JPH0861799A - Air conditioner - Google Patents

Abstract

PURPOSE: To provide an air conditioner which can realize the improvement of a counterflow type heat exchanging efficiency and a cycle efficiency can be improved in a refrigerating cycle using a non-azeotrope refrigerant. CONSTITUTION: Fractionating pipes 3a, 3a' for fractionating a mixed refrigerant of an exaporating step are provided in a first chamber heat exchanger 2a and an out-of-first chamber heat exchanger 4a, and a second chamber heat exchanger 2b for evaporating the fractionated mixed refrigerant and a second out-of- chamber heat exchanger 4b are installed in parallel with the exchanger 2a and the exchanger 4a. Accordingly, in the case, for example of cooling, a temperature difference between the exchangers 2a and 2b is increased, and a counterflow type heat exchanging efficiency can be improved. Even at the time of heating, solenoid valves 7, 8, 11 are closed, indoor side first solenoid valves 9, 12, 15 are opened, and the valve openings of solenoid valves 10, 16 are regulated to obtain similar effect.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner which performs air conditioning by a vapor compression refrigeration cycle using a non-azeotropic mixed refrigerant.

[0002]

2. Description of the Related Art From the viewpoint of protecting the global environment, HCFC refrigerants that have a significant effect on ozone depletion in the stratosphere are 2020
It was decided by the 4th Meeting of the Parties to the Protocol of the Montreal Protocol that R22, which has been generally used as a refrigerant for air conditioners, is subject to the above regulations. Therefore, the development of alternative refrigerants to replace them is an urgent task.

In order to meet such demands, several types of mixed refrigerants have been proposed as alternative refrigerants for the air conditioner in place of R22, and various studies have been tried, but the cycle efficiency is slightly lower than that of R22. is the current situation. By the way, R32 and R
The combination of 134a is a promising alternative refrigerant candidate because of its physical properties such as boiling point, pressure, cycle efficiency, etc., and it is attempted to improve cycle efficiency by utilizing its non-azeotropic property.

In the case of a refrigeration cycle using a non-azeotropic mixed refrigerant, the refrigerant liquid is in a vapor-liquid equilibrium in the evaporator (the indoor heat exchanger functions during cooling, and the outdoor heat exchanger functions during heating). While being kept, it becomes a refrigerant vapor, and during that time, the evaporation temperature gradually rises, while the fluid to be cooled is deprived of heat and becomes gradually lower in temperature. In the condenser, the condensing temperature is gradually decreased, and the fluid to be cooled gets heat and gradually becomes high temperature. Therefore, if so-called countercurrent heat exchange is performed, the efficiency of heat exchange between the refrigerant and the fluid to be cooled or the heat fluid to be cooled can be improved, and the efficiency of the cycle can be achieved.

FIG. 5 shows an example of a conventional heat exchanger. Referring to this figure, the flow of the counter-current type refrigerant in the conventional example will be described. The refrigerant flowing in from the refrigerant inlet 19 flows horizontally in the refrigerant pipe of the first heat exchanger HE1 at the end of the heat exchanger. It is folded back by the U-bend and flows horizontally toward the refrigerant inlet 19 again. After repeating the above operation, the refrigerant flows into the refrigerant pipe of the second heat exchanger HE2 at the lower end of the first heat exchanger HE1 and repeats the same operation as described above to horizontally move the second heat exchanger HE2. After flowing, it flows out from the refrigerant outlet 20. In the figure, F1 and F2 are fluids to be cooled,
That is, it indicates the flow of air.

In a refrigeration cycle using a non-azeotropic mixed refrigerant, as shown in FIG. 5, the inlet of the refrigerant is in the most downwind row of the flow of the fluid to be cooled, and the outlet is in the most upwind row. Pipes are arranged so that the refrigerant flows from the leeward row to the leeward row in sequence. That is, a countercurrent system in which a heat exchanger having a high refrigerant temperature is arranged on the windward side and a heat exchanger having a low refrigerant temperature is arranged on the leeward side is effective in improving the efficiency of the refrigeration cycle.

[0007]

The above-mentioned prior art utilizes the fact that the phase change temperature of the non-azeotropic mixed refrigerant depends on the concentration. FIG. 6 shows the relationship between the concentration of the mixed refrigerant of R32 and R134a, which is a strong candidate for the air conditioner alternative refrigerant, and the phase change temperature. In this figure, αE1β rays are saturated liquid lines and αGγ rays are saturated vapor lines.

