CN216203955U

CN216203955U - Air conditioning system

Info

Publication number: CN216203955U
Application number: CN202122619294.4U
Authority: CN
Inventors: 皇甫启捷; 吕如兵; 梁祥飞; 黄泽清; 徐璐
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2021-10-28
Filing date: 2021-10-28
Publication date: 2022-04-05
Anticipated expiration: 2031-10-28

Abstract

The present invention provides an air conditioning system comprising: the air conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger can be communicated to an exhaust end or a suction end of the compressor, and the other end of the outdoor first heat exchanger can be communicated to one end of the outdoor second heat exchanger and/or one end of the outdoor third heat exchanger; the other end of the outdoor second heat exchanger and the other end of the outdoor third heat exchanger can be communicated with one end of the indoor heat exchanger after being mixed, and the other end of the indoor heat exchanger can be communicated to a suction end or a discharge end of the compressor. According to the utility model, the main condenser does not frost or relieves the frosting speed, and the defrosting and defrosting can be realized while the system stably heats through the alternate work of the 2 auxiliary heat exchangers, so that the comfort of the indoor environment is improved.

Description

Air conditioning system

Technical Field

The utility model relates to the technical field of air conditioners, in particular to an air conditioning system.

Background

When the non-azeotropic working medium is applied to an air conditioning system, from the perspective of system circulation, the non-azeotropic mixed working medium can approach Lorenz circulation in the heat exchange process due to temperature slippage and temperature-enthalpy nonlinear relation in the heat exchange process, so that the circulation efficiency is improved.

Because the conventional air conditioning system in the prior art is used for heating and running, the problem that the outdoor unit is frosted and stops working when defrosting, so that the comfort of the indoor environment is influenced exists; the non-azeotropic working medium is applied to a cooling and heating system, but the technical problems of high-efficiency operation under both the refrigeration working condition and the heating working condition and the like cannot be considered, so that the air conditioning system is researched and designed.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem to be solved by the utility model is to overcome the defects that the heating operation of the conventional air conditioning system in the prior art has the defects that the outdoor unit is frosted and the indoor environment comfort is influenced by the shutdown when the outdoor unit is frosted, so that the air conditioning system is provided.

In order to solve the above problems, the present invention provides an air conditioning system including:

the air conditioning system comprises a compressor, an outdoor first heat exchanger, an outdoor second heat exchanger, an outdoor third heat exchanger, an indoor heat exchanger and a first throttling device, the air conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger can be communicated to a discharge end or a suction end of the compressor, and the other end of the outdoor first heat exchanger can be communicated to one end of the outdoor second heat exchanger and/or one end of the outdoor third heat exchanger;

the other end of the outdoor second heat exchanger is communicated with the other end of the outdoor third heat exchanger and then can be communicated with one end of the first throttling device, the other end of the first throttling device is communicated with one end of the indoor heat exchanger, and the other end of the indoor heat exchanger can be selectively communicated to a suction end or a discharge end of the compressor.

In some embodiments, one end of the outdoor first heat exchanger is selectively connectable to a discharge end or a suction end of the compressor through a first line, and the other end is connectable to one end of the outdoor second heat exchanger and/or one end of the outdoor third heat exchanger through a second line, the outdoor second heat exchanger being connected in parallel with the outdoor third heat exchanger.

In some embodiments, the outdoor second heat exchanger is located on a third pipeline, the outdoor third heat exchanger is located on a fourth pipeline, the third pipeline is connected in parallel with the fourth pipeline, one end of the third pipeline is communicated with one end of the fourth pipeline and then communicated with the second pipeline, and the other end of the third pipeline is communicated with the other end of the fourth pipeline and then can be communicated with one end of the indoor heat exchanger.

In some embodiments, a first control valve is disposed on the third line and a second control valve is disposed on the fourth line.

In some embodiments, the air conditioner further comprises a fifth pipeline, a sixth pipeline and a seventh pipeline, wherein the third pipeline and the fourth pipeline are merged and then communicated to one end of the throttling device through the fifth pipeline, the other end of the throttling device is communicated to one end of the indoor heat exchanger through the sixth pipeline, and the other end of the indoor heat exchanger is communicated to a suction end or a discharge end of the compressor through the seventh pipeline.

In some embodiments, the air conditioner further comprises a four-way valve, the four-way valve comprises an E end, an S end, a C end and a D end, the E end is communicated with the seventh pipeline, the S end is communicated with the air suction end of the compressor, the C end is communicated with the first pipeline, the D end is communicated with the air discharge end of the compressor, and the first communication state of the four-way valve is as follows: the end E is communicated with the end S, the end C is communicated with the end D, at the moment, the indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the end E is communicated with the end D, the end S is communicated with the end C, and at the moment, the indoor operation is in a heating state; the four-way valve can be switched between the first communication state and the second communication state.

In some embodiments, the outdoor heat exchanger further comprises a first fan, wherein the first fan can drive the outdoor air flow to partially flow through the outdoor first heat exchanger, partially flow through the outdoor second heat exchanger, and partially flow through the outdoor third heat exchanger;

the indoor heat exchanger is characterized by further comprising a second fan, and the second fan can drive indoor airflow to flow through the indoor heat exchanger.

