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

Abstract

The invention relates to the technical field of heat pumps, and discloses a non-azeotropic mixed working medium heat pump system and a control method thereof. The heat pump system comprises a compressor and a refrigerant circulation loop, wherein a condenser, a first throttling device, a rectifier, a heat regenerator, a second throttling device and an evaporator are sequentially arranged on the refrigerant circulation loop in the flowing direction of a refrigerant; the rectifier is provided with a rectification inlet, an air outlet and a liquid outlet, a cooling section is arranged in the rectifier, the liquid outlet is communicated with an air supply port of the compressor through a first branch, and the cooling section is connected to the first branch; the heat regenerator is provided with a first heat exchange channel and a second heat exchange channel, the first heat exchange channel is connected between the air outlet and an inlet of the second throttling device, and the second heat exchange channel is connected into the first branch. According to the heat pump system, efficient separation and energy recovery of refrigerant components are achieved by introducing the rectifier and the heat regenerator, so that the heating capacity of the heat pump system is improved, and the low-temperature heating capacity of the system is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pumps, and particularly to azeotropic mixture refrigerant heat pump system and its control method. Background Art

[0002] Heat pumps have evolved from household heating and cooling applications to whole - society heat applications, with a huge change in the application scenarios. Due to the large temperature change range between the heat source and the heat sink, traditional single refrigerants can hardly meet the usage requirements, such as heating at extremely low ambient temperatures in the building field and heating at extremely high water temperatures in the industrial field.

[0003] Azeotropic mixture refrigerants can flexibly select the refrigerant components and their proportions according to the application scenarios, increase the temperature difference between the heat source and the heat sink, and meet the large temperature - span requirements of specific application scenarios. In recent years, azeotropic mixture refrigerant systems have been more and more widely used.

[0004] However, in the actual application of the mixture refrigerant system, the mixture refrigerant cannot be well separated and purified in the separator, and not enough low - boiling - point refrigerant can enter the evaporator to absorb heat, resulting in limited heating capacity of the heat pump system. Summary of the Invention

[0005] The first technical problem to be solved by the present invention is to provide an azeotropic mixture refrigerant heat pump system, which effectively solves the problem of limited heating capacity of the heat pump system caused by low refrigerant utilization rate.

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

[0007] The above - mentioned first technical problem is solved by the following technical solutions: An azeotropic mixture refrigerant heat pump system, comprising: A compressor and a refrigerant circulation loop connected to the compressor to form a circuit. Along the refrigerant flow direction on the refrigerant circulation loop, a condenser, a first throttling device, a rectifier, a regenerator, a second throttling device, and an evaporator are sequentially arranged; The rectifier is provided with a rectification inlet, an air outlet, and a liquid outlet. A cooling section is arranged inside the rectifier. The liquid outlet is communicated with the gas - supplementing 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 for heat exchange 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.

[0008] Compared with the background art, the non-azeotropic mixture refrigerant heat pump system of the present invention has the following beneficial effects: In the heat pump system of the present invention, a rectifier and a regenerator are introduced, 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 refrigerant, after flowing through the condenser, most of the low-boiling refrigerant is in a gaseous state, and most of the high-boiling refrigerant is in a liquid state. Therefore, the mixed refrigerant will be separated into a gaseous refrigerant and a liquid refrigerant in the rectifier. Most of the gaseous refrigerant is the low-boiling refrigerant, and a small part is the high-boiling 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 suction port of the compressor. The liquid refrigerant will enter the first branch through the liquid outlet, provide cooling refrigerant for the cooling section, and flow through the second heat exchange channel. The refrigerant in the first branch finally converges into the gas supplement port of the compressor.

[0009] In the above circulation path, since part of the liquid refrigerant will pass 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 refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of the low-boiling refrigerant flowing through the evaporator, thereby increasing the heating capacity of the heat pump system, enabling the heat pump to be applicable to lower ambient temperatures, and further enhancing the low-temperature heating capacity of the system. In addition, in the present application, by introducing the liquid refrigerant into the gas supplement port of the compressor to achieve gas supplement and enthalpy increase, the exhaust pressure and exhaust temperature of the compressor can be reduced, so that the heat pump can operate stably at low ambient temperatures.

[0010] In addition, in the present application, the first throttling device and the second throttling device are used to throttle the refrigerant twice, and the low-boiling refrigerant is further cooled by the regenerator to fully condense the low-boiling refrigerant and have a large degree of subcooling, reducing the subsequent throttling loss, thereby increasing the heating capacity and energy efficiency of the heat pump system.

[0011] In one embodiment, a heating section is further provided inside the rectifier; The refrigerant circulation loop further includes a second branch, the two ends of the second branch are respectively connected to the exhaust port of the compressor and the rectification inlet, the heating section is connected to the second branch, and a first control valve is provided on the second branch.

[0012] In one embodiment, a gas storage cavity, a first purification cavity, a separation cavity, a second purification cavity and a liquid storage cavity are sequentially provided from top to bottom inside the rectifier, the cooling section is provided in the first purification cavity, and the heating section is provided in the second purification cavity.

[0013] In one embodiment, the cooling section has a cooling inlet and a cooling outlet, and the cooling inlet is located above the cooling outlet; And / or, the heating section has a heating inlet and a heating outlet, and the heating inlet is located below the heating outlet.

[0014] 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 through.

[0015] 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, and the other end of the third branch is connected between the outlet of the second heat exchange channel and the gas supplement port of the compressor. The cooling section is connected to the third branch; A second control valve and a third control valve are further included. The second control valve is arranged on the third branch, and the third control valve is arranged on the first branch.

[0016] In one embodiment, a defrosting branch is further included. Both ends of the defrosting branch are respectively communicated with the gas outlet and the inlet of the evaporator, and a defrosting control valve is arranged on the defrosting branch.

[0017] The above second technical problem is solved by the following technical solutions: A control method for azeotropic mixture refrigerant heat pump system, which is applied to the azeotropic mixture refrigerant heat pump system of the first aspect of the present invention. The control method includes: In response to the heating mode, control the first branch to be in a connected state, and control the refrigerant to flow through the condenser, the first throttling device, the rectifier, the first heat exchange channel of the regenerator, the second throttling device and the evaporator in sequence and enter the suction port of the compressor.

