specific applications.

[0003] However, due to the large difference in boiling points between the mixed working fluids, the components cannot be completely condensed in the condenser or completely evaporated in the evaporator, resulting in poor heating performance of the heat pump system. Utility Model Content

[0004] The technical problem solved by this utility model is to provide a non-azeotropic mixed working fluid heat pump system, which effectively solves the technical problem of poor heating performance when mixed working fluids are used in heat pumps.

[0005] The above-mentioned technical problems are solved by the following technical solutions:

[0006] A non-azeotropic mixed working fluid heat pump system, comprising:

[0007] A compressor and a refrigerant circulation loop connected to the compressor and forming a loop, wherein a condenser, a first throttling device, a heat exchange assembly, and a second throttling device are sequentially provided along the refrigerant flow direction in the refrigerant circulation loop;

[0008] The heat exchange assembly is provided with a first refrigerant inlet, a first refrigerant outlet, a second refrigerant inlet, and a second refrigerant outlet. The first refrigerant inlet is connected to the first throttling device, the first refrigerant outlet is connected to the inlet of the second throttling device, the second refrigerant inlet is connected to the outlet of the second throttling device, and the second refrigerant outlet is connected to the return port of the compressor.

[0009] Compared with the prior art, the non-azeotropic mixed working fluid heat pump system of this utility model has the following advantages: after the non-azeotropic mixed working fluid is discharged from the compressor, it enters the condenser for cooling. The cooled refrigerant enters the first throttling device for throttling, and the throttled refrigerant enters the heat exchange component through the first refrigerant inlet for heat exchange. The refrigerant after heat exchange is discharged from the first refrigerant outlet and enters the second throttling device, which throttles the refrigerant again. After being throttled again, the refrigerant is transported along the connecting pipeline and re-enters the heat exchange component from the second refrigerant inlet, so that the heat exchange component exchanges heat with the refrigerant. The refrigerant after heat exchange is discharged from the second refrigerant outlet and returns to the compressor along the connecting pipeline to complete the heating cycle.

[0010] During the heating cycle, the subcooling of the refrigerant increases due to the influence of cold air. The cold air absorbs heat from the pipe between the first refrigerant inlet and the first refrigerant outlet, causing the air temperature to rise. The heated air then flows through the pipe between the second refrigerant inlet and the second refrigerant outlet. The low-temperature, low-pressure refrigerant inside the pipe absorbs the air temperature, thereby increasing the evaporation temperature of the refrigerant in the heat exchange component. In this application, part of the heat exchange component acts as a regenerator, and the other part acts as an evaporator, enabling the refrigerant flowing through the heat exchange component to achieve self-heat exchange. This allows for more complete liquefaction of the refrigerant exiting the condenser and more complete evaporation of the refrigerant flowing through the evaporator. The non-azeotropic working fluid undergoes two throttling and reheating processes from the condenser outlet to the second refrigerant inlet, reducing the throttling temperature difference between the condenser and the heat exchange component compared to traditional heat pump systems. This ultimately reduces throttling losses and improves heating performance. Furthermore, this allows the non-azeotropic working fluid heat pump system provided by this invention to be applied in colder outdoor environments at the same evaporation temperature.

[0011] In one embodiment, the heat exchange assembly includes a first heat exchanger and a second heat exchanger. The first heat exchanger is provided with a first refrigerant inlet and a first refrigerant outlet, and the second heat exchanger is provided with a second refrigerant inlet and a second refrigerant outlet. The condenser, the first throttling device, the first heat exchanger, the second throttling device, and the second heat exchanger are sequentially arranged along the refrigerant flow direction in the refrigerant circulation loop.

[0012] In one embodiment, the heat exchange assembly includes a plurality of fins and a first flow channel and a second flow channel that meander through the plurality of fins. The first flow channel forms a first refrigerant inlet and a first refrigerant outlet at both ends, and the second flow channel forms a second refrigerant inlet and a second refrigerant outlet at both ends.

[0013] In one embodiment, a liquid receiver is also included, the liquid receiver having a third refrigerant inlet and a third refrigerant outlet, the third refrigerant inlet being connected to the first throttling device, and the third refrigerant outlet being connected to the first refrigerant inlet.

