WO2020066005A1

WO2020066005A1 - Refrigeration cycle apparatus

Info

Publication number: WO2020066005A1
Application number: PCT/JP2018/036530
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: JP6937935B2; CN112739962B; CN112739962A; JPWO2020066005A1

Abstract

In a refrigeration cycle apparatus (100) according to the present invention, a non-azeotropic mixture refrigerant is circulated through a compressor (1), a first heat exchanger (2), a refrigerant container (3), a first decompression device (4), and a second heat exchanger (5) in this order. A bypass flow channel (9) causes a part of the non-azeotropic mixture refrigerant in the refrigerant container (3) to join, in a gas-liquid two-phase state, the non-azeotropic mixture refrigerant flowing between the first decompression device (4) and a discharge port of the compressor (1). When a specific condition indicating that the enclosed amount of the non-azeotropic mixture refrigerant filled in the refrigeration cycle device (100) is lacking is satisfied, a control device (10) outputs the specific information from a notification unit (8). A third heat exchanger (6) cools the non-azeotropic mixture refrigerant. The control device (10) determines whether or not the specific condition is satisfied, by using a relationship of the ratio of the volume of the refrigerant container (3) with respect to the enclosed amount of the non-azeotropic mixture refrigerant, pressure (Ps) of the non-azeotropic mixture refrigerant flowing out of a second end part (N2), and temperature (Tb).

Description

Refrigeration cycle device

The present invention relates to a refrigeration cycle device that determines whether the amount of refrigerant charged is insufficient.

Conventionally, a refrigeration cycle device that determines whether the amount of refrigerant charged is insufficient is known. For example, Japanese Patent Laying-Open No. 2006-38453 (Patent Document 1) discloses a refrigeration apparatus including a liquid level detection circuit connected between a predetermined position of a receiver and a suction side of a compressor. . In the liquid level detection circuit, after the refrigerant flowing out of a predetermined position of the receiver is decompressed and heated, the temperature of the refrigerant is measured. When the refrigerant flowing out of a predetermined position of the receiver is in a gaseous state, the temperature rise due to heating increases, and when the refrigerant is in a liquid state, heat energy due to heating is consumed as latent heat of evaporation, and the temperature rise due to heating decreases. Therefore, when the temperature rise is small, it is determined that the liquid refrigerant has accumulated up to the predetermined position of the receiver, and it is possible to detect that the required refrigerant amount has been charged.

JP 2006-38453 A

The temperature of the refrigerant after being depressurized and heated in the liquid level detection circuit of the refrigeration apparatus disclosed in Patent Document 1 depends on the amount of refrigerant circulating in the refrigeration apparatus (circulating refrigerant amount) or the heating mechanism of the liquid level detection circuit. Depends on the amount of heating. Regarding the temperature rise of the refrigerant that has been depressurized and heated in the liquid level detection circuit, such that the temperature rise when the refrigerant flowing out of a predetermined position of the receiver is in a gas state is larger than the temperature rise in the liquid state, It is necessary to design a decompression mechanism and a heating mechanism included in the liquid level detection circuit for each type of refrigeration system. Therefore, a liquid level detection circuit designed for a certain type of refrigeration apparatus may not be applicable to another type of refrigeration apparatus. As a result, the manufacturing cost of the refrigeration system may increase.

The present invention has been made to solve the above-described problem, and an object of the present invention is to suppress the manufacturing cost of a refrigeration cycle device that determines whether the amount of refrigerant to be charged is insufficient. .

において In the refrigeration cycle device according to the present invention, the non-azeotropic mixed refrigerant circulates in the order of the compressor, the first heat exchanger, the refrigerant container, the first pressure reducing device, and the second heat exchanger. The refrigeration cycle device includes a bypass passage, a notification unit, and a control device. The bypass flow passage joins a part of the non-azeotropic mixed refrigerant in the refrigerant container to the non-azeotropic mixed refrigerant flowing between the first pressure reducing device and the discharge port of the compressor in a gas-liquid two-phase state. The control device outputs the specific information from the notification unit when a specific condition indicating that the amount of the non-azeotropic mixed refrigerant filled in the refrigeration cycle device is insufficient is satisfied. The bypass flow path includes a third heat exchanger and a second pressure reducing device connected in series between the first end and the second end of the bypass flow path. The first end is disposed in the refrigerant container. The third heat exchanger cools the non-azeotropic mixed refrigerant. The control device determines whether or not the specific condition is satisfied by using the relationship between the ratio of the volume of the refrigerant container to the amount of the non-azeotropic mixed refrigerant charged, the pressure of the non-azeotropic mixed refrigerant flowing out from the second end, and the temperature.