In some embodiments, a third control valve is disposed on the sixth pipeline, a sixth control valve is disposed on the seventh pipeline, the air conditioning system further includes an eighth pipeline and a ninth pipeline, one end of the eighth pipeline is connected to the sixth pipeline and is located between the third control valve and the throttling device, the other end of the eighth pipeline is connected to the seventh pipeline and is located between the sixth control valve and the indoor heat exchanger, one end of the ninth pipeline is connected to the sixth pipeline and is located between the indoor heat exchanger and the third control valve, the other end of the ninth pipeline is connected to the seventh pipeline and is located between the sixth control valve and the four-way valve, a fourth control valve is disposed on the eighth pipeline, and a fifth control valve is disposed on the ninth pipeline; the seventh pipeline is disposed close to the second fan with respect to the sixth pipeline, and the ninth pipeline is disposed far from the second fan with respect to the eighth pipeline.

The air conditioning system and the control method thereof provided by the utility model have the following beneficial effects:

1. the system adopts the non-azeotropic working medium, fully utilizes the temperature slip characteristic of the non-azeotropic working medium, simultaneously divides the outdoor heat exchanger into three parts (a main heat exchanger and two auxiliary heat exchangers, wherein the main heat exchanger and the auxiliary heat exchangers are arranged in series on the windward area, and the two auxiliary heat exchangers are arranged in parallel on the flow direction), sacrifices a small part of heat exchange area, and ensures that the main heat exchange area is not frosted. During heating operation, a refrigerant enters from one end of one auxiliary heat exchanger, a low-boiling-point refrigerant is evaporated in the auxiliary heat exchanger firstly, the surface temperature of the low-boiling-point refrigerant is low, and the low-boiling-point refrigerant is easy to frost. When an auxiliary heat exchanger defrosts, another auxiliary heat exchanger work through 2 auxiliary heat exchangers's work in turn for the system can also realize defrosting, the function of defrosting when steadily heating, improves the travelling comfort of indoor environment.

2. The utility model also sets four two-way valves and corresponding switching pipelines at the inlet and outlet of the indoor heat exchanger, so that the system can realize countercurrent heat exchange under both cooling and heating working conditions, has good heat exchange efficiency and reduces irreversible loss in the heat exchange process.

Drawings

FIG. 1 is a schematic diagram of the non-azeotropic working medium system cycle (refrigeration mode) of the main embodiment of the present invention;

FIG. 2 is a schematic diagram of the non-azeotropic working medium system cycle (general heating mode) of the main embodiment of the present invention;

FIG. 3 is a schematic diagram of the non-azeotropic working medium system cycle (low temperature heating mode) according to the main embodiment of the present invention;

FIG. 4 is a schematic diagram of the non-azeotropic refrigerant system cycle of the main embodiment of the present invention (low temperature heating mode and defrosting in the windward 21 a);

FIG. 5 is a schematic view of a refrigeration mode cycle (refrigeration mode) according to an alternate embodiment of the present invention;

FIG. 6 is a schematic view of a heating mode cycle (normal heating mode) according to an alternative embodiment of the present invention;

FIG. 7 is a schematic view of a cooling mode cycle (low temperature heating mode) according to an alternative embodiment of the present invention;

fig. 8 is a schematic view of a heating mode cycle (low temperature heating mode and defrosting in the windward 21a) according to an alternative embodiment of the present invention.

The reference numerals are represented as:

10. a compressor; 21. an outdoor first heat exchanger; 21a, an outdoor second heat exchanger; 21b, an outdoor third heat exchanger; 31. a throttling device; 41. an indoor heat exchanger; 51. a four-way valve; E. an E end; s, S end; C. a C terminal; D. a D end; 61. a first fan; 62. a second fan; 71. a first control valve; 72. a second control valve; 73. a third control valve; 74. a fourth control valve; 75. a fifth control valve; 76. a sixth control valve;

101. a first pipeline; 102. a second pipeline; 103. a third pipeline; 104. a fourth pipeline; 105. a fifth pipeline; 106. a sixth pipeline; 107. a seventh pipeline; 108. an eighth pipeline; 109. a ninth pipeline.

Detailed Description

Primary embodiment, as shown in fig. 1-8, the present invention provides an air conditioning system comprising:

the air conditioning system comprises a compressor 10, an outdoor first heat exchanger 21, an outdoor second heat exchanger 21a, an outdoor third heat exchanger 21b, an indoor heat exchanger 41 and a first throttling device 31, the air conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger 21 can be communicated to a discharge end or a suction end of the compressor 10, and the other end of the outdoor first heat exchanger 21 can be communicated to one end of the outdoor second heat exchanger 21a and/or one end of the outdoor third heat exchanger 21 b;

the other end of the outdoor second heat exchanger 21a is communicated with the other end of the outdoor third heat exchanger 21b and then can be communicated with one end of the first throttling device 31, the other end of the first throttling device 31 is communicated with one end of the indoor heat exchanger 41, and the other end of the indoor heat exchanger 41 can be selectively communicated to a suction end or a discharge end of the compressor 10.

The system adopts the non-azeotropic working medium, fully utilizes the temperature slip characteristic of the non-azeotropic working medium, simultaneously divides the outdoor heat exchanger into three parts (a main heat exchanger and two auxiliary heat exchangers, wherein the main heat exchanger and the auxiliary heat exchangers are arranged in series on the windward area, and the two auxiliary heat exchangers are arranged in parallel on the flow direction), sacrifices a small part of heat exchange area, and ensures that the main heat exchange area is not frosted. During heating operation, a refrigerant enters from one end of one auxiliary heat exchanger, a low-boiling-point refrigerant is evaporated in the auxiliary heat exchanger firstly, the surface temperature of the low-boiling-point refrigerant is low, and the low-boiling-point refrigerant is easy to frost. When an auxiliary heat exchanger defrosts, another auxiliary heat exchanger work through 2 auxiliary heat exchangers's work in turn for the system can also realize defrosting, the function of defrosting when steadily heating, improves the travelling comfort of indoor environment.