[0014] In one embodiment, the liquid reservoir is further provided with a gaseous refrigerant outlet, which is connected to the second refrigerant inlet via a bypass branch.

[0015] In one embodiment, a switching valve is provided on the bypass branch.

[0016] In one embodiment, the switching valve is a solenoid valve.

[0017] In one embodiment, a gas-liquid separator is also provided on the refrigerant circulation loop, and the gas-liquid separator is located near the return port of the compressor.

[0018] In one embodiment, a heat exchange fan is also included. The first heat exchanger and the heat exchange fan are respectively disposed on opposite sides of the second heat exchanger. The first heat exchanger is disposed on the air inlet side of the second heat exchanger. The heat exchange fan is used to drive air to flow sequentially through the first heat exchanger and the second heat exchanger.

[0019] In one embodiment, both the first throttling device and the second throttling device are expansion valves. Attached Figure Description

[0020] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the structure of a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention;

[0022] Figure 2 This is a schematic diagram of the structure of a non-azeotropic mixed working fluid heat pump system according to another embodiment of the present invention;

[0023] Figure 3 This is a three-dimensional structural diagram of a heat exchange unit in a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention.

[0024] Figure 4 This is a right view of a heat exchange unit in a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention.

[0025] Explanation of reference numerals in the attached figures:

[0026] 1. Compressor; 2. Condenser; 3. First throttling device; 4. Liquid receiver; 41. Bypass branch; 42. Third refrigerant inlet; 43. Third refrigerant outlet; 44. Gaseous refrigerant outlet; 5. Switch valve; 6. Second throttling device; 7. Second heat exchanger; 71. Second refrigerant inlet; 72. Second refrigerant outlet; 8. Gas-liquid separator; 9. First heat exchanger; 91. First refrigerant inlet; 92. First refrigerant outlet; 10. Heat exchange fan; 11. Fins. Detailed Implementation

[0027] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0028] In the description of this utility model, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0029] According to embodiments of the present invention, such as Figure 1 , Figure 3 , Figure 4 As shown, a non-azeotropic mixed refrigerant heat pump system is provided, including: a compressor 1 and a refrigerant circulation loop connected to the compressor 1 and forming a loop. The refrigerant circulation loop is provided with a condenser 2, a first throttling device 3, a heat exchange assembly, and a second throttling device 6 in sequence along the refrigerant flow direction. The heat exchange assembly is provided with a first refrigerant inlet 91, a first refrigerant outlet 92, a second refrigerant inlet 71, and a second refrigerant outlet 72. The first refrigerant inlet 91 is connected to the first throttling device 3, the first refrigerant outlet 92 is connected to the inlet of the second throttling device 6, the second refrigerant inlet 71 is connected to the outlet of the second throttling device 6, and the second refrigerant outlet 72 is connected to the return port of the compressor 1.

[0030] In this embodiment, the arrows in the figure indicate the refrigerant flow direction. The refrigerant can specifically be a non-azeotropic mixture. The non-azeotropic mixture heat pump system provided in this embodiment can operate in heating mode and defrosting mode. When the non-azeotropic mixture heat pump system is in heating mode, the refrigerant flow direction within the compressor 1 is: condenser 2, first throttling device 3, heat exchange assembly, second throttling device 6, heat exchange assembly, and compressor 1.

[0031] The specific heating principle is as follows: Compressor 1 compresses low-pressure, low-temperature refrigerant gas into high-pressure, high-temperature gas. This high-pressure, high-temperature refrigerant gas enters condenser 2, where it exchanges heat with the medium to be heated, transferring heat to the indoor air or water to achieve the heating effect. After heat exchange, the refrigerant's temperature and pressure decrease, becoming a high-pressure, low-temperature gas-liquid mixture. This high-pressure, low-temperature gas-liquid mixture expands rapidly after being throttled by the first throttling device 3, causing a sharp drop in pressure and temperature, transforming into a low-pressure, low-temperature gas-liquid mixture. This low-pressure, low-temperature gas-liquid mixture then enters the heat exchange assembly through the first refrigerant inlet 91, where the low-temperature liquid working fluid is further cooled. It then flows out from the first refrigerant outlet 92 and passes through the second throttling device 6 for further throttling, further reducing the refrigerant's pressure and temperature. The non-azeotropic working fluid, after passing through the second throttling device 6, flows along the connecting pipeline and re-enters the heat exchange assembly through the second refrigerant inlet 71. This allows the liquid working fluid to absorb heat in the heat exchange assembly and evaporate into a low-temperature, low-pressure gas. Subsequently, it flows out from the second refrigerant outlet 72 of the heat exchange assembly and is drawn into the compressor 1, continuing the cycle through the compressor 1. This completes one heating cycle.

