A heat pump air conditioning system with exhaust air full heat recovery using ejectors

Abstract

The utility model discloses an exhaust heat recovery heat pump air conditioning system using an ejector, including a compressor, a fresh air heat exchanger, an exhaust heat exchanger, an ejector, a gas-liquid separator, an indoor heat exchanger and an outdoor heat exchanger. Beneficial effects of the utility model: the exhaust heat recovery air conditioning system using an ejector can meet the exhaust heat recovery needs under various working conditions. In summer, the cold in the exhaust air can be recovered to deheat and dehumidify the indoor environment. In winter, the heat in the exhaust air can be recovered to heat the exhaust air. The recovery amount is fully adjustable within the range of 0 to 100%, and the ejector is used to recover the compression and expansion work, and the system COP is improved while increasing the system's cooling and heating capabilities; in both winter and summer working conditions, the indoor air conditioning can be regulated to the maximum extent possible using fresh air, and the energy consumption of the air conditioning system in both normal and epidemic conditions in hospitals can be greatly reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of exhaust air heat recovery heat pump air conditioners, in particular to an exhaust air full heat recovery heat pump air conditioner system adopting an ejector. Background Art

[0002] In hospital buildings, air conditioning consumes a huge amount of energy, accounting for 50% to 70% of the total energy consumption, which is about twice that of ordinary office buildings. Therefore, it is very necessary to take energy-saving measures for the hospital's air conditioning system. Among them, the fresh air load, as one of the components of the air conditioning load, generally accounts for 30% to 50% of the air conditioning load, and even exceeds 60% in winter, and even exceeds 70% in public buildings with a large population density. The use of exhaust heat recovery devices in the air conditioning system can recover and utilize the cold / heat contained in the exhaust air, pre-treat the fresh air, and thus reduce the energy consumption generated by processing the fresh air. Studies have shown that when the heat recovery efficiency of the heat recovery device reaches 70%, it can effectively reduce the heating energy consumption by 40% to 50%.

[0003] Compared with other public buildings, hospital buildings have more complex air composition. Some areas have high bacterial counts, some areas have high concentrations of chemical pollutants, some areas have strong odors, and some areas even contain radioactive pollutants. It is a very special place. Therefore, in hospital buildings, the fresh air volume and exhaust air volume are relatively large, which provides conditions for using heat recovery systems to achieve good energy-saving effects. When selecting heat recovery devices, avoid using heat recovery devices that are prone to exhaust air infiltration pollution.

[0004] For example, a Chinese patent discloses an electric vehicle heat pump air conditioning system with an ejector (publication number: CN217048192U), which relates to the technical field of electric vehicles. The exhaust port of the electric compressor is connected to the first interface of the four-way reversing valve, the second interface of the four-way reversing valve is connected to the first interface of the three-way valve through the indoor heat exchanger, the throttling device and the outdoor heat exchanger in turn, the air intake port of the electric compressor is connected to the third interface of the four-way reversing valve, and the fourth interface of the four-way reversing valve is connected to the second interface of the three-way valve; the second interface of the four-way reversing valve, the third interface of the three-way valve, and the fourth interface of the four-way reversing valve are also connected to the working fluid inlet, the ejection fluid inlet, and the ejection fluid outlet of the ejector, respectively. The expansion work before and after throttling can be recovered, and the suction pressure of the electric compressor can be increased, thereby improving the heating performance of the electric vehicle air conditioning system.

[0005] The main component of exhaust heat recovery in existing air conditioning systems is the heat exchanger, which mainly includes: it can be roughly divided into two categories: sensible heat recovery device and total heat recovery device. Sensible heat recovery devices can only recover sensible heat, and common ones include plate sensible heat heat exchangers, heat pipe heat exchangers and intermediate heat medium heat exchangers; total heat recovery devices can recover both sensible heat and latent heat, and common ones include plate-fin heat exchangers, rotary heat exchangers and heat pump heat exchangers.

