JPH08178445A - Heat pump type air conditioner - Google Patents

Abstract

PURPOSE: To reduce in size a heat exchanger, to improve the performance of the exchanger and to improve COP (coefficient of performance) by forming an opposite flow at the time of cooling or heating using a pseudo-opposite flow type heat exchanger as the exchanger in a heat pump type air conditioner using nonazeotrope refrigerant. CONSTITUTION: A user side heat exchanger 3 and a heat source side heat exchanger 5 are formed of a plurality of two or more of rows of heat exchangers. At the time of cooling, refrigerant flows from a leeward side row to the windward side row at the exchanger 3 so that the flow of the air cross- counters the flow of the refrigerant. At the time of cooling, the refrigerant flows from the leeward side row to the windward side row at the exchanger 5, and the flow of the air cross-counters the flow of the refrigerant.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improving the efficiency of a heat pump type air conditioner using a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio.

[0002]

2. Description of the Related Art In recent years, from the standpoint of protecting the global environment, regulations on CFCs that destroy the ozone layer have been strengthened, and it has been decided to abolish CFC (chlorofluorocarbon), which has a particularly high destructive power, at the end of 1995. Also, regarding the FCFC (hydrochlorofluorocarbon), which has a relatively small destructive power, the total amount regulation was started in 1996, and it has been decided that it will be completely abolished in the future. Therefore, for devices that use CFCs as refrigerants, alternative refrigerants are being developed, and HFCs (hydrofluorocarbons) that do not destroy the ozone layer are being studied, but HCFCs used in refrigerators and air conditioners are being investigated. No substitute refrigerant that can be used alone in HFC is found, and therefore a non-azeotropic mixed refrigerant obtained by mixing two or more kinds of HFC refrigerants is considered promising.

Conventionally, the evaporation temperature and the condensation temperature of a refrigerator or an air conditioner using a single refrigerant such as CFC or HCFC or an azeotropic mixed refrigerant are isothermal. However, when a non-azeotropic mixed refrigerant is used, the saturated refrigerant liquid temperature and the saturated refrigerant vapor temperature are different, and the saturated refrigerant liquid temperature is lower than the saturated refrigerant vapor temperature, which is non-isothermal. For this reason, some refrigerators using a non-azeotropic mixed refrigerant use a counterflow heat exchanger that can effectively utilize this non-isothermal property. Hereinafter, a refrigeration cycle of a conventional air conditioner will be described with reference to the drawings.

FIG. 6 is a refrigeration cycle diagram of a conventional heat pump type air conditioner. In the figure, 1 is a compressor,
2 is a four-way valve, 3 is a use side heat exchanger, 4 is a throttle valve, 5 is a heat source side heat exchanger, and these are sequentially connected in an annular shape. 6 and 7 are the use side heat exchanger and the heat source, respectively. It is a blower fan for the side heat exchanger.

Next, the specific operation of this refrigeration cycle will be described. First, the heating operation will be described. The flow direction of the refrigerant during heating operation is indicated by a solid arrow, and the refrigerant gas compressed by the compressor 1 passes through the four-way valve 2 to be condensed and liquefied in the heat exchanger 3 on the use side and decompressed and expanded by the decompressor 4 to the heat source side. It evaporates in the heat exchanger 5 and returns to the compressor 1 via the four-way valve 2. Here, the use side heat exchanger 3 and the heat source side heat exchanger 5 are provided with the blower fans 6 and 7 so that the air and the refrigerant flow in opposite directions.

Next, the case where the cooling operation is switched to will be described. The flow direction of the refrigerant during the cooling operation is indicated by a broken line arrow, and the refrigerant gas compressed by the compressor 1 passes through the four-way valve 2 to be condensed and liquefied in the heat source side heat exchanger 5, decompressed and expanded in the decompressor 4, and used. Air and refrigerant in the use side heat exchanger 3 and the heat source side heat exchanger 5 are evaporated and vaporized in the heat exchanger 3 and return to the compressor 1 via the four-way valve 2 and the flow direction of the refrigerant reverses to that during heating. The flow directions of are parallel flows.

[0007]

As described above, the conventional heat pump type air conditioner has the following problems.

