WO2020066003A1

WO2020066003A1 - Refrigerating cycle apparatus

Info

Publication number: WO2020066003A1
Application number: PCT/JP2018/036528
Authority: WO
Inventors: 悟梁池; 野本　宗; 亮築山; 智隆石川; 肇藤本; 池田　隆; 佐多　裕士
Original assignee: 三菱電機株式会社
Priority date: 2018-09-28
Filing date: 2018-09-28
Publication date: 2020-04-02
Also published as: JPWO2020066003A1; JP7105903B2; CN112714849A; CN112714849B

Abstract

A refrigerating cycle apparatus (100) is filled with a specific amount of non-azeotropic mixed refrigerant containing R463A in advance. The refrigerating cycle device (100) comprises a compressor (1), a first heat-exchanger (2), a refrigerating container (3), a decompression device (4), and a second heat exchanger (5). The non-azeotropic mixed refrigerant circulates in the order of the compressor (1), the first heat-exchanger (2), the refrigerating container (3), the decompression device (4), and the second head-exchanger (5). A volume ratio of the refrigerating container (3) with respect to the specific amount of the non-azeotropic mixed refrigerant is larger than 0 L/kg and equal to or smaller than 11 L/kg.

Description

Refrigeration cycle device

The present invention relates to a refrigeration cycle device using a non-azeotropic mixed refrigerant.

Conventionally, a refrigeration cycle device using a non-azeotropic refrigerant mixture is known. For example, Japanese Patent Laying-Open No. 7-139833 (Patent Document 1) discloses an air conditioner in which a non-azeotropic mixed refrigerant containing R32 as a low-boiling refrigerant and HFC134a as a high-boiling refrigerant is filled. In the air conditioner, a refrigerant regulator is provided between the heat source side heat exchanger and the expansion mechanism. The refrigerant regulator supplies the amount of refrigerant corresponding to the storage amount of the liquid non-azeotropic mixed refrigerant to the heat source side heat exchanger during the heating operation cycle, and adjusts the amount of circulating refrigerant. A large amount of HFC134a is stored in the refrigerant controller during the heating operation cycle, so that the ratio of R32 in the circulating refrigerant amount increases. As a result, the performance of the air conditioner can be improved.

JP-A-7-139833

冷媒 The refrigerant regulator of the air conditioner disclosed in Patent Document 1 stores excess non-azeotropic mixed refrigerant during a cooling operation cycle. When the capacity of the refrigerant regulator is increased while keeping the amount of the non-azeotropic mixed refrigerant to be pre-filled in the air conditioner constant, the amount of gas low-boiling refrigerant in the refrigerant regulator increases, and the low-boiling point in the circulating refrigerant amount increases. The amount of refrigerant decreases. As a result, the cooling capacity of the use side heat exchanger may decrease. However, in Patent Literature 1, depending on the relationship between the capacity of the refrigerant regulator and the amount of the non-azeotropic mixed refrigerant pre-filled, the cooling capacity of the use side heat exchanger is reduced, and may be lower than the desired cooling capacity. Is not taken into account.

The present invention has been made to solve the above-described problems, and an object thereof is to secure a desired cooling capacity of a refrigeration cycle device.

特定 The refrigeration cycle apparatus according to the present invention is charged in advance with a specific amount of non-azeotropic mixed refrigerant containing R463A. The refrigeration cycle device includes a compressor, a first heat exchanger, a refrigerant container, a pressure reducing device, and a second heat exchanger. The non-azeotropic mixed refrigerant circulates in the order of the compressor, the first heat exchanger, the refrigerant container, the pressure reducing device, and the second heat exchanger. The ratio of the volume of the refrigerant container to the specific amount of the non-azeotropic mixed refrigerant is more than 0 L / kg and 11 L / kg or less.

ADVANTAGE OF THE INVENTION According to the refrigeration cycle apparatus which concerns on this invention, since the ratio of the capacity | capacitance of the refrigerant | coolant container with respect to the quantity of the non-azeotropic mixed refrigerant previously filled into a refrigeration cycle apparatus is more than 0 L / kg and 11 L / kg or less, desired. Cooling capacity can be secured.

