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 heat pump loop connected with the compressor to form a loop, and a first condenser, a second condenser, a first throttling device and an evaporator are sequentially arranged on the heat pump loop in the refrigerant flow direction. And the heat regenerator comprises a first heat exchange channel and a second heat exchange channel, the first heat exchange channel is connected between the second condenser and the first throttling device, and the second heat exchange channel is connected between the evaporator and the compressor. By means of two-stage staged condensation, it is ensured that the mixed working medium can be liquefied more sufficiently, so that all latent heat is released, meanwhile, the mixed working medium is gasified more sufficiently in the evaporator to absorb more heat, and the heating capacity and energy efficiency of the system are 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] The application of heat pump technology has expanded from the heating and cooling needs of household appliances to a wide range of heating scenarios in buildings, industries, and other fields. However, traditional heat pump systems mostly use a single working fluid, and their performance is limited to a fixed operating temperature range. For example, in the building sector, heating needs at ultra-low ambient temperatures or the industrial sector's requirements for ultra-high water temperatures are difficult to achieve with traditional single working fluids due to the large temperature range between the heat source and the heat sink.

[0003] Non-azeotropic working fluids can expand the operating temperature range of the system and adapt to the needs of scenarios with large temperature differences by flexibly configuring the component ratios. However, due to the large differences in the boiling points of the working fluid components, for existing heat pump systems, the working fluid components may not be completely liquefied in the condenser or completely vaporized in the evaporator, resulting in uneven component distribution within the system and affecting the efficiency of the thermodynamic cycle. Utility Model Content

[0004] The first technical problem solved by this invention is to provide a non-azeotropic mixed working fluid heat pump system, which effectively solves the problem of low thermodynamic cycle efficiency of heat pump systems with mixed working fluid components in related technologies.

[0005] The first technical problem mentioned above is solved by the following technical solution:

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

[0007] The compressor and a heat pump circuit connected to the compressor to form a loop, wherein a first condenser, a second condenser, a first throttling device and an evaporator are sequentially arranged along the refrigerant flow direction in the heat pump circuit; a regenerator, including a first heat exchange channel and a second heat exchange channel that exchange heat with each other, wherein the first heat exchange channel is connected between the outlet of the second condenser and the inlet of the first throttling device, and the second heat exchange channel is connected between the outlet of the evaporator and the return port of the compressor.

[0008] Compared with the prior art, the non-azeotropic mixed working fluid heat pump system of this utility model has the following advantages: On the one hand, this utility model ensures that both the high-boiling-point and low-boiling-point components of the mixed working fluid can be liquefied more fully through the staged condensation of the first and second condensers, thereby releasing all latent heat and improving the heating capacity and energy efficiency of the system. At the same time, it allows the mixed working fluid to be more fully vaporized in the evaporator to absorb more heat. On the other hand, this utility model is equipped with a regenerator, which further absorbs the temperature of the refrigerant before throttling through the reverse heat exchange between the first and second heat exchange channels, thereby reducing throttling losses and making the refrigerant liquefy more completely after throttling. As a result, it absorbs more heat when flowing through the evaporator, further improving the working efficiency of the heat pump system.

[0009] In one embodiment, the non-azeotropic mixed working fluid heat pump system further includes:

[0010] The liquid receiver is provided with a refrigerant inlet and a first refrigerant outlet. The refrigerant inlet is connected to the outlet of the first condenser, and the first refrigerant outlet is connected to the inlet of the second condenser.

[0011] In one embodiment, the non-azeotropic mixed working fluid heat pump system further includes:

[0012] The second throttling device has its inlet connected to the outlet of the first condenser, and its outlet connected to the refrigerant inlet of the liquid receiver.

[0013] In one embodiment, both the first throttling device and the second throttling device are expansion valves.

[0014] In one embodiment, the non-azeotropic mixed working fluid heat pump system further includes a defrosting branch, the liquid receiver is also provided with a second refrigerant outlet, the two ends of the defrosting branch are respectively connected to the second refrigerant outlet and the inlet of the evaporator, and the defrosting branch is provided with an electrically controlled valve with adjustable opening.

[0015] In one embodiment, the second refrigerant outlet is located at the top of the liquid reservoir, and the first refrigerant outlet is located at the bottom of the liquid reservoir.

[0016] In one embodiment, the non-azeotropic mixed working fluid heat pump system further includes:

[0017] The first water circulation loop has its two ends connected to the two ends of the water-side channel of the first condenser, and the first water circulation loop is provided with at least one first water-using device connected to the water-side channel of the first condenser.