[0018] Compared with the background technology, the control method of the azeotropic mixture refrigerant heat pump system of the present invention has the following beneficial effects: After determining that the heat pump system operates in the heating mode, the control method of the present invention will control the first branch to remain in a connected state, and control the mixed refrigerant to flow through the condenser, the first throttling device and the rectifier in sequence. Since the boiling points of the mixed refrigerant are different, after flowing through the condenser, most of the low-boiling refrigerant is in a gaseous state, and most of the high-boiling refrigerant is in a liquid state. Therefore, the mixed refrigerant will be separated into a gaseous refrigerant and a liquid refrigerant in the rectifier. Most of the gaseous refrigerant is the low-boiling refrigerant, and a small part is the high-boiling refrigerant. The gaseous refrigerant will pass through the gas outlet, the first heat exchange channel, the second throttling device and the evaporator and finally flow into the suction port of the compressor, while the liquid refrigerant will enter the first branch through the liquid outlet, provide cooling refrigerant for the cooling section, and flow through the second heat exchange channel. The refrigerant in the first branch finally converges into the gas supplement port of the compressor.

[0019] In the above-mentioned circulation path, since part of the liquid refrigerant will pass through the cooling section after flowing out of the rectifier, the liquid refrigerant will exchange heat with the gaseous refrigerant when passing through the cooling section, thereby liquefying the high-boiling refrigerant contained in the gaseous refrigerant, so as to purify the gaseous refrigerant, increase the content of the low-boiling refrigerant flowing through the evaporator, improve the heating capacity of the heat pump system, enable the heat pump to be applicable to lower ambient temperatures, and further enhance the low-temperature heating capacity of the system. In addition, by introducing the liquid refrigerant into the gas replenishing port of the compressor, the present application realizes gas replenishing and enthalpy increase, which can reduce the exhaust pressure and exhaust temperature of the compressor, so that the heat pump can operate stably under low ambient temperatures.

[0020] In addition, when the first branch is controlled to be connected, the present application uses the first throttling device and the second throttling device to perform secondary throttling on the refrigerant, and further cools the low-boiling refrigerant through the regenerator, so that the low-boiling refrigerant is fully condensed and has a large degree of subcooling, reducing the subsequent throttling loss, thereby improving the heating capacity and energy efficiency of the heat pump system.

[0021] In one embodiment, the heat pump system further includes a second branch, both ends of the second branch are respectively connected to the exhaust port of the compressor and the rectification inlet, and a heating section is further provided inside the rectifier, and the heating section is connected to the second branch; The control method further includes: In response to the heating mode, control the second branch to be in a connected state, and control the refrigerant to flow through the condenser, the first throttling device, the rectifier, the first heat exchange channel of the regenerator, the second throttling device and the evaporator in sequence and enter the suction port of the compressor.

[0022] In one embodiment, the heat pump system further includes a defrosting branch, both ends of the defrosting branch are respectively connected to the air outlet and the inlet of the evaporator; The control method further includes: In response to the defrosting mode, control both the second branch and the defrosting branch to be in a connected state, control the first branch to be in a disconnected state, and control the refrigerant to flow through the second branch, the rectifier, the defrosting branch and the evaporator in sequence and enter the suction port of the compressor. Description of the Drawings

[0023] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the specific embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0024] Figure 1Schematic structural diagram of the zeotropic mixture refrigerant heat pump system according to an embodiment of the present invention in the heating mode; Figure 2 Schematic structural diagram of the zeotropic mixture refrigerant heat pump system according to an embodiment of the present invention in the defrosting mode; Figure 3 Schematic structural diagram of the rectifier according to an embodiment of the present invention; Figure 4 One of the schematic flowcharts of the control method of the zeotropic mixture refrigerant heat pump system according to an embodiment of the present invention; Figure 5 Another schematic flowchart of the control method of the zeotropic mixture refrigerant heat pump system according to an embodiment of the present invention; Figure 6 Schematic structural diagram of the zeotropic mixture refrigerant heat pump system according to another embodiment of the present invention.

[0025] Explanation of reference numerals: 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. Rectification inlet; 420. Gas storage chamber; 421. Gas outlet; 430. Liquid storage chamber; 431. Liquid outlet; 440. Second purification chamber; 441. Heating section; 442. Filler; 450. First purification chamber; 451. Cooling section. Detailed implementation manners

[0026] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present application without creative efforts shall fall within the protection scope of the present application.

[0027] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present application.

[0028] 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 quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of this application, unless otherwise specified, the meaning of "a plurality" is two or more.

[0029] In the description of this application, it should be noted that, unless otherwise clearly specified and defined, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0030] The following introduces azeotropic mixture refrigerant heat pump system and its control method according to the present invention with reference to the accompanying drawings.

[0031] As Figure 1 and Figure 2 shown, the azeotropic mixture refrigerant heat pump system according to the first aspect embodiment of the present invention includes a compressor 1 and a refrigerant circulation loop connected to the compressor 1 to form a loop. Along the refrigerant flow direction on the refrigerant circulation loop, a condenser 2, a first throttling device 3, a rectifier 4, a recuperator 6, a second throttling device 7, and an evaporator 8 are sequentially provided.

[0032] The rectifier 4 is provided with a rectification 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 communicated with the gas supplement port of the compressor 1 through a first branch 13, and the cooling section 451 is connected to the first branch 13. The recuperator 6 has a first heat exchange channel 601 and a second heat exchange channel 602 for heat exchange with each other. 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.

[0033] The azeotropic mixture refrigerant heat pump system according to the embodiment of the present invention is introduced in detail 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 recuperator 6, a second throttling device 7, and an evaporator 8. Among them, in the 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 the recuperator 6, second throttling device 7, evaporator 8, second heat exchange channel 602 of the recuperator 6, and finally returns to the compressor 1.

[0034] The rectifier 4 has three interfaces. Among them, the rectification inlet 411 is used to receive the refrigerant from the first throttling device 3; the gas outlet 421 is used to output the gaseous refrigerant; and the liquid outlet 431 is used to output the liquid refrigerant. The gas outlet 421 is located above the liquid outlet 431. A cooling section 451 is provided in the internal cavity of the rectifier 4. The cooling section 451 is connected through the first branch 13 to form a closed loop, and its function is to cool the refrigerant in the rectifier 4 to promote the liquefaction of the high-boiling refrigerant.

