WO2022224382A1

WO2022224382A1 - Binary refrigeration cycle device

Info

Publication number: WO2022224382A1
Application number: PCT/JP2021/016203
Authority: WO
Inventors: 拓未西山; 智隆石川
Original assignee: 三菱電機株式会社
Priority date: 2021-04-21
Filing date: 2021-04-21
Publication date: 2022-10-27
Also published as: CN117222853A; JP7471515B2; EP4328522A1; JPWO2022224382A1

Abstract

This binary refrigeration cycle device (51) comprises a first high-temperature refrigerant circuit (100) for circulating a first refrigerant, a second high-temperature refrigerant circuit (200) for circulating a second refrigerant, a low-temperature refrigerant circuit (300) for circulating a third refrigerant, a first cascade capacitor (104), and a second cascade capacitor (204). The first high-temperature refrigerant circuit (100) has a first compressor (101), a first heat exchanger (102), and a first expansion valve (103). The second high-temperature refrigerant circuit (200) has a second compressor (201), a second heat exchanger (202), and a second expansion valve (203). The first high-temperature refrigerant circuit (100) and the second high-temperature refrigerant circuit (200) are configured to have mutually different maximum cooling capabilities.

Description

Binary refrigeration cycle device

The present disclosure relates to a dual refrigeration cycle device.

A dual refrigeration cycle device has been known for some time. Patent Literature 1 describes a dual refrigerating cycle apparatus having a first higher refrigerating cycle, a second higher refrigerating cycle, and a lower refrigerating cycle.

International Publication No. 2012/066763

　When multiple refrigeration cycles are configured on the high-level refrigeration cycle side, it is desirable that the multiple high-level refrigeration cycles can realize flexible operation according to changes in the cooling capacity required for the load.

An object of the present disclosure is to provide a binary refrigerating cycle device capable of realizing flexible operation with a plurality of high-order refrigerating cycles according to changes in cooling capacity required for the load.

The binary refrigeration cycle device of the present disclosure includes a first high-order refrigerant circuit that circulates a first refrigerant, a second high-order refrigerant circuit that circulates a second refrigerant, a low-order refrigerant circuit that circulates a third refrigerant, A first cascade condenser that exchanges heat between the first refrigerant and the third refrigerant, and a second cascade condenser that exchanges heat between the second refrigerant and the third refrigerant. The first high-level refrigerant circuit has a first compressor, a first heat exchanger, and a first expansion valve, and comprises the first compressor, the first heat exchanger, the first expansion valve, and the first cascade condenser. , and the first compressor in order. The second high-level refrigerant circuit has a second compressor, a second heat exchanger, and a second expansion valve, and comprises the second compressor, the second heat exchanger, the second expansion valve, and the second cascade condenser. , and the second compressor in this order. The low-voltage refrigerant circuit has a third compressor, a third heat exchanger, and a third expansion valve, the third compressor, the first cascade condenser, the second cascade condenser, the third expansion valve, the third A third refrigerant is circulated in the order of the heat exchanger and the third compressor. The first high-order refrigerant circuit and the second high-order refrigerant circuit are configured to have different maximum cooling capacities.

According to the present disclosure, it is possible to provide a binary refrigerating cycle device capable of realizing flexible operation with a plurality of high-level refrigerating cycles according to changes in the cooling capacity required for the load.

1 is a diagram showing a configuration of a binary refrigerating cycle apparatus according to Embodiment 1; FIG. FIG. 4 is a diagram showing the arrangement relationship between the liquid receiver and the first and second cascade capacitors; FIG. 4 is a diagram showing a comparative example of configurations of a first high-order refrigerant circuit, a second high-order refrigerant circuit, and a low-order refrigerant circuit; FIG. 4 is a diagram showing Modification 1 of the binary refrigeration cycle apparatus according to Embodiment 1; It is a figure which shows the 5th heat exchanger which integrated the 1st heat exchanger and the 2nd heat exchanger. FIG. 2 is a diagram showing an example in which an uninterruptible power supply is provided in the binary refrigerating cycle apparatus according to Embodiment 1; It is a figure which shows the example which provided the uninterruptible power supply in the binary refrigerating-cycle apparatus of the modification 1. FIG. Fig. 1 is graph 1 showing the relationship between the frequency range and cooling capacity of a first high-order refrigeration cycle and the relationship between the frequency range and cooling capacity of a second high-order refrigeration cycle; Fig. 2 is graph 2 showing the relationship between the frequency range and cooling capacity of the first high-order refrigeration cycle and the relationship between the frequency range and cooling capacity of the second high-order refrigeration cycle; 4 is a flow chart showing the contents of control in an operation mode according to Embodiment 1. FIG. 4 is a flowchart showing the contents of control in a stop operation mode; 4 is a flowchart showing the contents of control in a cooling operation mode; 4 is a graph showing the relationship between the set value of the evaporating temperature inside the refrigerator and the cooling capacity (Embodiment 1). 4 is a flowchart showing details of control in a high capacity operation mode; 4 is a flowchart showing details of control in a low capacity operation mode; FIG. 6 is a diagram showing the configuration of a binary refrigeration cycle apparatus according to Embodiment 2; FIG. 4 is a diagram showing the ratio of the heat transfer area of the first heat exchanger and the second heat exchanger to the heat transfer area of the fourth heat exchanger; It is a figure which shows the 6th heat exchanger which integrated the 1st heat exchanger, the 2nd heat exchanger, and the 4th heat exchanger. It is a figure which shows the 1st heat exchanger used in combination with the 7th heat exchanger which integrated the 2nd heat exchanger and the 4th heat exchanger, and the 7th heat exchanger. 9 is a flow chart showing details of control in an operation mode according to Embodiment 2. FIG. 9 is a flowchart showing the contents of control in cooling operation mode 2 according to Embodiment 2. FIG. 9 is a graph showing the relationship between the set value of the evaporating temperature inside the refrigerator and the cooling capacity (Embodiment 2). 9 is a graph showing the relationship between the frequency of the third compressor (Comp301) and the set value of the evaporating temperature inside the refrigerator (Embodiment 2). 9 is a flow chart showing a modification of cooling operation mode 2 according to Embodiment 2. FIG.

Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings. A plurality of embodiments will be described below, and it is planned from the time of filing to appropriately combine the configurations described in the respective embodiments. The same or corresponding parts in the drawings are denoted by the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.
FIG. 1 is a diagram showing the configuration of a binary refrigeration cycle device 51 according to Embodiment 1. As shown in FIG. Based on FIG. 1, the circuit configuration and operation of the binary refrigeration cycle device 51 will be described. The binary refrigeration cycle device 51 includes a low-order refrigerant circuit 300 , a first high-order refrigerant circuit 100 , a second high-order refrigerant circuit 200 , and a control device 30 .

The first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200 are arranged in the outdoor unit 1 . The low-concentration refrigerant circuit 300 is arranged across the outdoor unit 1 and the indoor unit 2 by the extension pipe 15 . The control device 30 is arranged in the outdoor unit 1 or the indoor unit 2 . The outdoor unit 1 is provided with a temperature sensor 20 that detects the outside air temperature. The control device 30 may be arranged at a location other than the outdoor unit 1 and the indoor unit 2 . The control device 30 may wirelessly communicate with a remote controller operated by a user.

A first refrigerant is sealed in the first high-level refrigerant circuit 100 . A second refrigerant is sealed in the second high-level refrigerant circuit 200 . A third refrigerant is sealed in the low-concentration refrigerant circuit 300 . The outdoor unit 1 includes a first cascade condenser 104 for exchanging heat between the first refrigerant of the first high-order refrigerant circuit 100 and the third refrigerant of the low-order refrigerant circuit 300, and a second high-order refrigerant circuit. A second cascade condenser 204 is provided for exchanging heat between the second refrigerant of 200 and the third refrigerant of the lower refrigerant circuit 300 .

The first cascade capacitor 104 may be included in the first high-order refrigerant circuit 100 or may be included in the low-order refrigerant circuit 300 . The second cascade condenser 204 may be included in the second high-order refrigerant circuit 200 or may be included in the low-order refrigerant circuit 300 .
<Configuration of first high-level refrigerant circuit 100>
The first high-level refrigerant circuit 100 includes a first compressor 101 , a first heat exchanger 102 and a first expansion valve 103 . The first compressor 101, the first heat exchanger 102, and the first expansion valve 103 are connected by a refrigerant pipe through which the first refrigerant flows. The first heat exchanger 102 is provided with a first fan 1021 that facilitates heat exchange between the outside air and the first refrigerant. The first high-level refrigerant circuit 100 is configured such that the first refrigerant circulates through the first compressor 101, the first heat exchanger 102, the first expansion valve 103, the first cascade condenser 104, and the first compressor 101 in this order. configured to Therefore, the first heat exchanger 102 functions as a condenser. A microcomputer that operates in response to a command from the control device 30 is installed in the first high-level refrigerant circuit 100 . When the control device 30 activates the first high-order refrigerant circuit 100, the first high-order refrigeration cycle is started.
<Configuration of Second Higher Element Refrigerant Circuit 200>
The second high-level refrigerant circuit 200 includes a second compressor 201 , a second heat exchanger 202 and a second expansion valve 203 . The second compressor 201, the second heat exchanger 202, and the second expansion valve 203 are connected by a refrigerant pipe through which the second refrigerant flows. The second heat exchanger 202 is provided with a second fan 2021 that promotes heat exchange between the outside air and the second refrigerant. The second high-level refrigerant circuit 200 is configured such that the second refrigerant circulates through the second compressor 201, the second heat exchanger 202, the second expansion valve 203, the second cascade condenser 204, and the second compressor 201 in that order. configured to Therefore, the second heat exchanger 202 functions as a condenser. The second high-level refrigerant circuit 200 is equipped with a microcomputer that operates in response to commands from the control device 30 . The control device 30 activates the second high-order refrigerant circuit 200 to activate the second high-order refrigeration cycle.