1. The utility model is different from the conventional refrigeration system, the proposal adopts the non-azeotropic refrigerant with large slip temperature, the slip temperature is more than 5 ℃ and less than the temperature difference of inlet and outlet air; the problem that the comfort of the indoor environment is influenced by the halt of the conventional air-conditioning system during heating operation and outdoor unit frosting and defrosting is solved;

2. the utility model solves the problems of system performance reduction and indoor environment comfort reduction caused by frosting during heating operation of the air conditioning system, and solves the problem that the non-azeotropic working medium is applied to a cooling and heating system and can not give consideration to efficient operation under both the refrigerating and heating working conditions.

3. The utility model improves the heat exchange performance of the non-azeotropic working medium in the heat exchanger, fully utilizes the temperature slip characteristic of the non-azeotropic working medium, enables the heat exchange process to approach Lorenz circulation, reduces the heat exchange temperature difference, reduces the irreversible loss in the heat exchange process and improves the heat exchange efficiency.

The air conditioning system shown in fig. 1 includes a compressor 10, an outdoor first heat exchanger 21, an outdoor second heat exchanger 21a, an outdoor third heat exchanger 21b, a throttle device 31, an indoor heat exchanger 41, a four-way valve 51, a first fan 61, a second fan 62, a first control valve 71, a second control valve 72, and preferably a two-way valve.

The system circularly adopts non-azeotropic refrigerants, and the standard boiling points of the non-azeotropic refrigerants have certain difference, so that the non-azeotropic refrigerants can have different heat exchange characteristics from pure working media (or near-azeotropic working media) in the heat exchange process. In the evaporation process, the evaporation temperature of the non-azeotropic refrigerant is gradually increased, and the temperature of the external heat exchange fluid (air or water) is gradually reduced; in the same way, in the condensation process, the temperature of the non-azeotropic refrigerant is gradually reduced, and the temperature of the heat exchange fluid (air or water) is gradually increased, so that in order to fully utilize the slippage characteristic of the non-azeotropic working medium, the heat exchange process of the non-azeotropic working medium is preferably countercurrent heat exchange, and meanwhile, the non-azeotropic working medium is applied to the scene of heating defrosting, and the non-azeotropic working medium has a remarkable effect of inhibiting the frosting of a heat exchanger to further reduce the system performance.

In some embodiments, one end of the outdoor first heat exchanger 21 is selectively connectable to a discharge end or a suction end of the compressor 10 through a first pipe 101, and the other end is connected to one end of the outdoor second heat exchanger 21a and/or one end of the outdoor third heat exchanger 21b through a second pipe 102, and the outdoor second heat exchanger 21a is connected in parallel with the outdoor third heat exchanger 21 b. The first outdoor heat exchanger, the second outdoor heat exchanger and the third outdoor heat exchanger are preferably arranged, the first outdoor heat exchanger is connected with the second outdoor heat exchanger and/or the third outdoor heat exchanger in series, and the second outdoor heat exchanger is connected with the third outdoor heat exchanger in parallel, so that defrosting and defrosting can be realized by sacrificing a small part of heat exchange area. When in heating operation, 3 heat exchangers are arranged outdoors and are all used as evaporators. The non-azeotropic working medium has the temperature gradually increased in the heat exchange process in the evaporator due to the temperature slip characteristic, so that the evaporation temperature of the refrigerant in the small heat exchanger is lower than the dew point temperature of the outdoor working condition, the outdoor small heat exchanger frosts, the temperature of the refrigerant coming out of the outdoor second heat exchanger 21a is higher than the dew point temperature due to the temperature slip characteristic, and then the refrigerant enters the outdoor first heat exchanger 21 for heat exchange, and the temperature of the refrigerant exchanging heat in the refrigerant is higher than the dew point temperature and lower than the outdoor dry bulb temperature, so that the outdoor first heat exchanger cannot frost. When the frost layer of the outdoor second heat exchanger 21a is built up to a certain extent, the outdoor third heat exchanger 21b is caused to operate in place of the outdoor second heat exchanger 21 a. So as to realize frosting and defrosting in turn without stopping the machine.

In some embodiments, the outdoor second heat exchanger 21a is located on a third pipeline 103, the outdoor third heat exchanger 21b is located on a fourth pipeline 104, the third pipeline 103 is connected in parallel with the fourth pipeline 104, one end of the third pipeline 103 is communicated with one end of the fourth pipeline 104 and then communicated with the second pipeline 102, and the other end of the third pipeline 103 is communicated with the other end of the fourth pipeline 104 and then communicated with one end of the indoor heat exchanger 41.

According to the utility model, the compressor exhaust gas can be led out to the outdoor first heat exchanger 21 for condensation and heat release in the refrigeration mode through the first pipeline, the refrigerant coming out of the outdoor first heat exchanger can be led back to the air suction end of the compressor in the heating mode through the first pipeline, the refrigerant coming from the third pipeline and the refrigerant coming from the fourth pipeline can be mixed and led into the outdoor first heat exchanger in the heating mode through the second pipeline, the third pipeline and the fourth pipeline are respectively used for connecting the outdoor second heat exchanger and the outdoor third heat exchanger in parallel, so that two heat exchangers or only one heat exchanger is selected to be started according to different working conditions, and the defrosting effect is realized.