According to the refrigeration cycle device according to the present invention, using the relationship between the ratio of the volume of the refrigerant container to the amount of non-azeotropic mixed refrigerant enclosed, the pressure of the non-azeotropic mixed refrigerant flowing out from the second end, and the temperature, The manufacturing cost of the refrigeration cycle device is determined by determining whether the amount of the non-azeotropic mixed refrigerant filled in the refrigeration cycle device is insufficient by determining whether the amount of the refrigerant is insufficient. Can be suppressed.

FIG. 2 is a functional block diagram illustrating a configuration of the refrigeration cycle apparatus according to Embodiment 1 and a case where a liquid refrigerant flows into a bypass passage. FIG. 2 is a functional block diagram illustrating a configuration of the refrigeration cycle apparatus according to Embodiment 1 and a case where a gas refrigerant flows into a bypass passage. FIG. 2 is a diagram illustrating a relationship between a receiver volume ratio and a composition ratio of a non-azeotropic mixed refrigerant flowing out of a bypass flow path when a liquid refrigerant flows into a bypass flow path as shown in FIG. 1. FIG. 3 is a diagram showing a relationship between a receiver volume ratio and a composition ratio of a non-azeotropic mixed refrigerant flowing out of a bypass flow path when a gas refrigerant flows into a bypass flow path as shown in FIG. 2. FIG. 3 is a Mollier diagram showing a relationship among pressure, enthalpy, and temperature of a non-azeotropic mixed refrigerant. FIG. 7 is a diagram illustrating a relationship between a receiver volume ratio and a temperature when an evaporation temperature at a certain pressure is −40 ° C. FIG. 3 is a flowchart for explaining a flow of a process performed by the control device of FIGS. 1 and 2 to determine whether the amount of non-azeotropic mixed refrigerant charged is insufficient. FIG. 9 is a flowchart for explaining a flow of a process performed by the control device of the refrigeration cycle apparatus according to the first modification of the first embodiment for determining whether the amount of non-azeotropic mixed refrigerant charged is insufficient for the primary refrigerant amount. It is a flowchart. FIG. 5 is a functional block diagram illustrating a configuration of a refrigeration cycle device according to a second modification of the first embodiment. FIG. 7 is a functional block diagram illustrating a configuration of a refrigeration cycle device according to a third modification of the first embodiment. FIG. 9 is a functional block diagram illustrating a configuration of a refrigeration cycle device according to Modification 4 of Embodiment 1. FIG. 7 is a diagram illustrating a relationship between a receiver volume ratio and a temperature when an evaporation temperature at a certain pressure is −40 ° C. 15 is a flowchart for explaining a flow of a process performed by the control device of the refrigeration cycle apparatus according to Embodiment 2 to determine whether the amount of non-azeotropic mixed refrigerant charged is insufficient for the amount of secondary refrigerant. . FIG. 4 is a diagram illustrating a relationship between a receiver volume ratio and a cooling capacity ratio of a refrigeration cycle device. Determined by the control device of the refrigeration cycle device according to the first modification of the second embodiment, whether or not the amount of non-azeotropic mixed refrigerant charged is insufficient for the amount of refrigerant required to maintain the desired cooling capacity. It is a flowchart for explaining the flow of the determination process. 15 is a flowchart for explaining a flow of a process performed by the control device of the refrigeration cycle device according to the second modification of the second embodiment for determining whether or not refrigerant leakage has occurred. FIG. 9 is a diagram showing a configuration of a refrigeration cycle device according to Embodiment 3. Flowchart for explaining the flow of processing performed by the control device of FIG. 17 to determine whether the amount of non-azeotropic mixed refrigerant charged is insufficient for the amount of refrigerant necessary to maintain a desired cooling capacity. It is.

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.

Embodiment 1 FIG.
1 and 2 are functional block diagrams illustrating a configuration of a refrigeration cycle device 100 according to Embodiment 1. The difference between FIG. 1 and FIG. 2 is the liquid level of the non-azeotropic mixed refrigerant (liquid refrigerant) of the liquid in the receiver 3.

