Non-azeotropic mixed working fluid heat pump system and control method thereof

Abstract

The present invention relates to the field of heat pump technology, and discloses a non-azeotropic mixed working fluid heat pump system and a control method thereof. The heat pump system includes: a compressor and a refrigerant circulation loop, wherein a condenser, a first throttling device, a rectifier, a regenerator, a second throttling device and an evaporator are sequentially arranged on the refrigerant circulation loop along the flow direction of the refrigerant; the rectifier is provided with a rectification inlet, an air outlet and a liquid outlet, and a cooling section is provided inside the rectifier, and the liquid outlet is connected to the air supply port of the compressor through a first branch, and the cooling section is connected to the first branch; the regenerator has a first heat exchange channel and a second heat exchange channel, the first heat exchange channel is connected between the air outlet and the inlet of the second throttling device, and the second heat exchange channel is connected to the first branch. The present invention realizes efficient separation and energy recovery of refrigerant components by introducing a rectifier and a regenerator, thereby improving the heating capacity of the heat pump system, and further improving the low-temperature heating capacity of the system.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pumps, and in particular to a non-azeotropic mixed working fluid heat pump system and a control method thereof. Background Art

[0002] Heat pumps have evolved from household heating and cooling applications to heat applications throughout society, and their application scenarios have undergone tremendous changes. Due to the large temperature variation range of heat sources and heat sinks, traditional single working fluids have been difficult to meet the requirements of use, such as ultra-low ambient temperature heating in the construction field and ultra-high water temperature heating in the industrial field.

[0003] Non-azeotropic mixtures allow for flexible selection of components and proportions based on the application, increasing the temperature difference between the heat source and heat sink to meet the wide temperature span requirements of specific applications. In recent years, non-azeotropic mixture systems have become increasingly widely used.

[0004] However, in the actual application of the mixed working fluid system, the mixed working fluid cannot be well separated and purified in the separator, and more low-boiling-point working fluid cannot enter the evaporator to absorb heat, which limits the heating capacity of the heat pump system. Summary of the Invention

[0005] The first technical problem solved by the present invention is to provide a non-azeotropic mixed refrigerant heat pump system, which effectively solves the problem of limited heating capacity of the heat pump system due to low refrigerant utilization rate.

[0006] The second technical problem solved by the present invention is to provide a control method for a non-azeotropic mixed refrigerant heat pump system, which effectively solves the problem of limited heating capacity of the heat pump system due to low refrigerant utilization rate.

[0007] The first technical problem mentioned above is solved by the following technical solution:

[0008] A non-azeotropic mixed working fluid heat pump system, comprising:

[0009] A compressor and a refrigerant circulation circuit connected to the compressor to form a loop, wherein the refrigerant circulation circuit is provided with a condenser, a first throttling device, a rectifier, a regenerator, a second throttling device and an evaporator in sequence along the refrigerant flow direction;

[0010] The rectifier is provided with a rectification inlet, a gas outlet and a liquid outlet, a cooling section is provided inside the rectifier, the liquid outlet is connected to the gas supply port of the compressor through a first branch, and the cooling section is connected to the first branch;

[0011] The regenerator has a first heat exchange channel and a second heat exchange channel for exchanging heat with each other. The first heat exchange channel is connected between the air outlet and the inlet of the second throttling device, and the second heat exchange channel is connected to the first branch.

[0012] Compared with the background technology, the non-azeotropic mixed working fluid heat pump system of the present invention has the following beneficial effects:

[0013] The heat pump system of the present invention introduces a rectifier and a regenerator, so that the mixed refrigerant flows through the condenser, the first throttling device and the rectifier in sequence in the heating mode. Due to the different boiling points of the mixed refrigerants, after flowing through the condenser, the low-boiling-point refrigerant is mostly gaseous, and the high-boiling-point refrigerant is mostly liquid. Therefore, the mixed refrigerant will be separated into gaseous refrigerant and liquid refrigerant in the rectifier, among which the gaseous refrigerant is mostly low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. The gaseous refrigerant will pass through the air outlet, the first heat exchange channel, the second throttling device and the evaporator and finally flow into the return air port of the compressor, and the liquid refrigerant will enter the first branch through the liquid outlet and provide cooling refrigerant for the cooling section, and flow through the second heat exchange channel. The refrigerant in the first branch will eventually flow into the air supply port of the compressor.

[0014] In the above-mentioned circulation path, since part of the liquid refrigerant passes through the cooling section after flowing out of the rectifier, the liquid refrigerant will exchange heat with the gaseous refrigerant through the cooling section, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of low-boiling-point refrigerant flowing through the evaporator, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and thus improving the low-temperature heating capacity of the system. In addition, the present application introduces liquid refrigerant into the air supply port of the compressor to achieve air supply enthalpy increase, which can reduce the exhaust pressure and exhaust temperature of the compressor, thereby enabling the heat pump to operate stably at low ambient temperatures.

[0015] In addition, the present application utilizes the first throttling device and the second throttling device to perform secondary throttling on the refrigerant, and further cools the low-boiling-point refrigerant through the regenerator, so that the low-boiling-point refrigerant is fully condensed and has a large degree of supercooling, thereby reducing subsequent throttling losses, thereby improving the heating capacity and energy efficiency of the heat pump system.

[0016] In one embodiment, a heating section is further provided inside the rectifier;

[0017] The refrigerant circulation loop also includes a second branch, the two ends of which are respectively connected to the exhaust port of the compressor and the distillation inlet, the heating section is connected to the second branch, and a first control valve is provided on the second branch.

[0018] In one embodiment, the interior of the distillation vessel is provided with an interconnected gas storage chamber, a first purification chamber, a separation chamber, a second purification chamber and a liquid storage chamber from top to bottom, the first purification chamber is provided with the cooling section, and the second purification chamber is provided with the heating section.

[0019] In one embodiment, the cooling section has a cooling inlet and a cooling outlet, and the cooling inlet is located above the cooling outlet;

[0020] And / or, the heating section has a heating inlet and a heating outlet, and the heating inlet is located below the heating outlet.

[0021] In one embodiment, the first purification chamber and / or the second purification chamber is filled with a filler, and the filler has a flow gap for the refrigerant to flow.

[0022] In one embodiment, a third branch is further included, one end of the third branch is connected between the liquid outlet and the inlet of the second heat exchange channel, the other end of the third branch is connected between the outlet of the second heat exchange channel and the air supply port of the compressor, and the cooling section is connected to the third branch;

[0023] It also includes a second control valve and a third control valve, wherein the second control valve is arranged on the third branch, and the third control valve is arranged on the first branch.

[0024] In one embodiment, a defrost branch is further included, wherein two ends of the defrost branch are respectively connected to the air outlet and the inlet of the evaporator, and a defrost control valve is provided on the defrost branch.

[0025] The second technical problem mentioned above is solved by the following technical solution:

[0026] A control method for a non-azeotropic mixed working fluid heat pump system is applied to the non-azeotropic mixed working fluid heat pump system of the first aspect of the present invention, the control method comprising:

[0027] In response to the heating mode, the first branch is controlled to be in a connected state, and the refrigerant is controlled to flow through the condenser, the first throttling device, the distillation device, the first heat exchange channel of the regenerator, the second throttling device and the evaporator in sequence and enter the return air port of the compressor.

