WO2016169516A1

WO2016169516A1 - Heat pump-type refrigeration and heating device, refrigerant and heat exchanger

Info

Publication number: WO2016169516A1
Application number: PCT/CN2016/079999
Authority: WO
Inventors: 逸见好章
Original assignee: 格林雅思株式会社; 权基焕
Priority date: 2015-04-24
Filing date: 2016-04-22
Publication date: 2016-10-27
Also published as: CN106152605A

Abstract

A heat pump-type refrigeration and heating device (1), a refrigerant and a heat exchanger. The heat pump-type refrigeration and heating device (1) is provided with an additional condenser (8) which condenses the refrigerant during both refrigerating and heating operations. The cross-sectional area of the tubing through which flows the refrigerant of the additional condenser (8) is smaller than the cross-sectional area of the outlet tube (95), so as to prevent evaporation of the refrigerant of the additional condenser (8) during refrigerating and heating operations. The outlet tube (95) is connected to a compressor (2) and to a four-way valve (3). The refrigerant contains monochlorodifluoromethane or difluoromethane and 1, 1, 1, 2-tetrafluoroethane.

Description

Heat pump refrigeration and heating device, refrigerant and heat exchanger

Technical field

The present invention relates to a heat pump type cooling and heating device, a refrigerant, and a heat exchanger, and more particularly to a heat pump type cooling and heating device that selectively performs a cooling operation and a heating operation, and is used for heat pump type cooling and heating. The refrigerant of the device, and the heat exchanger for the heat pump type cooling and heating device.

Background technique

Conventionally, there are various known heat pump type cooling and heating apparatuses that selectively perform a cooling operation and a heating operation.

In the conventional heat pump type cooling and heating device, the refrigerant in a gaseous state compressed by the compressor during the cooling operation is condensed in the outdoor heat exchanger. Thereafter, the capillary on the indoor side decompresses the refrigerant from the outdoor heat exchanger. The refrigerant decompressed by the capillary on the indoor side evaporates in the heat exchanger in the room. Thereafter, the refrigerant evaporated in the indoor heat exchanger is returned to the compressor.

On the other hand, in the heating operation, the refrigerant in a gaseous state compressed by the compressor is condensed in the heat exchanger in the room. Thereafter, the capillary on the outdoor side decompresses the refrigerant from the heat exchanger in the chamber. The refrigerant decompressed by the capillary on the outdoor side evaporates in the outdoor heat exchanger. Thereafter, the refrigerant evaporated in the outdoor heat exchanger is returned to the compressor.

However, in the conventional heat pump type cooling and heating device, if the outdoor heat exchanger has a reduced coagulation ability during the cooling operation, it is impossible to change all the refrigerant from the compressor from the gas state to the liquid state. Therefore, in the conventional heat pump type cooling and heating device, there is a problem that the operating pressure increases and the amount of electric power consumed by the heat pump type cooling and heating device during operation increases.

In order to reduce the condensing ability during the cooling operation as described above, it is conceivable to add an outdoor heat exchanger in order to improve the condensing ability during the cooling operation.

However, in the heat pump type cooling and heating device that performs both the cooling operation and the heating operation, when the cooling operation is performed, the outdoor heat exchanger condenses the refrigerant and the indoor heat exchanger evaporates the refrigerant. Thus, when the heating operation is performed, the heat exchanger in the room condenses the refrigerant and the outdoor heat exchanger evaporates the refrigerant. Therefore, when only the outdoor heat exchanger is added, during the cooling operation and system Condensation and evaporation between heat runs will lose balance.

Further, in the conventional heat pump type cooling and heating device, monochlorodifluoromethane having a high ODP (Ozone Depletion Potential) and a global warming potential (GWP: Global Warning Potential) is used as a refrigerant ( R22), there are concerns about environmental damage.

Further, in the conventional heat pump type cooling and heating device, since R22 is used as the refrigerant, there is a problem in that the amount of electric power consumed by the heat pump type cooling and heating device during operation increases.

In recent years, reductions in carbon dioxide (CO ₂ ) emissions have been demanded not only in several countries but globally. Also, it is required to improve the energy efficiency ratio (EER) and the coefficient of performance (COP: Coefficient Of Performance).

Summary of the invention

The present invention has been made in view of the above problems, and it is an object of the present invention to provide a balance between coagulation and evaporation while maintaining a balance between condensation operation and heating operation, and to improve the coagulation ability and to reduce the amount of electricity consumed during operation. Heat pump refrigeration and heating devices, refrigerants and heat exchangers.

A heat pump type cooling and heating device according to the present invention includes a compressor, a four-way valve, a first heat exchanger, a second heat exchanger, a first pressure reducing mechanism, a second pressure reducing mechanism, and an additional condenser. The compressor compresses the refrigerant. The four-way valve switches the circulation direction of the refrigerant cycle during the cooling operation and the heating operation. The first heat exchanger condenses the refrigerant during the cooling operation and evaporates the refrigerant during the heating operation. The second heat exchanger condenses the refrigerant during the heating operation to evaporate the refrigerant during the cooling operation. The first pressure reducing mechanism decompresses the refrigerant during the cooling operation. The second pressure reducing mechanism decompresses the refrigerant during the heating operation. The additional condenser condenses the refrigerant. During the cooling operation, the four-way valve switches the circulation direction such that the refrigerant compressed by the compressor and flows from the compressor into the four-way valve via a discharge pipe is according to the first The heat exchanger, the additional condenser, the first pressure reducing mechanism, and the second heat exchanger sequentially flow and return to the compressor. The discharge pipe connects the compressor and the four-way valve. The first heat exchanger condenses the refrigerant compressed by the compressor. The additional condenser further condenses the refrigerant from the first heat exchanger. The first pressure reducing mechanism pair is caused by the first heat exchange The refrigerant and the refrigerant condensed by the additional condenser are decompressed. The second heat exchanger evaporates the refrigerant decompressed by the first pressure reducing mechanism. During the heating operation, the four-way valve switches the circulation direction to cause the refrigerant compressed by the compressor and flows from the compressor into the four-way valve via the discharge pipe. The second heat exchanger, the additional condenser, the second pressure reducing mechanism, and the first heat exchanger sequentially flow and return to the compressor. The second heat exchanger condenses the refrigerant compressed by the compressor. The additional condenser further condenses the refrigerant from the second heat exchanger. The second pressure reducing mechanism decompresses the refrigerant condensed by the second heat exchanger and the additional condenser. The first heat exchanger evaporates the refrigerant decompressed by the second pressure reducing mechanism. a cross-sectional area of the pipeline through which the refrigerant flows in the additional condenser is smaller than a cross-sectional area of the exhaust pipe, so that the additional condenser prevents the said during both the cooling operation and the heating operation The refrigerant evaporates. The refrigerant contains monochlorodifluoromethane or difluoromethane, and 1,1,1,2-tetrafluoroethane.