Utilization side heat exchanger 3 and heat source side heat exchanger 5
Since the counterflow type heat exchanger is used in the above, it is necessary to make the heat exchanger multi-pass or to lengthen the wind circuit, which complicates the structure of the heat exchanger. Further, there is a problem that a high static pressure is required for the blower and the device becomes large.

In view of the above problems, the refrigeration cycle of the present invention is
In a refrigeration cycle using a non-azeotropic mixed refrigerant, the performance of the heat exchanger is improved with a simple heat exchanger configuration, and the COP of the system is improved.

[0010]

In order to solve the above-mentioned problems, the refrigerating cycle of the present invention has two different boiling points as refrigerants.
A non-azeotropic mixed refrigerant in which more than one kind of refrigerant is mixed in a predetermined ratio is used, and the compressor, four-way valve, utilization side heat exchanger, pressure reducer, and heat source side heat exchanger are connected in an annular shape by piping in sequence. A circuit is configured, and the use side heat exchanger and the heat source side heat exchanger are configured by a plurality of rows of heat exchangers of two or more rows, and the use side heat exchanger is moved from the leeward side row to the windward side row during cooling operation. Refrigerant to flow, the flow of the wind and the flow of the refrigerant to be a cross counter, and during the cooling operation to flow the refrigerant from the leeward row to the windward row to the heat source side heat exchanger, the flow of the wind and the flow of the refrigerant. Is a cross counter.

In another refrigeration cycle of the present invention, a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a four-way valve, a heat exchanger on the utilization side are used. , A decompressor and a heat source side heat exchanger are sequentially connected in an annular shape to form a refrigerant circuit, and the use side heat exchanger and the heat source side heat exchanger are heat exchangers in two or more rows. The heating side heat exchanger is configured to flow a refrigerant from the downwind side row to the upwind side row during the heating operation, and the flow of the air and the flow of the refrigerant serve as a cross counter, and the heat source side heat exchanger during the cooling operation. In this configuration, the refrigerant flows from the leeward side row to the leeward side row, and the flow of the wind and the flow of the refrigerant serve as a cross counter.

In another refrigeration cycle of the present invention, a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a four-way valve, a heat exchanger on the utilization side are used. , A decompressor and a heat source side heat exchanger are sequentially connected in an annular shape to form a refrigerant circuit, and the use side heat exchanger and the heat source side heat exchanger are heat exchangers in two or more rows. And a configuration in which refrigerant flows from the leeward side row to the upwind side row in the use side heat exchanger during cooling operation, and the flow of the wind and the flow of the refrigerant become a cross counter, and the heat source side heat exchanger during heating operation. In this configuration, the refrigerant flows from the leeward side row to the leeward side row, and the flow of the wind and the flow of the refrigerant serve as a cross counter.

In another refrigeration cycle of the present invention, a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a four-way valve, a heat exchanger on the use side are used. , A decompressor and a heat source side heat exchanger are sequentially connected in an annular shape to form a refrigerant circuit, and the use side heat exchanger and the heat source side heat exchanger are heat exchangers in two or more rows. The heating source side heat exchanger is configured such that a refrigerant flows from the leeward side row to the windward side row in the use side heat exchanger during heating operation, and the flow of the wind and the refrigerant flow become a cross counter, and the heat source side heat exchanger during heating operation. In this configuration, the refrigerant flows from the leeward side row to the leeward side row, and the flow of the wind and the flow of the refrigerant serve as a cross counter.

[0014]

The present invention has the following actions due to the above means.

That is, the present invention provides a heat pump type air conditioner using a non-azeotropic mixed refrigerant,
The utilization-side heat exchanger and the heat-source-side heat exchanger are composed of a plurality of rows of heat exchangers of two or more rows, and the refrigerant is caused to flow from the leeward side row to the windward side row in the use-side heat exchanger during cooling operation, With a configuration in which the flow of air and the flow of refrigerant become a cross counter,
Moreover, during the cooling operation, the refrigerant flows from the leeward side row to the windward side row in the heat source side heat exchanger, and the flow of the wind and the flow of the refrigerant become a cross counter, and the use side heat exchanger and the heat source side during the cooling operation. The size of the heat exchanger can be reduced and the cooling operation can be performed by changing the flow direction of the air passing through the heat exchanger and the refrigerant flowing in the heat exchanger to a cross counter flow (pseudo-counterflow) that mixes a direct flow and a counterflow. In this case, the heat exchange performance of the evaporator and the condenser can be improved and the cooling COP can be significantly improved.