[0006] 1. Sensible exhaust heat recovery unit

[0007] There are two types of sensible heat recovery units for exhaust air: plate type sensible heat recovery unit and heat pipe type sensible heat recovery unit. They recover waste heat by temperature difference sensible heat exchange and are reliable and safe in operation. However, they can only recover part of the sensible heat energy of the exhaust air and have limited heat recovery efficiency.

[0008] 2. Full heat exhaust heat recovery unit

[0009] (1) The total heat recovery efficiency of the chemical solution absorption type fresh air unit is high, which can reach more than 60%. The total heat recovery effect is stable and will not weaken with the extension of the use time. When the solution is used for heat exchange, it can remove most of the microorganisms, bacteria and inhalable particles in the air, and can effectively purify the air. The built-in solution filter effectively ensures the cleanliness of the solution. During heat exchange, the channels between exhaust air and fresh air are completely independent, solving the problem of cross contamination. The equipment requires a large net height space for installation and a high initial investment.

[0010] (2) Rotary heat recovery unit: The equipment is large in size and occupies a large building area and clear height. The pressure resistance is large. A transmission device is required, and some power is consumed during operation. There is leakage, and cross contamination cannot be completely avoided during actual operation.

[0011] (3) The micropores on the surface of the specially treated filter paper of the wing-type full heat recovery unit with high-strength filter paper are blocked with special heat-generating polymer materials to prevent direct air flow. The wet transfer of latent heat exchange in the heat exchanger is completed by the capillary action of the paper fibers. When the outdoor temperature is below 0℃, ice blockage will occur.

[0012] (4) Heat pump type full heat recovery unit. The working principle of the heat pump is to transfer heat from the low-temperature heat source to the high-temperature heat source by absorbing heat from the evaporator and releasing heat from the condenser. That is, it can transfer the energy in the exhaust air to the fresh air. In summer conditions, the coil on the fresh air side is the evaporator, and the system extracts heat from the fresh air. The coil on the exhaust side is the condenser, which fully utilizes the coldness of the exhaust air and achieves the effect of cooling the fresh air. In winter conditions, the coil on the exhaust side is the evaporator, and the coil on the fresh air side is the condenser. The system absorbs heat from the exhaust side and achieves the purpose of heating the fresh air. When the coldness of the exhaust air and the fresh air in the system is unbalanced, an auxiliary cold and heat source can be set to supplement the cooling or heating of the fresh air.

[0013] Therefore, it is necessary to propose an exhaust air full heat recovery heat pump air conditioning system using an ejector to solve the above problems. Utility Model Content

[0014] In view of the above-mentioned deficiencies in the prior art, the purpose of the present utility model is to provide an exhaust air full heat recovery heat pump air conditioning system using an ejector to solve the above-mentioned problems.

[0015] A heat pump air conditioning system with exhaust full heat recovery using an ejector comprises a compressor, a fresh air heat exchanger, an exhaust air heat exchanger, an ejector, a gas-liquid separator, an indoor heat exchanger and an outdoor heat exchanger, the exhaust port of the compressor being connected to the a end of a first four-way valve through a first pipeline and to the e end of a second four-way valve through an eighteenth pipeline, the b end of the first four-way valve being connected to the fresh air heat exchanger through a second pipeline, the d end of the first four-way valve being connected to the exhaust air heat exchanger through a fifth pipeline, the h end of the second four-way valve being connected to the indoor heat exchanger through a fifteenth pipeline, the f end of the second four-way valve being connected to the outdoor heat exchanger through a nineteenth pipeline, the air inlet of the compressor being connected to the air outlet of the gas-liquid separator, and the gas-liquid separator being connected to an economizer and an ejector, respectively.

[0016] Preferably, the mixed fluid outlet of the ejector is connected via the eighth pipeline, and the liquid outlet of the gas-liquid separator is connected to the inlet of the gas-liquid separator via the tenth pipeline and is connected to the economizer.