[0028] Compared with the background technology, the control method of the non-azeotropic mixed refrigerant heat pump system described in the present invention has the following beneficial effects: after determining that the heat pump system enters the heating mode, the control method of the present invention will control the first branch to remain connected, and control the mixed refrigerant to flow through the condenser, the first throttling device and the rectifier in sequence. Due to the different boiling points of the mixed refrigerants, after flowing through the condenser, the low-boiling-point refrigerant is mostly gaseous, and the high-boiling-point refrigerant is mostly liquid. Therefore, the mixed refrigerant will be separated into gaseous refrigerant and liquid refrigerant in the rectifier, among which the gaseous refrigerant is mostly low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. The gaseous refrigerant will pass through the air outlet, the first heat exchange channel, the second throttling device and the evaporator and finally flow into the return air port of the compressor, and the liquid refrigerant will enter the first branch through the liquid outlet and provide cooling refrigerant for the cooling section, and flow through the second heat exchange channel. The refrigerant in the first branch will eventually flow into the air supply port of the compressor.

[0029] In the above-mentioned circulation path, since part of the liquid refrigerant passes through the cooling section after flowing out of the rectifier, the liquid refrigerant will exchange heat with the gaseous refrigerant through the cooling section, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of low-boiling-point refrigerant flowing through the evaporator, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and thus improving the low-temperature heating capacity of the system. In addition, the present application introduces liquid refrigerant into the air supply port of the compressor to achieve air supply enthalpy increase, which can reduce the exhaust pressure and exhaust temperature of the compressor, thereby enabling the heat pump to operate stably at low ambient temperatures.

[0030] In addition, while controlling the connectivity of the first branch, the present application utilizes the first throttling device and the second throttling device to perform secondary throttling on the refrigerant, and further cools the low-boiling-point refrigerant through the regenerator, allowing the low-boiling-point refrigerant to be fully condensed and have a large degree of supercooling, thereby reducing subsequent throttling losses and improving the heating capacity and energy efficiency of the heat pump system.

[0031] In one embodiment, the heat pump system further includes a second branch, the two ends of which are respectively connected to the exhaust port of the compressor and the distillation inlet, and the rectifier is further provided with a heating section, which is connected to the second branch;

[0032] The control method further includes:

[0033] In response to the heating mode, the second branch is controlled to be in a connected state, and the refrigerant is controlled to flow through the condenser, the first throttling device, the distillation device, the first heat exchange channel of the regenerator, the second throttling device and the evaporator in sequence and enter the return air port of the compressor.

[0034] In one embodiment, the heat pump system further includes a defrost branch, wherein both ends of the defrost branch are respectively connected to the air outlet and the inlet of the evaporator;

[0035] The control method further includes:

[0036] In response to the defrost mode, the second branch and the defrost branch are controlled to be in a connected state, the first branch is controlled to be in a disconnected state, and the refrigerant is controlled to flow through the second branch, the rectifier, the defrost branch and the evaporator in sequence and enter the return air port of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the specific embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0038] Figure 1 This is a schematic structural diagram of a non-azeotropic mixed working fluid heat pump system in a heating mode according to an embodiment of the present invention;

[0039] Figure 2 This is a schematic structural diagram of a non-azeotropic mixed working fluid heat pump system in a defrost mode according to an embodiment of the present invention;

[0040] Figure 3 Schematic diagram of the structure of a rectifier according to an embodiment of the present invention;

[0041] Figure 4 This is a flow chart of a control method for a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention;

[0042] Figure 5 This is a second flow chart of a control method for a non-azeotropic mixed working fluid heat pump system according to an embodiment of the present invention;

[0043] Figure 6 This is a structural schematic diagram of a non-azeotropic mixed working fluid heat pump system according to another embodiment of the present invention.

[0044] Description of reference numerals:

[0045] 1. Compressor; 2. Condenser; 3. First throttling device; 4. Rectifier; 5. Defrost control valve; 6. Regenerator; 601. First heat exchange channel; 602. Second heat exchange channel; 7. Second throttling device; 8. Evaporator; 9. Gas-liquid separator; 10. First control valve; 11. Second control valve; 12. Third control valve; 13. First branch; 14. Second branch; 15. Third branch; 17. Defrost branch; 18. Evaporator fan; 410. Separation chamber; 411. Distillation inlet; 420. Gas storage chamber; 421. Gas outlet; 430. Liquid storage chamber; 431. Liquid outlet; 440. Second purification chamber; 441. Heating section; 442. Filling material; 450. First purification chamber; 451. Cooling section. DETAILED DESCRIPTION

[0046] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0047] In the description of this application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and 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, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0048] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of such features. Throughout this application, unless otherwise specified, "plurality" means two or more.

[0049] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0050] A non-azeotropic mixed working fluid heat pump system and a control method thereof provided by the present invention will be described below with reference to the accompanying drawings.

[0051] like Figure 1 and Figure 2 As shown, the non-azeotropic mixed refrigerant heat pump system according to the embodiment of the first aspect of the present invention includes a compressor 1 and a refrigerant circulation loop connected to the compressor 1 to form a loop, and a condenser 2, a first throttling device 3, a distillation device 4, a regenerator 6, a second throttling device 7 and an evaporator 8 are sequentially provided on the refrigerant circulation loop along the flow direction of the refrigerant.

[0052] The rectifier 4 is provided with a distillation inlet 411, an air outlet 421, and a liquid outlet 431. A cooling section 451 is provided inside the rectifier 4. The liquid outlet 431 is connected to the air supply port of the compressor 1 via the first branch 13. The cooling section 451 is connected to the first branch 13. The regenerator 6 has a first heat exchange channel 601 and a second heat exchange channel 602 for mutual heat exchange. The first heat exchange channel 601 is connected between the air outlet 421 and the inlet of the second throttling device 7, and the second heat exchange channel 602 is connected to the first branch 13.

[0053] The specific structure of the non-azeotropic mixed refrigerant heat pump system according to an embodiment of the present invention is described as follows: This system is a closed refrigerant circulation system, including a compressor 1, a condenser 2, a first throttling device 3, a rectifier 4, a regenerator 6, a second throttling device 7, and an evaporator 8. In heating mode, the refrigerant circulates in the system along the following path: compressor 1, condenser 2, first throttling device 3, rectifier 4, first heat exchange channel 601 of regenerator 6, second throttling device 7, evaporator 8, second heat exchange channel 602 of regenerator 6, and finally returns to compressor 1.

[0054] The rectifier 4 has three interfaces: a rectifier inlet 411 for receiving refrigerant from the first throttling device 3; a gas outlet 421 for discharging gaseous refrigerant; and a liquid outlet 431 for discharging liquid refrigerant. Gas outlet 421 is located above liquid outlet 431. A cooling section 451 is located within the internal cavity of the rectifier 4. This cooling section 451 is connected to the first branch 13 to form a closed loop. Its function is to cool the refrigerant within the rectifier 4 to promote the liquefaction of the high-boiling-point refrigerant.

[0055] It can be understood that due to the different boiling points of the mixed refrigerant, after flowing through the condenser 2, the low-boiling-point refrigerant is mostly in a gaseous state, and the high-boiling-point refrigerant is mostly in a liquid state. Therefore, the mixed refrigerant will be separated into a gaseous refrigerant and a liquid refrigerant in the rectifier 4, thereby achieving a preliminary separation of the mixed refrigerant. At the same time, in the above-mentioned circulation path, since part of the liquid refrigerant will pass through the cooling section 451 after flowing out of the rectifier 4, the liquid refrigerant will exchange heat with the gaseous refrigerant through the cooling section 451, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of the low-boiling-point refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and thus improving the low-temperature heating capacity of the system.