As shown in FIGS. 1 and 2, the refrigeration cycle apparatus 100 includes a compressor 1, a condenser 2 (first heat exchanger), a receiver 3 (refrigerant container), and an expansion valve 4 (first pressure reducing device). ), An evaporator 5 (second heat exchanger), a display device 8 (notification unit), a bypass flow path 9, a control device 10, a temperature sensor 101, and a pressure sensor 102.

In the refrigeration cycle apparatus 100, the non-azeotropic mixed refrigerant circulates in the order of the compressor 1, the condenser 2, the receiver 3, the expansion valve 4, and the evaporator 5. An end portion N1 (first end portion) of the bypass flow passage 9 is arranged in the receiver 3. An end N2 (second end) of the bypass flow passage 9 is connected to a flow passage FP1 between the evaporator 5 and the suction port of the compressor 1. The bypass channel 9 includes a heat exchanger 6 (third heat exchanger) and a capillary tube 7 (second pressure reducing device). The heat exchanger 6 and the capillary tube 7 are connected in series in this order between the ends N1 and N2.

The non-azeotropic mixed refrigerant flowing into the bypass passage 9 from the end N1 is cooled in the heat exchanger 6. Thereafter, the pressure is reduced in the capillary tube 7 to be in a gas-liquid two-phase state, and merges with the non-azeotropic mixed refrigerant flowing through the flow path FP1 from the end N2.

The temperature sensor 101 measures the temperature Tb of the non-azeotropic refrigerant mixture flowing out from the end N2. The pressure sensor 102 detects the pressure Ps of the non-azeotropic mixed refrigerant sucked into the compressor 1. The pressure Ps is a pressure of the non-azeotropic refrigerant mixture flowing out from the end N2.

The control device 10 controls the amount of non-azeotropic mixed refrigerant discharged from the compressor 1 per unit time by controlling the drive frequency fc of the compressor 1. Control device 10 receives temperature Tb and pressure Ps from temperature sensor 101 and pressure sensor 102, respectively. When the amount of the non-azeotropic mixed refrigerant filled in the refrigeration cycle apparatus 100 is insufficient, the control device 10 displays on the display device 8 that the amount of the non-azeotropic mixed refrigerant is insufficient.

The control device 10 includes a storage unit 11. The storage unit 11 stores the relationship between the ratio of the volume of the receiver 3 to the amount of the non-azeotropic mixed refrigerant (receiver volume ratio), the pressure Ps, and the temperature Tb, or information necessary for deriving the relationship (for example, The physical property value of the azeotropic mixed refrigerant is stored in advance. Further, the storage unit 11 stores in advance control target values of specific parameters (for example, evaporation temperature or condensation temperature).

(4) The receiver 3 stores a liquid non-azeotropic mixed refrigerant and vaporizes a refrigerant (low-boiling refrigerant) having a relatively lower boiling point than other refrigerants among the refrigerants contained in the non-azeotropic mixed refrigerant. As the azeotropic mixed refrigerant, for example, R463A can be mentioned.

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 ensure operating 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.

In the following, the case where the non-azeotropic refrigerant mixed in the refrigeration cycle apparatus 100 is R463A will be described. In addition, the non-azeotropic mixed refrigerant filled in the refrigeration cycle apparatus 100 is not limited to R463A.

In FIG. 1, the liquid level of the receiver 3 is higher than the end N1. Since the end N1 is immersed in the liquid refrigerant, the liquid refrigerant flows into the end N1. In FIG. 2, the liquid level of the receiver 3 is lower than the end N1. Since the end N1 is not immersed in the liquid refrigerant, a gaseous refrigerant (gas refrigerant) flows into the end N1.

FIG. 3 is a diagram illustrating the relationship between the receiver volume ratio and the composition ratio of the non-azeotropic mixed refrigerant flowing out of the bypass passage 9 when the liquid refrigerant flows into the bypass passage 9 as shown in FIG. . FIG. 4 is a diagram showing the relationship between the receiver volume ratio and the composition ratio of the non-azeotropic mixed refrigerant flowing out of the bypass passage 9 when the gas refrigerant flows into the bypass passage 9 as shown in FIG. . 3 and FIG. 4, the composition ratio of the non-azeotropic mixed refrigerant flowing out of the bypass passage 9 differs depending on the state of the non-azeotropic mixed refrigerant flowing into the bypass passage 9. Such a difference in the composition ratio is significantly reflected in the temperature of the non-azeotropic mixed refrigerant in the gas-liquid two-phase state.