[0017] Preferably, the working fluid inlet of the ejector is connected to the second throttle valve through a seventh pipeline, and the injection fluid inlet of the ejector is connected to the economizer through a seventeenth pipeline.

[0018] Preferably, the C-end of the first four-way valve is connected to the seventh pipeline through the sixth pipeline.

[0019] Preferably, the fresh air heat exchanger is connected to the first throttle valve through a third pipeline, and the first throttle valve is connected to the exhaust air heat exchanger through a fourth pipeline.

[0020] Preferably, the g end of the second four-way valve is connected to the economizer through a sixteenth pipeline, and the economizer is connected to the third throttle valve through an eleventh pipeline.

[0021] Preferably, the third throttle valve is connected to the thirteenth pipeline through the twelfth pipeline, and the two ends of the thirteenth pipeline are respectively connected to the third one-way valve and the fourth one-way valve.

[0022] Preferably, the indoor heat exchanger is respectively connected to the first one-way valve and the third one-way valve through the fourteenth pipeline, the first one-way valve is connected to the second one-way valve through the twenty-first pipeline, and the second throttle valve is connected to the twenty-first pipeline through the twenty-second pipeline.

[0023] Preferably, the outdoor heat exchanger is connected to the second one-way valve and the fourth one-way valve respectively through the twentieth pipeline.

[0024] Preferably, the first throttle valve, the second throttle valve and the third throttle valve are all solenoid valves or capillaries.

[0025] Compared with the prior art, the utility model has the following beneficial effects:

[0026] 1. In summer working conditions, the utility model can recover the coldness in the exhaust air to deheat and dehumidify the fresh air and the indoor environment. In winter working conditions, the utility model can recover the heat in the exhaust air to heat the exhaust air and the indoor environment, thereby realizing sensible heat and latent heat recovery.

[0027] 2. The utility model solves the problem that the heat exchange effect of the conventional heat recovery device depends on the temperature difference and moisture content difference between the supply and exhaust air flows, and is greatly affected by the outdoor temperature and humidity. It solves the problem that the conventional exhaust heat recovery system cannot guarantee the supply air temperature under special climatic conditions (extremely cold or hot), and part of the energy in the exhaust of the conventional exhaust heat recovery system is wasted. By using the ejector to recover the compression and expansion work, the system COP is improved while increasing the system's cooling and heating capabilities.

[0028] 3. The utility model exhaust full heat recovery air conditioning system has a fully adjustable heat (cold) recovery rate within the range of 0 to 100%. It can achieve maximum utilization of fresh air for indoor air conditioning in both winter and summer working conditions, and greatly reduce the energy consumption of the air conditioning system in both normal and epidemic conditions in hospitals. By combining the air conditioning system with the wind system, it is possible to achieve full heat recovery of the exhaust air after centralized treatment of the fresh air and exhaust air, further ensuring the reliability of hygiene and heat recovery. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 This is the principle structure diagram of the exhaust full heat recovery heat pump air conditioning system of the utility model;

[0030] Figure 2 This is a structural diagram of the economizer of the utility model;

[0031] Figure 3 It is the structural diagram of the ejector of the utility model;

[0032] Figure 4 It is a structural diagram of the gas-liquid separator of the utility model.

[0033] The accompanying drawings are denoted as follows: 1. compressor; 101. exhaust port; 102. air inlet; 2. first four-way valve; 3. fresh air heat exchanger; 4. first throttle valve; 5. exhaust air heat exchanger; 6. second throttle valve; 7. economizer; 8. ejector; 801. working fluid inlet; 802. induced fluid inlet; 803. mixed fluid outlet; 9. gas-liquid separator; 901. inlet; 902. air outlet; 903. liquid outlet; 10. third throttle valve; 11. indoor heat exchanger; 12. second four-way valve; 13. outdoor heat exchanger; 14. first one-way valve; 15. second one-way valve; 16. third one-way valve; 17. fourth one-way valve.