[0032] During the heating cycle, the refrigerant subcooling increases due to the influence of cold air. The cold air absorbs heat from the pipe between the first refrigerant inlet 91 and the first refrigerant outlet 92, causing the air temperature to rise. The heated air then flows through the pipe between the second refrigerant inlet 71 and the second refrigerant outlet 72. The low-temperature, low-pressure refrigerant inside the pipe absorbs the air temperature, thereby increasing the evaporation temperature of the refrigerant in the heat exchange assembly. In this application, part of the heat exchange assembly serves as a regenerator, and the other part serves as an evaporator, enabling the refrigerant flowing through the heat exchange assembly to achieve self-heat exchange. This allows for more complete liquefaction of the refrigerant exiting the condenser and more complete evaporation of the refrigerant flowing through the evaporator. The heat exchange components absorb heat from the air, and the compressor 1 performs work, causing both parts of energy to be released as heat in the condenser 2, raising the temperature of the water or air. The non-azeotropic working fluid undergoes two throttling and reheating processes from the outlet of the condenser 2 to the second refrigerant inlet 71, which reduces the throttling temperature difference between the condenser 2 and the heat exchange components compared to traditional heat pump systems, ultimately reducing throttling losses and improving heating performance. Thus, the non-azeotropic working fluid heat pump system provided by this invention can be applied to lower outdoor environments at the same evaporation temperature.

[0033] In one embodiment, the heat exchange assembly includes a first heat exchanger 9 and a second heat exchanger 7. The first heat exchanger 9 is provided with a first refrigerant inlet 91 and a first refrigerant outlet 92, and the second heat exchanger 7 is provided with a second refrigerant inlet 71 and a second refrigerant outlet 72. A condenser 2, a first throttling device 3, a first heat exchanger 9, a second throttling device 6 and a second heat exchanger 7 are sequentially arranged along the refrigerant flow direction in the refrigerant circulation loop.

[0034] In this embodiment, the heat exchange assembly consists of a first heat exchanger 9 and a second heat exchanger 7. During the heating cycle, the non-azeotropic working fluid is discharged from the compressor 1 and enters the condenser 2 for cooling. The cooled refrigerant enters the first throttling device 3 for throttling. The throttled refrigerant enters the first heat exchanger 9 through the first refrigerant inlet 91 for heat exchange. The refrigerant after heat exchange is discharged from the first refrigerant outlet 92 and enters the second throttling device 6. The refrigerant is throttled again by the second throttling device 6. After being throttled again, the refrigerant is transported along the connecting pipeline and enters the second heat exchanger 7 from the second refrigerant inlet 71, so that the second heat exchanger 7 exchanges heat with the refrigerant. The refrigerant after heat exchange is discharged from the second refrigerant outlet 72 and returns to the compressor 1 along the connecting pipeline to complete the heating cycle.

[0035] In one embodiment, the heat exchange assembly includes a plurality of fins 11 and a first flow channel and a second flow channel that are circumferentially disposed in the plurality of fins 11. The two ends of the first flow channel form a first refrigerant inlet 91 and a first refrigerant outlet 92, and the two ends of the second flow channel form a second refrigerant inlet 71 and a second refrigerant outlet 72.

[0036] In this embodiment, the fins 11 increase the contact area between the heat exchange component and the air. When the heat exchange component is working, the non-azeotropic working fluid flows in the first and second flow channels and exchanges heat with the outside air through the pipe wall. When the fins 11 contact the pipe surface, the air can fully contact the first and second flow channels, allowing more heat to be transferred, thereby effectively improving the heat exchange effect of the heat exchange component. Moreover, the fins 11 can turbulentize the air flowing through the heat exchange component, allowing the air to exchange heat with the surface of the fins 11 more frequently, further improving the heat exchange efficiency.