FIG. 5 is a Mollier chart showing the relationship among the pressure, enthalpy, and temperature of the non-azeotropic refrigerant mixture. 5, the solid line shows the case of FIG. 1 in which the liquid refrigerant flows into the bypass passage 9, and the dotted line shows the case of FIG. 2 in which the gas refrigerant flows into the bypass passage 9. The same applies to FIG. In FIG. 5, a state C10 indicates a state of the non-azeotropic mixed refrigerant in a gas-liquid two-phase state flowing out of the bypass passage 9.

As shown in FIG. 5, in the region of the gas-liquid two-phase state (the region between the saturated liquid line and the saturated vapor line), the isotherm has a negative slope, and the enthalpy axis ( (Horizontal axis). Since the isotherm has a negative slope in the region of the gas-liquid two-phase state, the temperature of the non-azeotropic refrigerant mixture changes when the enthalpy is changed while the pressure is constant in the region of the gas-liquid two-phase state. A temperature gradient occurs.

温度 The temperature gradient when the liquid refrigerant flows into the bypass channel 9 is different from the temperature gradient when the gas refrigerant flows into the bypass channel 9. As a result, the temperature Tb in the state C10 when the gas refrigerant flows into the bypass passage 9 is lower than the temperature Tb in the state C10 when the liquid refrigerant flows into the bypass passage 9.

FIG. 6 is a diagram showing the relationship between the receiver volume ratio and the temperature Tb when the evaporation temperature at the pressure Ps is −40 ° C. In FIG. 6, the temperature Tp (reference temperature) is the minimum value of the temperature Tb of the non-azeotropic mixed refrigerant flowing out of the bypass passage 9 when the liquid refrigerant flows into the bypass passage 9. Note that the evaporation temperature at a certain pressure is an average temperature of a temperature at a point on the Mollier diagram corresponding to the pressure on the saturated liquid line and a temperature on the saturated vapor line corresponding to the pressure.

温度 As shown in FIG. 6, the temperature Tb when the gas refrigerant flows into the bypass passage 9 is lower than the temperature Tp. Therefore, in the refrigeration cycle apparatus 100, when the difference between the temperatures Tp and Tb is larger than the threshold value α, the liquid level of the receiver 3 becomes lower than the height H1, and the amount of the non-azeotropic mixed refrigerant is reduced. It is determined that there is a shortage. The method of determining the shortage of the amount of non-azeotropic mixed refrigerant using the relationship between the receiver volume ratio, the pressure Ps, and the temperature Tb does not require information unique to the model of the refrigeration cycle apparatus 100. It has versatility to refrigeration cycle devices that use azeotropic mixed refrigerants. By employing this method, it is possible to suppress the manufacturing cost of the refrigeration cycle device that determines whether the amount of the charged refrigerant is insufficient.

FIG. 7 is a flowchart for explaining the flow of processing performed by the control device 10 of FIGS. 1 and 2 to determine whether the amount of non-azeotropic mixed refrigerant charged is insufficient. The process shown in FIG. 7 is periodically called by a main routine (not shown) that integrally controls the refrigeration cycle apparatus 100. The same applies to the processing shown in FIGS. 8, 13, 15, 16, and 18. Hereinafter, a step is simply described as S.

制御 As shown in FIG. 7, in S101, control device 10 calculates temperature Tp corresponding to pressure Ps, and advances the processing to S102. The control device 10 determines whether or not the condition (specific condition) that the difference between the temperatures Tp and Tb is larger than the threshold value α in S102. If the difference between the temperatures Tp and Tb is larger than α (YES in S102), the control device 10 displays information (specific information) indicating that the encapsulation amount is insufficient in S103 on the display device 8, and performs the processing. Return to main routine. When the difference between temperature Tp and Tb is equal to or smaller than α (NO in S102), control device 10 returns the process to the main routine. The threshold α can be appropriately calculated by an actual machine experiment or simulation. The threshold value α may be zero.