As an example, the temperature and concentration changes of the evaporator when the mixing ratio is 30/70 (R32 / R134a) will be described with reference to FIG. For simplification, overheating in the evaporator is not taken into consideration. The inlet of the evaporator is at point E. By receiving heat from the air to be cooled, the mixed refrigerant is divided into a refrigerant liquid (point E1) and a refrigerant gas (point E2). Further, by receiving heat, the refrigerant liquid and the refrigerant gas are in equilibrium, the temperature rises while advancing on their respective saturation curves, and reaches the evaporator outlet (point G).

Therefore, the temperature difference of the phase change, that is, the temperature difference between the inlet and the outlet of the evaporator is ΔT1 ° C., and this temperature difference is used to improve the heat exchange efficiency by the countercurrent system. It is a known fact that the effect of improving the heat exchange efficiency by the counterflow method is more remarkable when the temperature difference between the evaporator inlet and outlet is large, but in the conventional refrigeration cycle, as described above, from the physical property value of the refrigerant. It was not possible to obtain more than the specified temperature difference, and the effect of improving the heat exchange efficiency by the countercurrent method was actually very small.

The present invention has been made in view of such conventional problems, and an object thereof is to provide an air conditioner capable of improving heat exchange efficiency by a countercurrent system. .

[0011]

In order to achieve the above object, in the air conditioner of the present invention, a non-coincidence unit having a compressor, a four-way valve, a first outdoor heat exchanger, an expansion valve and a first indoor heat exchanger is provided. A refrigerant circuit using a boiling mixed refrigerant, the first indoor heat exchanger and the first outdoor heat exchanger of the refrigerant circuit is connected to a fractionation pipe and a receiver tank for fractionating the mixed refrigerant in the evaporation process, and Two indoor heat exchangers and a second outdoor heat exchanger are installed in parallel, respectively, and the refrigerant flowing out from the receiver tank is introduced into the second indoor heat exchanger and the second outdoor heat exchanger, while the refrigerant is The inlet is set to the most leeward row of the flow of the fluid to be cooled, the outlet is set to the most leeward row, and the refrigerant circuit pipes are arranged in order from the leeward row to the leeward row of refrigerant It is configured to flow.

FIG. 1 showing an embodiment of the above technical means.
More specifically using FIG. 3, the refrigerant circuit is
The compressor 1, the four-way valve 22, the outdoor heat exchanger unit 4, the expansion valve 5, and the indoor heat exchanger unit 2 are sequentially connected by a refrigerant pipe, and the non-azeotropic mixed refrigerant is filled.
In this refrigerant circuit, the indoor heat exchanger unit 2 includes the first and second indoor heat exchangers 2a and 2b, while the outdoor heat exchanger unit 4 includes the first and second outdoor heat exchangers 4a and 4a. 4b is provided.

In the first and second indoor heat exchangers 2a and 2b and the first and second outdoor heat exchangers 4a and 4b, refrigerant pipes from the expansion valve 5 to the four-way valve 22 are branched and arranged in parallel. The indoor first solenoid valve 9 is connected to the refrigerant piping portion of the second indoor heat exchanger 2b on the refrigerant inlet side, and the indoor first solenoid valve 9 is connected to the refrigerant piping portion of the second outdoor heat exchanger 4b on the refrigerant inlet side. Outer first
Solenoid valves 12 are provided respectively, and further, an indoor second solenoid valve 15 is provided in a refrigerant pipe portion on the refrigerant outlet side of the first indoor heat exchanger 2a, and a refrigerant pipe on the refrigerant outlet side of the first outdoor heat exchanger 4a. The outdoor second solenoid valve 16 is provided in each section.

The first indoor heat exchanger 2a of the indoor heat exchanger unit 2 is arranged on the leeward side of the second indoor heat exchanger 2b, and the first outdoor heat exchanger 4a of the outdoor heat exchanger unit 4 is Similarly, it is arranged on the leeward side of the second outdoor heat exchanger 4b.

When the first indoor heat exchanger 2a acts as an evaporator, an indoor-side distilling pipe 3a for distilling the mixed refrigerant in the evaporation process and sending it to the second indoor heat exchanger 2b is provided in the first chamber. It is attached to the vicinity of the refrigerant outlet of the heat exchanger 2a through the indoor third solenoid valve 8.