[0034] L1, the first pipeline; L2, the second pipeline; L3, the third pipeline; L4, the fourth pipeline; L5, the fifth pipeline; L6, the sixth pipeline; L7, the seventh pipeline; L8, the eighth pipeline; L9, the ninth pipeline; L10, the tenth pipeline; L11, the eleventh pipeline; L12, the twelfth pipeline; L13, the thirteenth pipeline; L14, the fourteenth pipeline; L15, the fifteenth pipeline; L16, the sixteenth pipeline; L17, the seventeenth pipeline; L18, the eighteenth pipeline; L19, the nineteenth pipeline; L20, the twentieth pipeline; L21, the twenty-first pipeline; L22, the twenty-second pipeline. DETAILED DESCRIPTION

[0035] It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other.

[0036] In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model 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 therefore cannot be understood as a limitation on the present utility model. In addition, the terms "first", "second", etc. are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, features defined as "first", "second", etc. may explicitly or implicitly include one or more of the features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.

[0037] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood by specific circumstances.

[0038] The embodiments of the present invention are described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered by the claims.

[0039] like Figure 1 Combined with Figures 2 to 4 As shown, an exhaust full heat recovery heat pump air conditioning system using an ejector comprises a compressor 1, a fresh air heat exchanger 3, an exhaust air heat exchanger 5, an ejector 8, a gas-liquid separator 9, an indoor heat exchanger 11 and an outdoor heat exchanger 13. The exhaust port 101 of the compressor 1 is respectively connected to the a end of the first four-way valve 2 through the first pipeline L1 and to the e end of the second four-way valve 12 through the eighteenth pipeline L18. The b end of the first four-way valve 2 is connected to the fresh air heat exchanger 3 through the second pipeline L2, the d end of the first four-way valve 2 is connected to the exhaust air heat exchanger 5 through the fifth pipeline L5, the h end of the second four-way valve 12 is connected to the indoor heat exchanger 11 through the fifteenth pipeline L15, and the f end of the second four-way valve 12 is connected to the outdoor heat exchanger 13 through the nineteenth pipeline L19. The air inlet 102 of the compressor 1 is connected to the air outlet 902 of the gas-liquid separator 9, and the gas-liquid separator 9 is respectively connected to the economizer 7 and the ejector 8.

[0040] Furthermore, the inlet 901 of the gas-liquid separator is connected to the mixed fluid outlet 803 of the ejector 8 through the eighth pipeline L8, and the liquid outlet 903 of the gas-liquid separator 9 is connected to the inlet 901 of the gas-liquid separator 9 through the tenth pipeline L10 to the economizer 7.

[0041] Furthermore, the working fluid inlet 801 of the ejector 8 is connected to the second throttle valve 6 through the seventh pipeline L7, and the injection fluid inlet 802 of the ejector 8 is connected to the economizer 7 through the seventeenth pipeline L17.

[0042] Furthermore, the end c of the first four-way valve 2 is connected to the seventh pipeline L7 through the sixth pipeline L6.

[0043] Furthermore, the fresh air heat exchanger 3 is connected to the first throttle valve 4 through the third pipeline L3, and the first throttle valve 4 is connected to the exhaust air heat exchanger 5 through the fourth pipeline L4.

[0044] Furthermore, the g end of the second four-way valve 12 is connected to the economizer 7 through the sixteenth pipeline L16, and the economizer 7 is connected to the third throttle valve 10 through the eleventh pipeline L11.

[0045] Furthermore, the third throttle valve 10 is connected to the thirteenth pipeline L13 through the twelfth pipeline L12, and the two ends of the thirteenth pipeline L13 are respectively connected to the third one-way valve 16 and the fourth one-way valve 17.

[0046] Furthermore, the indoor heat exchanger 11 is respectively connected to the first one-way valve 14 and the third one-way valve 17 through the fourteenth pipeline L14, the first one-way valve 14 is connected to the second one-way valve 15 through the twenty-first pipeline L21, and the second throttle valve 6 is connected to the twenty-first pipeline L21 through the twenty-second pipeline L22.