Modification 1 of Embodiment 1
Depending on the refrigeration cycle device, the refrigerant may be charged stepwise. For example, the minimum filling amount (primary refrigerant amount) necessary to operate the refrigeration cycle device, and the secondary amount obtained by adding the fluctuation amount of the circulating refrigerant amount according to the change in the operation state of the refrigeration cycle device to the primary refrigerant amount The amount of refrigerant may be set. In the first modification of the first embodiment, a case will be described in which it is determined whether or not the charging of the primary refrigerant amount has been completed by determining whether the specific condition shown in S102 of FIG. 7 is satisfied.

FIG. 8 illustrates a flow of a process performed by the control device of the refrigeration cycle device according to the first modification of the first embodiment to determine whether the amount of the non-azeotropic mixed refrigerant charged is insufficient for the primary refrigerant amount. It is a flowchart for explaining. In the processing shown in FIG. 8, S103 of the processing shown in FIG. 7 is replaced with S103A, and processing S104 is added.

制御 As shown in FIG. 8, the control device calculates the temperature Tp in S101, and determines in S102 whether the difference between the temperatures Tp and Tb is larger than the threshold value α. When the difference between the temperatures Tp and Tb is larger than α (YES in S102), the control device determines that the amount of the filled refrigerant is insufficient for the primary refrigerant amount, and displays information (specific information) prompting the filling of the refrigerant in S103A with the display device. And returns the process to the main routine. When the difference between the temperatures Tp and Tb is equal to or less than α (NO in S102), the control device 10 displays information indicating that the filling of the primary refrigerant amount has been completed on the display device in S104, and shifts the processing to the main routine. return.

Modification 2 of Embodiment 1
In the first embodiment, the case where the second end of the bypass flow path is connected to the flow path between the second heat exchanger and the suction port of the compressor has been described. The bypass flow path may allow a part of the non-azeotropic mixed refrigerant in the refrigerant container to join the non-azeotropic mixed refrigerant flowing between the first pressure reducing device and the discharge port of the compressor in a gas-liquid two-phase state. Frequently, the connection position of the second end is not limited to the flow path between the second heat exchanger and the suction port of the compressor. In the second modification of the first embodiment, a case will be described in which the compressor has an injection port and the second end is connected to the injection port.

FIG. 9 is a functional block diagram showing a configuration of a refrigeration cycle apparatus 100B according to a second modification of the first embodiment. The configuration of the refrigeration cycle device 100B is a configuration in which the compressor 1 and the bypass channel 9 shown in FIG. 1 are replaced with a compressor 1B and a bypass channel 9B, respectively. The configuration other than these is the same, and thus the description will not be repeated.

圧縮 As shown in FIG. 9, the compressor 1B has an injection port Pinj. An end N2B (second end) of the bypass flow passage 9B is connected to the injection port Pinj.

Modification 3 of Embodiment 1
In the third modification of the first embodiment, a case will be described in which the second end of the bypass flow path is connected to the flow path between the first pressure reducing device and the second heat exchanger.

FIG. 10 is a functional block diagram showing a configuration of a refrigeration cycle apparatus 100C according to Modification 3 of Embodiment 1. The configuration of the refrigeration cycle device 100C is such that the bypass flow passage 9 shown in FIG. 1 is replaced with a bypass flow passage 9C. The other configuration is the same, and the description will not be repeated. As shown in FIG. 10, an end N2C (second end) of the bypass flow passage 9C is connected to a flow passage FP2 between the expansion valve 4 and the evaporator 5.

Modification 4 of Embodiment 1
In the first embodiment, the case where the third heat exchanger and the second pressure reducing device are connected in series in this order between the first end and the second end of the bypass flow passage has been described. The third heat exchanger and the second decompression device may be connected in series between the first end and the second end. In a fourth modification of the first embodiment, a case will be described in which the second pressure reducing device and the third heat exchanger are connected in series in this order between the first end and the second end.

FIG. 11 is a functional block diagram showing a configuration of a refrigeration cycle apparatus 100D according to Modification 4 of Embodiment 1. The configuration of the refrigeration cycle device 100D is a configuration in which the bypass channel 9 shown in FIG. 1 is replaced with a bypass channel 9D. The other configuration is the same, and the description will not be repeated. As shown in FIG. 11, the capillary tube 7 and the heat exchanger 6 are connected in series in this order between the ends N1 and N2.