The refrigerant flowing out from the indoor third solenoid valve 8 once flows into the indoor receiver tank 13, and then the indoor liquid transfer pump 14 connected to one end of the indoor receiver tank 13 2 Indoor heat exchanger 2b
Is connected so as to flow into the refrigerant pipe portion between the refrigerant inlet and the indoor first solenoid valve 9 via the indoor check valve 17. The other end of the indoor receiver tank 13 is provided between the indoor second electromagnetic valve 15 and the four-way valve 22 provided at the refrigerant outlet of the first indoor heat exchanger 2a via the indoor fourth electromagnetic valve 7. It is connected to the refrigerant piping section.

Further, when the first outdoor heat exchanger 4a acts as an evaporator, the outdoor refrigerant pipe 3a 'for collecting the mixed refrigerant in the evaporation process and sending it to the second outdoor heat exchanger 4b.
The third outdoor side is located near the refrigerant outlet of the first outdoor heat exchanger 4a.
It is attached via a solenoid valve 11.

The refrigerant flowing out from the outdoor side third solenoid valve 11 once flows into the outdoor side receiver tank 13 ', and thereafter, by the outdoor side liquid supply pump 14' connected to the outdoor side receiver tank 13 '. Second outdoor heat exchanger 4b
Is connected to the refrigerant pipe portion between the refrigerant inlet and the outdoor first solenoid valve 12 via the outdoor check valve 18. The other end of the outdoor receiver tank 13 ′ is connected to the first outdoor heat exchanger 4 via the outdoor fourth electromagnetic valve 10.
It is connected to the refrigerant pipe portion between the outdoor second electromagnetic valve 16 and the four-way valve 22 provided at the refrigerant outlet of a.

[0019]

[Operation] The operation of the above configuration will be described in the case of cooling.
1 to 3, the refrigerant that has left the expansion valve 5 and has become a gas-liquid two-phase is guided to the first indoor heat exchanger 2a by closing the indoor first electromagnetic valve 9. Of the mixed refrigerant in the evaporation process in the first indoor heat exchanger 2a, the mixed refrigerant liquid containing a large amount of high-boiling-point refrigerant is fractionated by the indoor-side fractionation pipe 3a and flows into the indoor-side receiver tank 13.

At this time, the third indoor solenoid valve 8 is opened, and the second indoor solenoid valve 15 adjusts the opening so that the refrigerant liquid does not flow out to the outlet of the first indoor heat exchanger 2a. Further, only the refrigerant liquid in the receiver tank 13 is sent to the second indoor heat exchanger 2b. On the other hand, the refrigerant gas containing a large amount of the low boiling point refrigerant evaporated in the first indoor heat exchanger 2a is received by the receiver tank 1
3 merges with the refrigerant gas containing a large amount of high-boiling-point refrigerant and flows toward the compressor 1. At this time, the indoor-side fourth solenoid valve 7 adjusts the valve opening so that the refrigerant liquid containing a large amount of high-boiling-point refrigerant does not flow out.

The first and second outdoor heat exchangers 4 during heating
In order to obtain the same effect for a and 4b, it is assumed that the first and second outdoor heat exchangers 4a and 4b also have the same structure as the first and second indoor heat exchangers 2a and 2b. 7, 8, 1
1 is closed, the indoor first solenoid valves 9, 12, 15 are open, and the solenoid valves 10, 16 adjust the valve opening so that the refrigerant liquid does not flow out like the solenoid valves 7, 15 during cooling. To do.

By the above technical means, the mixed refrigerant introduced into the second indoor heat exchanger 2b contains more high-boiling point refrigerant than the mixed refrigerant liquid flowing into the first indoor heat exchanger 2a.
Evaporation occurs at a temperature higher than that of the first indoor heat exchanger 2a. Therefore, the temperature difference between the inlet of the first indoor heat exchanger 2a and the outlet of the second indoor heat exchanger 2b becomes larger than the temperature difference between the indoor heat exchanger inlet and the outlet of the conventional non-azeotropic mixed refrigerant. The heat exchange efficiency can be improved by the countercurrent method.