[0056] The first branch 13 constitutes an air supply circuit, that is, the air supply circuit includes the liquid outlet 431, the first branch 13 and the air supply port of the compressor 1; the air supply enthalpy increase can reduce the exhaust pressure of the compressor 1, so that the heat pump can operate stably at low ambient temperature.

[0057] Regenerator 6 comprises two channels that exchange heat with each other without mixing. The first heat exchange channel 601 connects the outlet 421 of the rectifier 4 with the second throttling device 7 and is used to cool the low-boiling-point refrigerant. The second heat exchange channel 602, connected to the first branch 13, is used to heat the high-boiling-point refrigerant. It can be understood that regenerator 6 primarily functions to exchange heat between the high- and low-boiling-point refrigerants, thereby further cooling the low-boiling-point refrigerant and allowing it to fully condense with a high degree of subcooling. This reduces subsequent throttling losses, thereby improving the heating capacity and energy efficiency of the heat pump system.

[0058] Based on the above specific structure, the working principle of the heat pump system of the present invention is as follows:

[0059] On the one hand, the mixed refrigerant will be separated into gaseous refrigerant and liquid refrigerant after entering the rectifier 4, among which the gaseous refrigerant is mostly low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. The gaseous refrigerant will pass through the air outlet 421, the first heat exchange channel 601, the second throttling device 7 and the evaporator 8 and finally flow into the return air port of the compressor 1. The liquid refrigerant will enter the first branch 13 through the liquid outlet 431, and provide cooling refrigerant for the cooling section 451, and flow through the second heat exchange channel 602. The refrigerant in the first branch 13 will eventually flow into the air supply port of the compressor 1. In the above-described flow path, since some of the liquid refrigerant passes through cooling section 451 after flowing out of rectifier 4, it exchanges heat with the gaseous refrigerant in cooling section 451, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant. At this time, the high-boiling-point refrigerant liquefies and sinks to liquid outlet 431; the gaseous refrigerant continues to rise and is discharged through gas outlet 421. This closed-loop cooling method significantly enhances the liquefaction rate of the high-boiling-point component and improves the purity of the low-boiling-point refrigerant.

[0060] On the other hand, the present application can reduce the exhaust pressure of the compressor 1 by introducing liquid refrigerant into the air supply port of the compressor 1, thereby enabling the heat pump to operate stably at low ambient temperatures.

[0061] In addition, the present application utilizes the first throttling device 3 and the second throttling device 7 to perform secondary throttling on the refrigerant, and further cools the low-boiling-point refrigerant through the regenerator 6, so that the low-boiling-point refrigerant is fully condensed and has a large degree of supercooling, thereby reducing subsequent throttling losses, thereby improving the heating capacity and energy efficiency of the heat pump system.

[0062] Furthermore, the specific working process of the heat pump system of the present invention is as follows:

[0063] During the distillation process, the mixed refrigerant is depressurized through the first throttling device 3 and then enters the distillation inlet 411 of the rectifier 4; in the rectifier 4, due to the cooling effect of the cooling section 451, the high-boiling-point refrigerant is rapidly liquefied and sinks to the liquid outlet 431; the low-boiling-point refrigerant rises in the form of gas and is discharged through the gas outlet 421; the liquid refrigerant enters the first branch 13 from the liquid outlet 431, absorbs heat in the cooling section 451, cools the mixed refrigerant in the rectifier 4, and further promotes separation.

[0064] During the heat recovery process, the gaseous refrigerant discharged from the gas outlet 421 of the distillation device 4 enters the first heat exchange channel 601 of the regenerator 6, where it is cooled by the liquid refrigerant in the second heat exchange channel 602; the cooled refrigerant enters the second throttling device 7, and after being reduced in pressure again, enters the evaporator 8 to absorb heat and evaporate; after the liquid refrigerant is heated in the second heat exchange channel 602 of the regenerator 6, it returns to the air supply port of the compressor 1 through the first branch 13, and participates in the compression cycle as an intermediate pressure gas.

[0065] As can be seen from the above, the heat pump system of the present invention introduces a rectifier 4 and a regenerator 6, so that the mixed refrigerant flows through the condenser 2, the first throttling device 3 and the rectifier 4 in sequence in the heating mode. Due to the different boiling points of the mixed refrigerant, after flowing through the condenser 2, the low-boiling-point refrigerant is mostly gaseous, and the high-boiling-point refrigerant is mostly liquid. Therefore, the mixed refrigerant is separated into gaseous refrigerant and liquid refrigerant in the rectifier 4, wherein most of the gaseous refrigerant is low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. The gaseous refrigerant will pass through the air outlet 421, the first heat exchange channel 601, the second throttling device 7 and the evaporator 8 and finally flow into the return air port of the compressor 1, and the liquid refrigerant will enter the first branch 13 through the liquid outlet 431, and provide cooling refrigerant for the cooling section 451, and flow through the second heat exchange channel 602. The refrigerant in the first branch 13 finally flows into the air supply port of the compressor 1.

[0066] In the above-mentioned circulation path, since part of the liquid refrigerant passes through the cooling section 451 after flowing out of the rectifier 4, the liquid refrigerant will exchange heat with the gaseous refrigerant through the cooling section 451, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of the low-boiling-point refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and thus improving the low-temperature heating capacity of the system. In addition, the present application can reduce the exhaust pressure of the compressor 1 by introducing the liquid refrigerant into the air supply port of the compressor 1, thereby enabling the heat pump to operate stably at low ambient temperatures.

[0067] In addition, the present application utilizes the first throttling device 3 and the second throttling device 7 to perform secondary throttling on the refrigerant, and further cools the low-boiling-point refrigerant through the regenerator 6, so that the low-boiling-point refrigerant is fully condensed and has a large degree of supercooling, thereby reducing subsequent throttling losses, thereby improving the heating capacity and energy efficiency of the heat pump system; at the same time, the temperature of the high-boiling-point refrigerant is increased, which helps it to evaporate smoothly at the air inlet of the compressor 1 and participate in the compression cycle.

[0068] like Figure 3 As shown, according to some embodiments of the present invention, a heating section 441 is provided inside the rectifier 4.

[0069] The refrigerant circulation loop further includes a second branch 14 , the two ends of which are respectively connected to the exhaust port of the compressor 1 and the distillation inlet 411 , and the heating section 441 is connected to the second branch 14 .

[0070] like Figure 3 As shown, further, the interior of the distillation vessel 4 is provided with an interconnected gas storage chamber 420, a first purification chamber 450, a separation chamber, a second purification chamber 440 and a liquid storage chamber 430 from top to bottom, a cooling section 451 is provided in the first purification chamber, and a heating section 441 is provided in the second purification chamber 440.

[0071] In the above embodiment, within the internal cavity of rectifier 4, first purification chamber 450 is used for the initial separation of refrigerant components; gas storage chamber 420 is used to collect the separated gaseous refrigerant; and liquid storage chamber 430 is used to collect the separated liquid refrigerant. Cooling section 451 is disposed within first purification chamber 450 and connected via first branch 13 to form a closed loop. Its function is to cool the refrigerant within first purification chamber 450 to promote the liquefaction of high-boiling-point components.