[0018] And / or, a second water circulation loop, the two ends of which are connected to the two ends of the water-side channel of the second condenser, and the second water circulation loop is provided with at least one second water-using device connected to the water-side channel of the second condenser.

[0019] In one embodiment, a first water pump is provided on the first water circulation loop; and / or, a second water pump is provided on the second water circulation loop.

[0020] In one embodiment, the non-azeotropic mixed working fluid heat pump system further includes:

[0021] An evaporator fan is used to drive air through the evaporator.

[0022] In one embodiment, the heat pump circuit is further provided with a gas-liquid separator, which is located near the return port of the compressor. Attached Figure Description

[0023] 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.

[0024] Figure 1 This is a schematic diagram of the structure of the non-azeotropic mixed working fluid heat pump system in conventional heating mode according to an embodiment of the present utility model.

[0025] Figure 2 This is a schematic diagram of the non-azeotropic mixed working fluid heat pump system in defrosting mode according to an embodiment of the present invention;

[0026] Figure 3 This is a pressure-enthalpy diagram of a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention.

[0027] Explanation of reference numerals in the attached figures:

[0028] 1. Compressor; 11. Gas return port; 2. First condenser; 3. Second throttling device; 4. Liquid receiver; 41. Refrigerant inlet; 42. First refrigerant outlet; 43. Second refrigerant outlet;

[0029] 5. Solenoid valve; 6. Regenerator; 61. First heat exchange channel; 62. Second heat exchange channel; 7. First throttling device; 8. Evaporator; 9. Gas-liquid separator; 10. Second condenser; 20. Defrosting branch; 30. Electrically controlled valve; 40. First water circulation loop; 50. First water pump; 60. Second water circulation loop; 70. Second water pump; 80. Evaporator fan. Detailed Implementation

[0030] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0031] In the description of this application, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application 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 limitations on this application.

[0032] 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 technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0033] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" 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 between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0034] The following description, with reference to the accompanying drawings, illustrates a non-azeotropic mixed working fluid heat pump system provided by this invention.

[0035] like Figure 1 and Figure 2As shown, the non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention includes a compressor 1 and a heat pump circuit connected to the compressor 1 and forming a loop. A first condenser 2, a second condenser 10, a first throttling device 7 and an evaporator 8 are sequentially arranged along the refrigerant flow direction on the heat pump circuit.

[0036] The regenerator 6 includes a first heat exchange channel 61 and a second heat exchange channel 62 that exchange heat with each other. The first heat exchange channel 61 is connected between the outlet of the second condenser 10 and the inlet of the first throttling device 7, and the second heat exchange channel 62 is connected between the outlet of the evaporator 8 and the return gas port 11 of the compressor 1.

[0037] The specific structural composition of the non-azeotropic mixed working fluid heat pump system according to an embodiment of this utility model is described below:

[0038] Compressor 1 is used to compress low-pressure gaseous refrigerant, transforming it into a high-temperature, high-pressure gas. The exhaust port of compressor 1 is connected to the inlet of the first condenser 2, and the return port 11 is connected to the outlet of the evaporator 8 and the outlet of the second heat exchange channel 62 of the regenerator 6. The outlet of the first condenser 2 is connected to the inlet of the second condenser 10, used for heat exchange with the external water circulation loop to condense the high-temperature, high-pressure refrigerant gas. The outlet of the second condenser 10 is connected to the inlet of the first throttling device 7, and simultaneously connected to the regenerator 6 through the first heat exchange channel 61. It can be understood that the second condenser 10, as the second stage of a two-stage condenser, can further reduce the refrigerant temperature, resulting in more complete refrigerant liquefaction. The first throttling device 7 is located downstream of the second condenser 10, and its outlet is connected to the inlet of the evaporator 8. By throttling and reducing pressure, the first throttling device 7 can further lower the refrigerant temperature, providing a low-temperature working fluid for the evaporator 8.

[0039] The outlet of evaporator 8 is connected to the inlet of the second heat exchange channel 62 of regenerator 6, and then returns to compressor 1 via gas-liquid separator 9. Evaporator 8 is used for heat exchange with the air side, absorbing ambient heat to evaporate the refrigerant into a low-pressure gaseous state. Regenerator 6 contains two independent heat exchange channels. The first heat exchange channel 61 is connected between the outlet of the second condenser 10 and the inlet of the first throttling device 7, used to transport the refrigerant before throttling; while the second heat exchange channel 62 is connected between the outlet of evaporator 8 and the return port 11 of compressor 1, used to transport the evaporated low-pressure gaseous refrigerant. It can be understood that regenerator 6 can further absorb the refrigerant temperature before throttling through heat exchange between the channels, thereby reducing throttling losses.