In the heat pump type cooling and heating device, preferably, the refrigerant contains difluoromethane and 1,1,1,2-tetrafluoroethane, and 1,1,1,2-tetrafluoroethane and two The weight ratio of fluoromethane is 2.33 or more and 5.67 or less.

In the heat pump type cooling and heating device, preferably, the refrigerant contains chlorodifluoromethane and 1,1,1,2-tetrafluoroethane, and 1,1,1,2-tetrafluoroethane and The weight ratio of monochlorodifluoromethane is 0.67 or more and 1.86 or less.

In the heat pump type cooling and heating device, it is preferable that a cross-sectional area of the duct in which the condenser is added is 45% or less of a cross-sectional area of the discharge pipe.

In the heat pump type cooling and heating device, it is preferable that the duct in which the condenser is added is formed with a plurality of cavities arranged in parallel.

In the heat pump type cooling and heating device, it is preferable that the additional condenser is disposed such that it is located on a side where the first heat exchanger takes in air.

The refrigerant of the present invention is used in the heat pump type cooling and heating device, and contains chlorodifluoromethane or difluoromethane, and 1,1,1,2-tetrafluoroethane.

The refrigerant preferably contains difluoromethane and 1,1,1,2-tetrafluoroethane, and the weight ratio of 1,1,1,2-tetrafluoroethane to difluoromethane is 2.33 or more and 5.67. the following.

The refrigerant preferably contains chlorodifluoromethane and 1,1,1,2-tetrafluoroethane, and 1,1,1,2- The weight ratio of tetrafluoroethane to monochlorodifluoromethane is 0.67 or more and 1.86 or less.

The heat exchanger of the present invention is used as the additional condenser in the heat pump type cooling and heating device. a cross-sectional area of the pipe through which the refrigerant flows in the heat exchanger is smaller than a cross-sectional area of the discharge pipe, so that the heat exchanger prevents the said heat exchanger from both the cooling operation and the heating operation The refrigerant evaporates.

According to the present invention, it is possible to improve the coagulation ability while maintaining the balance between condensation and evaporation between the cooling operation and the heating operation, and it is possible to reduce the amount of electric power consumed during operation in the heat pump type refrigerating and heating device. Also, according to the present invention, it is possible to reduce the amount of CO2 emissions and to improve EER and COP.

DRAWINGS

Fig. 1 is a schematic view showing the operation of a heat pump type cooling and heating device according to an embodiment during a cooling operation.

FIG. 2 is a schematic view showing the operation of the heat pump type cooling and heating device according to the embodiment during the heating operation.

Fig. 3 is a cross-sectional view showing a main part of an additional condenser according to an embodiment.

4 is a schematic view for explaining the installation of an additional condenser on the first heat exchanger according to the embodiment.

[Symbol Description]

1-Heat pump type cooling and heating device 2-compressor 3-four-way valve 4-first heat exchanger 5-second heat exchanger 61-first capillary (first pressure reducing mechanism) 71-second capillary (first Two decompression mechanism) 8-additional condenser 81-pipe 811-cavity

detailed description

Hereinafter, the heat pump type cooling and heating device according to the embodiment will be described in further detail with reference to the drawings.

As shown in FIG. 1 , the heat pump type cooling and heating device 1 according to the present embodiment includes a compressor 2 , a four-way valve 3 , a first heat exchanger 4 , a second heat exchanger 5 , and a first pressure reducing unit 6 . The second decompressing unit 7 and the condenser 8 are additionally provided. In the heat pump type cooling and heating device 1, the compressor 2, the four-way valve 3, and the The heat exchanger 4 and the second decompressing unit 7 are integrated as one unit of the outdoor unit 11 and are installed outdoors. On the other hand, the second heat exchanger 5 and the first decompressing unit 6 are integrated into the indoor unit 12 as one device.

The refrigerant used in the heat pump type cooling and heating device 1 according to the present embodiment contains chlorodifluoromethane (R22, hereinafter referred to as "R22") or difluoromethane (R32, hereinafter referred to as "R32"), and 1,1,1,2-tetrafluoroethane (R134a, hereinafter referred to as "R134a"). In other words, in the present embodiment, a mixed refrigerant of R22 and R134a or a mixed refrigerant of R32 and R134a is used as the refrigerant.

The compressor 2 compresses the refrigerant. Specifically, the compressor 2 sucks a refrigerant (gas refrigerant) in a gaseous state from the four-way valve 3 via the intake pipe 96, compresses the sucked refrigerant, and compresses the compressed refrigerant via the discharge pipe 95. It is discharged to the four-way valve 3. According to the above configuration, the compressor 2 has not only a function of compressing the refrigerant but also a function of circulating the refrigerant. The refrigerant compressed by the compressor 2 is a refrigerant that is in a high temperature and high pressure and in a gaseous state. The discharge pipe 95 is a pipe for flowing the refrigerant from the compressor 2 to the four-way valve 3. The intake pipe 96 is a pipe for flowing the refrigerant from the four-way valve 3 to the compressor 2.

The four-way valve 3 switches the circulation direction of the refrigerant circulation during the cooling operation and the heating operation. Specifically, during the cooling operation, the four-way valve 3 circulates the refrigerant in the order of the compressor 2, the first heat exchanger 4, the additional condenser 8, and the second heat exchanger 5. On the other hand, during the heating operation, the four-way valve 3 circulates the refrigerant in the order of the compressor 2, the second heat exchanger 5, the additional condenser 8, and the first heat exchanger 4.