Further, during the heating operation, a refrigerant is made to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the wind and the flow of the refrigerant form a cross counter, and the heat source side heat exchanger is operated during the cooling operation. Refrigerant flows from the leeward row to the leeward row in the exchanger, and the flow of the air and the refrigerant becomes a cross counter, and flows through the heat source side heat exchanger and the air in the heat exchanger during cooling operation. The flow direction of the refrigerant is operated as a cross counter flow, and the air flowing through the heat exchanger on the utilization side and the flow direction of the refrigerant flowing through the heat exchanger are operated as a cross counter flow for the heating operation. The cooling COP can be improved by downsizing and improving the heat exchange performance of the condenser during the cooling operation. Further, the heat exchange performance of the condenser during the heating operation can be improved, and the heating COP can be improved.

Further, during the cooling operation, a refrigerant is made to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the wind and the flow of the refrigerant form a cross counter, and the heat source side heat exchanger is operated during the heating operation. Refrigerant flows from the leeward row to the upwind row in the exchanger, and the flow of the air and the refrigerant becomes a cross counter, and flows through the heat exchanger and the air that passes through the heat exchanger on the use side for cooling operation. The flow direction of the refrigerant is operated as a cross counter flow, and in the heating operation, the air flowing through the heat source side heat exchanger and the flow direction of the refrigerant flowing through the heat exchanger are operated as a cross counter flow, thereby It is possible to improve the cooling COP by downsizing and improving the heat exchange performance of the evaporator during the cooling operation. Further, even during the heating operation, the heat exchange performance of the evaporator can be improved to prevent frost formation and improve the heating COP.

Further, during the heating operation, a refrigerant is made to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the wind and the flow of the refrigerant become a cross counter, and the heat source side heat exchanger is operated during the heating operation. Refrigerant flows from the leeward side row to the exchanger side, and the flow of the air and the refrigerant flow becomes a cross counter, and the air that passes through the use side heat exchanger and the heat source side heat exchanger during heating operation By making the flow direction of the refrigerant flowing through the heat exchanger a cross counter flow, the heat exchanger can be downsized, and the heat exchange performance of the evaporator and the condenser during heating operation can be improved to significantly improve the heating COP and It is possible to prevent frost formation.

[0019]

Embodiments of the present invention will be described below with reference to the drawings. It should be noted that components having the same functions as those described in the section of the related art are designated by the same reference numerals and detailed description thereof will be omitted.

First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows the first of the present invention.
2 is a refrigeration cycle diagram in the embodiment of FIG. 2, and FIG. 2 shows a cross-counter flow type heat exchanger used in the utilization side heat exchanger 3 and the heat source side heat exchanger 5 of the first to fourth examples of the present invention. It is a side view.

In FIG. 1, 1 is a compressor, 2 is a four-way valve,
3 is a heat exchanger on the use side, 4 is a decompressor, and 5 is a heat exchanger on the heat source side, which are sequentially connected in an annular shape by piping. A non-azeotropic mixed refrigerant is used as the refrigerant.

In FIG. 2, 11 is a heat exchanger body, 12 is a heat exchange fin, and 13 is a tube. Refrigerant flows in from the leeward row, goes straight to the wind, and exchanges heat through the windward row. It flows out of the container 11.

Next, the specific operation of this refrigeration cycle will be described. First, the heating operation will be described. The flow direction of the refrigerant during heating operation is indicated by a solid arrow,
The refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, is condensed and liquefied by the use-side heat exchanger 3, is decompressed and expanded by the decompressor 4, is evaporated and vaporized by the heat-source-side heat exchanger 5, and is passed through the four-way valve 2 to be a compressor. Return to 1.

Next, the case of switching to the cooling operation will be described. The flow direction of the refrigerant during the cooling operation is indicated by a dashed arrow, and the refrigerant gas compressed by the compressor 1 is the four-way valve 2
Through the heat source side heat exchanger 5, condensed and liquefied by the pressure reducer 4, evaporated and vaporized by the use side heat exchanger 3, and returned to the compressor 1 via the four-way valve 2.