[0040] Based on the above specific structure, the specific working principle of the system of this utility model is as follows:

[0041] Firstly, the system of this invention, by setting up a first condenser 2 and a second condenser 10, can achieve a synergistic effect of two-stage condensation. Specifically, the two-stage condensation releases heat from the refrigerant in stages, avoiding incomplete liquefaction of refrigerant components due to insufficient temperature difference in a single condenser. The second condenser 10 further reduces the refrigerant temperature, ensuring sufficient liquefaction and improving system stability. Secondly, in the system of this invention, the refrigerant in the first heat exchange channel 61 and the refrigerant in the second heat exchange channel 62 exchange heat indirectly. At this time, the refrigerant in the second heat exchange channel 62 absorbs heat from the gas-liquid mixed refrigerant in the first heat exchange channel 61, reducing the temperature of the refrigerant before throttling, reducing energy loss during throttling, and simultaneously increasing the temperature of the refrigerant before entering the compressor 1, thereby increasing its superheat before entering the compressor 1 and reducing the risk of droplet carryover. It should also be noted that the system of this invention can also alleviate the component separation problem of non-azeotropic working fluids during condensation or evaporation by regenerating and balancing the temperature gradient of the refrigerant components, thereby improving the system's circulation efficiency.

[0042] Furthermore, the specific working process of the non-azeotropic mixed working fluid heat pump system of this utility model is as follows:

[0043] First, the high-temperature, high-pressure gaseous refrigerant discharged from compressor 1 enters the first condenser 2, releasing heat to the first water circulation loop 40, achieving the first condensation of the refrigerant. Then, the refrigerant enters the second condenser 10 for a second condensation, further condensing into a liquid state. Subsequently, the refrigerant flows through the first heat exchange channel 61 of the regenerator 6, exchanging heat with the low-pressure gaseous refrigerant in the second heat exchange channel 62, further reducing the refrigerant temperature. After throttling and depressurization, the refrigerant's temperature drops below the evaporation temperature and enters the evaporator 8. In the evaporator 8, the refrigerant absorbs heat from the environment and evaporates into a low-pressure gaseous state, then enters the second heat exchange channel 62 of the regenerator 6, further absorbing heat from the refrigerant in the first heat exchange channel 61. After its own temperature increases, it enters the gas-liquid separator 9. Finally, the separated pure gaseous refrigerant returns to compressor 1, completing the cycle.

[0044] In summary, this invention optimizes the refrigerant condensation process through a two-stage condensation process, combined with the heat recovery function of the regenerator 6, thus solving the efficiency loss problem caused by component separation in non-azeotropic working fluid systems. The dual-condensation structure ensures complete refrigerant liquefaction, while the regenerator 6 reduces energy loss through heat exchange, ultimately improving the system's heating performance and stability.

[0045] Specifically, on the one hand, this invention, through the series connection of the first condenser 2 and the second condenser 10, reduces the refrigerant temperature in stages, ensuring that both the high-boiling-point and low-boiling-point components of the mixed working fluid can be liquefied more fully. This avoids the refrigerant component separation problem caused by temperature slippage in a single-stage condenser, reduces heat matching losses between the condenser and the evaporator 8, and significantly improves the system's thermal efficiency. Simultaneously, it allows the mixed working fluid to evaporate more fully in the evaporator 8 to absorb more heat. On the other hand, the regenerator 6, through heat exchange between the first heat exchange channel 61 and the second heat exchange channel 62, further reduces the refrigerant temperature before throttling, thereby reducing throttling losses. Furthermore, the two-stage condensation ensures that the refrigerant is completely liquefied before throttling, avoiding the problem of gas-liquid coexistence at the evaporator 8 inlet due to temperature differences in non-azeotropic working fluids, and reducing fluctuations in the heat exchange efficiency of the evaporator 8. The regenerator 6 reduces energy loss through heat exchange, ultimately improving the system's heating performance and stability.

[0046] like Figure 1 As shown, according to some embodiments of the present invention, the non-azeotropic mixed working fluid heat pump system further includes a liquid receiver 4.

[0047] The liquid receiver 4 is provided with a refrigerant inlet 41 and a first refrigerant outlet 42. The refrigerant inlet 41 is connected to the outlet of the first condenser 2, and the first refrigerant outlet 42 is connected to the inlet of the second condenser 10.