The first heat exchanger 4 condenses the refrigerant during the cooling operation and evaporates the refrigerant during the heating operation. That is, the first heat exchanger 4 operates as a condenser during the cooling operation and as an evaporator during the heating operation. Specifically, the first heat exchanger 4 is connected to the first duct 91 that connects the four-way valve 3 and the first heat exchanger 4. That is, the first heat exchanger 4 is connected to the four-way valve 3 through the first duct 91. Further, the first heat exchanger 4 is connected to the second decompressing portion 7. The first heat exchanger 4 is made of a material having a high thermal conductivity such as copper or aluminum. Further, the first heat exchanger 4 constitutes a part of the flow path through which the refrigerant flows, and is configured to exchange heat between the refrigerant flowing into the first heat exchanger 4 and the air around the first heat exchanger 4. Specifically, in the cooling operation, the first heat exchanger 4 causes the refrigerant in a gaseous state to flow from the compressor 2 via the four-way valve 3 and the first pipe 91. Condensation. Thereby, the refrigerant changes from the gas state to the liquid state, and the volume of the refrigerant becomes small. However, for example, if the condensing ability of the first heat exchanger 4 is lowered due to clogging of the filter mesh or the like, the refrigerant cannot all become in a liquid state and a part of the refrigerant is still in a gas state. That is, the refrigerant in a gaseous state among the refrigerant output from the first heat exchanger 4 is mixed with the refrigerant in a liquid state. On the other hand, during the heating operation, the first heat exchanger 4 evaporates the refrigerant that has flowed in through the second capillary 71 to be described later. The refrigerant in a gaseous state which is evaporated by the first heat exchanger 4 flows into the compressor 2 via the first duct 91 and the four-way valve 3 and the intake pipe 96.

The second heat exchanger 5 condenses the refrigerant during the heating operation and evaporates the refrigerant during the cooling operation. That is, the second heat exchanger 5 operates as a condenser during the heating operation and as an evaporator during the cooling operation. Specifically, the second heat exchanger 5 is connected to the second duct 92 that connects the four-way valve 3 and the second heat exchanger 5. That is, the second heat exchanger 5 is connected to the four-way valve 3 through the second duct 92. Further, the second heat exchanger 5 is connected to the first decompressing portion 6. The second heat exchanger 5 is made of a material having a high thermal conductivity such as copper or aluminum. Further, the second heat exchanger 5 constitutes a part of the flow path through which the refrigerant flows, and is configured to exchange heat between the refrigerant flowing into the second heat exchanger 5 and the air around the second heat exchanger 5. Specifically, during the heating operation, the second heat exchanger 5 condenses the refrigerant in a gaseous state that flows from the compressor 2 through the four-way valve 3 and the second duct 92. Thereby, the refrigerant changes from the gas state to the liquid state, and the volume of the refrigerant becomes small. However, for example, if the condensation ability of the second heat exchanger 5 is lowered due to clogging of the filter mesh or the like, the refrigerant cannot all become in a liquid state and a part of the refrigerant is still in a gas state. That is, the refrigerant in a gaseous state among the refrigerant output from the second heat exchanger 5 is mixed with the refrigerant in a liquid state. On the other hand, during the cooling operation, the second heat exchanger 5 evaporates the refrigerant that has flowed in through the first capillary 61 to be described later. The refrigerant in a gaseous state which is evaporated by the second heat exchanger 5 flows into the compressor 2 via the second duct 92 and the four-way valve 3 and the intake pipe 96.

The first pressure reducing portion 6 includes a first capillary 61 (first pressure reducing mechanism) and a first check valve 62.

The first capillary 61 decompresses the refrigerant during the cooling operation. Specifically, the first capillary 61 is connected to the inlet side of the refrigerant during the cooling operation in the second heat exchanger 5 . Further, during the heating operation, the first capillary 61 decompresses and expands the refrigerant from the additional condenser 8.

Further, in the present embodiment, the first capillary 61 is used as the first pressure reducing mechanism. However, the first pressure reducing mechanism is not limited to the first capillary 61 as long as the refrigerant is decompressed during the cooling operation. As the first pressure reducing mechanism, an electronic expansion valve or the like may be used instead of the first capillary 61.

The first check valve 62 passes the refrigerant condensed by the second heat exchanger 5 during the heating operation. Specifically, the first check valve 62 is connected in parallel with the first capillary 61 between the second heat exchanger 5 and the fourth duct 94. Further, the first check valve 62 is opened during the heating operation. The resistance first flow check valve 62 when the refrigerant flows is smaller than the first capillary 61, so that the refrigerant from the second heat exchanger 5 flows through the first check valve 62. On the other hand, the first check valve 62 is closed during the cooling operation. Further, as the member through which the refrigerant that has been condensed by the second heat exchanger 5 during the heating operation flows, an on-off valve such as a solenoid valve may be used instead of the first check valve 62.

The second pressure reducing portion 7 includes a second capillary 71 (second pressure reducing mechanism) and a second check valve 72.

The second capillary 71 decompresses the refrigerant during the heating operation. Specifically, the second capillary 71 is connected to the inlet side of the refrigerant at the time of the heating operation in the first heat exchanger 4. Further, during the heating operation, the second capillary 71 decompresses and expands the refrigerant from the additional condenser 8.

Further, in the present embodiment, the second capillary 71 is used as the second pressurizing means. However, the second pressure reducing mechanism is not limited to the second capillary 71 as long as the refrigerant is decompressed during the cooling operation. As the second pressure reducing mechanism, an electronic expansion valve or the like may be used instead of the second capillary 71.

The second check valve 72 passes the refrigerant condensed by the first heat exchanger 4 during the cooling operation. Specifically, the second check valve 72 is connected in parallel with the second capillary 71 between the first heat exchanger 4 and the third duct 93. Further, the second check valve 72 is opened during the cooling operation. The resistance of the refrigerant flowing through the second check valve 72 is smaller than that of the second capillary 71, so that the refrigerant from the first heat exchanger 4 flows through the second check valve 72. On the other hand, the second check valve 72 is closed during the heating operation. In addition, as the member through which the refrigerant that has condensed by the first heat exchanger 4 during the cooling operation flows, an on-off valve such as a solenoid valve may be used instead of the second check valve 72.