As described above, during the cooling operation, the flow direction of the refrigerant in the use side heat exchanger 3 and the heat source side heat exchanger 5 is set to a pseudo counter flow (cross counter flow) with the air flow direction. We aim to reduce the size of the heat exchanger and improve the heat exchange performance of the evaporator and condenser during cooling operation.
It is possible to significantly improve the cooling COP.

Next, a second embodiment of the present invention will be described with reference to the drawings. FIG. 3 is a refrigeration cycle diagram in the second embodiment of the present invention. The difference from the first embodiment is that during the heating operation, the refrigerant flows through the utilization side heat exchanger 3 from the leeward side row to the windward side row, and the flow of the wind and the flow of the refrigerant serve as a cross counter, and the cooling is performed. At the time of operation, the heat source side heat exchanger 5 is made to flow a refrigerant from the leeward side row to the leeward side row, and the flow of the wind and the flow of the refrigerant serve as a cross counter.

Next, the specific operation of this refrigeration cycle will be described. First, the heating operation will be described. The flow direction of the refrigerant during heating operation is indicated by a solid arrow,
The refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, is condensed and liquefied by the use-side heat exchanger 3, is decompressed and expanded by the decompressor 4, is evaporated and vaporized by the heat-source-side heat exchanger 5, and is passed through the four-way valve 2 to be a compressor. Return to 1.

Next, the case of switching to the cooling operation will be described. The flow direction of the refrigerant during the cooling operation is indicated by a dashed arrow, and the refrigerant gas compressed by the compressor 1 is the four-way valve 2
Through the heat source side heat exchanger 5, condensed and liquefied by the pressure reducer 4, evaporated and vaporized by the use side heat exchanger 3, and returned to the compressor 1 via the four-way valve 2.

As described above, the flow direction of the refrigerant in the utilization side heat exchanger 3 during the heating operation and the flow direction of the air in the heat source side heat exchanger 5 during the cooling operation are set to be pseudo counter-currents to generate heat. It is possible to improve the cooling COP and the heating COP by downsizing the exchanger and improving the heat exchange performance of the condenser during the heating operation and the condenser during the cooling operation.

Next, a third embodiment of the present invention will be described with reference to the drawings. FIG. 4 is a refrigeration cycle diagram in the third embodiment of the present invention. The difference from the first and second embodiments is that the refrigerant flows from the leeward side row to the windward side row in the use side heat exchanger 3 during the cooling operation, and the flow of the air and the flow of the refrigerant are cross counters. In addition, during the heating operation, the refrigerant flows from the leeward side row to the windward side row in the heat source side heat exchanger 5, and the flow of the wind and the flow of the refrigerant serve as a cross counter.

Next, the specific operation of this refrigeration cycle will be described. First, the heating operation will be described. The flow direction of the refrigerant during heating operation is indicated by a solid arrow,
The refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, is condensed and liquefied by the use-side heat exchanger 3, is decompressed and expanded by the decompressor 4, is evaporated and vaporized by the heat-source-side heat exchanger 5, and is passed through the four-way valve 2 to be a compressor. Return to 1.

Next, the case of switching to the cooling operation will be described. The flow direction of the refrigerant during the cooling operation is indicated by a dashed arrow, and the refrigerant gas compressed by the compressor 1 is the four-way valve 2
Through the heat source side heat exchanger 5, condensed and liquefied by the pressure reducer 4, evaporated and vaporized by the use side heat exchanger 3, and returned to the compressor 1 via the four-way valve 2.

As described above, the flow direction of the refrigerant in the heat source side heat exchanger 3 during the heating operation and the flow direction of the refrigerant in the utilization side heat exchanger 5 during the cooling operation are set to be a pseudo counter-flow to thereby generate heat. By reducing the size of the exchanger and improving the heat exchange performance of the evaporator during heating operation and the evaporator during cooling operation, it is possible to improve cooling COP and heating COP and prevent frost formation.

Next, a fourth embodiment of the present invention will be described with reference to the drawings. FIG. 5 is a refrigeration cycle diagram in the fourth embodiment of the present invention. The difference from the first, second, and third embodiments is that the heat exchanger 3 on the use side during the heating operation.
The refrigerant is made to flow from the leeward row to the windward row, and the flow of the air and the refrigerant become a cross counter, and the heat source side heat exchanger 5 is made to flow the refrigerant from the leeward row to the leeward row during heating operation. The flow is such that the flow of the wind and the flow of the refrigerant become a cross counter.