流路 The flow resistance of the capillary tube 7 is usually larger than the flow resistance of the heat exchanger 6. Therefore, the amount of the refrigerant flowing out of the end N2 per unit time is limited to the amount of the refrigerant that can pass through the capillary tube 7 per unit time. When it is necessary to increase the amount of refrigerant per unit time flowing out from the end N2 to secure the amount of circulating refrigerant, as shown in FIG. 1, a heat exchanger 6 is provided between the ends N1 and N2. Preferably, the capillary tubes 7 are connected in series in this order, and the non-azeotropic refrigerant is cooled and depressurized in this order.

As described above, according to the refrigeration cycle apparatus according to Embodiment 1 and Modifications 1 to 4, it is possible to reduce the manufacturing cost of the refrigeration cycle apparatus that determines whether or not the amount of non-azeotropic mixed refrigerant is insufficient. it can.

Embodiment 2 FIG.
In the first embodiment, the case where the shortage of the charged amount is determined based on whether or not the end of the bypass passage arranged in the refrigerant container is immersed in the liquid refrigerant stored in the refrigerant container is described. . In the second embodiment, a case will be described in which, when the liquid refrigerant flows into the first end of the bypass flow passage, it is determined whether or not the amount of the non-azeotropic mixed refrigerant is not insufficient.

FIG. 12 is a diagram showing the relationship between the receiver volume ratio and the temperature Tb when the evaporation temperature at the pressure Ps is −40 ° C. As shown in FIG. 12, since the volume of the receiver is constant in the operating refrigeration cycle apparatus, the volume ratio of the receiver increases as the amount of the non-azeotropic mixed refrigerant decreases. As a result, the temperature Tb decreases. Therefore, in the second embodiment, by determining whether or not the temperature Tb is lower than the reference temperature β, it is determined whether or not the charged amount of the non-azeotropic mixed refrigerant is insufficient for a desired refrigerant amount. The case will be described. The reference temperature β is a temperature assumed in the non-azeotropic mixed refrigerant flowing out of the bypass passage when the desired refrigerant amount is charged.

FIG. 13 illustrates a flow of processing performed by the control device of the refrigeration cycle apparatus according to Embodiment 2 to determine whether the amount of non-azeotropic mixed refrigerant charged is insufficient for the amount of secondary refrigerant. It is a flowchart of FIG. As illustrated in FIG. 13, the control device determines in S201 whether a condition (specific condition) that the temperature Tb is lower than the reference temperature β is satisfied. When the temperature Tb is lower than the reference temperature β (YES in S201), in S202, the control device displays information (specific information) for prompting the charging of the refrigerant on the display device, and returns the process to the main routine. When the temperature Tb is equal to or higher than the reference temperature β (NO in S201), in S203, the control device displays information indicating that the filling of the secondary refrigerant amount is completed on the display device, and returns the process to the main routine.

Modification 1 of Embodiment 2
In the second embodiment, it is determined whether or not the temperature Tb is lower than the reference temperature β to determine whether or not the amount of non-azeotropic mixed refrigerant to be charged is insufficient for a desired amount of refrigerant. explained. Whether or not the amount of non-azeotropic mixed refrigerant charged is insufficient for the desired amount of refrigerant can also be determined using the receiver volume ratio. In the first modification of the second embodiment, it is determined whether or not the amount of the non-azeotropic mixed refrigerant is insufficient for maintaining the desired cooling capacity by using the receiver volume ratio. The case will be described.

FIG. 14 is a diagram showing the relationship between the receiver volume ratio and the cooling capacity ratio of the refrigeration cycle device. In FIG. 14, 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. 14, since the volume of the receiver is constant in the operating refrigeration cycle apparatus, the receiver volume ratio increases as the amount of non-azeotropic mixed refrigerant charged decreases. As a result, the cooling capacity ratio decreases. Therefore, in the first modification of the second embodiment, by determining whether the receiver volume ratio corresponding to the temperature Tb is smaller than the receiver volume ratio corresponding to the desired cooling capacity, the non-azeotropic mixed refrigerant is determined. A case will be described in which it is determined whether or not the charged amount is insufficient for a desired refrigerant amount. In the following, a desired cooling capacity is set to a cooling capacity ratio of 80% or more, and a receiver volume ratio corresponding to the cooling capacity ratio of 80% is set to Rc.