[0048] In this embodiment, the liquid receiver 4 is located between the first condenser 2 and the second condenser 10, and can serve as a buffer container for the refrigerant. Specifically, the refrigerant inlet 41 of the liquid receiver 4 is directly connected to the outlet of the first condenser 2, thereby receiving the refrigerant output from it; the first refrigerant outlet 42 of the liquid receiver 4 is connected to the inlet of the second condenser 10, thereby supplying refrigerant to the second condenser 10.

[0049] The refrigerant flow path within the system based on receiver 4 is as follows:

[0050] The high-temperature, high-pressure gaseous refrigerant undergoes initial condensation in the first condenser 2 and then enters the receiver 4. The receiver 4 stores refrigerant to cope with system load changes, such as fluctuations in demand from the evaporator 8, thereby preventing a decrease in condensation efficiency in the second condenser 10 due to uneven liquid supply. The receiver 4 supplies a gas-liquid mixture of refrigerant to the second condenser 10 through the first refrigerant outlet 42, ensuring further condensation in the second condenser 10 at low temperatures, ultimately achieving complete refrigerant liquefaction and resolving the problem of insufficient condensation caused by temperature glide in non-azeotropic refrigerants. In this way, the receiver 4 can dynamically adjust the amount of refrigerant stored, thereby regulating the condensation pressure within the system.

[0051] In some specific embodiments, the liquid reservoir 4 can be a high-pressure, low-temperature resistant metal container, and the interior can be coated with an anti-corrosion coating.

[0052] like Figure 1 As shown, according to some embodiments of the present invention, the non-azeotropic mixed working fluid heat pump system further includes a second throttling device 3. The inlet of the second throttling device 3 is connected to the outlet of the first condenser 2, and the outlet of the second throttling device 3 is connected to the refrigerant inlet 41 of the liquid receiver 4.

[0053] In this embodiment, the second throttling device 3 is located between the first condenser 2 and the liquid receiver 4, serving as a refrigerant flow and pressure regulating device. The inlet of the second throttling device 3 is directly connected to the outlet of the first condenser 2, receiving the refrigerant output from it, while its outlet is connected to the refrigerant inlet 41 of the liquid receiver 4, thereby providing the liquid receiver 4 with pressure-regulated refrigerant.

[0054] It is understandable that before the refrigerant enters the receiver 4, the second throttling device 3 can further control the refrigerant state by throttling and reducing pressure, ensuring that the inlet pressure and temperature of the receiver 4 meet the requirements of two-stage condensation.

[0055] Specifically, based on the second throttling device 3, the refrigerant flow path within this system is as follows: the high-temperature, high-pressure gaseous refrigerant condenses in the first condenser 2 and then enters the second throttling device 3. At this time, the second throttling device 3 can adjust the refrigerant pressure from the high-pressure state of the first condenser 2 to the working pressure required by the liquid receiver 4 by throttling and reducing pressure.

[0056] It should also be noted that by setting the second throttling device 3 and the first throttling device 7, this utility model can form a two-stage throttling structure in the system. Based on this two-stage throttling structure, firstly, in terms of energy efficiency, the two-stage throttling structure can decompose the total pressure difference between the condenser and evaporator 8 into two stages of gradual release, reducing the drastic energy loss of single-stage throttling, increasing the cooling capacity per unit mass, and improving system performance. Secondly, for non-azeotropic working fluids, the two-stage throttling can effectively suppress component separation caused by temperature slippage through staged pressure regulation.

[0057] Specifically, the first-stage throttling initially reduces the pressure of the refrigerant before it enters the intermediate liquid receiver 4, ensuring that the refrigerant is fully subcooled in the second condenser 10; the second-stage throttling precisely controls the inlet temperature of the evaporator 8, while reducing the local enrichment of high-boiling-point components during the throttling process.

[0058] Furthermore, both the first throttling device 7 and the second throttling device 3 are expansion valves. For example, the first throttling device 7 and the second throttling device 3 can be thermostatic expansion valves or electronic expansion valves. Of course, the above embodiment is only one of many embodiments of this utility model and does not constitute a specific limitation on the above throttling device.

[0059] like Figure 1As shown, according to some embodiments of the present invention, a gas-liquid separator 9 is also provided on the heat pump circuit, and the gas-liquid separator 9 is located near the return gas port 11 of the compressor 1.

[0060] like Figure 2 As shown, according to some embodiments of the present invention, the non-azeotropic mixed working fluid heat pump system further includes a defrosting branch 20, and the liquid receiver 4 is also provided with a second refrigerant outlet 43. The two ends of the defrosting branch 20 are respectively connected to the second refrigerant outlet 43 and the inlet of the evaporator 8. The defrosting branch 20 is provided with an electrically controlled valve 30 with adjustable opening.