[0072] The second purification chamber 440 is located within the rectifier 4 and communicates with the distillation inlet 411 and the liquid storage chamber 430. It receives the mixed refrigerant from the first purification chamber 450 or directly from the distillation inlet 411. Within the second purification chamber 440, the refrigerant is locally heated by the heating section 441. This heating causes the low-boiling-point components in the refrigerant to evaporate preferentially, forming a gas that rises to the gas storage chamber 420, while the high-boiling-point components that remain unevaporated remain in liquid form and sink into the liquid storage chamber 430.

[0073] Among them, the heating section 441 is connected to the second branch 14, that is, a part of the high-temperature and high-pressure gas drawn out from the exhaust port of the compressor 1 flows through here, releases heat and then re-enters the refrigerant circulation system to realize waste heat utilization.

[0074] Its working principle and working process are as follows: Due to the different boiling points of the mixed refrigerant, after flowing through the condenser 2, the low-boiling-point refrigerant is mostly gaseous, and the high-boiling-point refrigerant is mostly liquid. Therefore, the mixed refrigerant will be separated into gaseous refrigerant and liquid refrigerant in the distillation device, among which the gaseous refrigerant is mostly low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. In the process of the gaseous refrigerant rising and passing through the first purification chamber 450, the cooling section 451 can cool the gaseous refrigerant, so that the high-boiling-point refrigerant component in the gaseous refrigerant is condensed and liquefied, and the liquefied high-boiling-point refrigerant falls into the liquid storage chamber 430, and the gaseous refrigerant rises to the gas storage chamber 420 after purification by the first purification chamber 450, and is output to the first heat exchange channel 601 of the regenerator 6 through the air outlet 421. As the liquid refrigerant descends and passes through the second purification chamber 440, the high-temperature, high-pressure gas from the second branch 14 heats the liquid refrigerant through the heating section 441. This process causes the low-boiling-point refrigerant components in the liquid refrigerant to further evaporate into gas, while the remaining high-boiling-point components are more fully liquefied. The evaporated low-boiling-point refrigerant rises and flows into the gas storage chamber 420, while the liquefied high-boiling-point refrigerant flows into the liquid storage chamber 430. In this way, the dual purification effects of the first purification chamber 450 and the second purification chamber 440 enhance the refrigerant separation efficiency and ensure the high purity of the refrigerant components.

[0075] At the same time, the design of the second branch 14 enables energy recovery. Specifically, second branch 14 is directly connected to the exhaust port of compressor 1, directing some of the high-temperature, high-pressure exhaust gas that would otherwise be wasted into rectifier 4 as a heat source. After releasing heat through heating section 441, this high-temperature gas is returned to the refrigerant cycle, reducing the need for external energy and improving the system's energy efficiency.

[0076] Finally, the refrigerant, having undergone dual purification, continues to circulate along its own path. The gaseous refrigerant is cooled in the regenerator 6 before entering the second throttling device 7, where it absorbs heat and evaporates in the evaporator 8. The liquid refrigerant then returns to the air supply port of the compressor 1 through the first branch 13, replenishing the system's refrigerant circulation while avoiding the risk of a wet stroke.

[0077] In summary, the above design not only improves the separation efficiency of refrigerant components, but also achieves efficient energy utilization by utilizing the heat discharged from compressor 1 to heat the refrigerant in second purification chamber 440, eliminating the need for external energy sources. This not only optimizes system energy efficiency but also enhances operational stability and safety. Furthermore, a purer refrigerant composition helps improve the efficiency of subsequent components and reduces performance fluctuations caused by uneven refrigerant distribution, enabling the entire heat pump system to maintain efficient and stable operation under different operating conditions.

[0078] For example, the gas outlet 421 , the gas storage chamber 420 , the first purification chamber 450 , the distillation inlet 411 , the second purification chamber 440 , the liquid storage chamber 430 and the liquid outlet 431 are arranged in sequence from top to bottom.

[0079] A separation chamber 410 is formed between the first purification chamber 450 and the second purification chamber 440, and a distillation inlet 411 is connected to the separation chamber 410. This structural design allows the refrigerant to be initially separated according to its gas and liquid phases upon entry, with targeted component purification completed in the upper and lower purification chambers. For example, when the mixed refrigerant enters the separation chamber 410 through the distillation inlet 411, the gaseous component of the mixed refrigerant rises and is purified in the first purification chamber 450, while the liquid component of the mixed refrigerant descends and is purified in the second purification chamber 440.

[0080] Within the interior of rectifier 4, the refrigerant undergoes the following distillation process: After being throttled and depressurized by first throttling device 3, the refrigerant enters rectifier 4 as a gas-liquid mixture through distillation inlet 411 and flows into separation chamber 410. The gaseous component of the refrigerant rises and enters the upper first purification chamber 450; the liquid component descends and enters the lower second purification chamber 440. This stage achieves initial gas-liquid stratification of the refrigerant, laying the foundation for subsequent purification.

[0081] The gas entering the first purification chamber 450 is mainly low-boiling-point refrigerant, which is further purified here to remove the mixed high-boiling-point gas. Finally, the pure low-boiling-point refrigerant gas rises to the gas storage chamber 420 and is output through the gas outlet 421 and enters the first heat exchange channel 601 of the regenerator 6.

[0082] The liquid entering the second purification chamber 440 is primarily high-boiling-point refrigerant. Within this chamber, a heating section 441 is installed, which receives heat from the exhaust gas of compressor 1 to heat the liquid. This heating causes the remaining low-boiling-point refrigerant components to evaporate and rise, ultimately entering the gas storage chamber 420. The unevaporated high-boiling-point refrigerant, on the other hand, continues to descend, entering the liquid storage chamber 430, and is discharged through the liquid outlet 431. It then returns to the compressor 1 refill port via the first branch 13, achieving intermediate refill.

[0083] In this way, the system enhances separation accuracy by introducing a dual-chamber purification mechanism. Specifically, the upper first purification chamber 450 focuses on the purification of low-boiling-point gases, while the lower second purification chamber 440 further purifies high-boiling-point liquids by heating, thereby achieving graded processing and refined control of refrigerant components. At the same time, the system actively separates the mixed refrigerant according to the gas and liquid forms by introducing the separation chamber 410, avoiding mutual interference and improving the subsequent purification efficiency. As mentioned above, the above structural setting allows purer refrigerant to enter the subsequent circulation path, which helps to improve heat exchange efficiency.

[0084] like Figure 3 As shown, further, the cooling section 451 has a cooling inlet and a cooling outlet, and the cooling inlet is located above the cooling outlet. The heating section 441 has a heating inlet and a heating outlet, and the heating inlet is located below the heating outlet.

[0085] It needs to be explained that the refrigerant flowing in the cooling section 451 is liquid, and the liquid enters from the top and exits from the bottom, and flows downward naturally due to the action of gravity, without the need for additional power measures, while improving the cooling efficiency of the refrigerant in the rectifier 4; while the refrigerant flowing in the heating section is gaseous, and the gas enters from the bottom and exits from the top, and rises naturally due to the action of lift, without the need for additional power measures, while improving the heating efficiency of the refrigerant in the rectifier 4.