In some embodiments, a first control valve 71 is disposed on the third line 103 and a second control valve 72 is disposed on the fourth line 104. Whether the outdoor second heat exchanger and the outdoor third heat exchanger are connected or not can be controlled through a first control valve arranged on a third pipeline communicated with the outdoor second heat exchanger and a second control valve arranged on a fourth pipeline communicated with the outdoor third heat exchanger; can select to open two heat exchangers or only open a heat exchanger according to the operating mode condition of difference to the effect of defrosting is realized.

In some embodiments, the compressor further comprises a fifth pipeline 105, a sixth pipeline 106 and a seventh pipeline 107, the third pipeline 103 is merged with the fourth pipeline 104 and communicated to one end of the throttling device 31 through the fifth pipeline 105, the other end of the throttling device 31 is communicated to one end of the indoor heat exchanger 41 through the sixth pipeline 106, and the other end of the indoor heat exchanger 41 is communicated to the suction end or the exhaust end of the compressor 10 through the seventh pipeline 107. The second outdoor heat exchanger and the third outdoor heat exchanger can be effectively communicated with the indoor heat exchanger through the fifth pipeline and the sixth pipeline, the throttling and pressure reducing effects can be performed on indoor and outdoor refrigerants through the throttling device, the seventh pipeline can be used for communicating the indoor heat exchanger with the compressor, the indoor heat exchanger is communicated with the suction end of the compressor in the cooling mode, and the indoor heat exchanger is communicated with the exhaust end of the compressor in the heating mode.

In some embodiments, further comprises a four-way valve 51, the four-way valve comprises an E-end E, S end S, C end C and a D-end D, the E-end E is communicated with the seventh pipeline 107, the S-end S is communicated with the suction end of the compressor 10, the C-end C is communicated with the first pipeline 101, the D-end D is communicated with the discharge end of the compressor 10, and the first communication state of the four-way valve is: the E end E is communicated with the S end S, the C end C is communicated with the D end D, at the moment, the indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the E end E is communicated with the D end D, the S end S is communicated with the C end C, and at the moment, the indoor operation is in a heating state; the four-way valve 51 is switchable between the first communication state and the second communication state. The indoor heat exchanger, the outdoor first heat exchanger and the compressor can be connected into an integral system through the four-way valve, and can be switched to realize switching control between a cooling mode and a heating mode.

In some embodiments, the air conditioner further comprises a first fan 61, wherein the first fan 61 can drive the outdoor air to partially flow through the outdoor first heat exchanger 21, partially flow through the outdoor second heat exchanger 21a, and partially flow through the outdoor third heat exchanger 21 b;

and a second fan 62, wherein the second fan 62 can drive the indoor airflow to flow through the indoor heat exchanger 41.

According to the utility model, through the arrangement of the first fan, outdoor airflow can be driven to enter the outdoor first heat exchanger, the outdoor second heat exchanger and the outdoor third heat exchanger for heat exchange, and through the arrangement of the second fan, indoor airflow can be driven to enter the indoor heat exchanger for heat exchange.

In some embodiments, a third control valve 73 is provided on the sixth line 106, a sixth control valve 76 is provided on the seventh line 107, the air conditioning system further comprises an eighth line 108 and a ninth line 109, the eighth line 108 having one end connected to the sixth line 106 at a position between the third control valve 73 and the throttle device 31 and the other end connected to the seventh line 107 at a position between the sixth control valve 76 and the indoor heat exchanger 41, one end of the ninth piping 109 is connected to the sixth piping 106 at a position between the indoor heat exchanger 41 and the third control valve 73, and the other end is connected to the seventh piping 107 at a position between the sixth control valve 76 and the four-way valve 51, the eighth pipeline 108 is provided with a fourth control valve 74, and the ninth pipeline 109 is provided with a fifth control valve 75; the seventh pipe 107 is disposed close to the second fan 62 with respect to the sixth pipe 106, and the ninth pipe 109 is disposed far from the second fan 62 with respect to the eighth pipe 108.

This is disclosed sets up eighth pipeline and ninth pipeline through advancing, the export at indoor heat exchanger, thereby can make no matter under refrigeration, the working condition of heating through control, the homoenergetic makes the heat exchanger countercurrent flow heat transfer of indoor side, reduces the heat transfer difference in temperature, reduces heat transfer process's irreversible loss.

This disclosure sets up four control valves (third control valve 73, fourth control valve 74, fifth control valve 75 and sixth control valve 76) through the business turn over, the export at indoor heat exchanger to make no matter under refrigeration, the working condition of heating, the homoenergetic makes the heat exchanger countercurrent flow heat transfer of indoor side, reduces the heat transfer difference in temperature, reduces the irreversible loss of heat transfer process.

The present invention also provides a method for controlling an air conditioning system as described in any one of the above, comprising:

detecting the operation mode of the air conditioning system, the temperature Tout of the outdoor environment and the inlet temperatures Tin of the outdoor second heat exchanger and the outdoor third heat exchanger, wherein Tin refers to the inlet temperatures of the outdoor second heat exchanger and the outdoor third heat exchanger under the heating condition;

a judging step, namely judging the relation between Tout and a first preset value T1, and judging the relation between Tin and a second preset value T2 and a third preset value T3; wherein T2 > T3;

control step, when further comprising a first control valve 71 and a second control valve 72:

when the air conditioner is operated in the cooling mode: controlling both the first control valve 71 and the second control valve 72 to open; when the air conditioner operates in the heating mode: when Tout is larger than or equal to T1 and Tin is larger than or equal to T2, the first control valve 71 and the second control valve 72 are controlled to be opened; and when Tout is larger than or equal to T1 and lasts for time Tin < T3 within T1, or when Tout is smaller than T1 and continues for time Tin < T2 within T1, one of the first control valve 71 and the second control valve 72 is controlled to be opened, and the other is controlled to be closed, wherein T1 is a first preset time.