[0023]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 schematically shows a refrigerant circuit of an air conditioner according to this embodiment. The refrigerant circuit filled with the non-azeotropic mixed refrigerant in the present embodiment includes a compressor 1, an indoor heat exchanger unit 2, an outdoor heat exchanger unit 4, and an expansion valve 5.
Both ends of the refrigerant pipe passing through the outdoor heat exchanger unit 4, the expansion valve 5, and the indoor heat exchanger unit 2 are connected to a four-way valve 22 connected to the compressor 1 to form a refrigeration cycle.

In this refrigerant circuit, during the cooling operation, the compressor 1 → the four-way valve 22 → the outdoor heat exchanger unit 4 → the expansion valve 5
→ Indoor heat exchanger unit 2 → Four-way valve 22 → Compressor circulates in the cycle of compressor 1, and conversely, during heating operation,
By switching the four-way valve 22, the refrigerant circulates in the cycle of compressor 1 → four-way valve 22 → indoor heat exchanger unit 2 → expansion valve 5 → outdoor heat exchanger unit 4 → four-way valve 22 → compressor 1. become.

The indoor heat exchanger unit 2 includes first and second indoor heat exchanger units.
The indoor heat exchangers 2a and 2b are provided, and the second indoor heat exchanger 2b
An indoor blower 6a is provided at a position facing with.
Similarly, the outdoor heat exchanger unit 4 includes first and second outdoor heat exchangers 4a and 4b, and an outdoor blower 6b is provided at a position facing the second outdoor heat exchanger 4b. Therefore, in the case of the indoor heat exchanger unit 2, the first indoor heat exchanger 2a is arranged on the leeward side of the second indoor heat exchanger 2b, and similarly in the case of the outdoor heat exchanger unit 4, the first outdoor heat exchanger The heat exchanger 4a is arranged on the leeward side of the second outdoor heat exchanger 4b.

These first and second indoor heat exchangers 2a, 2b
The expansion valve 5 is provided between the first and second outdoor heat exchangers 4a and 4b.
The refrigerant pipes from the four-way valve 22 to the four-way valve 22 are branched and connected in parallel, and the indoor first solenoid valve 9 is provided in the refrigerant pipe portion of the second indoor heat exchanger 2b on the refrigerant inlet side.
The outdoor first electromagnetic valves 12 are provided in the refrigerant piping portions on the refrigerant inlet side of the outdoor heat exchanger 4b. Also, the first
An indoor second electromagnetic valve 15 is provided in the refrigerant piping portion on the refrigerant outlet side of the indoor heat exchanger 2a, and an outdoor second electromagnetic valve 16 is provided in the refrigerant piping portion on the refrigerant outlet side of the first outdoor heat exchanger 4a. It is provided.

Reference numeral 3a denotes a first indoor-side fractionation pipe, which separates the mixed refrigerant in the evaporation process when the first indoor heat exchanger 2a acts as an evaporator during the cooling operation. Which is stored and sent to the second indoor heat exchanger 2b,
It is attached to the vicinity of the refrigerant outlet of the first indoor heat exchanger 2a via an indoor third solenoid valve 8.

The refrigerant flowing out from the indoor third solenoid valve 8 once flows into the indoor receiver tank 13, and then the indoor liquid transfer pump 14 connected to one end of the receiver tank 13 makes the second The indoor heat exchanger 2b is connected to the second indoor distribution pipe 3b provided between the refrigerant inlet of the indoor heat exchanger 2b and the indoor first solenoid valve 9 so as to flow through the indoor check valve 17. The other end of the indoor receiver tank 13 has the other indoor second electromagnetic valve 1 provided at the refrigerant outlet of the first indoor heat exchanger 2a via the indoor fourth electromagnetic valve 7.
5 is connected to the refrigerant pipe portion between the four-way valve 22.

3a 'is a first outdoor-side distilling pipe,
When the first outdoor heat exchanger 4a acts as an evaporator during heating operation, the fractionation pipe 3a 'fractionates the mixed refrigerant in the evaporation process and sends it to the second outdoor heat exchanger 4b. The third outdoor side is provided near the refrigerant outlet of the first outdoor heat exchanger 4a.
It is attached via a solenoid valve 11.