[0086] In this way, the present invention fully utilizes the natural lift of gravity and gas by carefully designing the inlet and outlet positions and flow directions of the cooling section 451 and the heating section 441, avoids the need for additional power equipment, simplifies the system structure and reduces maintenance costs; at the same time, it achieves efficient cooling and heating, and improves the separation efficiency and energy efficiency performance of the non-azeotropic mixed working fluid heat pump system.

[0087] Furthermore, the first purification chamber 450 and / or the second purification chamber 440 is filled with a filler 442 , and the filler 442 has a flow gap for the refrigerant to flow.

[0088] Specifically, the filler 442 has the following advantages: First, the filler 442 can significantly enhance the heat and mass transfer efficiency between gas and liquid, and improve the separation accuracy of the refrigerant components; second, the filler 442 can extend the refrigerant flow path, thereby increasing the residence time of the refrigerant in the purification chamber, which is conducive to more thorough phase change separation; third, the filler 442 makes the refrigerant more evenly distributed in the purification chamber, avoiding local concentrations that are too high or too low; fourth, the filler 442 can improve the purification efficiency, for example, promoting the liquefaction of high-boiling-point refrigerant in the first purification chamber 450, and enhancing the evaporation of low-boiling-point refrigerant in the second purification chamber 440, thereby improving the overall refrigerant purity; fourth, the filler 442 is a mature industrial material, easy to install and maintain, and has a simple and reliable structure.

[0089] In this way, by arranging the filler 442 in the purification chamber, the system can increase the contact area and flow path length of the refrigerant in the purification chamber, thereby improving the gas-liquid separation efficiency and the component purification effect.

[0090] In some specific embodiments, the packing material 442 can be a commonly used structure for a packed tower, such as Pall rings, Raschig rings, structured packing, wire mesh packing, etc., or a porous medium material. The present invention does not impose any particular limitation on this.

[0091] like Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, the heat pump system further includes a first control valve 10 , which is provided on the second branch 14 and located upstream of the heating section 441 .

[0092] In this embodiment, the second branch 14 is used to introduce part of the high-temperature and high-pressure exhaust gas into the rectifier 4 to provide heat for the heating section 441. The first control valve 10 is provided upstream of the heating section 441 to regulate the flow of the high-temperature refrigerant gas entering the heating section 441.

[0093] For example, when the heating effect in the second purification chamber 440 needs to be enhanced, the first control valve 10 opens wider, increasing the flow of refrigerant into the heating section 441. When the heating intensity needs to be reduced or heating needs to be stopped, the first control valve 10 opens narrower or even closes, restricting the flow of refrigerant into the heating section 441. The control method can be manual or automatic, such as PID control based on feedback signals from a temperature sensor.

[0094] By adjusting the opening of first control valve 10, the flow rate of high-temperature gas entering heating section 441 can be flexibly controlled, thereby adjusting the heating power to meet different operating conditions. Furthermore, the system can dynamically adjust the heating intensity based on changes in refrigerant composition or fluctuations in external ambient temperature, avoiding overheating or underheating, thereby improving separation efficiency and system stability.

[0095] In addition, when additional heating is not required, the system can reduce or cut off the use of high-temperature gas through the first control valve 10, thereby reducing energy consumption and improving the overall energy efficiency ratio.

[0096] like Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, a third branch 15 is further included, one end of the third branch 15 is connected between the liquid outlet 431 and the inlet of the second heat exchange channel 602, the other end of the third branch 15 is connected between the outlet of the second heat exchange channel 602 and the air supply port of the compressor 1, and the cooling section 451 is connected to the third branch 15.

[0097] It also includes a second control valve 11 and a third control valve 12 . The second control valve 11 is provided on the third branch 15 and upstream of the cooling section 451 . The third control valve 12 is provided on the first branch 13 and upstream of the second heat exchange channel 602 .

[0098] In this embodiment, the third branch 15 can provide cooling medium for the cooling section 451 , that is, liquid refrigerant from the liquid storage chamber 430 .

[0099] It is understood that the second control valve 11 is provided on the third branch 15 and is located upstream of the cooling section 451. The second control valve 11 can adjust the flow of the cooling medium entering the cooling section 451. Specifically, according to the operating conditions, the opening of the second control valve 11 can be adjusted to control whether the cooling function is turned on or the cooling intensity. The third control valve 12 is provided on the first branch 13 and is located upstream of the second heat exchange channel 602 of the regenerator 6. The third control valve 12 can control the flow of refrigerant through the second heat exchange channel 602, thereby adjusting the air supply or switching the refrigerant flow path.

[0100] For example, if both second control valve 11 and third control valve 12 are open, liquid refrigerant is diverted from liquid outlet 431 to cooling section 451 and second heat exchange channel 602. A portion of the refrigerant flows through second heat exchange channel 602 of regenerator 6, where it is heated and then enters the compressor 1 air inlet as a gas. Another portion of the refrigerant flows through cooling section 451 and, after completing its cooling task, also enters the compressor 1 air inlet. This mode is suitable for applications requiring enhanced refrigerant separation efficiency, such as low-temperature environments or when loads fluctuate significantly.

[0101] For another example, the third control valve 12 is open and the second control valve 11 is closed. At this time, all the liquid refrigerant flows through the regenerator 6 to be heated and evaporated before being fed into the compressor 1. This mode is suitable for stable operation without additional cooling assistance.

[0102] For another example, when the second control valve 11 is open and the third control valve 12 is closed, all liquid refrigerant flows through the third branch 15 through the cooling section 451, thereby enhancing the cooling effect of the first purification chamber 450. This mode is suitable for the initial startup phase or high humidity environments where enhanced refrigerant separation accuracy is required.

[0103] Thus, the third branch 15 is connected in series with the cooling section 451 to provide an independent cooling pathway, allowing the cooling section 451 to flexibly participate in the system circulation and enhancing the refrigerant separation capability of the first purification chamber 450. Furthermore, the second control valve 11 is positioned upstream of the cooling section 451 to precisely control the cooling section 451, improving system adaptability and response speed. Furthermore, the third control valve 12 is positioned on the first branch 13 to regulate the flow of supplemental air into the compressor 1, optimizing system energy efficiency and compressor 1 performance.

[0104] like Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, the heat pump system further includes a defrost branch 17 , the two ends of which are respectively connected to the air outlet 421 and the inlet of the evaporator 8 , and a defrost control valve 5 is provided on the defrost branch 17 .

[0105] In this embodiment, the heat pump system is also equipped with a defrost branch 17, which is used to quickly increase the temperature of the evaporator 8 when the system enters defrost mode to remove frost from its surface and improve system operating efficiency and stability. Specifically, the gas outlet 421 outputs the gaseous refrigerant separated and purified by the rectifier 4. One end of the defrost branch 17 is connected downstream of the gas outlet 421, and the other end is connected to the pipeline before the inlet of the evaporator 8. The defrost control valve 5 is located on the defrost branch 17 and can be opened or closed according to the system operating status.

[0106] It can be understood that in the conventional heating / cooling mode, the defrost control valve 5 is in a closed state, and the refrigerant flows to the evaporator 8 through the first heat exchange channel 601 and the second throttling device 7; in the defrost mode, the defrost control valve 5 is opened, and part of the high-temperature and low-pressure gaseous refrigerant flows directly into the evaporator 8 through the defrost branch 17 to heat its surface and melt the frost.