An additional condenser 8 is connected between the first heat exchanger 4 and the second heat exchanger 5 to condense the refrigerant. The additional condenser 8 condenses the refrigerant during both the cooling operation and the heating operation. That is, the additional condenser 8 is operated as a condenser during both the cooling operation and the heating operation. Specifically, add cold The condenser 8 is connected between the first heat exchanger 4 and the second heat exchanger 5 through the third duct 93 to the second decompressing portion 7, and is connected to the first decompressing portion 6 through the fourth duct 94. The duct (heat exchange portion) 81 (see FIG. 3) in which the condenser 8 is added is made of a material having a high thermal conductivity such as copper or aluminum. The duct 81 constitutes a part of the flow path through which the refrigerant flows, and is configured to exchange heat between the refrigerant flowing through the duct 81 and the air around the duct 81.

The cross-sectional area of the pipe 81 through which the refrigerant in the condenser 8 flows is smaller than the cross-sectional area of the discharge pipe 95, so that the additional condenser 8 prevents the refrigerant from evaporating during both the cooling operation and the heating operation. The cross-sectional area of the duct 81 in which the condenser 8 is added is set within a range in which the refrigerant does not evaporate and the resistance value of the flow of the refrigerant does not increase. The cross-sectional area of the duct 81 in which the condenser 8 is added refers to the cross-sectional area of the cavity through which the refrigerant flows in the duct 81. The cross-sectional area of the discharge pipe 95 is the cross-sectional area of the cavity through which the refrigerant in the discharge pipe 95 flows. Here, the case of preventing evaporation of the refrigerant means not only the case where all the refrigerants are not evaporated at all, but also the case where almost all of the refrigerant does not evaporate.

When the refrigerant flowing into the additional condenser 8 functioning as a condenser is in a state in which the gas and the liquid are mixed together, the refrigerant in a state in which the gas and the liquid are mixed together is condensed into a liquid state by the additional condenser 8. On the other hand, when the refrigerant flowing into the additional condenser 8 is in a liquid state, the refrigerant in the liquid state does not evaporate and passes through the condenser 8 in the original liquid state. As described above, the refrigerant in which the gas and the liquid are mixed together is changed to the refrigerant in the liquid state by the addition of the condenser 8.

Thereby, even if the refrigerant in a state in which the gas and the liquid are mixed flows into the additional condenser 8, the refrigerant can be effectively brought into a liquid state in the duct 81 in which the condenser 8 is added. That is, by setting the cross-sectional area of the duct 81 to which the condenser 8 is added to be smaller than the cross-sectional area of the discharge pipe 95, evaporation of the refrigerant is suppressed, and since the heat-dissipating refrigerant is further condensed, the refrigerant flowing from the additional condenser 8 is discharged. All become liquid.

Further, the cross-sectional area of the discharge pipe 95 is substantially the same as the cross-sectional area of the first pipe 91. Therefore, the cross-sectional area of the duct 81 to which the condenser 8 is added can be considered to be smaller than the cross-sectional area of the first duct 91. The cross-sectional area of the first duct 91 refers to the cross-sectional area of the cavity through which the refrigerant flows in the first duct 91. Also, the cross-sectional area of the first duct 91 is substantially the same as the cross-sectional area of the duct through which the refrigerant in the first heat exchanger 4 flows. Therefore, the cross-sectional area of the pipe 81 to which the condenser 8 is added can be considered to be smaller than that of the first heat exchanger 4 The cross-sectional area of the pipe. The cross-sectional area of the pipe of the first heat exchanger 4 refers to the cross-sectional area of the cavity through which the refrigerant in the pipe of the first heat exchanger 4 flows. When the first heat exchanger 4 has a plurality of pipes, the cross-sectional area of the pipes of the first heat exchanger 4 is the sum of the cross-sectional areas of all the pipes.

Further, the cross-sectional area of the discharge pipe 95 is substantially the same as the cross-sectional area of the second pipe 92. Therefore, the cross-sectional area of the duct 81 to which the condenser 8 is added can be considered to be smaller than the cross-sectional area of the second duct 92. The cross-sectional area of the second duct 92 refers to the cross-sectional area of the cavity through which the refrigerant flows in the second duct 92. Also, the cross-sectional area of the second duct 92 is substantially the same as the cross-sectional area of the duct through which the refrigerant flows in the second heat exchanger 5. Therefore, the cross-sectional area of the duct 81 to which the condenser 8 is added can be considered to be smaller than the cross-sectional area of the duct of the second heat exchanger 5. The cross-sectional area of the pipe of the second heat exchanger 5 refers to the cross-sectional area of the cavity through which the refrigerant in the pipe of the second heat exchanger 5 flows. When the second heat exchanger 5 has a plurality of pipes, the cross-sectional area of the pipes of the second heat exchanger 5 is the sum of the cross-sectional areas of all the pipes.

However, in order to more effectively change the state in which the refrigerant is mixed from the gas and the liquid to the liquid state, that is, in order to improve the heat exchange efficiency, it is preferable that the cross-sectional area of the pipe 81 in the additional condenser 8 is set as the discharge pipe. The cross-sectional area of 95 is less than 45%. More preferably, the cross-sectional area of the duct 81 in the additional condenser 8 is set to be 40% or less of the cross-sectional area of the discharge pipe 95. More preferably, the cross-sectional area of the duct 81 in the additional condenser 8 is set to be 36% or less of the cross-sectional area of the discharge pipe 95.

When the cross section of the duct 81 in which the condenser 8 is added and the cross section of the discharge pipe 95 are both circular, it is preferable that the inner diameter of the duct 81 in which the condenser 8 is added is 67.1% or less of the inner diameter of the discharge pipe 95. More preferably, the inner diameter of the duct 81 in which the condenser 8 is added is 63.2% or less of the inner diameter of the discharge pipe 95. More preferably, the inner diameter of the duct 81 in which the condenser 8 is added is 60% or less of the inner diameter of the discharge pipe 95.

Further, when the cross-sectional area of the pipe 81 to which the condenser 8 is added is not constant in the pipe (i.e., changes in the pipe direction), at least the minimum cross-sectional area satisfies the above conditions.