[0047] Furthermore, the outdoor heat exchanger 13 is connected to the second one-way valve 15 and the fourth one-way valve 17 through the twentieth pipeline L20.

[0048] Furthermore, the first throttle valve 4, the second throttle valve 6 and the third throttle valve 10 are solenoid valves or capillaries.

[0049] When the fresh air heat exchanger 3 is an evaporator, the exhaust air heat exchanger 5 is a condenser; when the exhaust air heat exchanger 5 is an evaporator, the fresh air heat exchanger 3 is a condenser.

[0050] When the indoor heat exchanger 11 is a condenser, the outdoor heat exchanger 13 is an evaporator; when the outdoor heat exchanger 13 is a condenser, the indoor heat exchanger 11 is an evaporator.

[0051] Compared with the prior art, the utility model has the following beneficial effects:

[0052] 1. In summer working conditions, the utility model can recover the coldness in the exhaust air to deheat and dehumidify the fresh air and the indoor environment. In winter working conditions, the utility model can recover the heat in the exhaust air to heat the exhaust air and the indoor environment, thereby realizing sensible heat and latent heat recovery.

[0053] 2. The utility model solves the problem that the heat exchange effect of the conventional heat recovery device depends on the temperature difference and moisture content difference between the supply and exhaust air flows, and is greatly affected by the outdoor temperature and humidity. It solves the problem that the conventional exhaust heat recovery system cannot guarantee the supply air temperature under special climatic conditions (extremely cold or hot), and part of the energy in the exhaust of the conventional exhaust heat recovery system is wasted. By using the ejector to recover the compression and expansion work, the system COP is improved while increasing the system's cooling and heating capabilities.

[0054] 3. The utility model exhaust full heat recovery air conditioning system has a fully adjustable heat (cold) recovery rate within the range of 0 to 100%. It can achieve maximum utilization of fresh air for indoor air conditioning in both winter and summer working conditions, and greatly reduce the energy consumption of the air conditioning system in both normal and epidemic conditions in hospitals. By combining the air conditioning system with the wind system, it is possible to achieve full heat recovery of the exhaust air after centralized treatment of the fresh air and exhaust air, further ensuring the reliability of hygiene and heat recovery.

[0055] Embodiment 1:

[0056] Under summer conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a summer refrigeration cycle to realize only exhaust cooling recovery conditions: the indoor heat exchanger 11, the outdoor heat exchanger 13, the second throttle valve 6 and the third throttle valve 10 are closed, and all the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the d end of the first four-way valve 2 to the exhaust heat exchanger 5 for condensation, and the liquid working medium evaporates and absorbs heat in the fresh air heat exchanger 3 after throttling by the first throttle valve 4, and the gaseous working medium flows through the b end of the first four-way valve 2 and the c end of the first four-way valve 2, and then flows through the ejector 8 and the gas-liquid separator 9 back to the compressor 1.

[0057] Embodiment 2:

[0058] In summer conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a summer refrigeration cycle to achieve indoor refrigeration only, without exhaust cooling recovery conditions: the fresh air heat exchanger 3, the exhaust heat exchanger 5 and the first throttle valve 4 are closed, and all the exhaust gas of the compressor 1 flows through the e end of the second four-way valve 12 and the f end of the second four-way valve 12 to the outdoor heat exchanger 13 for condensation, and the liquid working medium enters the working fluid inlet of the ejector 8 after passing through the second throttle valve 6 without throttling. The low-pressure gaseous working medium in the indoor heat exchanger 11 is mixed and upgraded to a medium-pressure working medium, and the medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium; wherein, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1, and the liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 and is throttled by the third throttle valve 10, and then enters the indoor heat exchanger 11 to evaporate and absorb heat, and then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the fluid inlet of the ejector 8.