The system adopts the non-azeotropic working medium, fully utilizes the temperature slippage characteristic of the non-azeotropic working medium, and simultaneously divides the outdoor heat exchanger into three parts (a main heat exchanger and two auxiliary heat exchangers, wherein the main heat exchanger and the auxiliary heat exchangers are arranged in series on the windward area, and the two auxiliary heat exchangers are arranged in parallel on the flow direction), so that a small part of heat exchange area is sacrificed, and the main heat exchange area is not frosted. During heating operation, a refrigerant enters from one end of one auxiliary heat exchanger, a low-boiling-point refrigerant is evaporated in the auxiliary heat exchanger firstly, the surface temperature of the low-boiling-point refrigerant is low, and the low-boiling-point refrigerant is easy to frost. When an auxiliary heat exchanger defrosts, another auxiliary heat exchanger work through 2 auxiliary heat exchangers's work in turn for the system can also realize defrosting, the function of defrosting when steadily heating, improves the travelling comfort of indoor environment.

Generally, for pure working medium refrigerants, when the evaporation temperature is lower than 0 ℃, an outdoor heat exchanger is easy to frost, and a frost layer is thicker and thicker on the surface of an outdoor evaporator, and the heat exchange is worse and worse, so that a good heating effect cannot be achieved, and even shutdown occurs. However, as for the non-azeotropic working medium, the temperature slip characteristic exists, and the evaporation temperature is gradually increased in the heat exchange process, so that the evaporation temperature at the inlet of the evaporator is low, and the frosting is very easy to occur.

The utility model utilizes the characteristics of the non-azeotropic working medium to divide the outdoor heat exchanger into three parts, so that during heating operation, the frosting part only occurs on the two auxiliary heat exchangers, and the frosting of the main heat exchanger is avoided or delayed, thereby ensuring that the heating process can still be normally carried out. The two auxiliary heat exchangers run alternately in frosting and defrosting mode, and the main heat exchanger runs normally all the time.

The system circularly adopts non-azeotropic refrigerants, and the standard boiling points of the non-azeotropic refrigerants have certain difference, so that the non-azeotropic refrigerants can have different heat exchange characteristics from pure working media (or near-azeotropic working media) in the heat exchange process. In the evaporation process, the evaporation temperature of the non-azeotropic refrigerant is gradually increased, and the temperature of the external heat exchange fluid (air or water) is gradually reduced; in the same way, in the condensation process, the temperature of the non-azeotropic refrigerant is gradually reduced, and the temperature of the heat exchange fluid (air or water) is gradually increased, so that in order to fully utilize the slippage characteristic of the non-azeotropic working medium, the heat exchange process of the non-azeotropic working medium is preferably countercurrent heat exchange, and meanwhile, the non-azeotropic working medium is applied to the scene of heating defrosting, and has a remarkable effect of inhibiting the frosting of a heat exchanger to cause the performance reduction of a system, and the specific implementation mode is as follows:

1. in the cooling mode, as shown in fig. 1, both the first control valve 71 and the second control valve 72 are open.

The high-temperature and high-pressure refrigerant discharged by the compressor 10 enters the outdoor first heat exchanger 21, is divided into two paths after heat exchange in the outdoor first heat exchanger 21 is completed, and respectively enters the outdoor second heat exchanger 21a and the outdoor third heat exchanger 21b, then the two paths of refrigerant are mixed, the mixed refrigerant is throttled and depressurized by the throttling device 31 and then enters the indoor heat exchanger 41, enters the air suction port of the compressor 10 through the four-way valve 51 after heat exchange is completed, and is compressed into a high-temperature and high-pressure state in the compressor, so that the whole refrigeration cycle is completed.

2. The heating mode is divided into three conditions, namely general heating working condition, low-temperature heating working condition and severe working condition heating, and defrosting are needed under the low-temperature and severe heating working condition. The control system of the air conditioner detects the temperature Tout of the outdoor environment and the inlet temperature Tin of the outdoor heat exchanger, if Tout is more than 5 ℃ and Tin is more than 0 ℃, the outdoor heat exchanger cannot frost, and the system operates in a general heating mode; if Tout < 5 ℃ is detected and Tin < 0 ℃ is detected for one minute or Tout > 5 ℃ and Tin < 2 ℃ is detected, then frosting at the inlet of the outdoor heat exchanger is indicated. The specific operation mode is as follows:

2.1 the detection means detects Tout > 5 ℃ and Tin > 0 ℃, the general heating mode is operated, at which time the first control valve 71 and the second control valve 72 are both open, as shown in FIG. 2.

The high-temperature and high-pressure refrigerant discharged by the compressor 10 enters the indoor heat exchanger 41 through the D, E pipe of the four-way valve, is throttled and depressurized by the throttling device 31 after heat exchange is completed, and then is divided into two paths, the two paths of refrigerant respectively enter the outdoor second heat exchanger 21a and the outdoor third heat exchanger 21b through the first control valve 71 and the second control valve 72 for heat exchange, the two paths of refrigerant are mixed after heat exchange is completed, the mixed refrigerant enters the outdoor first heat exchanger 21 for heat exchange, and finally enters the air suction port of the compressor 10 through the C, S pipe of the four-way valve 51 and is compressed into a high-temperature and high-pressure state in the compressor, so that the whole heating cycle is completed.