[0061] In this embodiment, the system of this invention also includes a defrosting branch 20. It is understood that the refrigerant temperature in the receiver 4 is relatively high, and its direct entry into the evaporator 8 can quickly provide heat to melt the frost layer. Therefore, in defrosting mode, high-pressure gaseous refrigerant can be drawn from the receiver 4. This high-temperature, high-pressure refrigerant bypasses the second condenser 10 and the first throttling device 7, and is directly delivered to the inlet of the evaporator 8 through the defrosting branch 20. Its latent heat of superheat is used to quickly melt the frost layer, thereby achieving defrosting of the evaporator 8. Furthermore, in defrosting mode, the system can dynamically control the refrigerant flow rate by adjusting the opening of the electronically controlled valve 30 to achieve precise defrosting.

[0062] In the normal heating cycle path, that is, in the non-defrosting state, the electronically controlled valve 30 remains closed to prevent the refrigerant from flowing directly to the evaporator 8. At this time, the normal flow path of the refrigerant in the system is as follows: the refrigerant starts from the compressor 1, flows through the first condenser 2, the second throttling device 3, and the liquid receiver 4 in sequence. After the high temperature and high pressure refrigerant flows out from the first refrigerant outlet 42 of the liquid receiver 4, it further passes through the second condenser 10, the first throttling device 7, the evaporator 8, and the gas-liquid separator 9 and finally flows back to the compressor 1.

[0063] When defrosting is required, the electronically controlled valve 30 remains open, and the first throttling device 7 is closed, allowing refrigerant to flow to the evaporator 8. The defrosting flow path of the refrigerant in the system is as follows: The refrigerant starts from the compressor 1, flows sequentially through the first condenser 2, the liquid receiver 4, and the second throttling device 3. After the high-temperature, high-pressure refrigerant flows out from the second refrigerant outlet 43 of the liquid receiver 4, it further enters the defrosting branch 20. After passing through the electronically controlled valve 30, it defrosts the evaporator 8, then passes through the gas-liquid separator 9 and finally flows back to the compressor 1. It can be understood that when the high-temperature, high-pressure gaseous refrigerant enters the evaporator 8, the surface temperature of the evaporator 8 increases significantly, thereby achieving the defrosting process.

[0064] In this way, the system of this invention directly introduces high-pressure gaseous refrigerant into the evaporator 8 through the second refrigerant outlet 43 of the liquid receiver 4 and the dedicated defrosting branch 20, utilizing its latent heat of superheat for rapid defrosting. Compared with traditional four-way valve reversing or electric heating structures, the defrosting path design of this invention is simpler and reduces indoor temperature fluctuations or additional energy consumption.

[0065] like Figure 1 As shown, the second refrigerant outlet 43 is further disposed at the top of the liquid receiver 4, and the first refrigerant outlet 42 is disposed at the bottom of the liquid receiver 4.

[0066] It is understood that the first refrigerant outlet 42 is located at the bottom of the receiver 4 and is mainly responsible for outputting the gas-liquid mixed refrigerant. In normal operation, the compressor 1 compresses the gaseous refrigerant into a high-temperature, high-pressure gas, which is then sent to the first condenser 2 for cooling and condensation into a gas-liquid mixed refrigerant. The gas-liquid mixed refrigerant can flow out through the first refrigerant outlet 42 at the bottom of the receiver 4, be further condensed by the second condenser 10, and then enter the evaporator 8 to absorb heat after being depressurized by the first throttling device 7, thus completing the heating cycle.

[0067] The second refrigerant outlet 43 is located at the top of the receiver 4 and is mainly used for operation in defrost mode. When the system detects that defrosting is required, the electronically controlled valve 30 opens, allowing superheated gas from the top of the receiver 4 to flow directly to the evaporator 8. Since this superheated gas does not pass through the throttling device, it can maintain a high temperature and pressure, effectively heating the surface of the evaporator 8 and quickly melting the frost layer.

[0068] In this way, by using the superheated gas at the top of the reservoir 4, sufficient heat can be provided directly and efficiently to melt the frost layer, reducing defrosting time and improving the overall efficiency of the system.

[0069] like Figure 1 As shown, according to some embodiments of the present invention, the non-azeotropic mixed working fluid heat pump system further includes at least one of a first water circulation loop 40 and a second water circulation loop 60.