The lower limit of the cross-sectional area (or inner diameter) of the pipe 81 in which the condenser 8 is added may be set such that the resistance of the refrigerant flowing through the pipe 81 does not exceed the extent that the heat pump type cooling and heating device 1 cannot operate. For example, the cross-sectional area of the duct 81 in which the condenser 8 is added is 10% or more of the cross-sectional area of the discharge pipe 95. When the cross section of the pipe 81 in which the condenser 8 is added and the cross section of the discharge pipe 95 are both circular, the inner diameter of the pipe 81 in which the condenser 8 is added is 31.2% or more of the inner diameter of the discharge pipe 95.

However, as shown in FIG. 3, the duct 81 of the additional condenser 8 of the present embodiment is formed with Multiple holes 811 set by the column. That is, the additional condenser 8 of the present embodiment is a heat exchanger in which a refrigerant flows through a plurality of cavities 811 formed in parallel. When a plurality of cavities 811 are formed in the duct 81 in this manner, the cross-sectional area of the duct 81 in the additional condenser 8 is the sum of the cross-sectional areas of all the cavities 811. Further, the additional condenser 8 may include a plurality of pipes each having at least one cavity formed therein.

As shown in FIG. 4, the additional condenser 8 of the present embodiment is disposed such that it is located on the side where the first heat exchanger 4 takes in air. In other words, the additional condenser 8 of the present embodiment is attached to the outdoor unit 11 so as to be attached to the side of the intake air of the first heat exchanger 4. Air is taken in by the blower fan 111 in the outdoor unit 11 to pass through the first heat exchanger 4. Specifically, as shown by an arrow A3 in FIG. 4, air passes through the periphery of the duct 81 of the condenser 8 and then passes through the circumference of the duct of the first heat exchanger 4.

Further, since the additional condenser 8 is provided on the air suction side of the first heat exchanger 4, the installation of the additional condenser 8 can be made simple and easy, and it is not necessary to provide the blower provided for the first heat exchanger 4. Another fan other than 111.

Further, for example, even when the outdoor temperature is low in winter or the like, it is possible to suppress the frost from adhering to the first heat exchanger 4 that operates as an evaporator during the heating operation.

Next, a performance test of the heat pump type cooling and heating device 1 according to the present embodiment will be described. Here, the performance of the heat pump type cooling and heating device 1 in which the condenser 8 is added to the cooling and heating machine (model: RAS100H-R22) of Hitachi, Ltd. was tested.

First, in the cooling operation, a performance test in the case where the outdoor temperature is 35 ° C and the indoor temperature is 30 ° C will be described. The first embodiment is a heat pump type cooling and heating device 1 including a mixed refrigerant in which a condenser 8 is added and R22 and R134a are used as a refrigerant. That is, the first embodiment is the heat pump type cooling and heating device 1 of the present embodiment. On the other hand, Comparative Example 1 and Comparative Example 2 are heat pump type cooling and heating apparatuses using R22 as a refrigerant. Comparative Example 1 is a heat pump type cooling and heating device that does not include an additional condenser, and Comparative Example 2 is a heat pump type cooling and heating device including a condenser.

The items measured in the performance test are the suction temperature T1, the blowing temperature T2, and the amount of electricity. As a performance evaluation index, the temperature difference Δt1 is calculated from the measured suction temperature T1 and the blow-out temperature T2, and the power consumption reduction rate is calculated from the measured power amount. The suction temperature T1 is the temperature of the air sucked into the indoor unit in which the second heat exchanger is housed. The blowing temperature T2 is the temperature of the air blown from the indoor unit. Temperature The difference Δt1 is the absolute value of the difference between the suction temperature and the blow-out temperature. The amount of electricity is the amount of electricity consumed by the heat pump cooling and heating device during operation. The power consumption reduction rate is a value based on the electric quantity of Comparative Example 1. Specifically, the power consumption reduction rate is a ratio of the power amount reduced in Comparative Example 1 to the power amount in Comparative Example 1.

As shown in Table 1, in the first embodiment, compared with the comparative example 1 and the comparative example 2, the rate of reduction of the electric quantity was the largest while maintaining the temperature difference Δt1. That is, in the first embodiment, the amount of electric power can be reduced without lowering the performance of the cooling operation.

[Table 1]

Next, the performance test when changing the outdoor temperature will be described in the cooling operation and the heating operation, respectively. The performance was tested at outdoor temperatures of 40 ° C, 35 ° C, and 26 ° C during cooling operation and at 7 ° C, 2 ° C, and -3 ° C during heating operation. In addition, the indoor temperature during cooling operation was 30 °C. The indoor temperature during heating operation is 10 °C.

As shown in Table 2, in the case of the outdoor temperature of 40 ° C, 35 ° C, and 26 ° C during the cooling operation, the reduction rate of the electric quantity of Example 1 was higher than that of Comparative Example 1 and Comparative Example 2 The rate of power reduction. Further, in the heating operation, when the outdoor temperature was any of 7 ° C, 2 ° C, and -3 ° C, the reduction rate of the electric quantity of Example 1 was also higher than that of Comparative Example 1 and Comparative Example 2 The rate of power reduction.

[Table 2]

Next, the refrigerant used in the heat pump type cooling and heating device 1 according to the present embodiment will be described.

First, a case where a mixed refrigerant in which monochlorodifluoromethane (R22) and 1,1,1,2-tetrafluoroethane (R134a) are mixed is used as an example of the refrigerant of the present embodiment will be described. .

The performance when changing the weight ratio of R134a to R22 was tested. Specifically, the weight ratio of R134a to R22 is 0.43 (R22 is 70% by weight, R134a is 30% by weight), 0.54 (R22 is 65% by weight, R134a is 35% by weight), and 0.67 (R22 is 60% by weight). The performance when R134a was 40% by weight was tested. Further, the performance when the weight ratio of R134a to R22 was 0.82 (R22 was 55 wt%, R134a was 45 wt%), and 1.00 (R22 was 50 wt%, and R134a was 50 wt%) was tested. Further, the performance when the weight ratio of R134a to R22 was 1.22 (45% by weight of R22, 55% by weight of R134a), 1.50 (40% by weight of R22, and 60% by weight of R134a) was tested. Further, the performance when the weight ratio of R134a to R22 was 1.86 (35 wt% for R22 and 65 wt% for R134a) and 2.33 (30 wt% for R22 and 70 wt% for R134a) were tested.