2.2 when the detecting device detects Tout > 5 ℃ and Tin is less than-2 ℃ for one minute continuously, or when Tout < 5 ℃ and Tin is less than 0 ℃ for one minute continuously, it indicates that the inlet of the outdoor preferable heat exchanger is easy to frost, and a low-temperature heating mode needs to be operated, firstly, the first control valve 71 is conducted, the second control valve 72 is closed, when the differential pressure of the inlet and outlet air of the outdoor second heat exchanger 21a is increased to a certain value by using the differential pressure gauge, it indicates that the surface of the outdoor second heat exchanger 21a is frosted at the moment, and the defrosting treatment needs to be carried out, then, the outdoor third heat exchanger 21b is used for replacing the outdoor second heat exchanger 21a to work, at the moment, the first control valve 71 is closed, and the second control valve 72 is conducted, and the specific real-time mode is as follows:

a) first the first control valve 71 is opened and the second control valve 72 is closed as shown in fig. 3:

the high-temperature and high-pressure refrigerant discharged from the compressor 10 enters the indoor heat exchanger 41 through the D, E pipe of the four-way valve for heat exchange, then is throttled and depressurized by the throttling device 31, then sequentially passes through the outdoor second heat exchanger 21a and the outdoor first heat exchanger 21, enters the suction port of the compressor 10 through the C, S pipe of the four-way valve 51 after heat exchange is completed, and is compressed to complete the whole cycle.

In this mode, because the temperature of the outdoor environment is low, the inlet temperature Tin of the outdoor second heat exchanger 21a is lower than the dew point temperature of the outdoor environment, so that the evaporator of the outdoor second heat exchanger 21a is prone to frosting, but due to the temperature slip characteristic of the non-azeotropic working medium, the temperature of the refrigerant in the outdoor second heat exchanger 21a gradually increases along the process direction, and the temperature of the refrigerant at the outlet of the outdoor second heat exchanger 21a is ensured to be higher than the dew point temperature of the outdoor environment and lower than the dry bulb temperature of the outdoor environment through the previous heat exchanger matching, so that when the refrigerant enters the outdoor first heat exchanger 21 for heat exchange, the outdoor first heat exchanger 21 cannot frost, and the stable operation of the heating process is ensured. Meanwhile, as the heat exchange is continuously performed, the frost layer on the surface of the outdoor second heat exchanger 21a becomes thicker and thicker, and when the differential pressure of the inlet air and the outlet air of the outdoor second heat exchanger 21a is detected to be increased to a certain value by the micro differential pressure gauge, it is indicated that the frost layer is thicker at the moment and the heat exchange performance of the heat exchanger is affected, and the defrosting treatment needs to be performed on the outdoor second heat exchanger 21a, and then the first control valve 71 is closed, the second control valve 72 is switched on, and the outdoor third heat exchanger 21b works. The outdoor second heat exchanger 21a which is left idle may be defrosted by electric heating (if any).

In some embodiments, in the controlling step, when the air conditioner is operated in the heating mode, and when Tout is greater than or equal to T1 and Tin is less than T3 for a continuous time T1, or when Tout is less than T1 and Tin is less than T2 for a continuous time T1, the first control valve 71 is controlled to be opened, the second control valve 72 is controlled to be closed, and after the time T2, the time T2 is a second preset time; t3 is preferably-2 ℃, T2 is preferably 0 ℃ and T1 is preferably 5 ℃.

In the detecting step, the air inlet pressure and the air outlet pressure of the outdoor second heat exchanger 21a can also be detected;

in the judging step, whether a first pressure difference between the air inlet pressure and the air outlet pressure of the outdoor second heat exchanger 21a is greater than or equal to a first preset pressure difference value or not can be judged;

in the control step, when the first pressure difference is greater than or equal to the first preset pressure difference, the first control valve 71 is controlled to be closed, and the second control valve 72 is controlled to be opened; when the first pressure difference is smaller than the first preset pressure difference, the first control valve 71 is maintained to be opened, and the second control valve 72 is maintained to be closed.

In some embodiments, the controlling step can further control heating and defrosting of the outdoor second heat exchanger 21a when the first pressure difference is greater than or equal to the preset pressure difference, the first control valve 71 is controlled to be closed, and the second control valve 72 is controlled to be opened.

b) The first control valve 71 is closed and the second control valve 72 is open, as shown in fig. 4:

when the frost layer of the outdoor second heat exchanger 21a reaches a certain thickness and the defrosting process is performed, it is necessary to switch to this state, and the specific operation mode is the same as described above. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 10 enters the indoor heat exchanger 41 through the D, E pipe of the four-way valve for heat exchange, then is throttled and depressurized by the throttling device 31, then sequentially passes through the outdoor third heat exchanger 21b and the outdoor first heat exchanger 21, enters the suction port of the compressor 10 through the C, S pipe of the four-way valve 51 after heat exchange is completed, and is compressed to complete the whole cycle.