[0070] The two ends of the first water circulation loop 40 are connected to the two ends of the water side channel of the first condenser 2. The first water circulation loop 40 is provided with at least one first water-using device connected to the water side channel of the first condenser 2.

[0071] The two ends of the second water circulation loop 60 are connected to the two ends of the water side channel of the second condenser 10, and the second water circulation loop 60 is provided with at least one second water-using device connected to the water side channel of the second condenser 10.

[0072] like Figure 1 As shown, the first water circulation loop 40 is further provided with a first water pump 50; and / or the second water circulation loop 60 is provided with a second water pump 70.

[0073] In the above embodiment, the first water circulation loop 40 includes a water-side channel of the first condenser 2, a first water-using device, and a first water pump 50. The water-side channel of the first condenser 2 is used to absorb heat from the refrigerant. The first water-using device can be an application device such as a radiator or a hot water supply system. The first water pump 50 is used to enhance the power of the water circulation, ensuring that water can flow smoothly through the entire loop.

[0074] Cold water, driven by the first water pump 50, enters the water-side channel from one end of the first condenser 2. After absorbing heat released during the condensation process within the channel, it flows out from the other end. The heated water is then transported to the first water-using device, where it undergoes heat exchange or is used directly, for example, to provide domestic hot water. Afterward, the water returns to the first condenser 2 to restart the circulation process.

[0075] The second water circulation loop 60 includes a water-side channel of the second condenser 10, a second water-using device, and a second water pump 70. The water-side channel of the second condenser 10 serves different temperature requirements or application scenarios. The second water-using device is similar to the first water-using device, but its application scenario can differ, such as industrial heating processes or other specific needs. The second water pump 70 is used to drive the water flow in the second water circulation loop 60 to ensure the normal operation of the system.

[0076] The second water circulation loop 60 operates similarly to the first water circulation loop 40. Cold water is driven by the second water pump 70 and flows through the water-side channel of the second condenser 10 to absorb heat. Subsequently, hot water flows to the second water-using device to complete the corresponding heat exchange task or is used directly, and finally returns to the second condenser 10 to prepare for the next cycle.

[0077] As the two water circulation loops are independent of each other, their respective parameters, such as flow rate and temperature, can be adjusted individually to meet the needs of different water-using devices. This design also allows for customized configuration of each loop, making it suitable for various application scenarios. For example, the first water circulation loop 40 can be used for domestic water use in a residence, while the second water circulation loop 60 can be used for water needs in a garage.

[0078] In summary, through the above design, this utility model can not only effectively manage and distribute the heat generated by the condenser, but also flexibly adapt to various water demand, thereby improving the overall energy utilization efficiency.

[0079] like Figure 1 As shown, according to some embodiments of the present invention, the non-azeotropic mixed working fluid heat pump system further includes an evaporator fan 80, which is used to drive air to flow through the evaporator 8.

[0080] The following is a specific embodiment of the non-azeotropic mixed working fluid heat pump system of this utility model with reference to the accompanying drawings.

[0081] like Figure 1 and Figure 2 As shown, the system of this utility model includes a heat pump circuit, a first water circulation circuit 40, and a second water circulation circuit 60. The heat pump circuit includes a compressor 1, a first condenser 2, a second throttling device 3, a liquid receiver 4, a defrosting branch 20, an electrically controlled valve 30, a regenerator 6, a first throttling device 7, an evaporator 8, an evaporator fan 80, and a gas-liquid separator 9. The water-side channel of the first condenser 2 is connected to the first water circulation circuit 40, and the water-side channel of the second condenser 10 is connected to the second water circulation circuit 60.

[0082] like Figure 1 As shown, in heating operation mode, the electronically controlled valve 30 is closed. The mixed working fluid is compressed into a high-temperature, high-pressure gas in the compressor 1 and discharged, entering the first condenser 2 for cooling. It then passes through the second throttling device 3 and enters the liquid receiver 4, before further condensing in the second condenser 10. Afterward, the mixed working fluid flows through the regenerator 6 for further cooling and passes through the first throttling device 7 before entering the evaporator 8. The low-pressure gas exiting the evaporator 8 returns to the compressor 1 via the gas-liquid separator 9. During this process, the evaporator 8 absorbs heat from the air, and this heat, combined with the work done by the compressor 1, is released in the first condenser 2 and the second condenser 10, heating the water for heating applications.