[0037] The specific heating principle is as follows: Compressor 1 compresses low-pressure, low-temperature refrigerant gas into high-pressure, high-temperature gas. This high-pressure, high-temperature refrigerant gas enters condenser 2, where it exchanges heat with the medium requiring heating, transferring heat to the indoor air or water to achieve the heating effect. After heat exchange, the refrigerant's temperature and pressure decrease, becoming a high-pressure, low-temperature gas-liquid mixture. This high-pressure, low-temperature gas-liquid mixture expands rapidly after being throttled by the first throttling device 3, causing a sharp drop in pressure and temperature, transforming into a low-pressure, low-temperature gas-liquid mixture. Then, this low-pressure, low-temperature gas-liquid mixture enters the first flow channel through the first refrigerant inlet 91 to further cool the low-temperature liquid working fluid in the first heat exchanger 9. It then flows out from the first refrigerant outlet 92 of the first flow channel and passes through the second throttling device 6 for further throttling, further reducing the refrigerant's pressure and temperature, preparing for heat exchange in the second heat exchanger 7. The non-azeotropic working fluid then flows along the connecting pipe through the second throttling device 6 and enters the second flow channel through the second refrigerant inlet 71. This allows the liquid working fluid to absorb heat in the second heat exchanger 7 and evaporate into a low-temperature, low-pressure gas. Subsequently, it flows out from the second refrigerant outlet 72 of the second heat exchanger 7 and is drawn into the compressor 1, continuing the cycle through the compressor 1. This completes one heating cycle.

[0038] During the heating cycle, the subcooling of the refrigerant increases due to the influence of cold air. The cold air absorbs heat from the first flow channel, causing its temperature to rise. The heated air then flows through the second flow channel, where the low-temperature, low-pressure refrigerant absorbs the air temperature, thereby increasing the evaporation temperature of the refrigerant within the heat exchange components. Furthermore, the first heat exchanger 9 and the second heat exchanger 7 share fins 11, allowing some of the heat from the first flow channel to be transferred to the second heat exchanger 7 via the fins 11, thus improving heat transfer efficiency.

[0039] Taking an outdoor ambient temperature of -30℃ and a condensing temperature of 45℃ as an example, since the second heat exchanger 7 requires temperature difference heat exchange, its evaporation temperature is set at -35℃. At this temperature, the difference between the condensing and evaporating temperatures is 45℃ - (-35℃) = 80℃. After adding the first heat exchanger 9, the outdoor air temperature after passing through it is generally -22℃. Therefore, the evaporation temperature can be set to -27℃. At this temperature, the difference between the condensing and evaporating temperatures is 45℃ - (-27℃) = 72℃, increasing the evaporation temperature by 8℃. This reduces the pressure ratio of compressor 1, thereby improving the energy efficiency ratio of the non-azeotropic mixed refrigerant heat pump system. Under the same evaporation temperature, the non-azeotropic mixed refrigerant heat pump system provided by this embodiment can be applied in even colder outdoor environments.

[0040] like Figure 2As shown, in one embodiment, it also includes a liquid reservoir 4, which is provided with a third refrigerant inlet 42 and a third refrigerant outlet 43. The third refrigerant inlet 42 is connected to the first throttling device 3, and the third refrigerant outlet 43 is connected to the first refrigerant inlet 91.

[0041] In this embodiment, the specific heating principle is as follows: Compressor 1 compresses low-pressure, low-temperature refrigerant gas into high-pressure, high-temperature gas. This high-pressure, high-temperature refrigerant gas enters condenser 2, where it exchanges heat with the medium requiring heating, transferring heat to the indoor air or water to achieve the heating effect. After heat exchange, the refrigerant's temperature and pressure decrease, transforming into a high-pressure, low-temperature gas-liquid mixture. This high-pressure, low-temperature gas-liquid mixture expands rapidly after being throttled by the first throttling device 3, causing a sharp drop in pressure and temperature, transforming into a low-pressure, low-temperature gas-liquid mixture. The low-pressure, low-temperature gas-liquid mixture then enters the reservoir 4 through the third refrigerant inlet 42, where it is separated into gaseous and liquid working fluids. The liquid working fluid continues to exit from the third refrigerant outlet 43 and flows along the connecting pipe to the first refrigerant inlet 91 connected to the reservoir 4, thus entering the first flow channel to further cool the low-temperature liquid working fluid in the first heat exchanger 9. It then flows out from the first refrigerant outlet 92 of the first flow channel and passes through the second throttling device 6 for further throttling, further reducing the pressure and temperature of the refrigerant and preparing for heat exchange in the second heat exchanger 7. The non-azeotropic mixture, after passing through the second throttling device 6, flows along the connecting pipe and into the second flow channel through the second refrigerant inlet 71, allowing the liquid working fluid to absorb heat in the second heat exchanger 7 and evaporate into a low-temperature, low-pressure gas. This gas then flows out from the second refrigerant outlet 72 of the second heat exchanger 7 and is drawn into the compressor 1, continuing the cycle through the compressor 1. This completes one heating cycle.