The items measured in the performance test include a current value I1, a discharge pressure P1, a temperature of air taken into the indoor unit in which the second heat exchanger is housed, and a temperature of air blown from the indoor unit. As a performance evaluation index, the temperature difference Δt1 is calculated from the above two temperatures measured. The current value I1 is a value of the current required to drive the compressor. The temperature difference Δt1 is an absolute value of a difference between the temperature of the air taken into the indoor unit in which the second heat exchanger is housed and the temperature of the air blown from the indoor unit. The discharge pressure P1 is the pressure of the refrigerant discharged from the compressor.

Table 3 shows the results of the performance test when the weight ratio of R134a to R22 was changed.

[table 3]

As shown in Table 3, the larger the weight ratio of R134a to R22 is, the smaller the current value I1 is (the discharge pressure P1 becomes lower), so that the amount of electric power consumed by the heat pump type cooling and heating device during operation becomes smaller. Therefore, it is preferred that the weight ratio of R134a to R22 is 0.67 or more. More preferably, the weight ratio of R134a to R22 is 0.82 or more. More preferably, the weight ratio of R134a to R22 is 1.00 or more.

On the other hand, as the weight ratio of R134a to R22 becomes larger, the temperature difference Δt1 gradually becomes smaller. Therefore, it is preferable that the weight ratio of R134a to R22 is 1.86 or less. More preferably, the weight ratio of R134a to R22 is 1.50 or less. More preferably, the weight ratio of R134a to R22 is 1.22 or less.

As described above, it is preferable that the refrigerant used in the present embodiment contains R22 and R134a, and the weight ratio of R134a to R22 is 0.67 or more and 1.86 or less. That is, in the present embodiment, it is preferable to use a mixed refrigerant in which the weight ratio of R134a to R22 is 0.67 or more and 1.86 or less.

Next, a case where a mixed refrigerant in which difluoromethane (R32) and 1,1,1,2-tetrafluoroethane (R134a) are mixed is used as the refrigerant of the present embodiment will be described.

The performance when changing the weight ratio of R134a to R32 was tested. Specifically, the performance when the weight ratio of R134a to R32 was 1.86 (35 wt% for R32, 65 wt% for R134a) and 2.33 (30 wt% for R32 and 70 wt% for R134a) were tested. Further, the weight ratio of R134a to R32 is 3.00 (R32 is 25% by weight, R134a is 75% by weight), The performance at 4.00 (20% by weight of R32 and 80% by weight of R134a) was tested. Further, the performance when the weight ratio of R134a to R32 was 5.67 (15% by weight of R32, 85% by weight of R134a), 9.00 (10% by weight of R32, and 90% by weight of R134a) was tested. Further, the performance when R134a alone (0% by weight of R32 and 100% by weight of R134a) was tested.

Table 4 shows the results of the performance test when the weight ratio of R134a to R32 was changed.

[Table 4]

As shown in Table 4, the larger the weight ratio of R134a to R32 is, the smaller the current value I1 is (the discharge pressure P1 becomes lower), and therefore the amount of electric power consumed by the heat pump type cooling and heating device during operation becomes smaller. Therefore, it is preferable that the weight ratio of R134a to R32 is 2.33 or more. More preferably, the weight ratio of R134a to R32 is 3.00 or more.

On the other hand, as the weight ratio of R134a to R32 becomes larger, the temperature difference Δt1 gradually becomes smaller. Therefore, it is preferable that the weight ratio of R134a to R32 is 5.67 or less. More preferably, R134a and R32 The weight ratio is 4.00 or less.

As described above, it is preferable that the refrigerant used in the present embodiment contains R32 and R134a, and the weight ratio of R134a to R32 is 2.33 or more and 5.67 or less. That is, in the present embodiment, it is preferable to use a mixed refrigerant in which the weight ratio of R134a to R32 is 2.33 or more and 5.67 or less.

Next, the operation of the heat pump type cooling and heating device according to the present embodiment and the flow of the refrigerant in the heat pump type cooling and heating device will be described with reference to Fig. 1 .

First, the case of the cooling operation will be described. The four-way valve 3 switches the circulation direction so that the refrigerant compressed by the compressor 2 flows from the compressor 2 in the order of the first heat exchanger 4, the additional condenser 8, the first capillary 61, and the second heat exchanger 5, and Return to compressor 2.

The compressor 2 compresses the refrigerant. The refrigerant in a gaseous state compressed by the compressor 2 is discharged from the compressor 2 and flows into the first heat exchanger 4 through the first pipe 91 through the four-way valve 3. The first heat exchanger 4 condenses the refrigerant compressed by the compressor 2 and flowing in through the first duct 91. The refrigerant flows from the first heat exchanger 4 to the additional condenser 8 via the second check valve 72 and the third conduit 93. Thereafter, a condenser 8 is added to further condense the refrigerant from the first heat exchanger 4. The condenser 8 is additionally provided to condense the refrigerant in a gaseous state in which the first heat exchanger 4 does not become in a liquid state. The refrigerant in a liquid state does not evaporate and passes through the condenser 8 in the original liquid state. Thereafter, the first capillary 61 depressurizes the refrigerant in a liquid state condensed by the first heat exchanger 4 and the additional condenser 8. The second heat exchanger 5 evaporates the refrigerant flowing through the first capillary 61. The refrigerant evaporated by the second heat exchanger 5 flows into the compressor 2 via the second duct 92, the four-way valve 3, and the intake pipe 96. During the cooling operation, the refrigerant flows in the direction indicated by the arrow A1 of Fig. 1 .

Next, the case of the heating operation will be described with reference to Fig. 2 . The four-way valve 3 switches the circulation direction so that the refrigerant compressed by the compressor 2 flows from the compressor 2 in the order of the second heat exchanger 5, the additional condenser 8, the second capillary 71, and the first heat exchanger 4, and Return to compressor 2.