[0059] Embodiment 3:

[0060] Under summer conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system of an ejector as a summer refrigeration cycle to realize indoor refrigeration and exhaust cooling capacity recovery at the same time: a part of the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the d end of the first four-way valve 2 to the exhaust heat exchanger 5 for condensation, the liquid working medium is throttled by the first throttle valve 4 and evaporates and absorbs heat in the fresh air heat exchanger 3, the gaseous working medium flows through the b end of the first four-way valve 2 and the c end of the first four-way valve 2 to the working fluid inlet of the ejector 8; another part of the exhaust gas of the compressor 1 flows through the e end of the second four-way valve 12 and the f end of the second four-way valve 12 to the outdoor heat exchanger 13 for condensation, the liquid working medium is throttled by the second throttle valve 6 After throttling, before arriving at the working fluid inlet of the ejector 8, it is mixed with the gaseous working medium that previously flowed through the c-end of the first four-way valve 2 and then enters the working fluid inlet of the ejector 8. Under the action of the ejector 8, the low-pressure gaseous working medium in the indoor heat exchanger 11 is mixed and upgraded to a medium-pressure working medium. The medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium. Among them, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1. The liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 and enters the indoor heat exchanger 11 after throttling by the third throttle valve 10 to evaporate and absorb heat. Then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the ejector 8 injection fluid inlet.

[0061] Embodiment 4:

[0062] Under summer conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a summer refrigeration cycle to achieve indoor refrigeration and fresh air refrigeration conditions by only recovering the exhaust cold, and at the same time: the outdoor heat exchanger 13 and the second throttle valve 6 are closed, and all the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the d end of the first four-way valve 2 to the exhaust heat exchanger 5 for condensation, and the liquid working medium evaporates and absorbs heat in the fresh air heat exchanger 3 after being throttled by the first throttle valve 4, and the gaseous working medium flows through the b end of the first four-way valve 2 and the c end of the first four-way valve 2 to the ejector The working fluid inlet of the ejector 8 mixes the low-pressure gaseous working medium in the indoor heat exchanger 11 and raises it to a medium-pressure working medium under the action of the ejector 8. The medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium. Among them, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1. The liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 and enters the indoor heat exchanger 11 after throttling by the third throttle valve 10 to evaporate and absorb heat. Then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the ejector fluid inlet.

[0063] Embodiment 5:

[0064] Under winter conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a winter heating cycle to realize only exhaust heat recovery conditions: the indoor heat exchanger 11, the outdoor heat exchanger 13, the second throttle valve 6 and the third throttle valve 10 are closed, and all the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the b end of the first four-way valve 2 to the fresh air heat exchanger 3 for condensation, and the liquid working medium evaporates and absorbs heat in the exhaust heat exchanger 5 after being throttled by the first throttle valve 4, and the gaseous working medium flows through the d end of the first four-way valve 2 and the c end of the first four-way valve 2, and then flows through the ejector 8 and the gas-liquid separator 9 back to the compressor 1.

[0065] Embodiment 6:

[0066] Under winter conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a winter heating cycle to achieve indoor heating only, without exhaust heat recovery conditions: the fresh air heat exchanger 3, the exhaust heat exchanger 5 and the first throttle valve 4 are closed, and all the exhaust gas of the compressor 1 flows through the e end of the second four-way valve 12 and the h end of the second four-way valve 12 to the indoor heat exchanger 11 for condensation, and the liquid working medium enters the working fluid inlet of the ejector 8 after passing through the second throttle valve 6 without throttling. Under the action of the ejector 8 The low-pressure gaseous working fluid in the outdoor heat exchanger 13 is mixed and upgraded to a medium-pressure working fluid, and the medium-pressure working fluid enters the vapor-liquid separator 9 and is separated into a liquid working fluid and a gaseous working fluid; wherein, the gaseous working fluid in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1, and the liquid working fluid in the vapor-liquid separator 9 flows through the economizer 7 and is throttled by the third throttle valve 10, and then enters the outdoor heat exchanger 13 to evaporate and absorb heat, and then the low-pressure gaseous working fluid flows through the economizer 7 again and is sucked into the fluid inlet of the ejector 8.