Next, the specific operation of this refrigeration cycle will be described. First, the heating operation will be described. The flow direction of the refrigerant during heating operation is indicated by a solid arrow,
The refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, is condensed and liquefied by the use-side heat exchanger 3, is decompressed and expanded by the decompressor 4, is evaporated and vaporized by the heat-source-side heat exchanger 5, and is passed through the four-way valve 2 to be a compressor. Return to 1.

Next, the case of switching to the cooling operation will be described. The flow direction of the refrigerant during the cooling operation is indicated by a dashed arrow, and the refrigerant gas compressed by the compressor 1 is the four-way valve 2
Through the heat source side heat exchanger 5, condensed and liquefied by the pressure reducer 4, evaporated and vaporized by the use side heat exchanger 3, and returned to the compressor 1 via the four-way valve 2.

In this way, during the heating operation, the flow direction of the refrigerant in the use side heat exchanger 3 and the heat source side heat exchanger 5 is made to be a pseudo counterflow to the air flow direction, so that the evaporation in the heating operation is performed. It is possible to improve the heat exchange performance of the condenser and the condenser, and to significantly improve the heating COP and prevent frost formation.

Further, the refrigerating cycle of the present invention is not limited to the Freon type refrigerant, but can be applied to other refrigerants as long as it is a non-azeotropic mixed refrigerant. Further, in this embodiment, a two-row, upward-convex, two-pass, quasi-counterflow type heat exchanger is shown. However, two or more rows, downward convex, mixed upward convex and downward convex, X-type You may use the path of.

[0039]

As apparent from the above embodiment, the present invention is
It is intended to provide a heat pump type air conditioner using a non-azeotropic mixed refrigerant, flowing the refrigerant from the leeward side row to the windward side row in the utilization side heat exchanger during the cooling operation, the flow of the wind and the refrigerant flow. It is configured to be a cross counter, and the refrigerant is made to flow from the leeward row to the upwind row in the heat source side heat exchanger during cooling operation so that the flow of the wind and the refrigerant flow become a cross counter, which is used during cooling operation. By changing the flow direction of the air passing through the side heat exchanger and the heat source side heat exchanger and the refrigerant flowing in the heat exchanger to a cross counter flow (pseudo-counterflow) in which a direct flow and a counterflow are mixed, And the heat exchange performance of the evaporator and the condenser during the cooling operation can be improved, and the cooling COP can be significantly improved.

Further, during the heating operation, a refrigerant is made to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the air and the refrigerant flow become a cross counter, and the heat source side heat exchanger is operated during the cooling operation. Refrigerant flows from the leeward row to the leeward row in the exchanger, and the flow of the air and the refrigerant becomes a cross counter, and flows through the heat source side heat exchanger and the air in the heat exchanger during cooling operation. The flow direction of the refrigerant is operated as a cross counter flow, and the air flowing through the heat exchanger on the utilization side and the flow direction of the refrigerant flowing through the heat exchanger are operated as a cross counter flow for the heating operation. The cooling COP can be improved by downsizing and improving the heat exchange performance of the condenser during the cooling operation. Further, the heat exchange performance of the condenser during the heating operation can be improved, and the heating COP can be improved.

Further, during the cooling operation, a refrigerant is made to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the air and the flow of the refrigerant form a cross counter, and the heat source side heat exchanger is operated during the heating operation. Refrigerant flows from the leeward row to the upwind row in the exchanger, and the flow of the air and the refrigerant becomes a cross counter, and flows through the heat exchanger and the air that passes through the heat exchanger on the use side for cooling operation. The flow direction of the refrigerant is operated as a cross counter flow, and in the heating operation, the air flowing through the heat source side heat exchanger and the flow direction of the refrigerant flowing in the heat exchanger are operated as a cross counter flow, thereby It is possible to improve the cooling COP by downsizing and improving the heat exchange performance of the evaporator during the cooling operation. Further, even during the heating operation, the heat exchange performance of the evaporator can be improved to prevent frost formation and improve the heating COP.