[0035] It can be understood that due to the different boiling points of the mixed refrigerant, after flowing through the condenser 2, most of the low-boiling refrigerant is in a gaseous state, and most of the high-boiling refrigerant is in a liquid state. Therefore, the mixed refrigerant will be separated into gaseous and liquid refrigerants in the rectifier 4, realizing the preliminary separation of the mixed refrigerant. At the same time, in the above-mentioned flow path, since some 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 refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant to increase the content of the low-boiling refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, enabling the heat pump to be applicable to lower ambient temperatures, and further enhancing the low-temperature heating capacity of the system.

[0036] The first branch 13 constitutes a gas replenishment circuit, that is, the gas replenishment circuit includes the liquid outlet 431, the first branch 13, and the gas replenishment port of the compressor 1; it realizes gas replenishment and enthalpy increase, and can reduce the exhaust pressure of the compressor 1, so that the heat pump can operate stably at low ambient temperatures.

[0037] The regenerator 6 includes two channels that exchange heat with each other but do not mix. Among them, the first heat exchange channel 601 connects the gas outlet 421 of the rectifier 4 and the second throttling device 7, and is used to cool the low-boiling refrigerant; the second heat exchange channel 602 is communicated with the first branch 13 and is used to heat the high-boiling refrigerant. It can be understood that the regenerator 6 is mainly used to realize the heat exchange between the high- and low-boiling refrigerants, thereby further cooling the low-boiling refrigerant, enabling the low-boiling refrigerant to be fully condensed and having a large degree of subcooling, reducing the subsequent throttling loss, and thus increasing the heating capacity and energy efficiency of the heat pump system.

[0038] Based on the above specific structure, the working principle of the heat pump system of the present invention is as follows: On the one hand, after the mixed refrigerant enters the rectifier 4, it will be separated into gaseous refrigerant and liquid refrigerant. Most of the gaseous refrigerant is low-boiling refrigerant, and a small part is high-boiling refrigerant. The gaseous refrigerant will pass through the gas outlet 421, the first heat exchange channel 601, the second throttling device 7 and the evaporator 8 and finally flow into the suction port of the compressor 1. The liquid refrigerant will enter the first branch 13 through the liquid outlet 431, 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 finally flow into the gas supplement port of the compressor 1. In the above 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 refrigerant contained in the gaseous refrigerant. At this time, the high-boiling refrigerant liquefies and sinks to the liquid outlet 431; the gaseous refrigerant continues to rise and is discharged through the gas outlet 421. The above closed-loop cooling method significantly enhances the liquefaction rate of the high-boiling components and improves the purity of the low-boiling refrigerant.

[0039] On the other hand, by introducing the liquid refrigerant into the gas supplement port of the compressor 1, the present application can reduce the exhaust pressure of the compressor 1, so that the heat pump can operate stably at low ambient temperature.

[0040] In addition, the present application uses the first throttling device 3 and the second throttling device 7 to throttle the refrigerant twice, and further cools the low-boiling refrigerant through the regenerator 6, so that the low-boiling refrigerant is fully condensed and has a large degree of subcooling, reducing the subsequent throttling loss, thereby improving the heating capacity and energy efficiency of the heat pump system.

[0041] Furthermore, the specific working process of the heat pump system of the present invention is as follows: During the rectification process, the mixed refrigerant is depressurized by the first throttling device 3 and enters the rectification inlet 411 of the rectifier 4; in the rectifier 4, due to the cooling effect of the cooling section 451, the high-boiling refrigerant quickly liquefies and sinks to the liquid outlet 431; the low-boiling 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 the separation.

[0042] During the heat regeneration process, the gaseous refrigerant discharged from the gas outlet 421 of the rectifier 4 enters the first heat exchange channel 601 of the regenerator 6 and is cooled by the liquid refrigerant in the second heat exchange channel 602 here; the cooled refrigerant enters the second throttling device 7, is depressurized again and then 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 gas supplement port of the compressor 1 through the first branch 13 and participates in the compression cycle as an intermediate-pressure gas.

[0043] As described above, in the heat pump system of the present invention, a rectifier 4 and a regenerator 6 are introduced, such 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, most of the low-boiling refrigerant is in a gaseous state and most of the high-boiling refrigerant is in a liquid state. Therefore, the mixed refrigerant is separated into a gaseous refrigerant and a liquid refrigerant in the rectifier 4, wherein most of the gaseous refrigerant is the low-boiling refrigerant and a small part is the high-boiling 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 suction port of the compressor 1, while the liquid refrigerant will enter the first branch 13 through the liquid outlet 431, and provide the refrigerant for cooling for the cooling section 451, and flow through the second heat exchange channel 602. The refrigerant in the first branch 13 finally converges into the gas supply port of the compressor 1.

[0044] In the above 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 exchanges heat with the gaseous refrigerant through the cooling section 451, thereby liquefying the high-boiling refrigerant contained in the gaseous refrigerant, thereby purifying the gaseous refrigerant, so as to increase the content of the low-boiling refrigerant flowing through the evaporator 8, thereby increasing the heating capacity of the heat pump system, enabling the heat pump to be applicable to a lower ambient temperature, and further enhancing the low-temperature heating capacity of the system. In addition, by introducing the liquid refrigerant into the gas supply port of the compressor 1 in the present application, the exhaust pressure of the compressor 1 can be reduced, so that the heat pump can operate stably at a low ambient temperature.

[0045] In addition, the present application uses the first throttling device 3 and the second throttling device 7 to throttle the refrigerant twice, and further cools the low-boiling refrigerant through the regenerator 6, so that the low-boiling refrigerant is fully condensed and has a large degree of subcooling, reducing the subsequent throttling loss, thereby increasing the heating capacity and energy efficiency of the heat pump system; at the same time, the temperature of the high-boiling refrigerant is increased, which helps it to evaporate smoothly at the gas supply port of the compressor 1 and participate in the compression cycle.

[0046] As Figure 3 shown, according to some embodiments of the present invention, a heating section 441 is provided inside the rectifier 4.

[0047] The refrigerant circulation loop further includes a second branch 14, both ends of the second branch 14 are respectively communicated with the exhaust port of the compressor 1 and the rectification inlet 411, and the heating section 441 is connected to the second branch 14.

[0048] As Figure 3 shown, further, inside the rectifier 4, a gas storage cavity 420, a first purification cavity 450, a separation cavity, a second purification cavity 440 and a liquid storage cavity 430 are sequentially provided from top to bottom and are interconnected. A cooling section 451 is provided in the first purification cavity, and a heating section 441 is provided in the second purification cavity 440.