And when the pipe wall temperature Twa of the outdoor second heat exchanger 21a is detected to be more than or equal to 10 ℃, ending the defrosting. Because the outdoor second heat exchanger 21a on the windward side is subjected to defrosting treatment (electrical heating), if the differential pressure gauge detects that the pressure difference of the inlet air and the outlet air of the outdoor third heat exchanger 21b reaches a certain value, it indicates that the surface of the outdoor third heat exchanger 21b is frosted and reaches a certain thickness, and the defrosting treatment needs to be performed, at this time, the first control valve 71 needs to be conducted, the second control valve 72 needs to be closed, the defrosting treatment is performed on the outdoor third heat exchanger 21b, and the steps are repeated in such a circulating way, and the outdoor second heat exchanger and the outdoor third heat exchanger perform defrosting and defrosting in turn. In conclusion, the system fully utilizes the temperature slip characteristic of the non-azeotropic working medium, sacrifices a small part of the area of the outdoor heat exchanger, and ensures that the main body of the heat exchanger does not frost. The outdoor heat exchanger is switched by the valve to realize alternate defrosting and defrosting without stopping, thereby ensuring normal indoor heating. Meanwhile, the temperature slippage characteristic of the non-azeotropic working medium is fully utilized, because the non-azeotropic working medium gradually slips to the dew point temperature from the bubble point temperature in the heat exchange process in the evaporator, the temperature is gradually increased, and the slippage temperature of the non-azeotropic working medium is higher, the phenomenon is more obvious. Therefore, in the cold and dry season in the north, the dry bulb temperature and the dew point temperature of the outdoor air are different greatly, and the system can give full advantage. Therefore, when the outdoor first heat exchanger 21 is operated in a refrigerating mode under a low-temperature working condition, frosting can not occur, frosting can only occur on the outdoor second heat exchanger 21a and the outdoor third heat exchanger 21b, and then heating operation, defrosting and defrosting are conducted simultaneously through switching of the valves, and continuity and stability of system operation and comfort of a heating environment are improved.

In some embodiments, in the controlling step, when the air conditioner is operated in the heating mode, and when Tout is greater than or equal to T1 and Tin is less than T3 for a continuous time T1, or when Tout is less than T1 and Tin is less than T2 for a continuous time T1, the first control valve 71 is controlled to be closed, the second control valve 72 is controlled to be opened, and after the time T2, the time T2 is a second preset time;

in the detecting step, the air inlet pressure and the air outlet pressure of the outdoor third heat exchanger 21b can also be detected;

in the judging step, whether a second pressure difference between the air inlet pressure and the air outlet pressure of the outdoor third heat exchanger 21b is greater than or equal to a second preset pressure difference value or not can be judged;

in the control step, when the second pressure difference is greater than or equal to the second preset pressure difference, the first control valve 71 is controlled to be opened, and the second control valve 72 is controlled to be closed; when the second pressure difference is smaller than the second preset pressure difference, the first control valve 71 is kept closed, and the second control valve 72 is kept open.

In some embodiments, the controlling step may further control heating and defrosting the outdoor third heat exchanger 21b when the pressure difference is greater than or equal to the preset pressure difference, the first control valve 71 is controlled to be opened, and the second control valve 72 is controlled to be closed.

2.3 heating under severe working conditions

When the outdoor environment is very harsh, the heating load requirement is high, the evaporation temperature is very low, the outdoor first heat exchanger 21 cannot frost due to the temperature slippage of the two auxiliary heat exchangers (the outdoor second heat exchanger 21a and the outdoor third heat exchanger 21b), the surface of the outdoor first heat exchanger 21 also begins to frost, and the heating performance is seriously affected, the defrosting and defrosting treatment needs to be performed on all outdoor heat exchangers. At this time, the four-way valve 31 is switched to the cooling mode, the inside and outside fans are stopped, the first control valve 71 and the second control valve 72 are turned on, and the system cycle is as shown in fig. 1. When the defrosting and defrosting mode operates for 8mins and the wall temperature Tw of the finned tube of the outdoor heat exchanger is more than or equal to 10 ℃, defrosting is finished. The system then operates in heating mode again as shown in fig. 2.

In some embodiments, T3 < T2 < T1; when the air conditioning system further comprises a four-way valve 51:

the control step can also be carried out when the air conditioner operates in a heating mode: and when Tout is less than T4 (which indicates that the outdoor environment is very harsh, the heating load requirement is large, the evaporation temperature is very low, the outdoor first heat exchanger 21 cannot frost due to the temperature slippage of the two auxiliary heat exchangers, the surface of the outdoor first heat exchanger 21 also starts to frost, and the heating performance is seriously influenced; T4 is preferably-15 to-20 ℃ below zero), the first control valve 71 and the second control valve 72 are controlled to be opened, and the four-way valve 51 is controlled to be reversed and switched to the cooling mode to heat and defrost at least one of the outdoor first heat exchanger 21, the outdoor second heat exchanger 21a and the outdoor third heat exchanger 21b, wherein T4 is less than T3.

In some embodiments, when the air conditioning system further comprises a four-way valve, a third control valve, a fourth control valve, a fifth control valve, and a sixth control valve:

the controlling step may further include controlling the third control valve 73 to be opened and the sixth control valve 76 to be opened, and controlling the fourth control valve 74 and the fifth control valve 75 to be closed, when the air conditioner is operated in the cooling mode; when the air conditioner is operated in the heating mode, the third control valve 73 and the sixth control valve 76 are controlled to be closed, and the fourth control valve 74 and the fifth control valve 75 are controlled to be opened.