FIG. 15 shows that the amount of non-azeotropic mixed refrigerant charged by the control device of the refrigeration cycle apparatus according to Modification 1 of Embodiment 2 is insufficient for the amount of refrigerant necessary to maintain the desired cooling capacity. 9 is a flowchart for explaining a flow of a process for determining whether or not there is a presence. As shown in FIG. 15, the control device calculates the receiver volume ratio R1 from the pressure Ps and the temperature Tb in S211 and advances the processing to S212. In S212, the control device determines whether a condition (specific condition) that the receiver volume ratio R1 is larger than Rc is satisfied. When receiver volume ratio R1 is larger than Rc (YES in S212), control device 30 displays information indicating that the cooling capacity has decreased in S213 on display device 8, and provides the user with the non-azeotropic mixed refrigerant. Prompts for filling and returns the process to the main routine. When receiver volume ratio R1 is equal to or smaller than Rc (NO in S212), control device 30 returns the process to the main routine.

Modification 2 of Embodiment 2
In the second modification of the second embodiment, whether the non-azeotropic mixed refrigerant is leaking from the refrigeration cycle device using the initial value of the receiver volume ratio after the completion of charging the refrigeration cycle device with the secondary refrigerant amount is determined. The configuration for judging is described.

FIG. 16 is a flowchart illustrating a flow of a process performed by the control device of the refrigeration cycle device according to the second modification of the second embodiment to determine whether or not refrigerant leakage has occurred. In the processing illustrated in FIG. 16, S212 and S213 in FIG. 15 are replaced with S222 and S223, respectively.

As shown in FIG. 16, the control device calculates the receiver volume ratio R1 in S211 and, under S222, the condition (specific condition) that the difference between the receiver volume ratio R1 and the initial value R0 is larger than the threshold value γ. Determine success or failure. If the difference between the receiver volume ratio R1 and the initial value R0 is larger than the threshold value γ (YES in S222), the control device displays information (specific information) indicating that cooling leakage has occurred in S223. And returns the process to the main routine. When the difference between the receiver volume ratio R1 and the initial value R0 is equal to or smaller than the threshold value γ (NO in S222), the control device returns the process to the main routine.

The condition shown in S222 is a condition indicating that the amount of the non-azeotropic mixed refrigerant is insufficient for the amount of the secondary refrigerant. The threshold value γ can be appropriately calculated by an actual machine experiment or simulation. The threshold value γ may be zero.

As described above, according to the refrigeration cycle apparatus according to Embodiment 2 and

Modifications

1 and 2, it is possible to suppress the manufacturing cost of the refrigeration cycle apparatus that determines whether the amount of non-azeotropic mixed refrigerant charged is insufficient. it can.

Embodiment 3 FIG.
In the first and second embodiments, the case has been described where information indicating that the non-azeotropic refrigerant mixture is insufficient is displayed on the display device provided in the refrigeration cycle apparatus. In the third embodiment, a case will be described in which the refrigeration cycle device includes a communication device, and the shortage of the non-azeotropic mixed refrigerant is transmitted to an external display device by the communication device. According to the refrigeration cycle apparatus according to Embodiment 3, the user need not always be near the refrigeration cycle apparatus and monitor the occurrence of the shortage of the refrigerant. The user can be informed of the lack of the amount of the non-azeotropic refrigerant mixture by receiving a message from the maintenance manager at a remote location.

FIG. 17 is a diagram showing a configuration of a refrigeration cycle apparatus 300 according to Embodiment 3. In the configuration of the refrigeration cycle device 300, the display device 8 and the control device 10 shown in FIG. 1 are replaced with a communication device 38 (notification unit) and the control device 30, respectively. The configuration other than these is the same, and thus the description will not be repeated. As shown in FIG. 17, the communication device 38 is connected to an external display device 1000 via, for example, the Internet.

FIG. 18 shows a flow of processing performed by the control device 30 of FIG. 17 to determine whether or not the amount of non-azeotropic mixed refrigerant charged is insufficient for the amount of refrigerant necessary to maintain a desired cooling capacity. It is a flowchart for explaining. The process illustrated in FIG. 18 is a process in which S213 of the process illustrated in FIG. 15 is replaced with S313.