It is a functional block diagram showing the composition of the refrigeration cycle device concerning an embodiment. It is a figure which shows the ratio of the receiver volume with respect to the specific amount of R463A pre-filled in the refrigeration cycle apparatus (receiver volume ratio), and the relationship of a circulation composition ratio. FIG. 4 is a diagram illustrating a relationship between a receiver volume ratio and a cooling capacity ratio of a refrigeration cycle device. FIG. 4 is a diagram illustrating a relationship between a receiver volume ratio and a weight composition ratio of a slightly burnt refrigerant to an unburnt refrigerant.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the drawings, the same or corresponding portions have the same reference characters allotted, and description thereof will not be repeated in principle.

FIG. 1 is a functional block diagram showing a configuration of a refrigeration cycle apparatus 100 according to the embodiment. As shown in FIG. 1, the refrigeration cycle apparatus 100 includes a compressor 1, a condenser 2 (first heat exchanger), a receiver 3 (refrigerant container), an expansion valve 4 (decompression device), and an evaporator. 5 (second heat exchanger) and a control device 6.

(4) The refrigeration cycle apparatus 100 is charged in advance with a specific amount of R463A defined in the specifications of the refrigeration cycle apparatus 100. R463A, which is a non-azeotropic refrigerant mixture, circulates in the order of the compressor 1, the condenser 2, the receiver 3, the expansion valve 4, and the evaporator 5.

The pipe 7 connects the condenser 2 and the receiver 3. The end 71 of the pipe 7 is arranged in the receiver 3. R463A flows into the receiver 3 from the end 71. The pipe 8 communicates the receiver 3 and the expansion valve 4. The end 81 of the pipe 8 is arranged in the receiver 3. R463A in the receiver 3 flows out from the end 81. The receiver 3 has, for example, a tubular structure formed by welding both ends of a flat plate.

The control device 6 controls the amount of non-azeotropic refrigerant mixture discharged by the compressor 1 per unit time by controlling the drive frequency fc of the compressor 1. The control device 6 includes a storage unit 11. The storage unit 11 stores in advance, for example, physical property values of R463A, the volume of the receiver 3, and control target values of specific parameters (for example, evaporation temperature or condensation temperature).

(4) While the liquid R463A is stored in the receiver 3, a refrigerant having a relatively lower boiling point than other refrigerants (low-boiling refrigerant) among the refrigerants contained in the R463A is vaporized. As R463A circulates through the refrigeration cycle apparatus 100, the amount of gaseous refrigerant (gas refrigerant) contained in the receiver 3 increases. Since the low boiling point refrigerant contained in R463A circulating through refrigeration cycle apparatus 100 decreases, the composition ratio (circulation composition ratio) of R463A circulating through refrigeration cycle apparatus 100 changes.

R463A contains R32, R125, R1234yf, R134a, and CO2 in a weight percent (wt%) ratio (pure composition ratio) of 36: 30: 14: 14: 6. R463A contains CO2 to secure the refrigerant pressure. The boiling points of R32, R125, R1234yf, R134a, and CO2 at one atmosphere are -51.7 ° C, -48.1 ° C, -29.4 ° C, -26.1 ° C, and -78.5 ° C. It is. CO2 has the lowest boiling point among the refrigerants contained in R463A, and R32 has the second lowest boiling point after CO2. R463A has a low boiling point refrigerant including R32 and CO2.

FIG. 2 is a diagram showing the relationship between the ratio of the volume of the receiver 3 to the specific amount of R463A pre-filled in the refrigeration cycle apparatus 100 (receiver volume ratio) and the circulation composition ratio. As the receiver volume ratio increases, the ratio of the volume of the liquid refrigerant stored in the receiver 3 to the volume of the receiver 3 decreases. Therefore, the ratio of the volume of the gas refrigerant to the volume of the receiver 3 increases. As a result, as shown in FIG. 2, as the receiver volume ratio increases, the proportion of the low-boiling-point refrigerant in R463A circulating in refrigeration cycle apparatus 100 decreases. As a result, the cooling capacity of the refrigeration cycle device 100 is reduced, and may be lower than the desired cooling capacity.

Generally, the cooling capacity ratio of the refrigeration cycle device is often designed with a margin of about 20%. In this case, the desired cooling capacity of the refrigeration cycle apparatus is a cooling capacity ratio of 80% or more.