In the present embodiment, first high-level refrigerant circuit 100 and second high-level refrigerant circuit 200 are configured to have different maximum cooling capacities. In particular, the second compressor 201, the second heat exchanger 202, the second expansion circuit 201, the second heat exchanger 202, and the second expansion circuit 201 are arranged so that the maximum cooling capacity of the second high-order refrigerant circuit 200 is lower than the maximum cooling capacity of the first high-order refrigerant circuit 100. At least one component of the valve 203 and the second cascade condenser 204 is connected to the first compressor 101 , the first heat exchanger 102 , the first expansion valve 103 and the first cascade condenser 104 of the first higher order refrigerant circuit 100 . are made up of smaller components than the corresponding components of
<Configuration of low-concentration refrigerant circuit 300>
The low energy refrigerant circuit 300 includes a third compressor 301 , a third heat exchanger 302 , a third expansion valve 303 and a liquid receiver 304 . The third heat exchanger 302 and the third expansion valve 303 are arranged in the indoor unit 2 . The liquid receiver 304 is arranged in the outdoor unit 1 . The third compressor 301, the third heat exchanger 302, the third expansion valve 303, and the receiver 304 are connected by refrigerant pipes through which the third refrigerant flows. The third heat exchanger 302 is provided with a third fan 3021 that promotes heat exchange between the air inside the storage and the third refrigerant.

In the low-voltage refrigerant circuit 300, the third refrigerant is a third compressor 301, a first cascade condenser 104, a second cascade condenser 204, a liquid receiver 304, a third expansion valve 303, a third heat exchanger 302, and a third refrigerant. The three compressors 301 are configured to circulate in order. Therefore, the third heat exchanger 302 functions as an evaporator that cools the inside of the refrigerator. A microcomputer that operates in response to commands from the control device 30 is installed in the low-concentration refrigerant circuit 300 . When the control device 30 activates the low-concentration refrigerant circuit 300, the low-concentration refrigeration cycle is activated.

A pressure sensor 10 is provided in the refrigerant pipe located on the discharge side of the third compressor 301 . The pressure sensor 10 may be provided at any position in the section from the discharge port of the third compressor 301 to the inlet of the first cascade condenser 104 . However, it is preferable to provide the pressure sensor 10 at the discharge portion of the third compressor 301 . This is because the pressure of the third refrigerant becomes highest at the discharge portion of the third compressor 301 . The third compressor 301 circulates the third refrigerant in the low-concentration refrigerant circuit 300 by increasing the pressure of the third refrigerant. The third compressor 301 changes its operating capacity according to the situation by controlling a motor (not shown) inside the third compressor 301 with an inverter. The third compressor 301 controls the frequency of the third compressor 301 so that the temperature of the third refrigerant reaches the target outlet temperature set by the control device 30 .

The third expansion valve 303 adjusts the flow rate of the third refrigerant. Third expansion valve 303 is, for example, an electronic expansion valve or a capillary. The electronic expansion valve has a function of efficiently controlling the flow rate of the third refrigerant by adjusting the throttle opening.

The liquid receiver 304 stores high-pressure liquid refrigerant. The liquid receiver 304 is arranged between the second cascade condenser 204 and the third expansion valve 303 in the low-concentration refrigerant circuit 300 . In other words, the liquid receiver 304 is arranged downstream of the first cascade condenser 104 and the second cascade condenser 204 and upstream of the third expansion valve 303 .

The liquid receiver 304 and the second cascade condenser 204 are connected by the first refrigerant pipe 16 . The liquid receiver 304 and the third expansion valve 303 are connected by the second refrigerant pipe 17 and the extension pipe 15 . The first refrigerant pipe 16 is connected to the upper portion of the liquid receiver 304 . The second refrigerant pipe 17 is connected to the lower portion of the liquid receiver 304 . A return refrigerant pipe 18 is further connected to the upper portion of the liquid receiver 304 . The return refrigerant pipe 18 connects the refrigerant pipe positioned between the first cascade condenser 104 and the second cascade condenser 204 and the liquid receiver 304 . The return refrigerant pipe 18 is provided with a check valve 305 that prevents the first refrigerant from flowing into the liquid receiver 304 from the first cascade condenser 104 or the second cascade condenser 204 through the return refrigerant pipe 18 .

<Configuration of control device 30>
The control device 30 is equipped with a processor 31 and a memory 32 . Processor 31 executes an operating system and application programs stored in memory 32 . The processor 31 refers to various data stored in the memory 32 when executing the application program. Processor 31 collects data indicating operating conditions from first high-order refrigerant circuit 100 , second high-order refrigerant circuit 200 , and low-order refrigerant circuit 300 according to an application program stored in memory 32 .

The processor 31 acquires the pressure of the third refrigerant based on the detection value of the pressure sensor 10. The processor 31 acquires the outside air temperature based on the detection value of the temperature sensor 20 . Processor 31 controls first high-order refrigerant circuit 100 , second high-order refrigerant circuit 200 , and low-order refrigerant circuit 300 according to application programs stored in memory 32 .

The control device 30 can switch the operation mode between the cooling operation mode and the stop operation mode. The cooling operation mode is an operation mode for cooling the inside of the refrigerator where the third heat exchanger 302 is arranged. In the cooling operation mode, the low temperature refrigerant circuit 300 and the second high temperature refrigerant circuit 200 operate. In the cooling operation mode, the first high-order refrigerant circuit 100 may further operate depending on the operating conditions of the low-order refrigerant circuit 300 and the second high-order refrigerant circuit 200 .

The stop operation mode is an operation mode used when the inside of the refrigerator is not cooled. In the stop operation mode, the operation of the low-concentration refrigerant circuit 300 is stopped. In the stop operation mode, the second high-voltage refrigerant circuit 200 operates to prevent the pressure in the low-voltage refrigerant circuit 300 from abnormally increasing. In the stop operation mode, the first high-voltage refrigerant circuit 100 may be operated further.

The control device 30 can independently control the first high-order refrigerant circuit 100, the second high-order refrigerant circuit 200, and the low-order refrigerant circuit 300 in the cooling operation mode.

The control device 30 can select either the low-capacity operation mode or the high-capacity operation mode in the cooling operation mode. The low capacity operation mode is a mode in which the first high-level refrigerant circuit 100 is stopped and the low-level refrigerant circuit 300 and the second high-level refrigerant circuit 200 are operated. The high-capacity operation mode is a mode in which the first high-order refrigerant circuit 100, the second high-order refrigerant circuit 200, and the low-order refrigerant circuit 300 are operated.

The control device 30 is configured to be able to select an operation mode in which only the low-level refrigerant circuit 300 is operated among the first high-level refrigerant circuit 100, the second high-level refrigerant circuit 200, and the low-level refrigerant circuit 300. good too.

<Operation of first high-order refrigerant circuit 100 and second high-order refrigerant circuit 200>
The operation of the first high-level refrigerant circuit 100 will be described. The high-temperature and high-pressure gaseous first refrigerant discharged from the first compressor 101 flows into the first heat exchanger 102 functioning as a condenser. The first refrigerant changes from a gas state refrigerant to a liquid state refrigerant in the first heat exchanger 102 . The first refrigerant that has flowed out of the first heat exchanger 102 flows into the first expansion valve 103 and is decompressed. As a result, the liquid state first refrigerant changes to a low-pressure two-phase refrigerant. A low-pressure two-phase refrigerant flows from the first expansion valve 103 into the first cascade condenser 104 . The first refrigerant flowing into the first cascade condenser 104 takes heat from the third refrigerant flowing through the low-concentration refrigerant circuit 300 . As a result, the third refrigerant is condensed and the first refrigerant is gasified. The gasified first refrigerant is sucked into the first compressor 101 .

The operation of the second high-level refrigerant circuit 200 is the same as the operation of the first high-level refrigerant circuit 100, so the description thereof will not be repeated here. The difference between the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 is the maximum cooling capacity. In other words, the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 have different capacities to condense the third refrigerant flowing through the low-order refrigerant circuit 300 . The second higher order refrigerant circuit 200 is designed to be less capable of condensing the third refrigerant than the first higher order refrigerant circuit 100 .

<Operation of low-concentration refrigerant circuit 300>
The operation of the low-concentration refrigerant circuit 300 will be described. The high-temperature and high-pressure gaseous third refrigerant discharged from the third compressor 301 flows to the first cascade condenser 104 and the second cascade condenser 204 . When the first high-order refrigerant circuit 100 is operating, the first cascade condenser 104 functions as a condenser for the third refrigerant. When the second higher order refrigerant circuit 200 is operating, the second cascade condenser 204 functions as a condenser for the third refrigerant. The third refrigerant thereby changes from a gas state refrigerant to a liquid state refrigerant. The third refrigerant that has flowed out of the second cascade condenser 204 flows into the liquid receiver 304 . The liquid state third refrigerant accumulated in the liquid receiver 304 is pushed out to the second refrigerant pipe 17 by the gas pressure in the liquid receiver 304 . The third refrigerant flowing into the second refrigerant pipe 17 goes to the third expansion valve 303 via the extension pipe 15 .

The pressure of the third refrigerant that has flowed into the third expansion valve 303 is reduced by the third expansion valve 303 . As a result, the liquid third refrigerant changes to a low-pressure two-phase refrigerant. Low pressure two-phase refrigerant moves from the third expansion valve 303 to the third heat exchanger 302 . At this time, the third heat exchanger 302 functions as an evaporator. The third refrigerant that has flowed into the third heat exchanger 302 exchanges heat with the air inside the refrigerator. This cools the inside of the refrigerator. The third refrigerant gasified inside the third heat exchanger 302 is sucked into the third compressor 301 .