[0083] In this system, the mixed working fluid undergoes two stages of condensation, two stages of throttling, and one stage of regeneration treatment from the condenser outlet to the evaporator 8 inlet. This significantly reduces the throttling temperature difference between the condenser and evaporator 8 compared to traditional systems, thereby substantially reducing energy loss during throttling and improving heating performance. For example, with a condenser outlet temperature of 45℃ and an evaporator 8 inlet temperature of -35℃, the throttling temperature difference in a traditional system reaches 80℃. In contrast, this system typically reaches approximately 30℃ after the first stage of throttling, then drops to approximately 20℃ after passing through the second condenser 10, and finally reaches approximately -30℃ upon entering the regenerator 6. Therefore, the first-stage throttling temperature difference is 15℃, the second-stage throttling temperature difference is 5℃, and the total throttling temperature difference is 20℃, a reduction of 60℃ compared to traditional systems, significantly improving heating performance.

[0084] Residential heating in winter requires a water temperature of at least 40℃, and considering the heat exchange temperature difference, the condensing temperature usually needs to reach above 45℃. However, at this temperature, the mixed working fluid may not condense completely, and some low-boiling-point refrigerant remains in a gaseous state, failing to fully utilize its latent heat. This invention, by using a second condenser 10, allows the mixed working fluid to condense fully, releasing more latent heat. Although the condensing temperature is relatively low at this point, making it unsuitable for direct use in residential heating, it can be used in areas such as garages or basements. Therefore, the two-stage condensation increases the heating capacity of the heat pump system and improves the system's coefficient of performance.

[0085] Figure 3 For the system's pressure-enthalpy diagram, it's important to explain that the horizontal axis 'h' represents enthalpy: enthalpy is a state function in thermodynamics, usually denoted by the symbol 'h'. In a refrigeration cycle, enthalpy reflects the energy level of the working fluid under different states. The larger the value on the horizontal axis, the higher the enthalpy of the working fluid.

[0086] The vertical axis, lgp, represents the logarithm of pressure: the vertical axis represents the logarithm of pressure, i.e., log(p), where p is the pressure; the horizontal axis represents the enthalpy (h). Using the logarithmic form makes pressure values ​​of different orders of magnitude clearer on the graph. The larger the value on the vertical axis, the higher the pressure of the working fluid.

[0087] Figure 3 The meanings of each point are as follows: Point 1 represents the state point at the return port of compressor 1, where the working fluid is a low-pressure gas; Point 2 represents the state point at the outlet of compressor 1, where the working fluid becomes a high-temperature, high-pressure gas after compression; Point 3 represents the state point after the first condensation; Point 3' represents the state point after the first throttling and second condensation; 3" represents the state point after reheating through the regenerator 6; Point 4 represents the state point after the second throttling.

[0088] Figure 3The meanings of the respective line segments are as follows: The line segment 1→2 represents the compression process of the working medium in the compressor 1, where the working medium is compressed from low-pressure gas to high-temperature and high-pressure gas, with the enthalpy value increasing and the pressure rapidly rising. The line segment 2→3 represents the state change of the working medium during the first condensation process. At this time, the pressure remains basically unchanged, but due to the condensation process, its enthalpy value rapidly decreases. The line segment 3→3’ represents the process of primary throttling and secondary condensation. After the working medium undergoes primary throttling, its enthalpy value remains basically unchanged but its pressure drops. Subsequently, the working medium undergoes secondary condensation to release heat, so that the pressure of the refrigerant remains unchanged but its enthalpy value decreases. The line segment 3’→3” represents the stage where the refrigerant flows through the regenerator 6. At this time, the refrigerant is further cooled, resulting in a further decrease in the enthalpy value. The line segment 3”→4 represents the process of secondary throttling of the working medium. After the working medium undergoes secondary throttling, its pressure rapidly drops and its enthalpy value remains basically unchanged. The curve 4→1 represents the process where the working medium sequentially flows through the evaporator 8 and the regenerator 6. The working medium absorbs heat in both the evaporator 8 and the regenerator 6, resulting in an increase in the enthalpy value but its pressure remaining basically unchanged.

[0089] As can be seen from the above pressure-enthalpy diagram, the theoretical refrigeration cycle of the first-stage condenser and second-stage throttling regenerative system in the related technology is 1→2→3→3”→4, and the coefficient of performance cop1 of the system is (h2 - h3) / (h2 - h1). The theoretical refrigeration cycle of the present invention's second-stage condenser and second-stage throttling regenerative system is 1→2→3→3’→3”→4, and the coefficient of performance cop2 of the system is (h2 - h3’) / (h2 - h1). The comparison result is cop1 < cop2. Therefore, compared with the system of the first-stage condenser in the related technology, the coefficient of performance of the system of the present invention has been greatly improved.