[0067] Embodiment 7:

[0068] Under winter conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system of an ejector as a winter heating cycle to achieve indoor heating and exhaust heat recovery conditions at the same time: a part of the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the b end of the first four-way valve 2 to the fresh air heat exchanger 3 for condensation, the liquid working medium is throttled by the first throttle valve 4 and evaporates and absorbs heat in the exhaust heat exchanger 5, the gaseous working medium flows through the d end of the first four-way valve 2 and the c end of the first four-way valve 2 to the working fluid inlet of the ejector 8; another part of the exhaust gas of the compressor 1 flows through the e end of the second four-way valve 12 and the h end of the second four-way valve 12 to the indoor heat exchanger 11 for condensation, the liquid working medium is throttled by the second throttle valve 6 After throttling, before arriving at the working fluid inlet of the ejector 8, it is mixed with the gaseous working medium that previously flowed through the c-end of the first four-way valve 2 and then enters the working fluid inlet of the ejector 8. Under the action of the ejector 8, the low-pressure gaseous working medium in the outdoor heat exchanger 13 is mixed and upgraded to a medium-pressure working medium. The medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium. Among them, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1, and the liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 to the third throttle valve 10, and then enters the outdoor heat exchanger 13 to evaporate and absorb heat, and then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the ejector 8 injection fluid inlet.

[0069] Embodiment 8:

[0070] Under winter conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system using an ejector as a winter heating cycle to achieve fresh air heating only, while recovering exhaust heat and outdoor heat extraction conditions: the indoor heat exchanger 11 and the second throttle valve 6 are closed, and all the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the b end of the first four-way valve 2 to the fresh air heat exchanger 3 for condensation, and the liquid working medium evaporates and absorbs heat in the exhaust heat exchanger 5 after being throttled by the first throttle valve 4, and the gaseous working medium flows through the d end of the first four-way valve 2 and the c end of the first four-way valve 2 to the ejector At the working fluid inlet of 8, under the action of the ejector 8, the low-pressure gaseous working medium in the outdoor heat exchanger 13 is mixed and raised to a medium-pressure working medium, and the medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium; wherein, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1, and the liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 and enters the outdoor heat exchanger 13 after throttling by the third throttle valve 10 to evaporate and absorb heat, and then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the ejector 8 induced fluid inlet.

[0071] Embodiment 9:

[0072] Under winter conditions, the utility model adopts an exhaust heat recovery heat pump air conditioning system of an ejector as a winter heating cycle to realize outdoor defrosting at the same time, exhaust heat recovery working condition: a part of the exhaust gas of the compressor 1 flows through the a end of the first four-way valve 2 and the b end of the first four-way valve 2 to the fresh air heat exchanger 3 for condensation, the liquid working medium is throttled by the first throttle valve 4 and evaporates and absorbs heat in the exhaust heat exchanger 5, the gaseous working medium flows through the d end of the first four-way valve 2 and the c end of the first four-way valve 2 to the working fluid inlet of the ejector 8; another part of the exhaust gas of the compressor 1 flows through the e end of the second four-way valve 12 and the f end of the second four-way valve 12 to the outdoor heat exchanger 13 for condensation, the liquid working medium is throttled by the second throttle valve 6 after throttling to the working fluid inlet of the ejector 8, it is mixed with the gaseous working medium that previously flowed through the c end of the first four-way valve 2 and then enters the working fluid inlet of the ejector 8. Under the action of the ejector 8, the low-pressure gaseous working medium in the indoor heat exchanger 11 is mixed and upgraded to a medium-pressure working medium, and the medium-pressure working medium enters the vapor-liquid separator 9 and is separated into a liquid working medium and a gaseous working medium; wherein, the gaseous working medium in the vapor-liquid separator 9 flows through the suction port of the compressor 1 and returns to the compressor 1, and the liquid working medium in the vapor-liquid separator 9 flows through the economizer 7 to the third throttle valve 10, and then enters the indoor heat exchanger 11 to evaporate and absorb heat, and then the low-pressure gaseous working medium flows through the economizer 7 again and is sucked into the ejector fluid inlet of the ejector 8.