Fig. 5, 6, 7, and 8 are first alternative embodiments of the present disclosure, which differ from the main embodiment in that: two-way valves are respectively arranged at the inlet and the outlet of the indoor heat exchanger 41, when in cooling operation, the third control valve 73 and the sixth control valve 76 are conducted, and the fourth control valve 74 and the fifth control valve 75 are closed; in the heating operation, the fourth control valve 74 and the fifth control valve 75 are both open, and the third control valve 73 and the sixth control valve 76 are closed. Through the switching of the valve, the temperature slippage characteristic of the non-azeotropic working medium can be fully utilized under the working conditions of refrigeration and heating, the indoor heat exchanger 41 always performs countercurrent heat exchange, the heat exchange temperature difference is reduced, the irreversible loss in the heat exchange process is reduced, and the heat exchange efficiency is improved. The other modes of operation are consistent with the main embodiment.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims

1. An air conditioning system characterized by: the method comprises the following steps:

the air conditioning system comprises a compressor (10), an outdoor first heat exchanger (21), an outdoor second heat exchanger (21a), an outdoor third heat exchanger (21b), an indoor heat exchanger (41) and a first throttling device (31), wherein the air conditioning system comprises a first boiling point refrigerant and a second boiling point refrigerant, the boiling point of the first boiling point refrigerant is less than that of the second boiling point refrigerant, one end of the outdoor first heat exchanger (21) can be communicated to a gas discharge end or a gas suction end of the compressor (10), and the other end of the outdoor first heat exchanger can be communicated to one end of the outdoor second heat exchanger (21a) and/or one end of the outdoor third heat exchanger (21 b);

the other end of the outdoor second heat exchanger (21a) is communicated with the other end of the outdoor third heat exchanger (21b) and then can be communicated with one end of the first throttling device (31), the other end of the first throttling device (31) is communicated with one end of the indoor heat exchanger (41), and the other end of the indoor heat exchanger (41) can be selectively communicated to the suction end or the exhaust end of the compressor (10).

2. The air conditioning system of claim 1, wherein:

one end of the outdoor first heat exchanger (21) is selectively communicated to a discharge end or a suction end of the compressor (10) through a first pipeline (101), and the other end is communicated to one end of the outdoor second heat exchanger (21a) and/or one end of the outdoor third heat exchanger (21b) through a second pipeline (102), wherein the outdoor second heat exchanger (21a) is connected with the outdoor third heat exchanger (21b) in parallel.

3. The air conditioning system of claim 2, wherein:

the outdoor second heat exchanger (21a) is located on a third pipeline (103), the outdoor third heat exchanger (21b) is located on a fourth pipeline (104), the third pipeline (103) is connected with the fourth pipeline (104) in parallel, one end of the third pipeline (103) is communicated with one end of the fourth pipeline (104) and then communicated with the second pipeline (102), and the other end of the third pipeline (103) is communicated with the other end of the fourth pipeline (104) and then can be communicated with one end of the indoor heat exchanger (41).

4. The air conditioning system of claim 3, wherein:

a first control valve (71) is arranged on the third pipeline (103), and a second control valve (72) is arranged on the fourth pipeline (104).

5. The air conditioning system of claim 3, wherein:

the air conditioner further comprises a fifth pipeline (105), a sixth pipeline (106) and a seventh pipeline (107), the third pipeline (103) and the fourth pipeline (104) are converged and then communicated to one end of the throttling device (31) through the fifth pipeline (105), the other end of the throttling device (31) is communicated to one end of the indoor heat exchanger (41) through the sixth pipeline (106), and the other end of the indoor heat exchanger (41) is communicated to the suction end or the exhaust end of the compressor (10) through the seventh pipeline (107).

6. The air conditioning system of claim 5, wherein:

the four-way valve further comprises a four-way valve (51), the four-way valve comprises an E end (E), an S end (S), a C end (C) and a D end (D), the E end (E) is communicated with the seventh pipeline (107), the S end (S) is communicated with the air suction end of the compressor (10), the C end (C) is communicated with the first pipeline (101), the D end (D) is communicated with the air exhaust end of the compressor (10), and the first communication state of the four-way valve is as follows: the E end (E) is communicated with the S end (S), the C end (C) is communicated with the D end (D), at the moment, the indoor operation is in a refrigerating state, and the second communication state of the four-way valve is as follows: the end E is communicated with the end D, the end S is communicated with the end C, and the indoor operation is in a heating state; the four-way valve (51) can be switched between the first communication state and the second communication state.

7. The air conditioning system of claim 6, wherein:

the outdoor heat exchanger also comprises a first fan (61), wherein the first fan (61) can drive the outdoor airflow to partially flow through the outdoor first heat exchanger (21), partially flow through the outdoor second heat exchanger (21a) and partially flow through the outdoor third heat exchanger (21 b);

and the air conditioner also comprises a second fan (62), wherein the second fan (62) can drive the air flow in the room to flow through the indoor heat exchanger (41).

8. The air conditioning system of claim 7, wherein:

a third control valve (73) is arranged on the sixth pipeline (106), a sixth control valve (76) is arranged on the seventh pipeline (107), the air conditioning system further comprises an eighth pipeline (108) and a ninth pipeline (109), one end of the eighth pipeline (108) is communicated to the sixth pipeline (106) and is positioned between the third control valve (73) and the throttling device (31), the other end of the eighth pipeline is connected to the seventh pipeline (107) and is positioned between the sixth control valve (76) and the indoor heat exchanger (41), one end of the ninth pipeline (109) is communicated to the sixth pipeline (106) and is positioned between the indoor heat exchanger (41) and the third control valve (73), the other end of the ninth pipeline is connected to the seventh pipeline (107) and is positioned between the sixth control valve (76) and the four-way valve (51), a fourth control valve (74) is arranged on the eighth pipeline (108), and a fifth control valve (75) is arranged on the ninth pipeline (109); the seventh pipe (107) is arranged close to the second fan (62) with respect to the sixth pipe (106), and the ninth pipe (109) is arranged distant from the second fan (62) with respect to the eighth pipe (108).