The control device 30 adjusts the frequency of the third compressor 301 and the rotation speed of the third fan 3021 based on various parameters. Parameters can include, for example, intake temperature, discharge temperature, heat exchanger temperature, air intake temperature, and humidity. The control device 30 can acquire these parameters using the values of sensors arranged in the low-concentration refrigerant circuit 300 .

For example, a temperature sensor may be provided at the discharge portion of the third compressor 301 to detect the discharge temperature of the third refrigerant. The control device 30 sends a control signal to the low-concentration refrigerant circuit 300 based on the temperature difference between the detection result of the temperature sensor and the preset discharge temperature of the third compressor 301 . The low-concentration refrigerant circuit 300 adjusts the rotation speed of the third compressor 301, the rotation speed of the third fan 3021, or the opening degree of the third expansion valve 303 based on the control signal. By this adjustment, the control device 30 can control the temperature of various devices provided in the low-concentration refrigerant circuit 300 so as not to rise above the heat-resistant temperature.

From the viewpoint of accuracy, it is desirable to directly detect various parameters by sensors. However, some of those parameters can also be estimated by computation without using sensors. For example, the condensation temperature (CT) may be estimated from the detected value of the pressure sensor 10 .

FIG. 2 is a diagram showing the arrangement relationship between the liquid receiver 304 and the first cascade capacitor 104 and the second cascade capacitor 204. FIG. As shown in FIG. 2, the liquid receiver 304 is arranged at a position lower than the first cascade capacitor 104 and the second cascade capacitor 204 in the vertical direction. Therefore, even when the low-concentration refrigerant circuit 300 is not activated, the third refrigerant cooled and liquefied by the first cascade condenser 104 or the second cascade condenser 204 falls to the liquid receiver 304 due to gravity. This is especially effective in the stop operation mode that controls when the low-order refrigerating cycle is not activated. The operation of the stop operation mode will be described in detail below with reference to FIGS. 1 and 2. FIG.

<Operation in stop operation mode>
The control device 30 activates the high-order refrigeration cycle when the low-order refrigeration cycle is stopped. Such an operation mode is called a stop operation mode. By operating the binary refrigerating cycle device 51 in the stop operation mode, the control device 30 prevents the pressure increase due to the temperature increase of the third refrigerant staying in the low temperature refrigerant circuit 300 . The control device 30 activates the high-level refrigeration cycle when the outside air temperature becomes equal to or higher than the reference temperature while the low-level refrigeration cycle is stopped. The reference temperature is, for example, -5°C.

When the low-level refrigeration cycle is stopped, the pressure in the low-level refrigerant circuit 300 is equalized, and eventually the pressure becomes the pressure corresponding to the outside air temperature. When the amount of the third refrigerant enclosed with respect to the internal volume of the low-concentration refrigerant circuit 300 is small, the average density of the third refrigerant is small. Therefore, the pressure decreases according to Boyle-Charles' law (P∝ρ×T). However, when the average density of the third refrigerant is high, the pressure inside the low-concentration refrigerant circuit 300 increases.

If the outside air temperature is high when the low-level refrigeration cycle is stopped, the third refrigerant in the low-level refrigerant circuit 300 evaporates by absorbing heat from the outside air. This increases the pressure in the low-concentration refrigerant circuit 300 . In a typical refrigeration cycle, not all of the refrigerant becomes liquid or gas relative to the internal volume, so if the pressure is uniform, the pressure depends on the relationship between pressure and temperature based on the type of refrigerant. becomes. For example, if the refrigerant is CO2 (carbon dioxide) and the temperature is 20° C., the pressure is 5.6 MPaG.

The third refrigerant can be forcibly cooled by activating the high-level refrigeration cycle when the low-level refrigeration cycle is stopped. As a result, the temperature of the third coolant is lower than the outside air. Then, the pressure of the third refrigerant in the low-concentration refrigerant circuit 300 decreases.

The high-level refrigeration cycle activated by the control device 30 in the stop operation mode is the second high-level refrigeration cycle. The control device 30 controls the frequency of the second compressor 201 of the second high-order refrigerating cycle, the rotation speed of the second fan 2021, and the degree of opening of the second expansion valve 203 . If the abnormal rise in pressure in the low-order refrigerant circuit 300 cannot be suppressed only by starting the second high-order refrigeration cycle, the control device 30 starts the first high-order refrigeration cycle with higher condensing capacity. may

In the stop operation mode, by activating the second high-order refrigerating cycle, the second cascade condenser 204 existing between the second high-order refrigerant circuit 200 and the low-order refrigerant circuit 300 becomes a condenser for the third refrigerant. function as As a result, the third refrigerant in the second cascade condenser 204 is condensed. The third refrigerant condensed by the second cascade condenser 204 is liquefied. The liquefied third refrigerant passes through the first refrigerant pipe 16 and drips into the liquid receiver 304 . At this time, as shown in FIG. 2, there is a difference in height between the second cascade condenser 204 and the liquid receiver 304 in the vertical direction, so the third refrigerant falls to the liquid receiver 304 due to its own weight.

As the liquid third refrigerant drips into the liquid receiver 304, the volume of the gas phase decreases. The gaseous third refrigerant, which is not easily affected by gravity, is sucked up to the upstream side of the second cascade condenser 204 via the return refrigerant pipe 18 .

As shown in FIG. 2, the return refrigerant pipe 18 is connected to the upper part of the liquid receiver 304, so that the third refrigerant existing above the liquid receiver 304 can be naturally sucked. Also, the check valve 305 prevents the third refrigerant, which should flow from the first cascade condenser 104 to the second cascade condenser 204 , from flowing into the liquid receiver 304 via the return refrigerant pipe 18 . In particular, in the cooling operation mode, it is possible to prevent the third refrigerant from bypassing the second cascade condenser 204 and flowing into the liquid receiver 304 .

The vaporous third refrigerant sucked up to the upstream side of the second cascade condenser 204 is cooled by the second cascade condenser 204 and liquefied. The liquefied third refrigerant drips into the liquid receiver 304 . In the stop operation mode, the low-concentration refrigeration cycle is not activated, but the third refrigerant flows through the low-concentration refrigerant circuit 300 due to such natural circulation.

By repeating the natural circulation of the third refrigerant in this manner, the pressure rise in the low-concentration refrigerant circuit 300 can be effectively suppressed. Further, only the gas to be condensed can be allowed to flow through the return refrigerant pipe 18 in order to suppress the pressure from rising. Furthermore, by providing the second cascade condenser 204 , the liquid third refrigerant can be stored in the liquid receiver 304 without directly cooling the liquid receiver 304 .

Both the first cascade condenser 104 and the second cascade condenser 204 function as condensers for the third refrigerant and cool the third refrigerant before it flows into the liquid receiver 304 . Therefore, it is not necessary to provide the liquid receiver 304 with a cooling function. The first cascade capacitor 104 and the second cascade capacitor 204 exhibit a cooling function even in the cooling operation mode. Therefore, the configuration of the liquid receiver 304 can be simplified compared to a configuration in which the liquid receiver 304 is provided with the function of cooling the third refrigerant during the cooling operation. This is because the liquid receiver 304 requires an evaporator when the third refrigerant is cooled in the liquid receiver 304 . If an evaporator is provided in the liquid receiver 304, the volume of the liquid receiver 304 must be reduced. Further, when a heat transfer tube is provided around the container of the liquid receiver 304, there arises a problem that the contact portion is easily deteriorated due to thermal fatigue, and furthermore, the container has a complicated structure. According to this embodiment, the configuration of the liquid receiver 304 can be simplified, and the manufacturing cost can be reduced.

The binary refrigeration cycle device 51 according to the first embodiment activates at least the second high-order refrigeration cycle even when the low-order refrigeration cycle is stopped, and the second cascade condenser 204 supplies the low-order refrigerant circuit 300 with Cool the remaining third refrigerant. At this time, by circulating the third refrigerant in the low-concentration refrigerant circuit 300, it is possible to effectively suppress the pressure increase due to the temperature increase of the third refrigerant. This eliminates the need to set the design pressures of various devices such as the third compressor 301, the third heat exchanger 302, the third expansion valve 303, the liquid receiver 304, and the refrigerant pipes to high values. As a result, it is possible to reduce the cost of the equipment that constitutes the low-concentration refrigerant circuit 300 .

<Comparison of refrigerant circuits>
FIG. 3 is a diagram showing a comparative example of configurations of the first high-order refrigerant circuit 100, the second high-order refrigerant circuit 200, and the low-order refrigerant circuit 300. As shown in FIG. In the present embodiment, first high-level refrigerant circuit 100 and second high-level refrigerant circuit 200 are configured to have different maximum cooling capacities. More specifically, the cooling capacity of the second high-order refrigerant circuit 200 is configured to be lower than the cooling capacity of the first high-order refrigerant circuit 100 . In FIG. 3, numerical values relating to the capacity of the low-concentration refrigerant circuit 300 are omitted.

FIG. 3 shows an example in which the rated capacity of the first high-level refrigerant circuit 100 is 41 kW and the rated capacity of the second high-level refrigerant circuit 200 is 10 kW. In this case, the high-side capacity (cooling capacity) is calculated as 51 kW by adding 41 kW and 10 kW. The ratio of the rated capacity of the second higher-order refrigerant circuit 200 to 51 kW is approximately 20% as shown in FIG.