[0090] As Figure 2 shown, in the defrosting mode, the electro-control valve 30 is opened and the first throttling device 7 is closed. The mixed working medium is compressed into high-temperature and high-pressure gas in the compressor 1 and then discharged, enters the first condenser 2 for cooling and is throttled by the second throttling device 3. At this time, the second throttling device 3 is set to a larger opening to ensure a higher temperature after throttling. The relatively high gas-liquid mixture enters the liquid storage device 4. Most of the liquid components accumulate inside the liquid storage device 4, while the gaseous components mainly enter the evaporator 8 directly through the defrosting branch 20 from the top of the liquid storage device 4 for condensation, releasing a large amount of heat to achieve defrosting. Subsequently, the mixed working medium returns to the regenerator 6 to absorb heat and evaporate, and then returns to the compressor 1 after passing through the gas-liquid separator 9.

[0091] During this process, gas-liquid separation occurs when the gas-liquid two-phase working fluid enters the liquid receiver 4. The low-boiling-point components account for a large proportion of the gaseous working fluid separated at the top. Therefore, the refrigerant components actually participating in the defrosting cycle contain more low-boiling-point components compared to the heating mode. This leads to an increase in high pressure and mass flow rate in the cycle, which ultimately increases the work done by the compressor 1. In other words, the condensation heat dissipation of the evaporator 8 during the defrosting process is greater, thereby improving the defrosting effect.

[0092] 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.

[0093] 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: A compressor (1) and a heat pump circuit connected to the compressor (1) to form a circuit, wherein a first condenser (2), a second condenser (10), a first throttling device (7) and an evaporator (8) are sequentially arranged along the refrigerant flow direction on the heat pump circuit; The regenerator (6) includes a first heat exchange channel (61) and a second heat exchange channel (62) that exchange heat with each other. The first heat exchange channel (61) is connected between the outlet of the second condenser (10) and the inlet of the first throttling device (7). The second heat exchange channel (62) is connected between the outlet of the evaporator (8) and the return port (11) of the compressor (1).

2. The non-azeotropic mixed working fluid heat pump system according to claim 1, characterized in that, Also includes: The liquid receiver (4) is provided with a refrigerant inlet (41) and a first refrigerant outlet (42). The refrigerant inlet (41) is connected to the outlet of the first condenser (2), and the first refrigerant outlet (42) is connected to the inlet of the second condenser (10).

3. The non-azeotropic mixed working fluid heat pump system according to claim 2, characterized in that, Also includes: The second throttling device (3) has its inlet connected to the outlet of the first condenser (2) and its outlet connected to the refrigerant inlet (41) of the liquid receiver (4).

4. The non-azeotropic mixed working fluid heat pump system according to claim 3, characterized in that, Both the first throttling device (7) and the second throttling device (3) are expansion valves.

5. The non-azeotropic mixed working fluid heat pump system according to claim 2, characterized in that, It also includes a defrosting branch (20), and the liquid receiver (4) is also provided with a second refrigerant outlet (43). The two ends of the defrosting branch (20) are respectively connected to the second refrigerant outlet (43) and the inlet of the evaporator (8). The defrosting branch (20) is provided with an electrically controlled valve (30) with adjustable opening.

6. The non-azeotropic mixed working fluid heat pump system according to claim 5, characterized in that, The second refrigerant outlet (43) is located at the top of the liquid reservoir (4), and the first refrigerant outlet (42) is located at the bottom of the liquid reservoir (4).

7. The non-azeotropic working fluid heat pump system according to any one of claims 2 to 6, characterized in that, Also includes: The first water circulation loop (40) is connected to the two ends of the water side channel of the first condenser (2). The first water circulation loop (40) is provided with at least one first water-using device connected to the water side channel of the first condenser (2). And / or, a second water circulation loop (60), the two ends of which are connected to the two ends of the water side channel of the second condenser (10), and the second water circulation loop (60) is provided with at least one second water-using device connected to the water side channel of the second condenser (10).

8. The non-azeotropic mixed working fluid heat pump system according to claim 7, characterized in that, The first water circulation loop (40) is equipped with a first water pump (50); and / or the second water circulation loop (60) is equipped with a second water pump (70).

9. The non-azeotropic mixed working fluid heat pump system according to any one of claims 2 to 6, characterized in that, It also includes an evaporator fan (80) for driving air through the evaporator (8).

10. The non-azeotropic mixed working fluid heat pump system according to any one of claims 2 to 6, characterized in that, The heat pump circuit is also equipped with a gas-liquid separator (9), which is located near the return gas port (11) of the compressor (1).

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