[0042] Specifically, taking a condenser 2 outlet temperature of 45℃ and a second heat exchanger 7 inlet temperature of -35℃ as an example, the throttling temperature difference of a traditional heat pump system reaches 80℃. However, the non-azeotropic mixed working fluid heat pump system provided in this embodiment typically has a temperature of around 20℃ after the first-stage throttling and around -30℃ after the first flow channel. That is, the first-stage throttling temperature difference is 45℃ - 20℃ = 25℃, the second-stage throttling temperature difference is -30℃ - (-35℃) = 5℃, and the total throttling temperature difference is 25℃ + 5℃ = 30℃. Therefore, the total throttling temperature difference of the non-azeotropic mixed working fluid heat pump system provided in this embodiment is reduced by 80℃ - 30℃ = 50℃ compared to the traditional system, thereby significantly reducing the throttling temperature difference from condenser 2 to second heat exchanger 7, greatly reducing throttling losses, and thus improving the heating performance of the non-azeotropic mixed working fluid heat pump system.

[0043] When non-azeotropic working fluids are used in traditional heat pump systems, reverse defrosting is usually required using a four-way valve, which results in a complex flow path for the heat pump system and low defrosting efficiency.

[0044] In one embodiment, the liquid receiver 4 is further provided with a gaseous refrigerant outlet 44, which is connected to the second refrigerant inlet 71 via a bypass branch 41. Furthermore, a switching valve 5 is provided on the bypass branch 41.

[0045] In this embodiment, due to the low ambient temperature, the unit's evaporation capacity is weakened, therefore, the second heat exchanger 7 may frost over in low-temperature environments. When the non-azeotropic mixed refrigerant heat pump system is in defrost mode, the gaseous refrigerant in the non-azeotropic mixed refrigerant heat pump system is discharged through the gaseous refrigerant outlet 44 and enters the bypass branch 41. Therefore, in the refrigerant circulation loop, the refrigerant flow direction within the compressor 1 is: condenser 2, first throttling device 3, liquid receiver 4, switching valve 5, second heat exchanger 7, compressor 1.

[0046] The specific defrosting working principle is as follows: When the non-azeotropic refrigerant heat pump system defrosts, the switch valve 5 is opened, and the opening degree of the first throttling device 3 is maximized. The compressor 1 compresses the low-pressure, low-temperature refrigerant gas into a high-pressure, high-temperature gas. The high-pressure, high-temperature refrigerant gas enters the condenser 2, where it exchanges heat with the medium to be heated (such as indoor air or water), transferring heat to the indoor air or water to achieve a heating effect. After heat exchange, the refrigerant's own temperature and pressure decrease, becoming a high-pressure, low-temperature gas-liquid mixture. During the defrosting cycle, because the opening degree of the first throttling device 3 is adjusted to the maximum, the throttling effect is poor. Therefore, the temperature and pressure of the non-azeotropic refrigerant mixture remain high after flowing through the first throttling device 3, and most of the low-boiling-point refrigerant is in a gaseous state. The gas-liquid mixture enters the receiver 4 through the third refrigerant inlet 42, where it is separated into gaseous and liquid refrigerant. In the receiver 4, most of the gaseous refrigerant exits from the gaseous refrigerant outlet 44 into the bypass branch 41, and is then transported to the second heat exchanger 7 for condensation via the switching valve 5. Subsequently, it is drawn into the compressor 1 and continues to circulate through the compressor 1. This completes one defrosting cycle.