[0049] In the above embodiments, in the internal cavity of the rectifier 4, the first purification chamber 450 is used for the preliminary separation of the refrigerant components; the gas storage chamber 420 is used to collect the separated gaseous refrigerant; the liquid storage chamber 430 is used to collect the separated liquid refrigerant. The cooling section 451 is arranged in the first purification chamber 450, is connected through the first branch 13 and forms a closed loop, and its function is to cool the refrigerant in the first purification chamber 450 to promote the liquefaction of the high-boiling components.

[0050] The second purification chamber 440 is arranged inside the rectifier 4, is communicated with the rectification inlet 411 and the liquid storage chamber 430, and its function is to receive the mixed refrigerant from the first purification chamber 450 or directly from the rectification inlet 411. Inside the second purification chamber 440, the refrigerant is locally heated through the heating section 441. The heating promotes the preferential evaporation of the low-boiling components in the refrigerant to form a gas and rise to the gas storage chamber 420, while the unevaporated high-boiling components remain liquid and sink into the liquid storage chamber 430.

[0051] 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 led 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.

[0052] Its working principle and process are as follows: Due to the different boiling points of the mixed refrigerant, after flowing through the condenser 2, most of the low-boiling refrigerant is gaseous and most of the high-boiling refrigerant is liquid. Therefore, the mixed refrigerant will be separated into gaseous refrigerant and liquid refrigerant in the rectifier. Among them, most of the gaseous refrigerant is low-boiling refrigerant and a small part is high-boiling refrigerant. During 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 refrigerant component in the gaseous refrigerant condenses and liquefies. The liquefied high-boiling refrigerant falls into the liquid storage chamber 430, while the gaseous refrigerant rises to the gas storage chamber 420 after being purified 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. During the process of the liquid refrigerant descending and passing through the second purification chamber 440, the high-temperature and high-pressure gas from the second branch 14 heats the liquid refrigerant through the heating section 441. This process promotes the further evaporation of the low-boiling refrigerant component in the liquid refrigerant into gas, while the remaining high-boiling component liquefies more fully. The low-boiling refrigerant evaporated into gas rises and merges into the gas storage chamber 420, and the liquefied high-boiling refrigerant merges into the liquid storage chamber 430. In this way, through the dual purification effects of the first purification chamber 450 and the second purification chamber 440, the refrigerant separation effect is improved, ensuring a high degree of purity of the refrigerant components.

[0053] Meanwhile, the design of the second branch 14 enables energy recovery. Specifically, the second branch 14 is directly connected to the exhaust port of the compressor 1, introducing some of the high-temperature and high-pressure exhaust gas that might otherwise be wasted into the rectifier 4 as a heat source. After these high-temperature gases release heat through the heat generation section 441, they return to the refrigerant cycle, reducing the demand for external energy and improving the energy efficiency ratio of the system.

[0054] Finally, the refrigerant after double purification continues to circulate along their respective paths. The gaseous refrigerant is cooled in the regenerator 6 and then enters the second throttling device 7, where it absorbs heat and evaporates in the evaporator 8; the liquid refrigerant returns to the gas supplement port of the compressor 1 through the first branch 13 to supplement the refrigerant cycle of the system and avoid the risk of wet stroke at the same time.

[0055] In summary, the above design not only improves the separation efficiency of the refrigerant components, but also heats the refrigerant in the second purification chamber 440 by utilizing the heat discharged from the compressor 1, without introducing external energy, achieving effective utilization of energy. This not only optimizes the energy efficiency of the system, but also enhances the operation stability and safety. In addition, the purer refrigerant components contribute to improving the working efficiency of subsequent components and reducing performance fluctuations caused by uneven refrigerant distribution, enabling the entire heat pump system to maintain a highly efficient and stable operating state under different working conditions.

[0056] For example, the air outlet 421, the gas storage chamber 420, the first purification chamber 450, the rectification 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.

[0057] Among them, a separation chamber 410 is also formed between the first purification chamber 450 and the second purification chamber 440, and the rectification inlet 411 is communicated with the separation chamber 410. The above structural design enables the refrigerant to be preliminarily stratified according to the gas-liquid phase state after entering, and targeted component purification is completed in the upper and lower purification chambers respectively. For example, when the mixed refrigerant enters the separation chamber 410 through the rectification inlet 411, the gas component in the mixed refrigerant rises and is purified in the first purification chamber 450, while the liquid component in the mixed refrigerant descends and is purified in the second purification chamber 440.

[0058] In the internal space of the entire rectifier 4, the specific rectification process of the refrigerant is as follows: After being throttled and depressurized by the first throttling device 3, the refrigerant enters the rectifier 4 in a gas-liquid mixed state through the rectification inlet 411 and flows into the separation chamber 410. The gas component in the refrigerant rises and enters the upper first purification chamber 450; the liquid component in the refrigerant descends and enters the lower second purification chamber 440. This stage realizes the preliminary gas-liquid stratification of the refrigerant and lays a foundation for subsequent purification.

[0059] The gas entering the first purification chamber 450 is mainly a low-boiling refrigerant, which is further purified here to remove the entrained high-boiling gas. Finally, the pure low-boiling 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.

[0060] The liquid entering the second purification chamber 440 is mainly a high-boiling refrigerant. A heating section 441 is provided in this chamber to receive the heat from the exhaust of the compressor 1 and heat the liquid. The heating effect promotes the evaporation and rise of the remaining low-boiling refrigerant components, which finally also flow into the gas storage chamber 420; while the unevaporated high-boiling refrigerant continues to sink, enters the liquid storage chamber 430, and is output through the liquid outlet 431 and returns to the gas supplement port of the compressor 1 through the first branch 13 to achieve intermediate gas supplement.

[0061] In this way, the system enhances the separation precision by introducing a dual-chamber purification mechanism. Specifically, the upper first purification chamber 450 focuses on the purification of low-boiling gas, while the lower second purification chamber 440 further purifies the high-boiling liquid through heating, thereby realizing the hierarchical treatment and refined control of the refrigerant components. At the same time, the system actively separates the mixed refrigerant according to the gas-liquid state by introducing the separation chamber 410, avoiding mutual interference and improving the subsequent purification efficiency. From the above, the above structural settings enable purer refrigerant to enter the subsequent circulation path, which helps to improve the heat exchange efficiency.