[0107] The defrosting process of the heat pump system of the present invention is specifically as follows:

[0108] like Figure 1 As shown, under normal operating conditions, the system operates according to a standard cooling or heating cycle. The refrigerant flows sequentially through compressor 1, condenser 2, first throttling device 3, rectifier 4, regenerator 6, second throttling device 7, and then enters evaporator 8, completing the heat absorption process. At this time, the defrost control valve 5 remains closed, and the defrost branch 17 does not participate in the cycle.

[0109] like Figure 2As shown, when frost on the surface of evaporator 8 reaches a set threshold, as determined by, for example, a temperature sensor or operating time, the control system initiates defrost mode. At this point, the controller opens defrost control valve 5, allowing the gaseous refrigerant from outlet 421 to bypass the regenerator 6 and second throttling device 7 and flow directly into evaporator 8 through defrost branch 17. Because this refrigerant is gaseous and has a relatively high temperature, it can quickly raise the internal temperature of evaporator 8, effectively melting the frost on its surface.

[0110] After defrosting is completed, the system returns to normal operation mode, the defrost control valve 5 is closed, and the refrigerant circulates along the original path again.

[0111] In summary, this embodiment introduces the defrost branch 17 and the defrost control valve 5 on the basis of the original non-azeotropic mixed working fluid heat pump system, thereby achieving effective control of the frosting problem of the evaporator 8.

[0112] like Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, the heat pump system also includes an evaporator fan 18, which is used to drive air to flow through the evaporator 8; a gas-liquid separator 9 is also provided on the refrigerant circulation loop, and the gas-liquid separator 9 is arranged on the refrigerant circulation loop and is located between the evaporator 8 and the return air port of the compressor 1.

[0113] As will be appreciated, evaporator fan 18 is positioned near evaporator 8 to force ambient air across the surface of evaporator 8, enhancing heat exchange efficiency between evaporator 8 and the refrigerant. By controlling the fan speed, the amount of heat absorbed by evaporator 8 can be adjusted to accommodate varying ambient temperatures and loads, improving overall system energy efficiency.

[0114] The gas-liquid separator 9 is used to separate the liquid component in the refrigerant returning from the evaporator 8 to the compressor 1 to prevent the liquid refrigerant from directly entering the compressor 1 and causing liquid hammer or damaging the internal components of the compressor 1.

[0115] A control method for a non-azeotropic mixed working fluid heat pump system provided by the present invention is described below. It should be noted that this control method is applied to the non-azeotropic mixed working fluid heat pump system described in the first aspect of the present invention.

[0116] like Figure 4 As shown, the control method includes: step S1, in response to the heating mode, controlling the first branch 13 to be in a connected state, and controlling the refrigerant to flow through the condenser 2, the first throttling device 3, the distillation device 4, the first heat exchange channel 601 of the regenerator 6, the second throttling device 7 and the evaporator 8 in sequence and enter the return air port of the compressor 1.

[0117] From the above, it can be seen that the control method of the present invention, after determining that the heat pump system enters the heating mode, will control the first branch 13 to remain connected, and control the refrigerant to flow through the condenser 2, the first throttling device 3 and the rectifier 4 in sequence. Due to the different boiling points of the mixed refrigerants, after flowing through the condenser 2, the low-boiling-point refrigerant is mostly gaseous, and the high-boiling-point refrigerant is mostly liquid. Therefore, the mixed refrigerant is separated into gaseous refrigerant and liquid refrigerant in the rectifier 4, wherein most of the gaseous refrigerant is low-boiling-point refrigerant and a small part is high-boiling-point refrigerant. The gaseous refrigerant will pass through the air outlet 421, the first heat exchange channel 601, the second throttling device 7 and the evaporator 8 and finally flow into the return air port of the compressor 1, and the liquid refrigerant will enter the first branch 13 through the liquid outlet 431, and provide cooling refrigerant for the cooling section 451, and flow through the second heat exchange channel 602. The refrigerant in the first branch 13 will eventually flow into the air supply port of the compressor 1.

[0118] In the above-mentioned circulation path, since part of the liquid refrigerant passes through the cooling section 451 after flowing out of the rectifier 4, the liquid refrigerant will exchange heat with the gaseous refrigerant through the cooling section 451, thereby liquefying the high-boiling-point refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of the low-boiling-point refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and thus improving the low-temperature heating capacity of the system. In addition, the present application can reduce the exhaust pressure of the compressor 1 by introducing the liquid refrigerant into the air supply port of the compressor 1, thereby enabling the heat pump to operate stably at low ambient temperatures.

[0119] In addition, while controlling the connectivity of the first branch 13, the present application utilizes the first throttling device 3 and the second throttling device 7 to perform secondary throttling on the refrigerant, and further cools the low-boiling-point refrigerant through the regenerator 6, so that the low-boiling-point refrigerant is fully condensed and has a large degree of supercooling, thereby reducing subsequent throttling losses, thereby improving the heating capacity and energy efficiency of the heat pump system; at the same time, the temperature of the high-boiling-point refrigerant is increased, which helps it to evaporate smoothly at the air inlet of the compressor 1 and participate in the compression cycle.

[0120] like Figure 4 As shown, in some embodiments of the present invention, the control method further includes:

[0121] Step S2, in response to the defrost mode, control the second branch 14 and the defrost branch 17 to be in a connected state, control the first branch 13 to be in a disconnected state, and control the refrigerant to flow through the second branch 14, the rectifier 4, the defrost branch 17 and the evaporator 8 in sequence and enter the return air port of the compressor 1.

[0122] In this way, in the above-mentioned defrosting process, since it does not pass through the condenser 2, the first throttling device 3 and the second throttling device 7, the pressure difference of the entire flow path is small, thereby increasing the refrigerant flow through the compressor 1, making the compressor 1 do more work, and improving the defrosting effect of the evaporator 8.

[0123] For example, in the heat pump system, the refrigerant circulation loop also includes a second branch 14, a third branch 15, a first control valve 10, a second control valve 11 and a third control valve 12 and a defrost branch 17; the two ends of the second branch 14 are respectively connected to the exhaust port of the compressor 1 and the distillation inlet 411 and are connected in parallel with the condenser 2, and the heating section 441 is connected to the second branch 14; the first control valve 10 is arranged on the second branch 14 and is located upstream of the heating section 441.

[0124] The third branch 15 is connected in parallel with the first branch 13 and its two ends are respectively connected to the pipeline between the liquid outlet 431 and the air supply port of the compressor 1, and the cooling section 451 is connected to the third branch 15; the second control valve 11 is arranged on the third branch 15 and is located upstream of the cooling section 451, and the third control valve 12 is arranged on the first branch 13 and is located upstream of the second heat exchange channel 602; the defrost branch 17 is connected between the air outlet 421 and the inlet of the evaporator 8 and is arranged in parallel with the first heat exchange channel 601 and the second throttling device 7, and a defrost control valve 5 is provided on the defrost branch 17.