Further, during the heating operation, the refrigerant is caused to flow from the leeward side row to the upwind side row in the utilization side heat exchanger so that the flow of the air and the flow of the refrigerant serve as a cross counter, and the heat source side heat is applied during the heating operation. Refrigerant flows from the leeward side row to the exchanger side, and the flow of the air and the refrigerant flow becomes a cross counter, and the air that passes through the use side heat exchanger and the heat source side heat exchanger during heating operation By making the flow direction of the refrigerant flowing through the heat exchanger a cross counter flow, the heat exchanger can be downsized, and the heat exchange performance of the evaporator and the condenser during heating operation can be improved to significantly improve the heating COP and It is possible to prevent frost formation.

[Brief description of drawings]

FIG. 1 is a refrigeration cycle diagram of a heat pump type air conditioner according to a first embodiment of the present invention.

FIG. 2 is a utilization side heat exchanger according to first to fourth embodiments of the present invention,
Side view of cross counter flow type heat exchanger used for heat source side heat exchanger

FIG. 3 is a refrigeration cycle diagram of the heat pump type air conditioner in the second embodiment of the present invention.

FIG. 4 is a refrigeration cycle diagram of a heat pump type air conditioner according to a third embodiment of the present invention.

FIG. 5 is a refrigeration cycle diagram of a heat pump type air conditioner according to a fourth embodiment of the present invention.

FIG. 6 is a refrigeration cycle diagram of a heat pump type air conditioner in a conventional example.

[Explanation of symbols]

 1 Compressor 2 Four-way valve 3 Use side heat exchanger 4 Pressure reducer 5 Heat source side heat exchanger 6 Blower fan (use side heat exchanger) 7 Blower fan (heat source side heat exchanger)

Claims (4)

[Claims] 1. A compressor, a four-way valve, a use side heat exchanger, a pressure reducer, a heat source side heat exchanger, wherein a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as the refrigerant. Are connected to each other in an annular shape to form a refrigerant circuit, and the heat exchanger on the use side and the heat exchanger on the heat source side are constituted by heat exchangers in a plurality of rows of two or more rows. Refrigerant flows from the downwind side row to the upwind side row in the heat exchanger, and the flow of the air and the refrigerant flow becomes a cross counter, and the heat source side heat exchanger moves from the downwind side row to the upwind side row during cooling operation. A heat pump type air conditioner in which the refrigerant flows and the flow of the air and the flow of the refrigerant become a cross counter. 2. A compressor, a four-way valve, a utilization side heat exchanger, a pressure reducer, a heat source side heat exchanger, wherein a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as the refrigerant. Are connected to each other in an annular shape to form a refrigerant circuit, and the heat exchanger on the use side and the heat exchanger on the heat source side are constituted by heat exchangers in a plurality of rows of two or more rows, and the heat exchanger on the use side during heating operation. Refrigerant flows from the downwind side row to the upwind side row in the heat exchanger, and the flow of the air and the refrigerant flow becomes a cross counter, and the heat source side heat exchanger moves from the downwind side row to the upwind side row during cooling operation. A heat pump type air conditioner in which the refrigerant flows and the flow of the air and the flow of the refrigerant become a cross counter. 3. A compressor, a four-way valve, a utilization side heat exchanger, a pressure reducer, a heat source side heat exchanger, wherein a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as the refrigerant. Are connected to each other in an annular shape to form a refrigerant circuit, and the heat exchanger on the use side and the heat exchanger on the heat source side are constituted by heat exchangers in a plurality of rows of two or more rows. Refrigerant flows from the leeward row to the windward row in the heat exchanger, and the flow of the air and the refrigerant flow becomes a cross counter, and the heating source side heat exchanger moves from the leeward row to the upwind row during heating operation. A heat pump type air conditioner in which the refrigerant flows and the flow of the air and the flow of the refrigerant become a cross counter. 4. A compressor, a four-way valve, a utilization side heat exchanger, a pressure reducer, a heat source side heat exchanger, wherein a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as the refrigerant. Are connected to each other in an annular shape to form a refrigerant circuit, and the heat exchanger on the use side and the heat exchanger on the heat source side are constituted by heat exchangers in a plurality of rows of two or more rows, and the heat exchanger on the use side during heating operation. Refrigerant flows from the leeward row to the windward row in the heat exchanger, and the flow of the air and the refrigerant flow becomes a cross counter, and the heating source side heat exchanger moves from the leeward row to the upwind row during heating operation. A heat pump type air conditioner in which the refrigerant flows and the flow of the air and the flow of the refrigerant become a cross counter.