As shown in FIG. 3 , the maximum cooling capacity of the second high-level refrigerant circuit 200 should be less than 50% of the maximum cooling capacity of the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200 . That is, the upper limit of the cooling capacity of the second high-order refrigerant circuit 200 may be less than 50% of the upper limit of the cooling capacity of the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 . The upper limit of the cooling capacity of the second high-order refrigerant circuit 200 is preferably 35% or less of the upper limit of the cooling capacity of the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 . Furthermore, the upper limit of the cooling capacity of the second high-order refrigerant circuit 200 is more preferably 20% or less of the upper limit of the cooling capacity of the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 .

Thus, in order to provide a difference in cooling capacity between the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200, the second compressor 201 of the second high-level refrigerant circuit 200, the second heat At least one component of the exchanger 202 , the second expansion valve 203 and the second cascade condenser 204 is connected to the first compressor 101 , the first heat exchanger 102 and the first expansion of the first high-level refrigerant circuit 100 . The valve 103 and first cascade capacitor 104 may be configured with components having a smaller capacity than the corresponding components.

The size of the compressor has the greatest impact on the cost and cooling capacity of the refrigerant circuit. Therefore, by configuring the second compressor 201 with a compact compressor having a smaller capacity than the first compressor 101, the cooling capacity between the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200 is increased. It is desirable to have a difference. By downsizing the second compressor 201, the cost of the second high-order refrigerant circuit 200 can also be reduced. By miniaturizing the second compressor 201, the material costs required for the second compressor 201 can be reduced. Moreover, since the volume of the second compressor 201 is reduced, the amount of refrigerant required for the second high-order refrigerant circuit 200 can be reduced.

By allocating the cost saved by downsizing the second compressor 201 to the first compressor 101, the performance of the first compressor 101 may be improved. For example, in the present embodiment, second compressor 201 is composed of a compact compressor having a smaller capacity than first compressor 101 . Also, in the present embodiment, the refrigerant capacity of the second high-order refrigerant circuit 200 is smaller than that of the first high-order refrigerant circuit 100 .

As shown in FIG. 3, when the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200 are compared in terms of lower limit capacity, the lower limit capacity of the first high-level refrigerant circuit 100 is 10 kW, and the second high-level refrigerant circuit 100 has a lower limit capacity of 10 kW. The lower limit capability of circuit 200 is 2.5 kW. Here, it is assumed that the lower limit capacity is 25% of the rated capacity from the frequency range of the compressor.

By differentiating the rated capacities of the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200, it is possible to finely operate the high-order refrigeration cycle according to the operating conditions. That is, in the present embodiment, the high-level refrigerating cycle is composed of a first high-level refrigerating cycle and a second high-level refrigerating cycle, and by providing a difference in the capacity of each cycle, the operating range is expanded. ing. Differentiating the rated capacity between the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 is effective both in the cooling operation mode and the stop operation mode.

When cooling the inside of the refrigerator, the control device 30 selects between the low-capacity operation mode and the high-capacity operation mode according to environmental conditions such as the set temperature in the refrigerator where the third heat exchanger 302 is arranged and the outside air temperature. Select one of the cooling operation modes.

The control device 30 activates the second high-level refrigerant circuit 200 having a lower cooling capacity than the first high-level refrigerant circuit 100 in the stop operation mode. In the stop mode of operation, the cooling load is usually smaller than in the cooling mode of operation. This is because the purpose of the cooling operation mode is to cool the inside of the refrigerator, while the purpose of the stop operation mode is to suppress an abnormal increase in pressure in the low-concentration refrigerant circuit 300 . In the stop operation mode in which the cooling load is small, if the higher capacity refrigerating cycle is started, the compressor on the higher refrigerating cycle side is frequently started and stopped.

Here, consider the case where the high-level refrigeration cycle is composed of a single refrigeration cycle. Assume that the rated capacity of a single high-order refrigeration cycle is 51 kW. The value of 51 kW is the sum of the rated capacity of the first high-level refrigerant circuit 100 and the rated capacity of the second high-level refrigerant circuit 200 shown in FIG.

Assuming that about 25% of the required cooling capacity is the lower limit of the operating range of the compressor on the high-level refrigeration cycle side, if the rated capacity is 51 kW, the lower limit capacity is 13 kW. A value of 13 kW may be too large for the cooling capacity required for the shutdown mode of operation. In this case, the capacity of the high-order refrigeration cycle is too large for the required cooling capacity, so the suction pressure of the compressor of the high-order refrigeration cycle drops. As a result, the compressor will repeat starting and stopping, which may reduce the reliability of the binary refrigeration cycle apparatus. Moreover, since the excessive cooling operation is continued in the stop operation mode, power consumption may increase.

Therefore, in the present embodiment, two cycles form a high-level refrigeration cycle. As shown in FIG. 3, the operating range of 2.5 kW to 51 kW is ensured by dividing the capacity of the high-level refrigeration cycle into two. The operating capacity of 2.5 kW, which is the lower limit, can be realized by the second high-voltage refrigerant circuit 200 . The upper limit of the operating capacity of 51 kW can be realized by the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 .

In the stop operation mode, the second high-level refrigerant circuit 200 is activated. This prevents the compressor of the high-level refrigeration cycle from repeatedly starting and stopping in the stop operation mode. Of course, not only in the stop operation mode, but also in the cooling operation mode, the high-level refrigeration cycle side can demonstrate appropriate capacity according to needs, so the compressor of the high-level refrigeration cycle is prevented from repeatedly starting and stopping. be done. That is, in the present embodiment, the high-level refrigerating cycle is composed of a first high-level refrigerating cycle and a second high-level refrigerating cycle, and by providing a difference in the capacity of each cycle, the operating range is expanded. ing. It should be noted that the required cooling capacity in the stop operation mode is assumed to be approximately 1 kW to 4 kW, for example.

According to the present embodiment, it is possible to prevent the first compressor 101 and the second compressor 201 on the high-level refrigerating cycle side from repeatedly starting and stopping. Therefore, energy saving can be improved. In particular, it is important that the compressor does not repeatedly start and stop because starting loss occurs when the compressor starts.

<Refrigerant type>
Various combinations of refrigerant types to be sealed in the low-order refrigerant circuit 300, the first high-order refrigerant circuit 100, and the second high-order refrigerant circuit 200 can be determined. The refrigerant in each refrigerant circuit may be the same refrigerant. Further, the same refrigerant is sealed in the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200, and is sealed in the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 in the low-order refrigerant circuit 300. A refrigerant different from the refrigerant may be used.

In general, refrigerants differ in theoretical performance, GWP (Global-warming potential), combustibility, toxicity, etc., depending on the type. For example, refrigerants such as R290 and R32 have high theoretical performance, but high combustibility, toxicity, and global-warming potential (GWP). Therefore, considering flammability, toxicity, and GWP, it should be avoided to enclose a large amount of these refrigerants in the refrigerant circuit. On the other hand, R1234yf and the like have a low ozone depletion potential and a low global warming potential, and are considered to be extremely environmentally friendly refrigerants. Natural refrigerants such as CO2 have the advantage of significantly reducing the total GWP of equipment. Furthermore, incombustible gas such as CO2 is desirably used in the indoor unit in consideration of possible refrigerant leakage.

Therefore, it is preferable to select an appropriate refrigerant in consideration of the characteristics of the refrigerant and the characteristics of the refrigerant circuit that encloses the refrigerant. Specifically, the type of refrigerant is determined whether the refrigerant circuit to be enclosed is the low-level refrigerant circuit 300 passing through the indoor unit 2, or the first high-level refrigerant circuit 100 or the second high-level refrigerant circuit 200 used in the outdoor unit 1. It is conceivable to select from the viewpoint of whether Also, the type of refrigerant can be selected from the viewpoint of whether the refrigerant circuit to be enclosed is the first high-level refrigerant circuit 100 with high cooling performance or the second high-level refrigerant circuit 200 with low cooling performance. Conceivable. In the present embodiment, the refrigerant capacity of the second high-order refrigerant circuit 200 is smaller than that of the first high-order refrigerant circuit 100 .

FIG. 3 shows an example in which different refrigerants are sealed in the first high-order refrigerant circuit 100, the second high-order refrigerant circuit 200, and the low-order refrigerant circuit 300, respectively. Here, an example is shown in which an appropriate refrigerant is selected in consideration of the characteristics of the refrigerant and the characteristics of the refrigerant circuit that encloses the refrigerant.

<Refrigerant for high-level refrigerant circuit>
R1234yf, which is friendly to the global environment, is enclosed in the high-capacity first high-level refrigerant circuit 100, and R32, which has high theoretical performance, is enclosed in the low-capacity second high-level refrigerant circuit 200, respectively. That is, the first refrigerant is R1234yf and the second refrigerant is R32. In addition, the low-concentration refrigerant circuit 300 passing through the indoor unit 2 is filled with CO2, which is a non-combustible gas. That is, the first refrigerant is CO2. R290 or R714 (ammonia) may be sealed in the second high-concentration refrigerant circuit 200 instead of R32. The low-concentration refrigerant circuit 300 may contain hfc1132A instead of CO2.

Refrigerants such as R290 and R32, which have high theoretical performance but are concerned about being filled in large amounts in consideration of combustibility, toxicity, and high GWP, have a refrigerant capacity larger than that of the first high-level refrigerant circuit 100. It is enclosed in a small second high-order refrigerant circuit 200 . In this way, for the second high-order refrigerant circuit 200 having a small capacity, a refrigerant having higher theoretical performance or higher performance in practical use than the refrigerant to be enclosed in the first high-order refrigerant circuit 100 and the low-order refrigerant circuit 300 By enclosing , the COP (Coefficient Of Performance) of the system can be improved.

Supposing that R1234yf, which is extremely environmentally friendly refrigerant, is used for both the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200, the refrigerant in the second high-level refrigerant circuit 200 is R1234yf. It is desirable to change to R290, which has a higher theoretical performance.