[0125] Furthermore, in some embodiments of the present invention, the control method further includes:

[0126] Step S3: In response to the heating mode, the second branch 14 is controlled to be in a connected state, and the refrigerant is controlled to flow sequentially through the condenser 2, the first throttling device 3, the rectifier 4, the first heat exchange channel 601 of the regenerator 6, the second throttling device 7, and the evaporator 8, and then into the return air port of the compressor 1. In this way, the heating section 441 heats the liquid refrigerant in the rectifier 4. The heating causes the low-boiling-point components in the liquid refrigerant to evaporate preferentially, forming a gaseous state that rises to the gas storage chamber 420, while the high-boiling-point components that have not been evaporated remain in a liquid state and sink into the liquid storage chamber 430. This improves the separation efficiency of the refrigerant components and increases the content of the low-boiling-point refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, making the heat pump suitable for lower ambient temperatures, and further enhancing the low-temperature heating capacity of the system.

[0127] like Figure 5 As shown, the control method specifically includes:

[0128] Step S100, in response to the heating mode, controlling the defrost control valve 5 to be in a closed state, and controlling the first throttling device 3, the second throttling device 7, the first control valve 10, the second control valve 11 and the third control valve 12 to be in an open state;

[0129] Step S200, in response to the defrost mode, controlling the first control valve 10 and the defrost control valve 5 to be in the open state, and controlling the first throttling device 3, the second throttling device 7, the second control valve 11 and the third control valve 12 to be in the closed state.

[0130] The following is a detailed introduction to the heating mode and the defrosting mode of the heat pump system of the present invention based on the above control method.

[0131] like Figure 1 As shown, in the heating mode, the specific control logic is as follows: the defrost control valve 5 is closed, at this time, the defrost branch 17 does not participate in the work, and the refrigerant flows along the normal path. The second throttling device 7 is opened, allowing the refrigerant to enter the evaporator 8 after throttling to absorb heat. The first control valve 10 is opened, thereby guiding part of the high-temperature and high-pressure gas discharged from the compressor 1 to flow through the second branch 14 to the heating section 441 in the distillation device 4 to provide heat for the second purification chamber 440. The second control valve 11 is opened, so that the cooling section 451 is connected to the third branch 15, which is used to cool the refrigerant in the first purification chamber 450. The third control valve 12 is opened, thereby allowing the high-boiling-point refrigerant to enter the second heat exchange channel 602 of the regenerator 6 through the first branch 13 for heating and then replenishing the compressor 1.

[0132] like Figure 1 As shown, in heating mode, the specific operating process is as follows: Compressor 1 compresses the refrigerant into high-temperature, high-pressure gas. A portion enters condenser 2 directly to release heat, while the remaining portion enters heating section 441 through second branch 14 to provide heat to the second purification chamber 440. After being reduced in pressure by the first throttling device 3, the refrigerant enters rectifier 4, where initial gas-liquid stratification occurs in separation chamber 410. The gas rises to the first purification chamber 450, while the liquid sinks to the second purification chamber 440. Within the first purification chamber 450, the cooling section 451 locally cools the refrigerant, promoting the liquefaction and descent of high-boiling-point components. Within the second purification chamber 440, the heating section 441 heats the refrigerant, causing the low-boiling-point components to evaporate and rise. The purified low-boiling-point gas flows out of the gas outlet 421, passes through the first heat exchange channel 601 of the regenerator 6, and after cooling, passes through the second throttling device 7 and enters the evaporator 8, absorbing ambient heat before returning to compressor 1. The high-boiling-point refrigerant liquid selectively flows to the air supply port of the compressor 1 through the first branch 13 or the third branch 15 to supplement the input of the compressor 1.

[0133] like Figure 2As shown, in defrost mode, the specific control logic is as follows: the defrost control valve 5 opens, thereby connecting the defrost branch 17, allowing high-temperature, low-boiling-point gas to flow directly into the evaporator 8, which is used to quickly heat the surface of the evaporator 8. The first throttling device 3 closes, preventing the high-temperature, high-pressure gas flowing out of the compressor 1 from continuing to flow through the condenser 2. Instead, all of it passes through the second branch 14 to participate in the subsequent defrost process. The first control valve 10 opens to direct all high-temperature, high-pressure gas flowing out of the compressor 1 through the second branch 14 and into the rectifier 4, thereby short-circuiting the condenser 2 and allowing more high-temperature, high-pressure gas to participate in the defrost process. The second throttling device 7 closes, preventing the refrigerant from continuing to enter the evaporator 8 through the original path, avoiding interference with the defrost process. The second control valve 11 closes, thereby stopping the cold supply to the cooling section 451 to avoid affecting the thermal balance inside the rectifier 4. The third control valve 12 closes, which means that the high-boiling-point refrigerant replenishment operation is suspended, concentrating resources on defrosting.

[0134] like Figure 2 As shown, in the defrost mode, the specific working process is as follows: the compressor 1 compresses the mixed working fluid into a high-temperature and high-pressure gas. The high-temperature and high-pressure gas does not pass through the condenser 2, but directly enters the second branch 14 through the opened first control valve 10, and enters the top of the rectifier 4. At this time, the first control valve 10 is in a larger step position to ensure sufficient gas flow. The high-temperature and high-pressure gas flows out from the top of the rectifier 4, passes through the defrost control valve 5 and enters the defrost branch 17, and then flows directly into the evaporator 8 for defrosting. The high-temperature and high-pressure gas entering the evaporator 8 releases a large amount of heat, rapidly raising the surface temperature of the evaporator 8 and melting the surface frost. After defrosting, the mixed working fluid flows through the gas-liquid separator 9, and the separated gaseous part directly returns to the compressor 1 to continue circulation.

[0135] It can be understood that in the above-mentioned defrosting process, since it does not pass through the condenser 2, the first throttling device 3 and the second throttling device 7, the pressure difference of the entire flow path is small, thereby increasing the refrigerant flow through the compressor 1, making the compressor 1 do more work, and improving the defrosting effect of the evaporator 8.

[0136] In summary, the heat pump system of the present invention directly utilizes the high-temperature, high-pressure gas discharged from compressor 1 for defrosting, eliminating the need for an additional heating source and achieving energy conservation and environmental protection. Furthermore, since the high-temperature, high-pressure gas does not pass through condenser 2, unnecessary energy loss is reduced, improving the overall energy efficiency of the system. Furthermore, the pressure differential across the entire flow path is small, increasing the refrigerant flow through compressor 1, allowing compressor 1 to perform more work and further enhancing the defrosting effect.

[0137] In summary, according to the control method of the non-azeotropic mixed refrigerant heat pump system of the present invention, the separation purity of the mixed refrigerant is improved, allowing the low-boiling point refrigerant with higher purity to enter the evaporator 8 for heat absorption, thereby improving the low-temperature performance of the unit; at the same time, the defrost branch 17 is used to reduce the system pressure difference, increase the mixed refrigerant flow rate, and increase the work of the compressor 1, thereby improving the defrost effect.

[0138] Figure 6 The schematic structural diagram of an embodiment of a non-azeotropic mixed working fluid heat pump system provided by an embodiment of the present invention is shown. The specific embodiment of the present invention does not limit the specific implementation of the non-azeotropic mixed working fluid heat pump system.

[0139] like Figure 6 As shown, the heat pump may include: a processor 502 , a communications interface 504 , a memory 506 , and a communication bus 508 .

[0140] Processor 502, communication interface 504, and memory 506 communicate with each other via communication bus 508. Communication interface 504 is used to communicate with other devices, such as client devices or other server network elements. Processor 502 is used to execute program 510, which may specifically perform the steps of the aforementioned embodiment of the control method for a non-azeotropic mixed working fluid heat pump system.