The refrigerant flowing out from the outdoor third solenoid valve 11 once flows into the outdoor receiver tank 13 ',
After that, by the outdoor liquid sending pump 14 'connected to the receiver tank 13', the second external heat exchanger 4b is provided between the refrigerant inlet of the second outdoor heat exchanger 4b and the outdoor first electromagnetic valve 12.
It is connected so as to flow into the outdoor-side collecting pipe 3b ′ through the outdoor-side check valve 18. The other end of the outdoor receiver tank 13 ′ is connected to the outdoor second electromagnetic valve 16 and the four-way valve 22 provided at the refrigerant outlet of the first outdoor heat exchanger 4 a via the outdoor fourth electromagnetic valve 10. It is connected to the refrigerant pipe section in between.

Next, the operation of the present embodiment during the cooling operation will be described. The non-azeotropic mixed refrigerant which is compressed by the compressor 1 and becomes high-temperature high-pressure gas is the first and second outdoor heat exchangers 4a and 4a.
In b, the heat is radiated to the outdoor air sent by the blower 6b to be condensed and become a mixed refrigerant liquid. At that time, the outdoor fourth and third electromagnetic valves 10 and 11 are closed, and the outdoor first and second electromagnetic valves 12 and 16 are open, whereby the first and second outdoor heat exchangers 4a, 4b fulfills the same function as a known outdoor heat exchanger.

The mixed refrigerant liquid is decompressed by the expansion valve 5,
The first and second indoor heat exchangers 2a become low-temperature gas-liquid two-phase,
Go to 2b. At that time, since the indoor first solenoid valve 9 is closed, the mixed refrigerant liquid flows into the first indoor heat exchanger 2a.

In the first indoor heat exchanger 2a, the blower 6
By receiving heat from the indoor air sent by a,
The mixed refrigerant liquid starts to evaporate, and the mixed refrigerant liquid containing a large amount of high-boiling-point refrigerant that is in equilibrium with the evaporated gas is fractionated by the fractionation pipe 3a and passes through the open third indoor solenoid valve 8 to receive the receiver tank. It flows into 13. At that time, the third indoor side
The solenoid valve 8 is opened, and the indoor second solenoid valve 15 adjusts the opening degree so that the refrigerant liquid does not flow out to the outlet of the first indoor heat exchanger 2a. A part of the refrigerant gas containing a large amount of low-boiling-point refrigerant passes through the indoor second electromagnetic valve 15 toward the outlet of the indoor first indoor heat exchanger 2a, while the remaining refrigerant gas contains the receiver tank 13. Flow into.

Therefore, the refrigerant liquid containing a large amount of high-boiling point refrigerant and the refrigerant gas containing a large amount of low-boiling point refrigerant coexist in the receiver tank 13, and the refrigerant below the receiver tank 13 due to the difference in specific gravity between the refrigerant liquid and the refrigerant gas. The liquid and the refrigerant gas are located above. Therefore, only the refrigerant liquid containing a large amount of high-boiling-point refrigerant flows out from the second fractionation pipe 3b installed below the receiver tank 13, and the liquid feed pump 14
Will be guided to the second indoor heat exchanger 2b,
Refrigerant gas containing a large amount of low-boiling-point refrigerant flows out from the indoor-side fourth electromagnetic valve 7 installed above the receiver tank 13.

The pressure increase by the liquid feed pump 14 is
It is equal to the pressure loss of the pipe connecting the receiver tank 13 and the second indoor heat exchanger 2b. At this time, the pressure at the outlet of the first indoor heat exchanger 2a and the pressure of the outlet of the second indoor heat exchanger 2b are made uniform by throttling the indoor fourth electromagnetic valve 7. That is, since it is possible to obtain a pressure drop equivalent to the pressure loss of the pipe, the present invention is effective even if the liquid feed pump 14 is removed.

By the above operation, during the cooling operation,
A refrigerant liquid containing a large amount of high boiling point refrigerant and a refrigerant gas containing a large amount of low boiling point refrigerant can be fractionated.

The mixed refrigerant liquid containing a large amount of high-boiling-point refrigerant, which has flowed into the second indoor heat exchanger 2b, starts to evaporate at a temperature higher than that of the first indoor heat exchanger 2a, and becomes a gas completely at the outlet.
It evaporates in the first indoor heat exchanger 2a, is mixed with a mixed refrigerant gas containing a large amount of low boiling point refrigerant, and has the same mixing ratio as the third and second outdoor heat exchangers 4a, 4b on the outdoor side. Inhaled. At this time, the indoor-side fourth solenoid valve 7 adjusts the valve opening so that the refrigerant liquid containing a large amount of high-boiling-point refrigerant does not flow out.