[0047] When the gaseous refrigerant condenses in the second heat exchanger 7, it releases a large amount of heat for defrosting. Due to the characteristics of non-azeotropic working fluids, the low-boiling-point components in the gaseous working fluid constitute a larger proportion. This means that the refrigerant components actually participating in the entire defrosting cycle have a larger proportion of low-boiling-point components compared to the heating cycle. Furthermore, because the density of the low-boiling-point working fluid is greater than that of the high-boiling-point working fluid, the high pressure and mass flow rate of the working fluid increase during the defrosting cycle, ultimately resulting in greater work done by the compressor 1. This means that the condensation heat dissipation during defrosting in the second heat exchanger 7 is greater, effectively improving the defrosting effect of the non-azeotropic working fluid heat pump system. Moreover, the absence of a four-way valve for reverse heat exchange defrosting simplifies the flow path of the non-azeotropic working fluid heat pump system, thereby reducing costs.

[0048] In one embodiment, the switching valve 5 is a solenoid valve. The solenoid valve can precisely control the valve opening degree via electrical signals, thereby regulating parameters such as fluid flow rate and pressure. This helps improve the stability and control accuracy of the non-azeotropic heat pump system, enabling it to more accurately meet the operating requirements under different conditions. Furthermore, the solenoid valve has a fast response speed, completing opening and closing actions in a short time. When the operating state of the non-azeotropic heat pump system changes, the solenoid valve can react quickly and adjust the operating mode of the heat pump system in a timely manner, thereby improving the dynamic performance and regulation capability of the heat pump system.

[0049] In one embodiment, a gas-liquid separator 8 is also provided on the refrigerant circulation loop, and the gas-liquid separator 8 is located near the return port of the compressor 1.

[0050] In this embodiment, the gas-liquid separator 8 can separate the liquid refrigerant from the non-azeotropic working fluid returned from the second heat exchanger 7, preventing the liquid working fluid from directly entering the compressor 1. Liquid refrigerant entering the compressor 1 may cause liquid slugging, meaning that when the liquid is compressed inside the compressor 1, because the liquid is incompressible, it will exert a huge impact force on the compressor 1's components, potentially damaging valves, pistons, and other parts, and in severe cases, even rendering the compressor 1 unusable. Furthermore, by separating the gas and liquid, the flow rate of the gaseous working fluid entering the compressor 1 becomes more stable and uniform, helping the compressor 1 to operate more efficiently, thereby improving the performance and energy efficiency ratio of the entire heat pump system.

[0051] In one embodiment, a heat exchange fan 10 is also included. The first heat exchanger 9 and the heat exchange fan 10 are respectively disposed on opposite sides of the second heat exchanger 7. The first heat exchanger 9 is disposed on the air inlet side of the second heat exchanger 7. The heat exchange fan 10 is used to drive air to flow sequentially through the first heat exchanger 9 and the second heat exchanger 7.

[0052] In this embodiment, the heat exchange fan 10 is used to drive airflow, allowing air to flow continuously and evenly across the surfaces of the first heat exchanger 9 and the second heat exchanger 7, accelerating heat transfer between the air and the first and second heat exchangers 9 and 7. By placing the first heat exchanger 9 and the heat exchange fan 10 on opposite sides of the second heat exchanger 7, and placing the first heat exchanger 9 on the air inlet side of the second heat exchanger 7, the first and second heat exchangers 9 and 7 share the same heat exchange fan 10. When cold air flows, it first undergoes preliminary heat exchange through the first heat exchanger 9, absorbing heat from the first flow channel of the first heat exchanger 9, thus raising the air temperature. Under the action of the heat exchange fan 10, the heated air then flows through the second flow channel of the second heat exchanger 7, allowing the low-temperature, low-pressure refrigerant inside the second flow channel to absorb the air temperature, thereby increasing the evaporation temperature of the refrigerant within the heat exchange assembly. Furthermore, by delivering air evenly, the heat exchange fan 10 helps maintain a uniform surface temperature of the second heat exchanger 7, reducing the possibility of frost formation or making frost formation more uniform, thereby extending the effective working time of the second heat exchanger 7, reducing the defrosting frequency, and improving the overall operating efficiency of the non-azeotropic working fluid heat pump system.