FIG. 3 is a diagram showing the relationship between the receiver volume ratio and the cooling capacity ratio of the refrigeration cycle device 100. In FIG. 3, the cooling capacity ratio on the vertical axis indicates that the cooling capacity when the circulation composition ratio of R463A is a pure composition ratio is 100%. As shown in FIG. 3, the cooling capacity ratio decreases as the receiver volume ratio increases, and when the receiver volume ratio is 11, the cooling capacity ratio becomes 80%. If the receiver volume ratio is greater than 11, the cooling capacity ratio will be less than 80%.

Therefore, in the refrigeration cycle apparatus 100, the receiver volume ratio is set to be larger than 0 L / kg and 11 L / kg. By limiting the range of the receiver volume ratio to the range, a cooling capacity ratio of 80% or more can be secured.

Next, the flammability of R463A will be described. Among the refrigerants included in R463A, according to the classification of, for example, ASHRAE (American Society of Heating, Refrigerating and Air-Conditioning Engineers), R32 and R1234yf are classified as low-flammable refrigerants, and R125, R134a, and CO2 are classified as noncombustible refrigerants. You. In the pure composition ratio of R463A, the weight composition ratio of the slightly combustible refrigerant to the non-combustible refrigerant is 1. In order for R463A to suppress the combustibility of the refrigerant leaked from the refrigeration cycle apparatus 100 due to slow leak or the like, the weight composition ratio of the slightly burnt refrigerant to the nonburnable refrigerant is desirably 1 or less. Since the welded portion has a relatively low strength and is easily broken, the leaked portion of the refrigerant may be, for example, a welded portion of the cylindrical receiver 3.

FIG. 4 is a diagram showing the relationship between the receiver volume ratio and the weight composition ratio of the slightly-burning refrigerant to the non-burning refrigerant. As shown in FIG. 4, the weight composition ratio of the slightly-burning refrigerant to the non-burning refrigerant is determined when the receiver volume ratio is greater than 0 L / kg and not more than 2.4 L / kg, or not less than 9.8 L / kg. The weight composition ratio of the slightly-burning refrigerant to the non-burning refrigerant is 1 or less. Therefore, in refrigeration cycle apparatus 100, the receiver volume ratio is greater than 0 L / kg and not more than 2.4 L / kg, or 9.8 L / kg or more and 11 L / kg or less. By limiting the receiver volume ratio to this range, a desired cooling capacity can be ensured, and the combustibility of the refrigerant leaked from the refrigeration cycle device 100 can be suppressed.

As described above, according to the refrigeration cycle apparatus according to the embodiment, a desired cooling capacity can be ensured. Further, according to the refrigeration cycle device according to the embodiment, the combustibility of the leaked refrigerant can be suppressed.

The embodiments disclosed this time are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

{1} compressor, 2} condenser, 3} receiver, 4} expansion valve, 5} evaporator, 6} control device, 7, 8 piping, 11} storage unit, 100} refrigeration cycle device.

Claims

A refrigeration cycle apparatus in which a specific amount of a non-azeotropic mixed refrigerant including R463A is pre-filled,
A compressor,
A first heat exchanger;
A refrigerant container,
A decompression device;
A second heat exchanger,
The non-azeotropic mixed refrigerant circulates in the order of the compressor, the first heat exchanger, the refrigerant container, the pressure reducing device, and the second heat exchanger,
The refrigeration cycle apparatus, wherein a ratio of the volume of the refrigerant container to the specific amount of the non-azeotropic mixed refrigerant is greater than 0 L / kg and equal to or less than 11 L / kg.
The refrigeration cycle apparatus according to claim 1, wherein the ratio is greater than 0 L / kg and not more than 2.4 L / kg, or not less than 9.8 L / kg and not more than 11 L / kg.
One end of a first pipe that communicates the first heat exchanger and the refrigerant container is disposed in the refrigerant container,
The refrigeration cycle apparatus according to claim 1, wherein one end of a second pipe that communicates the refrigerant container and the decompression device is disposed inside the refrigerant container.
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant container has a tubular structure formed by welding both ends of a flat plate.