As shown in FIG. 18, the control device 30 calculates the receiver volume ratio R1 in S211 and determines whether the condition (specific condition) that the receiver volume ratio R1 is larger than Rc is satisfied in S212. When receiver volume ratio R1 is larger than Rc (YES in S212), control device 30 transmits information indicating that the cooling capacity is reduced in S313 to external display device 1000, and returns the process to the main routine. . When receiver volume ratio R1 is equal to or smaller than Rc (NO in S212), control device 30 returns the process to the main routine.

Note that S103 in FIG. 7, S103A and S104 in FIG. 8, S202 and S203 in FIG. 13, S213 in FIG. 15, and S223 in FIG. It can be replaced by a transmission process to the device.

As described above, according to the refrigeration cycle apparatus according to Embodiment 3, it is possible to suppress the manufacturing cost of the refrigeration cycle apparatus that determines whether or not the amount of the non-azeotropic mixed refrigerant is insufficient. Further, according to the refrigeration cycle apparatus according to Embodiment 3, the user can be informed of the shortage of the amount of the non-azeotropic mixed refrigerant by receiving the notification from the maintenance manager at a remote location. .

各 The embodiments and modifications disclosed this time are also expected to be implemented in appropriate combinations within a consistent range. It should be understood that the embodiments and modifications disclosed herein are illustrative in all respects 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.

1,1B compressor, 2 condenser, 3 receiver, 4 expansion valve, 5 evaporator, 6 heat exchanger, 7 capillary tube, 8,1000 display, 9, 9B to 9D bypass flow path, FP1, FP2 flow path , 10, 30 control device, 11 storage unit, 38 communication device, 100, 100B to 100D, 300 refrigeration cycle device, 101 temperature sensor, 102 pressure sensor, N1, N2, N2B, N2C end, Pinj injection port.

Claims

A non-azeotropic mixed refrigerant is a refrigeration cycle device that circulates in the order of a compressor, a first heat exchanger, a refrigerant container, a first pressure reducing device, and a second heat exchanger,
A bypass flow for joining a part of the non-azeotropic mixed refrigerant in the refrigerant container to the non-azeotropic mixed refrigerant flowing between the first pressure reducing device and the discharge port of the compressor in a gas-liquid two-phase state; Road and
The reporting department,
When a specific condition indicating that the amount of the non-azeotropic mixed refrigerant charged in the refrigeration cycle device is insufficient is satisfied, a control device that outputs specific information from the notification unit,
The bypass flow path includes a third heat exchanger and a second pressure reducing device connected in series between a first end and a second end of the bypass flow path,
The first end is disposed in the refrigerant container,
The third heat exchanger cools the non-azeotropic mixed refrigerant,
The control device is configured to use the relationship between the ratio of the volume of the refrigerant container to the amount of the non-azeotropic mixed refrigerant enclosed, the pressure of the non-azeotropic mixed refrigerant flowing out from the second end, and the temperature to determine the specific condition. A refrigeration cycle device that determines the success or failure of
The specific condition includes a condition that a difference between a reference temperature and a temperature of the non-azeotropic mixed refrigerant flowing out from the second end is larger than a threshold value,
The said reference temperature is the minimum value of the temperature of the said non-azeotropic mixed refrigerant which flows out from the said 2nd end when the said 1st end part is immersed in the said non-azeotropic mixed refrigerant. 2. The refrigeration cycle apparatus according to 1.
2. The refrigeration cycle apparatus according to claim 1, wherein the specific condition includes a condition that a difference between a ratio of a volume of the refrigerant container to a charged amount of the non-azeotropic mixed refrigerant and a reference value is larger than a threshold value.
The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein the second end is connected to a flow path between the second heat exchanger and a suction port of the compressor.
(4) The refrigeration cycle apparatus according to any one of (1) to (3), wherein the second end is connected to a flow path between the first decompression device and the second heat exchanger.
(4) The refrigeration cycle apparatus according to any one of (1) to (3), wherein the compressor has an injection port to which the second end is connected.
The device according to any one of claims 1 to 6, wherein the third heat exchanger and the second pressure reducing device are connected in series in this order between the first end and the second end. Refrigeration cycle equipment.
The notification unit includes a communication device,
The refrigeration system according to any one of claims 1 to 7, wherein when the specific condition is satisfied, the control device transmits the specific information to a display device external to the refrigeration cycle device via the communication device. Cycle equipment.