[0053] In one embodiment, both the first throttling device 3 and the second throttling device 6 are expansion valves. The first throttling device 3 and the second throttling device 6 are electrically connected to a controller, which controls the start and stop of the first throttling device 3 and the second throttling device 6, and controls the opening degree of the first throttling device 3 and the second throttling device 6 according to the operating requirements of different working conditions, so as to control the flow rate of refrigerant.

[0054] In the specific implementation of the above embodiments, the technical features can be combined in any non-contradictory way. For the sake of brevity, not all possible combinations of the above technical features are described. However, as long as the combination of these technical features is not contradictory, it should be considered to be within the scope of this specification.

[0055] The specific embodiments described above are merely illustrative of several implementations of this utility model, and while the descriptions are detailed, they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model patent should be determined by the appended claims.

Claims

1. A non-azeotropic mixed working fluid heat pump system, characterized in that, include: The compressor (1) and the refrigerant circulation loop connected to the compressor (1) and forming a loop are provided in sequence along the refrigerant flow direction, including a condenser (2), a first throttling device (3), a heat exchange assembly, and a second throttling device (6); The heat exchange assembly is provided with a first refrigerant inlet (91), a first refrigerant outlet (92), a second refrigerant inlet (71) and a second refrigerant outlet (72). The first refrigerant inlet (91) is connected to the first throttling device (3), the first refrigerant outlet (92) is connected to the inlet of the second throttling device (6), the second refrigerant inlet (71) is connected to the outlet of the second throttling device (6), and the second refrigerant outlet (72) is connected to the return port of the compressor (1).

2. The non-azeotropic mixed working fluid heat pump system according to claim 1, characterized in that, The heat exchange assembly includes a first heat exchanger (9) and a second heat exchanger (7). The first heat exchanger (9) is provided with a first refrigerant inlet (91) and a first refrigerant outlet (92). The second heat exchanger (7) is provided with a second refrigerant inlet (71) and a second refrigerant outlet (72). The condenser (2), the first throttling device (3), the first heat exchanger (9), the second throttling device (6) and the second heat exchanger (7) are arranged sequentially along the refrigerant flow direction in the refrigerant circulation loop.

3. The non-azeotropic mixed working fluid heat pump system according to claim 1, characterized in that, The heat exchange assembly includes a plurality of fins (11) and a first flow channel and a second flow channel that meander through the plurality of fins (11). The first flow channel forms a first refrigerant inlet (91) and a first refrigerant outlet (92) at both ends, and the second flow channel forms a second refrigerant inlet (71) and a second refrigerant outlet (72) at both ends.

4. The non-azeotropic mixed working fluid heat pump system according to any one of claims 1-3, characterized in that, It also includes a liquid reservoir (4), which has a third refrigerant inlet (42) and a third refrigerant outlet (43). The third refrigerant inlet (42) is connected to the first throttling device (3), and the third refrigerant outlet (43) is connected to the first refrigerant inlet (91).

5. The non-azeotropic mixed working fluid heat pump system according to claim 4, characterized in that, The liquid reservoir (4) is also provided with a gaseous refrigerant outlet (44), which is connected to the second refrigerant inlet (71) through a bypass branch (41).

6. The non-azeotropic mixed working fluid heat pump system according to claim 5, characterized in that, The bypass branch (41) is equipped with a switch valve (5).

7. The non-azeotropic mixed working fluid heat pump system according to claim 6, characterized in that, The switching valve (5) is a solenoid valve.

8. The non-azeotropic mixed working fluid heat pump system according to any one of claims 1-3, characterized in that, The refrigerant circulation loop is also equipped with a gas-liquid separator (8), which is located near the return port of the compressor (1).

9. The non-azeotropic mixed working fluid heat pump system according to claim 2, characterized in that, It also includes a heat exchange fan (10), the first heat exchanger (9) and the heat exchange fan (10) are respectively arranged on opposite sides of the second heat exchanger (7), the first heat exchanger (9) is arranged on the air inlet side of the second heat exchanger (7), and the heat exchange fan (10) is used to drive air to flow through the first heat exchanger (9) and the second heat exchanger (7) in sequence.

10. The non-azeotropic mixed working fluid heat pump system according to any one of claims 1-3, characterized in that, Both the first throttling device (3) and the second throttling device (6) are expansion valves.

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