The above operation will be described with reference to FIG. FIG. 4 shows the relationship between the concentration of the mixed refrigerant R32 / R134a and the phase change temperature similarly to FIG. 6 described above. In this figure, the inlet of the first indoor heat exchanger 2a is point A. The mixed refrigerant receives heat and evaporates at point A, and is divided into a mixed refrigerant liquid (point A1) containing a large amount of high boiling point refrigerant and a mixed refrigerant gas (point A2) containing a large amount of low boiling point refrigerant while maintaining equilibrium. By further receiving heat from indoor air, the mixed refrigerant liquid is at point B1, and the mixed refrigerant gas is at point B1.
Move to B2.

At the point B1, the mixed refrigerant containing a large amount of high boiling point refrigerant is guided to the second indoor heat exchanger 2b by the first and second fractionating pipes 3a and 3b. Therefore, the inlet of the second indoor heat exchanger 2b is the point B1. The mixed refrigerant liquid begins to evaporate at point B1, splits into points C1 and C2, and continues to evaporate to point D.
To reach.

Therefore, the first and second indoor heat exchangers 2
The maximum temperature difference between a and 2b is ΔT2 ° C. Compared with the above-mentioned conventional example, the temperature difference between the inlet and the outlet of the indoor heat exchanger becomes large, and the heat exchange efficiency by the countercurrent system can be improved.

The operation during the heating operation is opposite to that during the cooling operation. Therefore, the indoor fourth and third electromagnetic valves 7 and 8 and the outdoor third electromagnetic valve 11 are closed, and the indoor first and second electromagnetic valves 9 and 15 and the outdoor first electromagnetic valve 12 are open, and the indoor The outer fourth and second solenoid valves 10 and 16 are the third inner valve during cooling operation,
The effect of the present embodiment can be realized by adjusting the valve opening so that the refrigerant liquid does not flow out like the second electromagnetic valves 7 and 15.

[0042]

As is clear from the above description, in a non-azeotropic mixed refrigerant, the temperature of the refrigerant increases in the evaporator (indoor heat exchanger during cooling, outdoor heat exchanger during heating) as heat is exchanged. To do. Therefore, in the air conditioner according to the present invention,
Performing fractionation in the evaporator, guiding the fractionated mixed refrigerant liquid to a heat exchanger installed in parallel with the evaporator, and evaporating the air flow, which is the heat fluid to be cooled, by a countercurrent method. It is possible to increase the refrigerant temperature difference between the inlet and the outlet of the container and improve the heat exchange efficiency of the counterflow system between the refrigerant and the air.

Further, due to the improvement of the heat exchange efficiency in the evaporator, the temperature of the refrigerant sucked into the compressor rises and the suction pressure rises. As a result, the density of the refrigerant is increased, the refrigerant circulation amount of the compressor is increased, and the capacity can be improved.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a refrigeration cycle showing an embodiment according to the present invention.

FIG. 2 is a schematic diagram of an indoor heat exchanger of the present invention.

FIG. 3 is a perspective view of the indoor heat exchanger of the present invention.

FIG. 4 is a diagram showing the relationship between the concentration of the non-azeotropic mixed refrigerant R32 / R134a and the phase change temperature in the cycle operation of the present embodiment.

FIG. 5 is a perspective view of a conventional heat exchanger.

FIG. 6 is a diagram showing the relationship between the concentration of the non-azeotropic mixed refrigerant R32 / R134a and the phase change temperature in the cycle operation of the conventional example.

[Explanation of Codes] 1 Compressor 2 Indoor heat exchanger unit 2a First indoor heat exchanger 2b Second indoor heat exchanger 3a Indoor first first distilling pipe 3a 'Outdoor first distilling pipe 3b Indoor second Distributing pipe 3b 'Outdoor second distilling pipe 4 Outdoor heat exchanger unit 4a First outdoor heat exchanger 4b Second outdoor heat exchanger 5 Expansion valve 6a Indoor blower 6b Outdoor blower 7 Indoor fourth solenoid valve 8 Chamber Inner third solenoid valve 9 Indoor first solenoid valve 10 Outdoor fourth solenoid valve 11 Outdoor third solenoid valve 12 Outdoor first solenoid valve 13 Indoor receiver tank 13 'Outdoor receiver tank 14 Indoor liquid transfer pump 14 'Outdoor-side liquid feed pump 15 Indoor-side second solenoid valve 16 Outdoor-side second solenoid valve 17 Indoor-side check valve 18 Outdoor-side check valve 19 Refrigerant inlet 20 Refrigerant outlet 22 Four-way valve