As described above, in the present embodiment, a refrigerant such as R32 that has high theoretical performance but does not have high combustibility, toxicity, and GWP is used in the second high-order refrigerant circuit 200 that uses a small amount of refrigerant. . As a result, it is possible to suppress the influence of the disadvantages of the refrigerant on the device. On the other hand, a refrigerant such as R1234yf, which is said to be friendly to the global environment, is used in the first high-level refrigerant circuit 100 that uses a large amount of refrigerant. This improves the COP of the system while suppressing the increase in GWP in the dual refrigeration cycle device that employs a refrigerant such as R32 in both the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200. can be made

Furthermore, according to this embodiment, it is possible to flexibly respond to the regulatory situation of each country. For example, in countries where GWP regulations are loose, R32 and R290 are sealed in the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200, respectively. This makes it possible to aim at maximizing the system COP. On the other hand, in countries with strict GWP regulations, R1234yf is sealed in the first high-order refrigerant circuit 100, and R290 or R32 is sealed in the second high-order refrigerant circuit 200, respectively. As a result, it is possible to improve the system COP while keeping the GWP below the regulation value.

<Refrigerant for low-concentration refrigerant circuit>
FIG. 3 shows an example of enclosing CO2 in the low-concentration refrigerant circuit 300 . Since the third refrigerant in the low-concentration refrigerant circuit 300 flows through the indoor unit 2 , it is preferable to use CO 2 , which is nonflammable and high-pressure refrigerant, as the third refrigerant in the low-concentration refrigerant circuit 300 . Since CO2 is a natural refrigerant, it can significantly reduce the total GWP of equipment.

The dual refrigerating cycle device 51 according to the present embodiment realizes two types of refrigerating cycles, a low-level refrigerating cycle and a high-level refrigerating cycle. Therefore, the condensation pressure on the low temperature side can be reduced in the high temperature refrigeration cycle. Therefore, even if CO2, which is a high-pressure refrigerant, is used in the low-concentration refrigerant circuit 300, the low-concentration refrigerant circuit 300 can be applied with refrigerant pipes and element devices with low pressure resistance. For this reason, it is possible to use element devices that could not be used conventionally in the low-concentration refrigerant circuit 300 .

For example, the liquid receiver 304 only needs to be pressure resistant to Freon (R410A). Similarly, the portion of the first cascade capacitor 104 and the second cascade capacitor 204 through which the low-concentration refrigerant circuit 300 passes should also have pressure resistance against Freon. Since the low-concentration refrigerant circuit 300 is provided with a large number of element devices such as refrigerant pipes, it is possible to reduce costs by reducing the required pressure resistance.

A single-stage refrigeration cycle device or a two-stage refrigeration cycle device requires high pressure resistance, so there is no choice but to use expensive equipment with high pressure resistance. However, in this embodiment, since the dual refrigerating cycle is adopted, such a need is eliminated.

In general, the production volume of CO2 is small, and the pressure resistance standards required when using CO2 as a refrigerant are strict. Therefore, if CO2 is used, the cost tends to be high. The binary refrigerating cycle device 51 according to the present embodiment requires a lower pressure on the side of condensing CO2 than when CO2 is applied to a single-stage refrigerating cycle device or a two-stage refrigerating cycle device. The lower the pressure, the smaller the density of the refrigerant.

Therefore, if the condenser volume is the same, the amount of CO2 required as a refrigerant can be reduced. As a result, according to the present embodiment, it is possible to meet the strict pressure resistance standards required for CO2 and to reduce the cost of CO2. Further, according to the present embodiment, it is possible to use element devices and pipes with low pressure resistance that cannot be used in a single-stage refrigeration cycle apparatus or a two-stage refrigeration cycle apparatus.

As described above, according to the present embodiment, it is possible to operate in a state where the condensing temperature on the low-concentration refrigerant circuit 300 side is reduced, thereby reducing the withstand pressure required for the refrigerant piping of the low-concentration refrigerant circuit 300. can be done. In addition, since separate refrigerating cycles are provided for the high energy side and the low energy side, it is possible to flexibly comply with the regulations of each country regarding the high energy side refrigerant and the low energy side refrigerant.

For example, in countries that allow only natural refrigerants, CO2 is applied to the low-level refrigerant circuit 300, and R290 is applied to the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200, respectively. In countries requiring low GWP, CO2 is applied to the low-level refrigerant circuit 300, and R1234yf is applied to the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200, respectively. In this way, by changing the high-concentration side refrigerant without changing the specifications of the refrigerant in the low-concentration refrigerant circuit 300, it is possible to comply with the refrigerant regulations of each country.

FIG. 4 is a diagram showing Modification 1 of the binary refrigeration cycle device 51 related to Embodiment 1. FIG. In Modification 1, the return refrigerant pipe 18 extending from the liquid receiver 304 is connected between the first cascade condenser 104 and the third compressor 301 . Therefore, the gasified third refrigerant flows from the liquid receiver 304 into the first cascade condenser 104 . The third refrigerant flowing into the first cascade condenser 104 is cooled by the first cascade condenser 104 and then flows into the second cascade condenser 204 . Therefore, in comparison with the configuration shown in FIG. 1, in Modification 1, a further cooling effect for the third refrigerant can be obtained.

The position where the return refrigerant pipe 18 extending from the liquid receiver 304 is connected may be any position from the discharge portion of the third compressor 301 to the inlet portion of the first cascade condenser 104 . More preferably, the return refrigerant pipe 18 extending from the liquid receiver 304 is connected to the discharge portion of the third compressor 301 . This is because the pressure of the third refrigerant is highest at the discharge portion of the third compressor 301 .

<Integration of heat exchanger>
FIG. 5 is a diagram showing a fifth heat exchanger 502 in which the first heat exchanger 102 and the second heat exchanger 202 are integrated. The fifth heat exchanger 502 corresponds to an integrated structure of the components indicated by symbol A in FIG. 1 .

The fifth heat exchanger 502 is divided into the first high-level refrigerant circuit 100 in which the first refrigerant flows and the second high-level refrigerant circuit 200 in which the second refrigerant flows, and the first heat exchanger 102 and the second heat exchanger 502 are separated. It has a configuration in which it is integrated with the exchanger 202 . A fifth fan 5021 is provided in the fifth heat exchanger 502 . However, a plurality of fans may be provided for the fifth heat exchanger 502 .

By integrating the first heat exchanger 102 and the second heat exchanger 202, the space for arranging equipment can be effectively utilized. Further, by integrating the first heat exchanger 102 and the second heat exchanger 202, the cost can be reduced. Note that the integrated fifth heat exchanger 502 may be applied to Modification 1 shown in FIG.

FIG. 6 is a diagram showing an example in which an uninterruptible power supply 205 is provided in the binary refrigerating cycle device 51 according to Embodiment 1. FIG. As shown in FIG. 6 , the second high-voltage refrigerant circuit 200 is connected to an uninterruptible power supply 205 .

Note that the control device 30 may be connected to the uninterruptible power supply 205. Alternatively, the uninterruptible power supply 205 and another uninterruptible power supply may be connected to the control device 30 . As a result, even when the low temperature refrigerant circuit 300 is stopped due to a power failure, the control device 30 can operate in the stop operation mode using the second high temperature refrigerant circuit 200 . As a result, it is possible to prevent the pressure in the low-concentration refrigerant circuit 300 from abnormally increasing during a power failure. Therefore, it is not necessary to suppress the pressure rise by extracting the third refrigerant from the low-concentration refrigerant circuit 300 to the outside at the time of power failure. According to this configuration, it is possible to suppress the pressure rise accompanying the temperature rise of the low-order refrigeration cycle without lowering the reliability.

An uninterruptible power supply 205 may be provided in the first high-voltage refrigerant circuit 100 as well. However, it is preferable to preferentially provide the uninterruptible power supply 205 for the second high-order refrigerant circuit 200 of the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 . This is because the second high-level refrigerant circuit 200 is activated in the stop operation mode.

Also, since the capacity of the second high-order refrigerant circuit 200 is smaller than that of the first high-order refrigerant circuit 100, the power supply capacity required for the uninterruptible power supply 205 can be small. Therefore, it is more economical to provide the uninterruptible power supply 205 in the second high-order refrigerant circuit 200 than in the first high-order refrigerant circuit 100 . In addition, a small capacity uninterruptible power supply 205 can be used for the second high-level refrigerant circuit 200 .

FIG. 7 is a diagram showing an example in which an uninterruptible power supply 205 is provided in the binary refrigeration cycle apparatus 51 of Modification 1. FIG. As shown in FIG. 7, the uninterruptible power supply 205 can be applied to Modification 1 as well as the configuration shown in FIG. The uninterruptible power supply 205 may be applied to the binary refrigerating cycle device 51 employing the integrated fifth heat exchanger 502 in the same manner as the configuration shown in FIG.

FIG. 8 is a graph 1 showing the relationship between the frequency range and cooling capacity of the first high-order refrigeration cycle and the relationship between the frequency range and cooling capacity of the second high-order refrigeration cycle. In FIG. 8, L1a indicates the frequency range of the first compressor 101 that constitutes the first high-order refrigeration cycle. Symbol L2a indicates the frequency range of the second compressor 201 that constitutes the second high-order refrigeration cycle.

As shown in FIG. 8, the maximum cooling capacity of the first high-order refrigeration cycle is higher than that of the second high-order refrigeration cycle. On the other hand, the second high-order refrigeration cycle has a lower minimum cooling capacity than the first high-order refrigeration cycle. The lower limit frequency of the first higher refrigeration cycle is f1min, and the upper limit frequency of the first higher refrigeration cycle is f1max. The lower limit frequency of the second higher refrigeration cycle is f2min, and the upper limit frequency of the second higher refrigeration cycle is f2max.