[0062] As Figure 3 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.

[0063] It should be explained that the liquid refrigerant flows in the cooling section 451. The liquid flows in from the upper part and out from the lower part, realizing natural downward flow through the action of gravity without additional power measures, and at the same time improving the cooling efficiency of the refrigerant in the rectifier 4; while the gaseous refrigerant flows in the heating section, the gas flows in from the lower part and out from the upper part, realizing natural upward flow through the action of lift force, also without additional power measures, and at the same time improving the heating efficiency of the refrigerant in the rectifier 4.

[0064] In this way, the present invention fully utilizes the action of gravity and the natural lift force of the gas by carefully designing the inlet and outlet positions and their flow directions of the cooling section 451 and the heating section 441, avoiding the need for additional power equipment, simplifying the system structure and reducing the maintenance cost; at the same time, realizing efficient cooling and heating, and improving the separation efficiency and energy efficiency performance of the zeotropic mixture heat pump system.

[0065] Further, 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 through.

[0066] Specifically, the packing material 442 has the following advantages: First, the packing material 442 can significantly enhance the heat and mass transfer efficiency between gas and liquid, and improve the separation accuracy of refrigerant components; Second, the packing material 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 packing material 442 makes the refrigerant distribution in the purification chamber more uniform, avoiding local concentration being too high or too low; Fourth, the packing material 442 can improve the purification efficiency. For example, it promotes the liquefaction of high-boiling refrigerants in the first purification chamber 450 and strengthens the evaporation of low-boiling refrigerants in the second purification chamber 440, thus overall improving the refrigerant purity; Fourth, the packing material 442 is a mature industrial material, which is easy to install, maintain, and has a simple and reliable structure.

[0067] In this way, by arranging the packing material 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 component purification effect.

[0068] In some specific embodiments, the packing material 442 can be the common structural forms of a packed tower, such as Pall rings, Raschig rings, structured packings, wire mesh packings, etc., or can be a porous medium material. The present invention does not make special restrictions here.

[0069] As Figure 1 and Figure 2 shown, according to some embodiments of the present invention, the heat pump system further includes a first control valve 10, and the first control valve 10 is arranged on the second branch 14 and upstream of the heating section 441.

[0070] In this embodiment, the function of the second branch 14 is 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 arranged upstream of the heating section 441 and can adjust the flow rate of the high-temperature refrigerant gas entering the heating section 441.

[0071] For example, when it is necessary to enhance the heating effect in the second purification chamber 440, the opening of the first control valve 10 is increased to increase the refrigerant flow rate entering the heating section 441; when it is necessary to reduce the heating intensity or stop heating, the opening of the first control valve 10 is reduced or even closed to limit the refrigerant from flowing into the heating section 441. Among them, the control method can be manual adjustment or automatic control, such as PID adjustment based on the feedback signal of the temperature sensor, etc.

[0072] In this way, by adjusting the opening of the first control valve 10, the flow rate of the high-temperature gas entering the heating section 441 can be flexibly controlled, thereby adjusting the heating power to meet the requirements of different working conditions. At the same time, the system can dynamically adjust the heating intensity according to the change of refrigerant components or the fluctuation of the external environment temperature, avoiding overheating or insufficient heating, and improving the separation efficiency and system stability.

[0073] 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, reduce energy consumption, and thus improve the overall energy efficiency ratio.

[0074] Such as Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, it further 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, and the other end of the third branch 15 is connected between the outlet of the second heat exchange channel 602 and the gas supplement port of the compressor 1. The cooling section 451 is connected to the third branch 15.

[0075] It further includes a second control valve 11 and a third control valve 12. The second control valve 11 is arranged on the third branch 15 and upstream of the cooling section 451, and the third control valve 12 is arranged on the first branch 13 and upstream of the second heat exchange channel 602.

[0076] In this embodiment, the third branch 15 can provide a cooling medium for the cooling section 451, that is, the liquid refrigerant from the liquid storage chamber 430.

[0077] It can be understood that the second control valve 11 is arranged on the third branch 15 and upstream of the cooling section 451. The second control valve 11 can adjust the flow rate 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 to turn on the cooling function or adjust the cooling intensity. The third control valve 12 is arranged on the first branch 13 and upstream of the second heat exchange channel 602 of the regenerator 6. The third control valve 12 can control the refrigerant flow rate through the second heat exchange channel 602, so as to adjust the gas supplement amount or switch the refrigerant flow path.

[0078] For example, both the second control valve 11 and the third control valve 12 are opened. At this time, the liquid refrigerant is split from the liquid outlet 431 to the cooling section 451 and the second heat exchange channel 602. Among them, a part of the refrigerant flows through the second heat exchange channel 602 of the regenerator 6 and is heated and enters the gas supplement port of the compressor 1 in a gaseous form; another part of the refrigerant flows through the cooling section 451 and also enters the gas supplement port of the compressor 1 after completing the cooling task. This mode is applicable to occasions where it is necessary to enhance the refrigerant separation efficiency, such as in a low-temperature environment or when the load fluctuates greatly.

[0079] Another example is that the third control valve 12 is opened and the second control valve 11 is closed. At this time, all the liquid refrigerant flows through the regenerator 6, is heated and evaporated, and then supplemented into the compressor 1. This mode is applicable to a stable operating state where no additional cooling assistance is required.

[0080] For another example, when the second control valve 11 is opened and the third control valve 12 is closed, all the liquid refrigerant flows through the third branch 15 and passes through the cooling section 451 at this time, which is used to enhance the cooling effect of the first purification chamber 450. This mode is applicable to the initial startup stage or high-humidity environment that requires enhanced refrigerant separation accuracy.

[0081] In this way, the third branch 15 is set in series with the cooling section 451 to provide an independent cooling path, enabling the cooling section 451 to flexibly participate in the system cycle and enhancing the refrigerant separation ability of the first purification chamber 450. Additionally, on the one hand, the second control valve 11 is arranged upstream of the cooling section 451 to achieve precise control of the cooling section 451, improving the system adaptability and response speed; on the other hand, the third control valve 12 is arranged on the first branch 13 to adjust the make-up gas flow rate entering the compressor 1, optimizing the system energy efficiency and the performance of the compressor 1.