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI technical display location F25B 6/02 Z

Claims (2)

[Claims] 1. A refrigerant circuit using a non-azeotropic mixed refrigerant having a compressor, a four-way valve, a first outdoor heat exchanger, an expansion valve and a first indoor heat exchanger, the first indoor heat exchange of the refrigerant circuit. The receiver and the first outdoor heat exchanger are connected to a fractionation pipe and a receiver tank that fractionate the mixed refrigerant in the evaporation process, and the second indoor heat exchanger and the second outdoor heat exchanger are installed in parallel, The refrigerant flowing out from the receiver tank is configured to be introduced into the second indoor heat exchanger and the second outdoor heat exchanger, while the refrigerant inlet is set to the most leeward row of the flow of the cooled fluid, and An air conditioner characterized in that the outlet is set to the most windward row, and the piping of the refrigerant circuit is configured so that the refrigerant sequentially flows from the leeward row to the upwind row. 2. A compressor, a four-way valve, an outdoor heat exchanger unit, an expansion valve, and an indoor heat exchanger unit are sequentially connected by a refrigerant pipe, and a refrigerant circuit filled with a non-azeotropic mixed refrigerant is provided. In, the indoor heat exchanger unit is provided with first and second indoor heat exchangers, while the outdoor heat exchanger unit is provided with first and second outdoor heat exchangers, and first and second indoor heat exchangers are provided. The refrigerant pipes from the expansion valve to the four-way valve are branched and connected in parallel to the exchanger and the first and second outdoor heat exchangers, respectively, and the refrigerant on the refrigerant inlet side of the second indoor heat exchanger is connected. The first solenoid valve on the indoor side is
The outdoor side of the refrigerant pipe section on the refrigerant inlet side of the outdoor heat exchanger is
Solenoid valves are provided respectively, and further, an indoor second solenoid valve is provided on the refrigerant outlet side of the first indoor heat exchanger, and an indoor second electromagnetic valve is provided on the refrigerant outlet side of the first outdoor heat exchanger. The outdoor second electromagnetic valves are respectively provided, the first indoor heat exchanger of the indoor heat exchanger unit is disposed on the leeward side of the second indoor heat exchanger, and the first indoor heat exchanger of the outdoor heat exchanger unit. The outdoor heat exchanger is also arranged on the leeward side of the second outdoor heat exchanger, and when the first indoor heat exchanger acts as an evaporator, it collects the mixed refrigerant in the evaporation process to collect the second indoor heat exchanger. An indoor side distilling pipe for sending to the indoor side heat exchanger is attached to the vicinity of the refrigerant outlet of the first indoor heat exchanger via the indoor side third electromagnetic valve, and the refrigerant flowing out from the indoor side third electromagnetic valve is temporarily stored in the room. It flows into the inner receiver tank and is then connected to one end of its indoor receiver tank. The indoor liquid feed pump is connected to the refrigerant pipe portion between the refrigerant inlet of the second indoor heat exchanger and the indoor first solenoid valve so as to flow through the indoor check valve, and the indoor side The other end of the receiver tank is the fourth indoor side
It is connected via a solenoid valve to a refrigerant pipe portion between the indoor second solenoid valve provided at the refrigerant outlet of the first indoor heat exchanger and the four-way valve, and the first outdoor heat exchanger serves as an evaporator. An outdoor-side distilling pipe for distilling the mixed refrigerant in the process of evaporating and sending it to the second outdoor heat exchanger when acting is provided near the refrigerant outlet of the first outdoor heat exchanger via the outdoor third solenoid valve. The refrigerant that has been attached to the outdoor side third solenoid valve once flows into the outdoor side receiver tank, and then the second outdoor side liquid feed pump connected to the outdoor side receiver tank
The refrigerant inlet of the outdoor heat exchanger is connected to the refrigerant pipe portion between the outdoor first electromagnetic valve via the outdoor check valve, and the other end of the outdoor receiver tank is Outer fourth
An air conditioner characterized by being respectively connected to a refrigerant pipe section between an outdoor second electromagnetic valve provided at a refrigerant outlet of the first outdoor heat exchanger and a four-way valve via an electromagnetic valve.