As shown in FIG. 8, the cooling capacity that can be output at the upper limit frequency f2max of the second higher refrigeration cycle is designed to be greater than the cooling capacity that can be output at the lower limit frequency f1min of the first higher refrigeration cycle. there is Therefore, a range Ca is generated in which the cooling capacity of the first high-order refrigeration cycle and the cooling capacity of the second high-order refrigeration cycle overlap.

Consider a hypothetical example in which the cooling capacity range of the first high-order refrigeration cycle is designed to be 10 kW to 40 kW, and the cooling capacity range of the second high-order refrigeration cycle is designed to be 2 kW to 10 kW. In the case of a hypothetical example, the cooling capacities of both high-order refrigeration cycles are divided into lower capacities and upper capacities with 10 kW as the boundary.

For this reason, there is no overlapping range as shown in FIG. The minimum cooling capacity when both high-level refrigeration cycles are activated is 12 kW. When the required capacity of the low-order refrigeration cycle is smaller than the cooling capacity of the high-order refrigeration cycle, the first high-order refrigeration cycle is stopped to reduce the cooling capacity, and only the second high-order refrigeration cycle is used as the high-order refrigeration cycle. When put into operation, the problem arises that cooling capacities between 10 and 12 kW cannot be provided by high-order refrigeration cycles.

However, as shown in FIG. 8, by providing a range Ca in which the cooling capacity of the first high-level refrigerating cycle and the cooling capacity of the second high-level refrigerating cycle overlap, the occurrence of such a problem can be prevented. can. For example, in the case of the above hypothetical example, by raising the maximum cooling capacity of the second high-order refrigeration cycle to 12 kW, as shown in FIG. It is possible to provide a range Ca overlapping with the cooling capacity of .

FIG. 9 is graph 2 showing the relationship between the frequency range and cooling capacity of the first high-order refrigeration cycle and the relationship between the frequency range and cooling capacity of the second high-order refrigeration cycle. In the example shown in FIG. 9, the lower limit frequency f1min of the first higher refrigerating cycle and the lower limit frequency f2min of the second higher refrigerating cycle match, and the upper limit frequency f1max of the first higher refrigerating cycle and the second higher refrigerating cycle It matches the upper limit frequency f2max of the high-order refrigerating cycle. However, in the case of the example shown in FIG. 9, similarly to the example shown in FIG. 8, the cooling capacity of the first high-order refrigeration cycle and the cooling capacity of the second high-order refrigeration cycle are designed to overlap with each other. there is Therefore, similar to the example shown in FIG. 8, the above-described problems caused by the virtual example can be resolved.

Thus, in the present embodiment, the upper limit value of the cooling capacity of the first high-level refrigerant circuit 100 is greater than the upper limit value of the cooling capacity of the second high-level refrigerant circuit 200 . Further, in the present embodiment, the range of the cooling capacity of the first high-order refrigerant circuit 100 includes the upper limit of the cooling capacity of the second high-order refrigerant circuit 200 . The frequency and cooling capacity of the high-level refrigerating cycle of the binary refrigerating cycle device 51 according to the first embodiment may be designed in either pattern shown in FIGS.

<Control of operation mode>
FIG. 10 is a flow chart showing the contents of the operation mode control according to the first embodiment. The control device 30 switches the operation mode between the cooling operation mode and the stop operation mode by executing the processing based on this flowchart.

The control device 30 first determines whether or not the cooling operation has stopped (step S1). When the operation of the low-concentration refrigerant circuit 300 is stopped due to a power failure or other circumstances, the control device 30 determines YES in step S1, and shifts to the stop operation mode (step S2). When the operation of the low-concentration refrigerant circuit 300 has not stopped, the control device 30 determines NO in step S1, and shifts to the cooling operation mode (step S3). The processing of the stop mode of operation is disclosed in FIG. The processing of the cooling mode of operation is disclosed in FIG.

<Control of stop operation mode>
FIG. 11 is a flow chart showing the contents of control in the stop operation mode. Control device 30 first determines whether P10 exceeds threshold value B (step S10). P10 indicates the pressure of the low-concentration refrigerant circuit 300 . Control device 30 specifies pressure P<b>10 based on the output value of pressure sensor 10 provided in low-concentration refrigerant circuit 300 .

The control device 30 controls the pressure P10 of the low-concentration refrigerant circuit 300 within a certain range in the stop operation mode. A frame W10 in FIG. 11 shows the relationship between the pressure P10 and the threshold. The control device 30 controls the pressure so that it does not exceed the threshold value B. FIG. (1), (2), and (3) shown in frame W10 in FIG. 11 indicate the range of pressure P10 detected by pressure sensor 10. In FIG. Among (1) to (3), the reference range of pressure targeted by the control device 30 is (2).

For example, when CO2 is adopted as the third refrigerant in the low-concentration refrigerant circuit 300, the threshold A is preferably 3.38 MPaG. It is assumed that the pressure of CO2 is 3.38 MPaG when the saturation temperature of CO2 is 0°C. Threshold B is preferably 3.67 MPaG. It is assumed that the pressure of CO2 is 3.67 MPaG when the saturation temperature of CO2 is 3°C.

However, the threshold pressure range may be 3.38 MPaG to 4.15 MPaG. This corresponds to a saturation temperature of CO2 of 0°C to 7.7°C. Also, the threshold A may be a value corresponding to the temperature when the saturation temperature of CO2 is less than 0.degree. However, in order to suppress the adhesion of frost to the first cascade capacitor 104 and the second cascade capacitor 204, it is desirable to set the value corresponding to the temperature when the saturation temperature of CO2 is 0.degree.

When the control device 30 determines that P10 does not exceed the threshold B in step S10, the determination in step S10 is repeated until P10 exceeds the threshold B. When the control device 30 determines in step S10 that the pressure P10 exceeds the threshold value B, the control device 30 operates the second high-order refrigerating cycle (step S11). Thereby, the second high-level refrigerant circuit 200 is activated. When the second high-order refrigerant circuit 200 is activated, the second cascade condenser 204 cools the third refrigerant.

After step S11, the control device 30 executes the process of step S101 indicated by the dashed line. Step S101 is a process for adjusting the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203, and is composed of steps S12 and S13. In step S12, the control device 30 determines whether the current rotation speed of the second fan 2021 has reached the target condensation temperature (CT), and whether the current opening degree of the second expansion valve (LEV) 203 is It is determined whether the target degree of superheat (SH: superheat) has been achieved. When each target is achieved, the control device 30 proceeds to S14. If the respective targets are not achieved, the control device 30 resets the rotational speed of the second fan 2021 and the opening degree of the second expansion valve 203, and then proceeds to step S12 again.

After step S101, the control device 30 determines whether the pressure P10 satisfies "pressure P10<threshold B" and "pressure P10>threshold A" (step S14). That is, the control device 30 determines whether or not the pressure P10 is within the range (2) shown in the frame W10.

When the pressure P10 is within the range of (2) shown in the frame W10, the control device 30 repeats the process of step S14. When the pressure P10 deviates from the range (2) shown in the frame W10, the control device 30 determines whether the pressure P10 satisfies "pressure P10<threshold A". Here, it is determined whether or not the pressure P10 is within the range (1) shown in the frame W10.

In step S15, when the pressure P10 does not satisfy "pressure P10<threshold A", the pressure P10 is within the range of (3) shown in the frame W10. Therefore, when the control device 30 determines NO in step S15, the frequency of the second compressor 201 (Comp 201) is increased by a constant value (step S16). After that, the control device 30 executes the same process as that of step S101 already described (step S17). After that, the control device 30 proceeds to the process of step S14.

In step S15, when the pressure P10 satisfies "pressure P10<threshold A", the pressure P10 is within the range (1) shown in the frame W10. In this case, it can be determined that the pressure in the low-concentration refrigerant circuit 300 is sufficiently low. In other words, it can be determined that the cooling capacity of the high-order refrigeration cycle is too high. In this case, it is necessary to lower the frequency of the second compressor 201 . However, there is a possibility that the frequency of the second compressor 201 has already reached the lower limit frequency. Also, even if the frequency of the second compressor 201 has already reached the lower limit frequency, if the operation of the second high-side refrigerating cycle is immediately stopped while the outside air temperature is high, the pressure of the low-side refrigerating cycle may rise sharply. There is

Therefore, if the control device 30 determines YES in step S15, it determines whether the frequency of the second compressor 201 (Comp 201) is the lower limit frequency and whether the outside air temperature is equal to or lower than the set temperature (step S20). Control device 30 identifies the outside air temperature based on the output value of temperature sensor 20 .

When the control device 30 determines NO in step S20, the frequency of the second compressor 201 (Comp 201) is lowered by a certain value (step S18). After that, the control device 30 executes the same process as that of step S101 already described (step S19). After that, the control device 30 proceeds to the process of step S14.

When determining YES in step S20, the control device 30 stops the second high-level refrigeration cycle (step S21). If the outside air temperature is equal to or less than the set temperature and the frequency of the second compressor 201 (Comp 201) is the lower limit frequency, it can be determined that there is no danger of the pressure of the low-level refrigerant circuit 300 suddenly rising. Therefore, the second high-level refrigeration cycle is stopped in step S21. After that, the processing of the stop operation mode is terminated.

As described with reference to FIG. 11, control device 30 controls first high-level refrigerant circuit 100 and second high-level refrigerant circuit 100 so that the pressure detected by pressure sensor 10 falls within the range of threshold A to threshold B in the stopped operation mode. The high-level refrigerant circuit 200 is controlled.