[0082] As Figure 1 and Figure 2 shown, according to some embodiments of the present invention, the heat pump system further includes a defrosting branch 17. The two ends of the defrosting branch 17 are respectively connected to the air outlet 421 and the inlet of the evaporator 8, and a defrosting control valve 5 is arranged on the defrosting branch 17.

[0083] In this embodiment, a defrosting branch 17 is also provided in the heat pump system, which is used to rapidly increase the temperature of the evaporator 8 when the system enters the defrosting mode to remove the frost on its surface and improve the system operation efficiency and stability. Specifically, the gas outlet 421 outputs the gaseous refrigerant that has been separated and purified by the rectifier 4. One end of the defrosting branch 17 is connected downstream of the air outlet 421, and the other end is connected to the pipeline before the inlet of the evaporator 8. The defrosting control valve 5 is arranged on the defrosting branch 17 and can be opened or closed according to the system operation state; It can be understood that in the normal heating / cooling mode, the defrosting control valve 5 is in the closed state, and the refrigerant flows through the first heat exchange channel 601 and the second throttling device 7 to the evaporator 8; in the defrosting mode, the defrosting control valve 5 is opened, and part of the high-temperature and low-pressure gaseous refrigerant directly flows into the evaporator 8 through the defrosting branch 17 for heating the surface to defrost.

[0084] The defrosting process of the heat pump system of the present invention is specifically as follows: As Figure 1 shown, in the normal operating state, the system operates according to the standard refrigeration or heating cycle, and the refrigerant flows through the compressor 1, condenser 2, first throttling device 3, rectifier 4, regenerator 6, second throttling device 7 in sequence and then enters the evaporator 8 to complete the endothermic process. At this time, the defrosting control valve 5 remains closed, and the defrosting branch 17 does not participate in the cycle.

[0085] As Figure 2As shown, when it is detected that the frosting on the surface of the evaporator 8 reaches the set threshold, for example, judged by a temperature sensor or the running time, the control system starts the defrosting mode. At this time, the controller opens the defrost control valve 5, so that the gaseous refrigerant from the air outlet 421 bypasses the regenerator 6 and the second throttling device 7, and directly flows into the evaporator 8 through the defrosting branch 17. Since this part of the refrigerant is gaseous and has a relatively high temperature, it can quickly increase the internal temperature of the evaporator 8, thereby effectively melting the frost on its surface.

[0086] After the defrosting is completed, the system returns to the normal operation mode, the defrost control valve 5 is closed, and the refrigerant circulates along the original path again.

[0087] In summary, in this embodiment, the defrosting branch 17 and the defrost control valve 5 are introduced on the basis of the original azeotropic mixture refrigerant heat pump system, realizing effective control of the frosting problem of the evaporator 8.

[0088] As Figure 1 and Figure 2 shown, according to some embodiments of the present invention, the heat pump system further includes an evaporator fan 18, and the evaporator fan 18 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 between the evaporator 8 and the suction port of the compressor 1.

[0089] It can be understood that the evaporator fan 18 is arranged near the evaporator 8, and is used to drive the ambient air to flow through the surface of the evaporator 8, enhancing the heat exchange efficiency between it and the refrigerant. By controlling the fan speed, the heat absorption of the evaporator 8 can be adjusted, so as to adapt to different ambient temperatures and load changes, and improve the overall energy efficiency of the system.

[0090] The gas-liquid separator 9 is used to separate the liquid component in the refrigerant returning from the evaporator 8 to the compressor 1, preventing the liquid refrigerant from directly entering the compressor 1 and causing liquid hammer or damaging the internal components of the compressor 1.

[0091] Next, a control method for an azeotropic mixture refrigerant heat pump system given by the present invention will be introduced. It should be noted that this control method is applied to the azeotropic mixture refrigerant heat pump system described in the first aspect of the present invention.

[0092] As Figure 4 shown, the control method includes: Step S1, in response to the heating mode, control the first branch 13 to be in a connected state, and control the refrigerant 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 suction port of the compressor 1.

[0093] As described above, for the control method of the present invention, after determining that the heat pump system operates in the heating mode, it controls the first branch 13 to remain in a connected state, and controls the refrigerant to flow through the condenser 2, the first throttling device 3, and the rectifier 4 in sequence. Since the boiling points of the mixed refrigerants are different, after flowing through the condenser 2, most of the low-boiling-point refrigerants are in a gaseous state, and most of the high-boiling-point refrigerants are in a liquid state. Therefore, the mixed refrigerant is separated into a gaseous refrigerant and a liquid refrigerant in the rectifier 4, where most of the gaseous refrigerant is the low-boiling-point refrigerant and a small part is the 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 suction port of the compressor 1. The liquid refrigerant will enter the first branch 13 through the liquid outlet 431, 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 converges into the gas injection port of the compressor 1.

[0094] In the above circulation path, since some 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, enabling the heat pump to be applicable to lower ambient temperatures, and further enhancing the low-temperature heating capacity of the system. In addition, by introducing the liquid refrigerant into the gas injection port of the compressor 1 in the present application, the exhaust pressure of the compressor 1 can be reduced, so that the heat pump can operate stably at low ambient temperatures.

[0095] In addition, when controlling the first branch 13 to be connected, the present application performs secondary throttling on the refrigerant by using the first throttling device 3 and the second throttling device 7, and further cools the low-boiling-point refrigerant through the regenerator 6, allowing the low-boiling-point refrigerant to be fully condensed and having a large degree of subcooling, reducing the subsequent throttling loss, thereby increasing the heating capacity and energy efficiency of the heat pump system; at the same time, increasing the temperature of the high-boiling-point refrigerant, which helps it to evaporate smoothly at the gas injection port of the compressor 1 and participate in the compression cycle.

[0096] As Figure 4 shown, in some embodiments of the present invention, the control method further includes: Step S2, in response to the defrosting mode, control both the second branch 14 and the defrosting 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 defrosting branch 17, and the evaporator 8 in sequence and enter the suction port of the compressor 1.

[0097] In this way, during the above 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 smaller, thereby increasing the refrigerant flow rate through the compressor 1, enabling the compressor 1 to do more work, and improving the defrosting effect of the evaporator 8.

[0098] For example, in this heat pump system, the refrigerant circulation loop further includes a second branch 14, a third branch 15, a first control valve 10, a second control valve 11, a third control valve 12, and a defrosting branch 17; both ends of the second branch 14 are respectively connected to the exhaust port of the compressor 1 and the rectification inlet 411 and are 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.