The compressor 2 compresses the refrigerant. The refrigerant in a gaseous state compressed by the compressor 2 is discharged from the compressor 2 and flows into the second heat exchanger 5 through the second pipe 92 through the four-way valve 3. The second heat exchanger 5 condenses the refrigerant compressed by the compressor 2 and flowing in through the second duct 92. The refrigerant flows from the second heat exchanger 5 to the additional condenser 8 via the first check valve 62 and the fourth duct 94. Thereafter, a condenser 8 is added to further condense the refrigerant from the second heat exchanger 5. Add condensation The burner 8 condenses the refrigerant in a state in which the gas and the liquid are mixed together. The refrigerant in a liquid state does not evaporate and passes through the condenser 8 in the original liquid state. Thereafter, the second capillary 71 depressurizes the refrigerant in a liquid state condensed by the second heat exchanger 5 and the additional condenser 8. The first heat exchanger 4 evaporates the refrigerant flowing through the second capillary 71. The refrigerant evaporated by the first heat exchanger 4 flows into the compressor 2 via the first duct 91, the four-way valve 3, and the intake pipe 96. During the heating operation, the refrigerant flows in the direction indicated by the arrow A2 of Fig. 2 .

The heat pump type cooling and heating device 1 according to the above-described embodiment includes an additional condenser 8 that condenses the refrigerant during both the cooling operation and the heating operation. Therefore, in the heat pump type cooling and heating device 1 according to the present embodiment, for example, even if the condensation ability of the first heat exchanger 4 and the second heat exchanger 5 is lowered due to clogging of the filter mesh or the like, It is possible to improve the coagulation ability while maintaining the balance between condensation and evaporation between the cooling operation and the heating operation. As a result, in the heat pump type cooling and heating device 1 according to the present embodiment, the amount of electric power consumed during operation can be reduced.

Further, in the heat pump type cooling and heating device 1 according to the present embodiment, the refrigerant contains chlorodifluoromethane (R22) or difluoromethane (R32), and 1,1,1,2-tetrafluoroethane. Alkane (R134a). Therefore, the heat pump type cooling and heating device 1 according to the present embodiment can reduce the ozone depletion potential (ODP) and the global warming potential (GWP: Global Warning) compared with the case of using a single refrigerant of R22. Potential). Further, the heat pump type cooling and heating device 1 according to the present embodiment can reduce the amount of electric power consumed during the operation of the heat pump type cooling and heating device 1 as compared with the case of using a single refrigerant of R22.

Further, in the heat pump type cooling and heating device 1 according to the present embodiment, the amount of CO ₂ discharged can be reduced, and the energy efficiency ratio (EER: Energy Efficiency Ratio) and the coefficient of performance (COP: Coefficient of Performance) can be improved.

However, when a near-azeotropic mixed refrigerant (R410) composed of difluoromethane (R32) and pentafluoroethane (R125) is used, an expensive inverter-controlled compressor is required. On the other hand, when a refrigerant containing chlorodifluoromethane (R22) or difluoromethane (R32) and 1,1,1,2-tetrafluoroethane (R134a) is used as shown in the present embodiment, A compressor that does not require inverter control. Therefore, the heat pump type cooling and heating device 1 according to the present embodiment includes a compressor that does not require inverter control and a heat pump type that uses a near-azeotropic refrigerant (R410), even if the condenser 8 is provided. Cooling and heating Compared to the device, the cost can be reduced. Specifically, when a new heat pump type cooling and heating device is purchased, it is not necessary to purchase a high-priced compressor (inverter-controlled compressor), so that the initial cost of the user can be reduced. Further, when the heat pump type cooling and heating device having the refrigerant R22 is modified, it is not necessary to increase the expensive compressor (inverter controlled compressor), so that the initial cost of the user can be reduced. Further, for the manufacturer, the manufacturing cost can be reduced.

In the heat pump type cooling and heating device 1 according to the present embodiment, the weight ratio of 1,1,1,2-tetrafluoroethane (R134a) to difluoromethane (R32) is 2.33 or more and 5.67 or less. Thus, in the heat pump type cooling and heating device 1 according to the present embodiment, it is possible to sufficiently ensure the temperature difference between the intake air temperature and the discharge temperature in the room while reducing the ozone depletion potential and the global warming potential.

Further, in the heat pump type cooling and heating device 1 according to the present embodiment, a mixed refrigerant of difluoromethane (R32) and 1,1,1,2-tetrafluoroethane (R134a) is used, and thus The flammability can be reduced compared to the case of using a single refrigerant of R32.

In the heat pump type cooling and heating device 1 according to the present embodiment, the weight ratio of 1,1,1,2-tetrafluoroethane (R134a) to monochlorodifluoromethane (R22) is 0.67 or more and 1.86 or less. Thus, in the heat pump type cooling and heating device 1 according to the present embodiment, it is possible to sufficiently ensure the temperature difference between the intake air temperature and the discharge temperature in the room while reducing the ozone depletion potential and the global warming potential.

In the heat pump type cooling and heating device 1 according to the present embodiment, the cross-sectional area of the duct 81 in the additional condenser 8 is 45% or less of the cross-sectional area of the discharge pipe 95. Therefore, in the heat pump type cooling and heating device 1 according to the present embodiment, for example, when the condensation ability of the first heat exchanger 4 and the second heat exchanger 5 is lowered due to clogging of the filter mesh or the like, Effectively improve the coagulation ability.

In the heat pump type cooling and heating device 1 according to the present embodiment, the duct 81 through which the condenser 8 is added as a refrigerant flows includes a plurality of cavities 811 which are arranged in parallel. Thus, in the heat pump type cooling and heating device 1 according to the present embodiment, the area of heat exchange can be increased in the additional condenser 8, so that the coagulation ability can be improved.

In the heat pump type cooling and heating device 1 according to the present embodiment, the additional condenser 8 is provided so as to be located on the side where the first heat exchanger 4 takes in air. Therefore, in the heat pump type cooling and heating device 1 according to the present embodiment, the hot air after the heat exchange by the additional condenser 8 is added from the cold. The condenser 8 is blown onto the first heat exchanger 4. As a result, in the heat pump type cooling and heating device 1 according to the present embodiment, for example, even when the outdoor temperature is low in winter or the like, it is possible to suppress the frost from adhering to the first heat exchanger that operates as an evaporator during the heating operation. 4 on.