In the process of the stop operation mode shown in FIG. 11, the second high-order refrigeration cycle prevents the pressure of the low-order refrigerant circuit 300 from abnormally increasing. However, the first high-order refrigeration cycle may also be utilized in the stop operation mode. For example, in step S16 of FIG. 11, when the frequency of the second compressor 201 (Comp 201) has reached the upper limit frequency, it is conceivable to start the first high-order refrigeration cycle.

<Control of cooling operation mode>
FIG. 12 is a flow chart showing the contents of control in the cooling operation mode. The control device 30 first sets the target frequency of the third compressor 301 (Comp 301) from the outside air temperature and the evaporation temperature set in the indoor unit 2 (step S30). Control device 30 identifies the outside air temperature based on the output value of temperature sensor 20 .

After step S30, the control device 30 determines whether or not the frequency of the third compressor 301 (Comp 301) exceeds the threshold value X (step S31). The threshold X is a value for determining the required operability of the high-order refrigeration cycle. When controller 30 determines that the frequency of third compressor 301 (Comp 301) exceeds threshold value X, controller 30 operates the first and second high-order refrigeration cycles (step S32). When the control device 30 determines that the frequency of the third compressor 301 (Comp 301) does not exceed the threshold value X, it operates the second high-order refrigerating cycle (step S34).

In this way, the control device 30 determines the timing of starting the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 based on the frequency set when starting the third compressor 301 (Comp 301). Control.

FIG. 13 is a graph showing the relationship between the set value of the evaporation temperature inside the refrigerator and the cooling capacity. Here, the threshold value X will be described with reference to FIG. 13 . In the graph, the horizontal axis indicates the condensation temperature (ET: Evaporation Temperature) set in the indoor unit 2 arranged in the refrigerator. The vertical axis indicates the compressor frequency (Hz) corresponding to the cooling capacity. As shown in FIG. 13, the required cooling capacity changes depending on the outside air temperature AT (Outside Air Temperature).

In general, the higher the outside temperature, the higher the required cooling capacity. For example, FIG. 13 shows an example in which the outside air temperature is 20.degree. C. and -15.degree. In this embodiment, the threshold X is set to 60 Hz based on this graph. However, this value is only an example.

Returning to the flowchart in Fig. 12, the explanation continues. When the first and second high-order refrigerating cycles are operated in step S32, the control device 30 performs the same process as in step S101 already described in the first and second high-order refrigerating cycles (step S33).

As a result, in the first high-level refrigerant circuit 100, the rotational speed of the first fan 1021 of the first heat exchanger 102 and the opening degree of the first expansion valve 103 are adjusted as necessary. Also, in the second high-level refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary. After step S33, the control device 30 executes the high capacity operation mode. The processing of the high capacity mode of operation is disclosed in FIG.

When the second high-level refrigerating cycle is operated in step S34, the control device 30 performs the same processing as in step S101 already described in the second high-level refrigerating cycle (step S35). Thereby, in the second high-voltage refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary. After step S35, the control device 30 executes the low capacity operation mode. The processing of the low capacity mode of operation is disclosed in FIG.

<High capacity operation mode>
FIG. 14 is a flow chart showing the contents of control in the high capacity operation mode. The control device 30 first determines whether or not the pressure P10 satisfies "P10≦threshold B" and "P10≧threshold A" (step S40). As already explained using FIG. 11 , P10 indicates the pressure of the low-concentration refrigerant circuit 300 . Control device 30 specifies pressure P<b>10 based on the output value of pressure sensor 10 provided in low-concentration refrigerant circuit 300 . The relationship between pressure P10 and threshold A and threshold B is shown in frame W10 in FIG.

When the pressure P10 satisfies "P10≦threshold B" and "P10≧threshold A", the pressure P10 is in the range (2) indicated by the frame W10 in FIG. In this case, it can be determined that the pressure P10 is appropriate. Therefore, control device 30 returns the process to step S40. When the pressure P10 does not satisfy "P10≦threshold B" and "P10≧threshold A", the control device 30 determines whether the pressure P10 satisfies "P10<threshold A" (step S41).

In step S41, when the pressure P10 satisfies "P10<threshold A", the pressure P10 is within the range (1) indicated by the frame W10 in FIG. At this time, the pressure P10 is a value lower than the lower threshold A. In this case, it can be determined that the pressure in the low-concentration refrigerant circuit 300 is sufficiently low. In other words, it can be determined that the cooling capacity of the high-order refrigeration cycle is too high. In this case, it is necessary to lower the frequency of the compressor on the high-order refrigerating cycle side. However, there is a possibility that both the frequencies of the first compressor 101 and the second compressor 201 on the high-order refrigerating cycle side have already reached the lower limit frequency.

Therefore, if the control device 30 determines YES in step S41, it determines whether or not the frequencies of the first compressor 101 (Comp 101) and the second compressor 201 (Comp 201) both reach the lower limit frequency ( step S43).

When determining NO in step S43, the control device 30 reduces the frequency of the compressor of the high-level refrigeration cycle (step S52). In step S52, control device 30 preferentially lowers the frequency of first compressor 101 (Comp101) out of first compressor 101 (Comp101) and second compressor 201 (Comp201).

More specifically, when the frequency of the first compressor 101 (Comp 101) has not reached the lower limit, the frequency of the first compressor 101 (Comp 101) is decreased by a certain value, and then the control device 30 performs the following steps: Proceed to S53. At this time, the frequency of the second compressor 201 (Comp 201) is not lowered. In step S43, if the frequency of the first compressor 101 (Comp 101) has reached the lower limit and the frequency of the second compressor 201 (Comp 201) has not reached the lower After lowering the frequency of the compressor 201 (Comp 201) by a constant value, the process proceeds to step S53.

In step S53, the control device 30 executes the same process as in step S101 already described in the first and second high-level refrigeration cycles.

As a result, in the first high-level refrigerant circuit 100, the rotational speed of the first fan 1021 of the first heat exchanger 102 and the opening degree of the first expansion valve 103 are adjusted as necessary. Also, in the second high-level refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary. After step S53, control device 30 returns the process to step S40.

If the process of step S43 is repeated, the frequencies of both the first compressor 101 (Comp101) and the second compressor 201 (Comp201) may eventually reach the lower limit. When the frequencies of both the first compressor 101 (Comp101) and the second compressor 201 (Comp201) reach the lower limit values, the controller 30 determines YES in step S43. At this time, the cooling capacity of the high-order refrigeration cycle when both the first and second high-order refrigeration cycles are activated reaches the lower limit.

When determining YES in step S43, the control device 30 stops the first high-level refrigeration cycle (step S54), and then switches the operation mode from the high-capacity operation mode to the low-capacity operation mode.

In step S41, when the pressure P10 does not satisfy "P10<threshold A", the pressure P10 is within the range (3) indicated by the frame W10 in FIG. At this time, the pressure P10 has a value exceeding the upper limit threshold B.

When the pressure P10 exceeds the upper limit threshold B, it is necessary to increase the capacity of the high-level refrigeration cycle. When the controller 30 determines in step S41 that the pressure P10 does not satisfy "P10<threshold A", the frequencies of the first compressor 101 (Comp101) and the second compressor 201 (Comp201) are both upper limit values. is reached (step S42).

When determining NO in step S42, the control device 30 increases the frequency of the compressor of the high-level refrigeration cycle (step S44). In step S44, control device 30 preferentially increases the frequency of second compressor 201 (Comp 201) out of first compressor 101 (Comp 101) and second compressor 201 (Comp 201).

More specifically, when the frequency of the second compressor 201 (Comp 201) has not reached the upper limit, the frequency of the second compressor 201 (Comp 201) is increased by a certain value, and then the process proceeds to the next step S45. At this time, the frequency of the first compressor 101 (Comp101) is not increased. In step S42, when the frequency of the second compressor 201 (Comp 201) has reached the upper limit and the frequency of the first compressor 101 (Comp 101) has not reached the upper limit, in step S44, the control device 30 controls the first After increasing the frequency of the compressor 101 (Comp 101) by a constant value, the process proceeds to step S45.

In step S45, the control device 30 executes the same process as in step S101 already described in the first and second high-level refrigerating cycles.

As a result, in the first high-level refrigerant circuit 100, the rotational speed of the first fan 1021 of the first heat exchanger 102 and the opening degree of the first expansion valve 103 are adjusted as necessary. Also, in the second high-level refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary. After step S45, control device 30 returns the process to step S40.

If the process of step S44 is repeated, the frequencies of both the first compressor 101 (Comp101) and the second compressor 201 (Comp201) may eventually reach the upper limits. When the frequencies of both the first compressor 101 (Comp101) and the second compressor 201 (Comp201) reach the upper limits, the control device 30 determines YES in step S42. At this time, the cooling capacity of the high-level refrigeration cycle has reached its upper limit.

If it is determined YES in step S42, the control device 30 notifies the user of the lack of ability (step S46). The control device 30 displays, for example, a message indicating insufficient capacity on a remote controller for operating the indoor unit 2 .

After the processing of step S46, the control device 30 lowers the frequency of the third compressor 301 (Comp 301) constituting the low-concentration refrigerant circuit 300 by a certain value (step S47). Control device 30 performs the same processing as step S101 already described for each refrigerating cycle (step S48). After that, the control device 30 determines whether or not the pressure P10 satisfies "P10≦threshold B" (step S49).

In step S49, if the pressure P10 does not satisfy "P10≤threshold B", the control device 30 returns the process to step S46. In step S49, when pressure P10 satisfies "P10≦threshold B", control device 30 determines whether or not a user's operation to stop the low-order refrigeration cycle has been detected (step S50). Control device 30 continues the processing of step S50 until the user's operation for stopping the low-order refrigeration cycle is detected. A user's operation is input to the control device 30 from, for example, a remote controller corresponding to the indoor unit 2 . Note that, when the control device 30 determines NO in step S50, the control device 30 may return the processing to step S46 and notify the user of the lack of ability again.