[0099] The third branch 15 is in parallel with the first branch 13 and both ends thereof are respectively connected to the pipeline between the liquid outlet 431 and the gas supplement 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 defrosting 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 defrosting control valve 5 is arranged on the defrosting branch 17.

[0100] Furthermore, in some embodiments of the present invention, the control method further includes: Step S3: In response to the heating mode, control the second branch 14 to be in a connected state, and control the refrigerant 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 suction port of the compressor 1. In this way, the heating section 441 heats the liquid refrigerant in the rectifier 4, and the heating promotes the preferential evaporation of the low-boiling components in the liquid refrigerant, forming a gas that rises to the gas storage cavity 420, while the unevaporated high-boiling components remain liquid and sink into the liquid storage cavity 430, improving the separation efficiency of the refrigerant components. At the same time, the content of the low-boiling refrigerant flowing through the evaporator 8 is increased, thereby increasing the heating capacity of the heat pump system, enabling the heat pump to be applicable to lower ambient temperatures, and further enhancing the low-temperature heating capacity of the system.

[0101] As Figure 5 shown, the control method specifically includes: Step S100: In response to the heating mode, control the defrosting control valve 5 to be in a closed state, and control 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; Step S200: In response to the defrosting mode, control the first control valve 10 and the defrosting control valve 5 to be in an open state, and control the first throttling device 3, the second throttling device 7, the second control valve 11, and the third control valve 12 to be in a closed state.

[0102] The heating mode and defrosting mode of the heat pump system of the present invention will be introduced in detail based on the above control method respectively.

[0103] As Figure 1 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 operation, and the refrigerant flows along the normal path. The second throttling device 7 is opened, allowing the refrigerant to enter the evaporator 8 to absorb heat after throttling. The first control valve 10 is opened, guiding a 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 rectifier 4, providing heat for the second purification chamber 440. The second control valve 11 is opened, connecting the cooling section 451 to the third branch 15 for cooling the refrigerant in the first purification chamber 450. The third control valve 12 is opened, allowing the high-boiling refrigerant to enter the second heat exchange channel 602 of the regenerator 6 through the first branch 13, heated and then replenished into the compressor 1.

[0104] As Figure 1 shown, in the heating mode, the specific working process is as follows: The compressor 1 compresses the refrigerant into high-temperature and high-pressure gas. A part directly enters the condenser 2 to release heat, and the other part enters the heating section 441 through the second branch 14 to provide heat for the second purification chamber 440. The refrigerant after being depressurized by the first throttling device 3 enters the rectifier 4, and preliminary gas-liquid stratification is achieved in the separation chamber 410. The gas rises to the first purification chamber 450, and the liquid sinks to the second purification chamber 440. In the first purification chamber 450, the cooling section 451 locally cools the refrigerant to promote the liquefaction and sinking of the high-boiling components; in the second purification chamber 440, the heating section 441 heats to promote the evaporation and rising of the low-boiling components. The purified low-boiling gas flows out from the air outlet 421, is cooled by the first heat exchange channel 601 of the regenerator 6, enters the evaporator 8 through the second throttling device 7, absorbs the ambient heat and then returns to the compressor 1. The high-boiling refrigerant liquid selectively flows to the air supplement port of the compressor 1 through the first branch 13 or the third branch 15 to supplement the input of the compressor 1.

[0105] As Figure 2As shown, in the defrosting mode, the specific control logic is as follows: The defrost control valve 5 is opened, thereby conducting the defrosting branch 17, enabling the high-temperature low-boiling-point gas to directly flow into the evaporator 8 for rapidly heating the surface of the evaporator 8. The first throttling device 3 is closed, thereby preventing the high-temperature and high-pressure gas flowing out of the compressor 1 from continuing to flow through the condenser 2, but all passing through the second branch 14 to participate in the subsequent defrosting process. The first control valve 10 is opened to guide all the high-temperature and high-pressure gas flowing out of the compressor 1 to pass through the second branch 14 and enter the rectifier 4, thereby short-circuiting the condenser 2, enabling more high-temperature and high-pressure gas to participate in the defrosting process. The second throttling device 7 is closed to prevent the refrigerant from continuing to enter the evaporator 8 through the original path and avoid interfering with the defrosting process. The second control valve 11 is closed to stop cooling the cooling section 451, so as not to affect the thermal balance inside the rectifier 4. The third control valve 12 is closed, that is, the gas supplement operation of the high-boiling-point refrigerant is suspended, and resources are concentrated for defrosting.

[0106] As Figure 2 shown, in the defrosting mode, the specific working process is as follows: The compressor 1 compresses the mixed refrigerant into 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 at a large 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 defrosting branch 17, and then directly flows into the evaporator 8 for defrosting. The high-temperature and high-pressure gas entering the evaporator 8 releases a large amount of heat, rapidly increasing the surface temperature of the evaporator 8 and melting the surface ice and frost. The mixed refrigerant after defrosting flows through the gas-liquid separator 9, and the separated gaseous part directly returns to the compressor 1 for continuous circulation.

[0107] It can be understood that in the above 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 rate through the compressor 1, enabling the compressor 1 to do more work, and improving the defrosting effect of the evaporator 8.

[0108] In summary, the heat pump system of the present invention uses the high-temperature and high-pressure gas discharged from the compressor 1 directly for defrosting, without the need for an additional heating source, which is energy-saving and environmentally friendly. At the same time, since the high-temperature and high-pressure gas does not pass through the condenser 2, unnecessary energy losses are reduced, and the overall energy efficiency of the system is improved. Further, the pressure difference of the entire flow path is small, increasing the refrigerant flow rate through the compressor 1, enabling the compressor 1 to do more work, and further enhancing the defrosting effect.

[0109] In summary, according to the control method of the zeotropic mixture refrigerant heat pump system of the present invention, the separation purity of the mixture refrigerant is improved, and the lower boiling point refrigerant with higher purity enters the evaporator 8 for heat absorption, thereby improving the low-temperature performance of the unit; at the same time, the defrosting branch 17 is used to reduce the system pressure difference, increase the mixture refrigerant flow rate, improve the work done by the compressor 1, and thus improve the defrosting effect.