[0073] The above description is only a preferred embodiment of the present invention, and does not limit the patent scope of the present invention. Any equivalent structure or equivalent process transformation made by using the contents of the specification and drawings of the present invention, or directly or indirectly applied in other related technical fields, are also included in the patent protection scope of the present invention.

Claims

1. A heat pump air conditioning system with exhaust full heat recovery using an ejector, characterized in that: The invention comprises a compressor (1), a fresh air heat exchanger (3), an exhaust air heat exchanger (5), an ejector (8), a gas-liquid separator (9), an indoor heat exchanger (11) and an outdoor heat exchanger (13); the exhaust port (101) of the compressor (1) is connected to the a end of the first four-way valve (2) through a first pipeline (L1) and is connected to the e end of the second four-way valve (12) through an eighteenth pipeline (L18); the b end of the first four-way valve (2) is connected to the fresh air heat exchanger (3) through a second pipeline (L2); The d end of the four-way valve (2) is connected to the exhaust heat exchanger (5) via a fifth pipeline (L5), the h end of the second four-way valve (12) is connected to the indoor heat exchanger (11) via a fifteenth pipeline (L15), the f end of the second four-way valve (12) is connected to the outdoor heat exchanger (13) via a nineteenth pipeline (L19), the air inlet (102) of the compressor (1) is connected to the air outlet (902) of the gas-liquid separator (9), and the gas-liquid separator (9) is respectively connected to the economizer (7) and the ejector (8).

2. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 1, characterized in that: The inlet (901) of the gas-liquid separator is connected to the mixed fluid outlet (803) of the ejector (8) via the eighth pipeline (L8), and the liquid outlet (903) of the gas-liquid separator (9) is connected to the inlet (901) of the gas-liquid separator (9) via the tenth pipeline (L10) and is connected to the economizer (7).

3. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 2, characterized in that: The working fluid inlet (801) of the injector (8) is connected to the second throttle valve (6) through the seventh pipeline (L7), and the injection fluid inlet (802) of the injector (8) is connected to the economizer (7) through the seventeenth pipeline (L17).

4. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 3, characterized in that: The c-end of the first four-way valve (2) is connected to the seventh pipeline (L7) via the sixth pipeline (L6).

5. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 4, characterized in that: The fresh air heat exchanger (3) is connected to the first throttle valve (4) via a third pipeline (L3), and the first throttle valve (4) is connected to the exhaust air heat exchanger (5) via a fourth pipeline (L4).

6. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 5, characterized in that: The g end of the second four-way valve (12) is connected to the economizer (7) through the sixteenth pipeline (L16), and the economizer (7) is connected to the third throttle valve (10) through the eleventh pipeline (L11).

7. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 6, characterized in that: The third throttle valve (10) is connected to the thirteenth pipeline (L13) through the twelfth pipeline (L12), and the two ends of the thirteenth pipeline (L13) are respectively connected to the third one-way valve (16) and the fourth one-way valve (17).

8. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 7, characterized in that: The indoor heat exchanger (11) is respectively connected to the first one-way valve (14) and the third one-way valve (16) via a fourteenth pipeline (L14); the first one-way valve (14) is connected to the second one-way valve (15) via a twenty-first pipeline (L21); and the second throttle valve (6) is connected to the twenty-first pipeline (L21) via a twenty-second pipeline (L22).

9. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 8, characterized in that: The outdoor heat exchanger (13) is respectively connected to the second one-way valve (15) and the fourth one-way valve (17) via a twentieth pipeline (L20).

10. The exhaust air full heat recovery heat pump air conditioning system using an ejector as claimed in claim 9, characterized in that: The first throttle valve (4), the second throttle valve (6) and the third throttle valve (10) are all solenoid valves or capillaries.

Images