[0141] Specifically, the program 510 may include program code including computer-executable instructions.

[0142] Processor 502 may be a central processing unit (CPU), an application-specific integrated circuit (ASIC), or one or more integrated circuits configured to implement embodiments of the present invention. The one or more processors included in the non-azeotropic mixture heat pump system may be processors of the same type, such as one or more CPUs, or may be processors of different types, such as one or more CPUs and one or more ASICs.

[0143] The memory 506 is used to store the program 510. The memory 506 may include a high-speed RAM memory, and may also include a non-volatile memory (non-volatile memory), such as at least one disk memory.

[0144] The program 510 can be specifically called by the processor 502 to enable the non-azeotropic mixed working fluid heat pump system to execute the relevant steps in the above-mentioned control method embodiment for the non-azeotropic mixed working fluid heat pump system.

[0145] It can be understood by those skilled in the art that Figure 6 The structure shown is only for illustration and does not limit the structure of the above-mentioned equipment. For example, the non-azeotropic mixed working fluid heat pump system may also include Figure 6 More or fewer components than shown, or with Figure 6 Different configurations shown.

[0146] The embodiment of the present invention also provides a computer-readable storage medium. The above-mentioned method according to the embodiment of the present invention can be implemented in hardware, firmware, or implemented as a computer code that can be recorded in a storage medium, or implemented as a computer code that is originally stored in a remote storage medium or a non-temporary machine-readable storage medium and downloaded through a network and will be stored in a local storage medium, so that the method described herein can be stored in such software processing on a storage medium using a general-purpose computer, a dedicated processor, or programmable or dedicated hardware. Among them, the storage medium can be a magnetic disk, an optical disk, a read-only storage memory, a random access memory, a flash memory, a hard disk or a solid-state drive, etc.; further, the storage medium can also include a combination of the above-mentioned types of memory. It can be understood that a computer, a processor, a microprocessor controller or programmable hardware includes a storage component that can store or receive software or computer code. When the software or computer code is accessed and executed by a computer, a processor or hardware, the method shown in the above embodiment is implemented.

[0147] In the specific contents of the above-mentioned specific implementation methods, the various technical features can be combined in any non-contradictory manner. In order to make the description concise, not all possible combinations of the above-mentioned technical features are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0148] The specific contents of the above-mentioned specific embodiments merely represent several embodiments of the present invention. While the description is relatively specific and detailed, it should not be construed as limiting the scope of the present invention. It should be noted that a person skilled in the art may make various modifications and improvements without departing from the scope of the present invention, and these modifications and improvements fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be based on the appended claims.

Claims

1. A non-azeotropic mixed working fluid heat pump system, characterized in that: include: A compressor (1) and a refrigerant circulation circuit connected to the compressor (1) to form a circuit, wherein the refrigerant circulation circuit is provided with a condenser (2), a first throttling device (3), a rectifier (4), a regenerator (6), a second throttling device (7) and an evaporator (8) in sequence along the refrigerant flow direction; The rectifier (4) is provided with a rectification inlet (411), a gas outlet (421) and a liquid outlet (431); a cooling section (451) is provided inside the rectifier (4); the liquid outlet (431) is connected to the gas supply port of the compressor (1) through a first branch (13); and the cooling section (451) is connected to the first branch (13); The regenerator (6) has a first heat exchange channel (601) and a second heat exchange channel (602) for exchanging heat with each other, the first heat exchange channel (601) being connected between the air outlet (421) and the inlet of the second throttling device (7), and the second heat exchange channel (602) being connected to the first branch (13); A heating section (441) is further provided inside the rectifier (4); The refrigerant circulation loop further includes a second branch (14), the two ends of which are respectively connected to the exhaust port of the compressor (1) and the distillation inlet (411), the heating section (441) is connected to the second branch (14), and the second branch (14) is provided with a first control valve (10).

2. The non-azeotropic mixed working fluid heat pump system according to claim 1, characterized in that: The interior of the rectifier (4) is provided with a gas storage chamber (420), a first purification chamber (450), a separation chamber, a second purification chamber (440) and a liquid storage chamber (430) which are interconnected from top to bottom. The first purification chamber (450) is provided with the cooling section (451), and the second purification chamber (440) is provided with the heating section (441).

3. The non-azeotropic mixed working fluid heat pump system according to claim 1, characterized in that: The cooling section (451) has a cooling inlet and a cooling outlet, and the cooling inlet is located above the cooling outlet; And / or, the heating section (441) has a heating inlet and a heating outlet, and the heating inlet is located below the heating outlet.

4. The non-azeotropic mixed working fluid heat pump system according to claim 2, characterized in that: The first purification chamber (450) and / or the second purification chamber (440) are filled with a filler (442), and the filler (442) has a circulation gap for the circulation of the refrigerant.

5. The non-azeotropic mixed working fluid heat pump system according to any one of claims 1 to 4, characterized in that: It also includes a third branch (15), one end of the third branch (15) is connected between the liquid outlet (431) and the inlet of the second heat exchange channel (602), the other end of the third branch (15) is connected between the outlet of the second heat exchange channel (602) and the air supply port of the compressor (1), and the cooling section (451) is connected to the third branch (15); It also includes a second control valve (11) and a third control valve (12), wherein the second control valve (11) is arranged on the third branch (15), and the third control valve (12) is arranged on the first branch (13).

6. The non-azeotropic mixed working fluid heat pump system according to any one of claims 1 to 4, characterized in that: It also includes a defrost branch (17), the two ends of which are respectively connected to the air outlet (421) and the inlet of the evaporator (8), and a defrost control valve (5) is provided on the defrost branch (17).

7. A control method for a non-azeotropic mixed working fluid heat pump system, applied to the non-azeotropic mixed working fluid heat pump system according to any one of claims 1 to 6, characterized in that: The control method includes: In response to the heating mode, the first branch (13) is controlled to be in a connected state, and the refrigerant is controlled to flow through the condenser (2), the first throttling device (3), the rectifier (4), the first heat exchange channel (601) of the regenerator (6), the second throttling device (7) and the evaporator (8) in sequence and enter the return air port of the compressor (1).

8. The control method of the non-azeotropic mixed working fluid heat pump system according to claim 7, characterized in that: The heat pump system further comprises a second branch (14), the two ends of which are respectively connected to the exhaust port of the compressor (1) and the distillation inlet (411); a heating section (441) is further provided inside the rectifier (4), and the heating section (441) is connected to the second branch (14); The control method further includes: In response to the heating mode, the second branch (14) is controlled to be in a connected state, and the refrigerant is controlled to flow through the condenser (2), the first throttling device (3), the rectifier (4), the first heat exchange channel (601) of the regenerator (6), the second throttling device (7) and the evaporator (8) in sequence and enter the return air port of the compressor (1).

9. The control method of the non-azeotropic mixed working fluid heat pump system according to claim 8, characterized in that: The heat pump system further comprises a defrost branch (17), wherein both ends of the defrost branch (17) are respectively connected to the air outlet (421) and the inlet of the evaporator (8); The control method further includes: In response to the defrost mode, the second branch (14) and the defrost branch (17) are controlled to be in a connected state, the first branch (13) is controlled to be in a disconnected state, and the refrigerant is controlled to flow through the second branch (14), the rectifier (4), the defrost branch (17) and the evaporator (8) in sequence and enter the return air port of the compressor (1).

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