[0110] Figure 6 FIG. shows a schematic structural diagram of an embodiment of the zeotropic mixture refrigerant heat pump system provided by an embodiment of the present invention. The specific implementation of the zeotropic mixture refrigerant heat pump system in the specific embodiment of the present invention is not limited.

[0111] As Figure 6 shown, the heat pump may include: a processor 502, a communication interface 504, a memory 506, and a communication bus 508.

[0112] Among them: the processor 502, the communication interface 504, and the memory 506 communicate with each other through the communication bus 508. The communication interface 504 is used to communicate with network elements of other devices such as clients or other servers. The processor 502 is used to execute the program 510, and specifically can execute the relevant steps in the above-mentioned control method embodiment for the zeotropic mixture refrigerant heat pump system.

[0113] Specifically, the program 510 may include program codes, and the program codes include computer-executable instructions.

[0114] The processor 502 may be a central processing unit CPU, or a specific integrated circuit ASIC (Application Specific Integrated Circuit), or one or more integrated circuits configured to implement the embodiments of the present invention. One or more processors included in the zeotropic mixture refrigerant heat pump system may be of the same type of processor, such as one or more CPUs; or they may be of different types of processors, such as one or more CPUs and one or more ASICs.

[0115] 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, such as at least one disk memory.

[0116] The program 510 can specifically be called by the processor 502 to enable the zeotropic mixture refrigerant heat pump system to execute the relevant steps in the above-mentioned control method embodiment for the zeotropic mixture refrigerant heat pump system.

[0117] Those of ordinary skill in the art can understand that Figure 6 the structure shown is only illustrative and does not limit the structure of the above-mentioned device. For example, the zeotropic mixture refrigerant heat pump system may further include more or fewer components than those shown in Figure 6 and may have a different configuration from that shown in Figure 6 .

[0118] Embodiments of the present invention also provide a computer-readable storage medium. The methods according to the embodiments of the present invention can be implemented in hardware, firmware, or be implemented as computer code that can be recorded on a storage medium, or be implemented as computer code that is originally stored in a remote storage medium or a non-transitory machine-readable storage medium and downloaded through a network and will be stored in a local storage medium, so that the methods described herein can be stored in such software processes 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 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 memories. 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, and when the software or computer code is accessed and executed by the computer, the processor, or the hardware, the methods shown in the above embodiments are implemented.

[0119] In the specific content of the above specific embodiments, the technical features can be combined arbitrarily without contradiction. For the sake of brevity of description, not all possible combinations of the above technical features are described. However, as long as the combinations of these technical features do not exist in contradiction, they should all be considered as within the scope described in this specification.

[0120] The specific content of the above specific embodiments only expresses several embodiments of the present invention, and its description is relatively specific and detailed, but it should not be understood as a limitation to the scope of the patent of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several modifications and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the patent of the present invention should be subject to the appended claims.

Claims

1. Azeotropic-mixture-free refrigerant heat pump system, characterized in that, Comprising: A compressor (1) and a refrigerant circulation loop connected to the compressor (1) and forming a circuit. Along the refrigerant flow direction on the refrigerant circulation loop, a condenser (2), a first throttling device (3), a rectifier (4), a regenerator (6), a second throttling device (7), and an evaporator (8) are sequentially provided; The rectifier (4) is provided with a rectification inlet (411), an air outlet (421), and a liquid outlet (431). Inside the rectifier (4), a cooling section (451) is provided. The liquid outlet (431) is communicated with the gas supplement 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) that exchange heat with each other. 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).

2. The non-azeotropic mixture refrigerant heat pump system according to claim 1, wherein Inside the rectifier (4), a heating section (441) is further provided; The refrigerant circulation loop further includes a second branch (14). The two ends of the second branch (14) are respectively communicated with the exhaust port of the compressor (1) and the rectification inlet (411). The heating section (441) is connected to the second branch (14), and a first control valve (10) is provided on the second branch (14).

3. The non-azeotropic mixture refrigerant heat pump system according to claim 2, characterized in that, Inside the rectifier (4), a gas storage cavity (420), a first purification cavity (450), a separation cavity, a second purification cavity (440), and a liquid storage cavity (430) are sequentially provided from top to bottom and are interconnected. The cooling section (451) is provided in the first purification cavity (450), and the heating section (441) is provided in the second purification cavity (440).

4. The non-azeotropic mixture working fluid heat pump system according to claim 2, 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.

5. The non-azeotropic mixture refrigerant heat pump system according to claim 3, characterized in that, The first purification cavity (450) and / or the second purification cavity (440) is filled with a filler (442), and the filler (442) has a flow gap for the refrigerant to flow through.

6. The zeotropic mixture refrigerant heat pump system according to any one of claims 1 to 5, characterized in that It further 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), and the other end of the third branch (15) is connected between the outlet of the second heat exchange channel (602) and the gas supplement port of the compressor (1). The cooling section (451) is connected to the third branch (15); It further 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 the third control valve (12) is provided on the first branch (13).

7. The non-azeotropic mixture working medium heat pump system according to any one of claims 1 to 5, characterized in that It further includes a defrosting branch (17), both ends of the defrosting branch (17) are respectively communicated with the air outlet (421) and the inlet of the evaporator (8), and a defrosting control valve (5) is provided on the defrosting branch (17).

8. A control method for a non-azeotropic mixture refrigerant heat pump system, applied to the non-azeotropic mixture refrigerant heat pump system described in any one of claims 1 to 7, characterized in that, The control method includes: 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 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 suction port of the compressor (1).

9. The control method of the zeotropic mixture refrigerant heat pump system according to claim 8, characterized in that, The heat pump system further includes a second branch (14), both ends of the second branch (14) are respectively communicated with the exhaust port of the compressor (1) and the rectification inlet (411), and 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, controlling the second branch (14) to be in a connected state, and controlling the refrigerant 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 suction port of the compressor (1).

10. The control method of the zeotropic mixture refrigerant heat pump system according to claim 9, characterized in that, The heat pump system further includes a defrosting branch (17), both ends of the defrosting branch (17) are respectively communicated with the air outlet (421) and the inlet of the evaporator (8); The control method further includes: In response to the defrosting mode, controlling both the second branch (14) and the defrosting branch (17) to be in a connected state, controlling the first branch (13) to be in a disconnected state, and controlling the refrigerant to flow through the second branch (14), the rectifier (4), the defrosting branch (17) and the evaporator (8) in sequence and enter the suction port of the compressor (1).

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