Further, in the present embodiment, a case where an additional condenser 8 is connected between the first heat exchanger 4 and the second heat exchanger 5 has been described, but it is also possible to use the first heat exchanger 4 and the first A plurality of additional condensers are connected between the two heat exchangers 5. In this case, a plurality of additional condensers are connected in parallel.

As a modification of the present embodiment, the additional condenser 8 can be provided separately from the outdoor unit 11. That is, the additional condenser 8 may be attached to the side of the outdoor unit 11 that sucks in air as shown in FIG. 4, or may be provided separately from the outdoor unit 11. For example, when the outdoor unit 11 is placed in a hot place, the additional condenser 8 can be disposed in a cooler place than the outdoor unit 11. When the additional condenser 8 is provided separately from the outdoor unit 11, the blower fan for adding the condenser 8 is also provided together with the additional condenser 8.

In the modification of the embodiment, the first heat exchanger 4 and the additional condenser 8 are both air-cooled heat exchangers, but at least one of the first heat exchanger 4 and the additional condenser 8 may be water-cooled. Heater.

Claims

A heat pump type cooling and heating device characterized by comprising:

a compressor that compresses a refrigerant;

a four-way valve that switches a circulation direction of the refrigerant cycle during a cooling operation and a heating operation;

a first heat exchanger that condenses the refrigerant during the cooling operation to evaporate the refrigerant during the heating operation;

a second heat exchanger that condenses the refrigerant during the heating operation and evaporates the refrigerant during the cooling operation;

a first pressure reducing mechanism that decompresses the refrigerant during the cooling operation;

a second pressure reducing mechanism that decompresses the refrigerant during the heating operation;

Adding a condenser that causes the refrigerant to condense,

During the cooling operation, the four-way valve switches the circulation direction to be compressed by the compressor and flows from the compressor into the four via a discharge pipe connecting the compressor and the four-way valve The refrigerant passing through the valve flows in the order of the first heat exchanger, the additional condenser, the first pressure reducing mechanism, and the second heat exchanger, and returns to the compressor, the first a heat exchanger that condenses the refrigerant compressed by the compressor, the additional condenser further condensing the refrigerant from the first heat exchanger, the first pressure reducing mechanism The first heat exchanger and the refrigerant condensed by the additional condenser are depressurized, and the second heat exchanger evaporates the refrigerant decompressed by the first pressure reducing mechanism,

During the heating operation, the four-way valve switches the circulation direction to cause the refrigerant compressed by the compressor and flows from the compressor into the four-way valve via the discharge pipe. The second heat exchanger, the additional condenser, the second pressure reducing mechanism, and the first heat exchanger sequentially flow and return to the compressor, and the second heat exchanger is caused by the compression The refrigerant compressed by the machine is condensed, the additional condenser further condenses the refrigerant from the second heat exchanger, the second pressure reducing mechanism is paired by the second heat exchanger and the Depressurizing the refrigerant condensed by a condenser, the first heat exchanger evaporating the refrigerant decompressed by the second pressure reducing mechanism,

a cross-sectional area of the pipeline through which the refrigerant flows in the additional condenser is smaller than a cross-sectional area of the exhaust pipe, so that the additional condenser prevents the said during both the cooling operation and the heating operation The refrigerant evaporates,

The refrigerant contains monochlorodifluoromethane or difluoromethane, and 1,1,1,2-tetrafluoroethane.
The heat pump type cooling and heating device according to claim 1, wherein

The refrigerant contains difluoromethane and 1,1,1,2-tetrafluoroethane, and the weight ratio of 1,1,1,2-tetrafluoroethane to difluoromethane is 2.33 or more and 5.67 or less.
The heat pump type cooling and heating device according to claim 1, wherein

The refrigerant contains chlorodifluoromethane and 1,1,1,2-tetrafluoroethane, and the weight ratio of 1,1,1,2-tetrafluoroethane to chlorodifluoromethane is 0.67 or more. 1.86 or less.
The heat pump type cooling and heating device according to any one of claims 1 to 3, characterized in that

The cross-sectional area of the duct in which the condenser is added is 45% or less of the cross-sectional area of the discharge pipe.
The heat pump type cooling and heating device according to any one of claims 1 to 3, characterized in that

The duct of the additional condenser is formed with a plurality of cavities arranged in parallel.
The heat pump type cooling and heating device according to claim 4, wherein

The duct of the additional condenser is formed with a plurality of cavities arranged in parallel.
The heat pump type cooling and heating device according to any one of claims 1 to 3, characterized in that

The additional condenser is arranged such that it is located on the side of the first heat exchanger that draws in air.
The heat pump type cooling and heating device according to claim 4, wherein

The additional condenser is arranged such that it is located on the side of the first heat exchanger that draws in air.
The heat pump type cooling and heating device according to claim 5, wherein

The additional condenser is arranged such that it is located on the side of the first heat exchanger that draws in air.
The heat pump type cooling and heating device according to claim 6, wherein

The additional condenser is arranged such that it is located on the side of the first heat exchanger that draws in air.
A refrigerant for use in heat pump refrigeration according to any one of claims 1 to 10. Heating device, characterized in that

Contains chlorodifluoromethane or difluoromethane, and 1,1,1,2-tetrafluoroethane.
The refrigerant according to claim 11, wherein

It contains difluoromethane and 1,1,1,2-tetrafluoroethane, and the weight ratio of 1,1,1,2-tetrafluoroethane to difluoromethane is 2.33 or more and 5.67 or less.
The refrigerant according to claim 11, wherein

It contains monochlorodifluoromethane and 1,1,1,2-tetrafluoroethane, and the weight ratio of 1,1,1,2-tetrafluoroethane to monochlorodifluoromethane is 0.67 or more and 1.86 or less.
A heat exchanger used as the additional condenser in the heat pump type cooling and heating device according to any one of claims 1 to 10, characterized in that

a cross-sectional area of the pipe through which the refrigerant flows in the heat exchanger is smaller than a cross-sectional area of the discharge pipe, so that the heat exchanger prevents the said heat exchanger from both the cooling operation and the heating operation The refrigerant evaporates.