When the control device 30 detects the user's operation in step S50, it stops the low-level refrigerating cycle and the first high-level refrigerating cycle (step S51). Next, the control device 30 switches the operation mode to the stop operation mode. By switching the operation mode to the stop operation mode, the pressure of the low-concentration refrigerant circuit 300 is prevented from increasing abnormally.

As described with reference to FIG. 14, control device 30 controls first high-level refrigerant circuit 100 and second high-level refrigerant circuit 100 so that the pressure detected by pressure sensor 10 falls within the range of threshold A to threshold B in the high-capacity operation mode. It controls the two-level refrigerant circuit 200 .

<Low capacity operation mode>
FIG. 15 is a flowchart showing the details of control in the low capacity operation mode. The control device 30 first determines whether or not the pressure P10 satisfies "P10≦threshold B" and "P10≧threshold A" (step S70). As already explained using FIG. 11 , P10 indicates the pressure of the low-concentration refrigerant circuit 300 . Control device 30 specifies pressure P<b>10 based on the output value of pressure sensor 10 provided in low-concentration refrigerant circuit 300 . The relationship between pressure P10 and threshold A and threshold B is shown in frame W10 in FIG.

When the pressure P10 satisfies "P10≦threshold B" and "P10≧threshold A", the pressure P10 is in the range (2) indicated by the frame W10 in FIG. In this case, it can be determined that the pressure P10 is appropriate. In this case, control device 30 returns the process to step S70. When the pressure P10 does not satisfy "P10≦threshold B" and "P10≧threshold A", the control device 30 determines whether the pressure P10 satisfies "P10<threshold A" (step S71).

In step S71, when the pressure P10 satisfies "P10<threshold A", the pressure P10 is within the range (1) indicated by the frame W10 in FIG. At this time, the pressure P10 is a value lower than the lower threshold A. In this case, it can be determined that the pressure in the low-concentration refrigerant circuit 300 is sufficiently low. In other words, it can be determined that the cooling capacity of the high-order refrigeration cycle is too high. In this case, it is necessary to lower the frequency of the second compressor 201 activated on the high-order refrigerating cycle side. However, there is a possibility that the frequency of the second compressor 201 has already reached the lower limit frequency.

Therefore, if the control device 30 determines YES in step S71, it determines whether or not the frequency of the second compressor 201 (Comp 201) has reached the lower limit frequency (step S73).

When determining NO in step S73, the control device 30 reduces the frequency of the second compressor 201 (Comp 201) by a constant value (step S76). After that, in step S77, control device 30 performs the same process as in step S101 already described in the second high-order refrigeration cycle. After step S77, control device 30 returns the process to step S70.

If the process of step S76 is repeated, the frequency of the second compressor 201 (Comp 201) may eventually reach the lower limit. When the frequency of the second compressor 201 (Comp 201) reaches the lower limit, the control device 30 determines YES in step S73. At this time, the cooling capacity of the second high-order refrigeration cycle has reached its lower limit.

When determining YES in step S73, the control device 30 increases the target degree of superheat (SH) by adjusting the degree of opening of the third expansion valve 303 that constitutes the low-concentration refrigerant circuit 300 (step S78). After that, in step S79, control device 30 performs the same process as in step S101 already described in the low-order refrigeration cycle. Specifically, control device 30 adjusts the rotation speed of third fan 3021 of third heat exchanger 302 .

After step S79, the control device 30 determines whether or not the pressure P10 satisfies "P10≦threshold B" and "P10≧threshold A" (step S80). If the pressure P10 does not satisfy "P10≦threshold B" and "P10≧threshold A", the control device 30 again adjusts the target degree of superheat (SH) of the third expansion valve 303 (step S81). Thereafter, control device 30 executes the same process as step S79 (step S82), and returns the process to step S70.

When determining YES in step S80, the control device 30 determines whether or not the user's stop operation has been detected (step S83). The user, for example, operates the remote controller to stop the low-level refrigeration cycle. When determining NO in step S83, the control device 30 returns the process to step S70. When the determination in step S83 is YES, control device 30 stops the low-order refrigeration cycle (step S84). After that, the control device 30 switches the operation mode to the stop operation mode.

In step S71, if the pressure P10 does not satisfy "P10<threshold A", the pressure P10 is within the range (3) indicated by the frame W10 in FIG. At this time, the pressure P10 has a value exceeding the upper limit threshold B.

When the pressure P10 exceeds the upper limit threshold B, it is necessary to increase the capacity of the high-level refrigeration cycle. When the controller 30 determines in step S71 that the pressure P10 does not satisfy "P10<threshold A", it determines whether the frequency of the second compressor 201 (Comp 201) has reached the upper limit (step S72).

When the determination in step S72 is NO, the control device 30 increases the frequency of the second compressor 201 (Comp 201) by a constant value (step S74). After that, the control device 30 executes the same process as the already described step S101 in the second high-level refrigerating cycle (step S75). After step S75, control device 30 returns the process to step S70.

If the process of step S74 is repeated, the frequency of the second compressor 201 (Comp 201) may eventually reach the upper limit. When the frequency of the second compressor 201 (Comp 201) reaches the upper limit, the controller 30 determines YES in step S72 and switches the operation mode to the high capacity operation mode. By switching the operation mode to the high-capacity operation mode, the second high-level refrigerating cycle is activated and the refrigerating capacity of the high-level refrigerating cycle increases.

As described with reference to FIG. 15, control device 30 controls first high-level refrigerant circuit 100 and second high-level refrigerant circuit 100 so that the pressure detected by pressure sensor 10 falls within the range of threshold A to threshold B in the low capacity operation mode. It controls the two-level refrigerant circuit 200 .

As can be understood from the description so far, the control device 30 switches the operation mode between the stop operation mode and the cooling operation mode depending on the situation. More specifically, in both the stop operation mode and the cooling operation mode, the control device 30 controls the pressure detected by the pressure sensor 10 to fall within the range of the threshold A to the threshold B. The high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 are controlled. Note that the threshold may be varied according to each mode.

Further, as shown in FIG. 12, the control device 30 operates in the low capacity operation mode or in the high capacity operation mode based on the frequency set when starting the third compressor 301 (Comp 301). decide whether to In particular, in the high-capacity operation mode, both the first and second high-order refrigeration cycles are activated on the high-order side. On the other hand, in the low capacity operation mode, only the second high-order refrigeration cycle is started on the high-order side. Therefore, the control device 30 controls the timing of starting the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 based on the frequency set when starting the third compressor 301 .

Furthermore, as described with reference to FIGS. 11, 14, and 15, the control device 30 switches the cooling operation mode between the low-capacity operation mode and the high-capacity operation mode according to the degree of required cooling capacity. switch.

As described above, the control device 30 changes the cooling capacity of the high-level refrigeration cycle provided by the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit 200 based on the state of the refrigeration cycle of the low-level refrigerant circuit 300. Let

Further, as described with reference to FIGS. 8 and 9, the high-level refrigeration cycle is designed so that the cooling capacity of the first high-level refrigeration cycle and the cooling capacity of the second high-level refrigeration cycle overlap. is effective when the starting high-side refrigeration cycle changes in this way.

That is, as shown in FIGS. 8 and 9, the cooling capacity that can be output at the upper limit frequency of the second higher refrigeration cycle is set to be greater than the cooling capacity that can be output at the lower limit frequency of the first higher refrigeration cycle. By doing so, it is possible to suppress the start and stop of the compressor that occur when the critical cooling capacity is required.

Also, the operation can be switched smoothly from the second high-order refrigeration cycle to the first high-order refrigeration cycle. Therefore, the required cooling capacity can be obtained without excessively lowering the frequency of the second compressor 201 .

Furthermore, unlike the present embodiment, in the case of a refrigeration cycle system in which the frequency of the compressor must be excessively lowered, the refrigerating machine oil that is discharged when the compressor discharges the refrigerant is , the amount of refrigerating machine oil returning to the compressor may decrease when the compressor sucks refrigerant. In this case, the compressor motor may burn out. However, in the present embodiment, since it is not necessary to excessively lower the frequency of the second compressor 201, it is possible to prevent the motor of the second compressor 201 from burning out due to lack of refrigerating machine oil. reliability can be improved.

Embodiment 2.
Next, Embodiment 2 will be described. FIG. 16 is a diagram showing the configuration of a dual refrigeration cycle device 52 according to the second embodiment. As shown in FIG. 16, the binary refrigerating cycle device 52 according to the second embodiment has a fourth heat exchanger 402 added to the configuration of the binary refrigerating cycle device 51 according to the first embodiment. . The fourth heat exchanger 402 is provided with a fourth fan 4021 that facilitates heat exchange between the outside air and the third refrigerant.

A fourth heat exchanger 402 is provided in the low-concentration refrigerant circuit 300 . A fourth heat exchanger 402 is connected between the first cascade condenser 104 and the first compressor 101 . The high-temperature and high-pressure gaseous third refrigerant discharged from the first compressor 101 is input to the fourth heat exchanger 402 . As the fourth fan 4021 rotates, the fourth heat exchanger 402 radiates the heat of the third refrigerant discharged from the first compressor 101 to the air. Therefore, the fourth heat exchanger 402 functions as a condenser.

The binary refrigerating cycle device 51 related to Embodiment 1 already described has two cooling operation modes, a low-capacity operation mode and a high-capacity operation mode. In these two modes, the high order refrigeration cycle is activated and the third refrigerant of the low order refrigeration cycle is cooled.

The binary refrigeration cycle device 52 according to Embodiment 2 cools the third refrigerant by the fourth heat exchanger 402 without starting the high-capacity refrigeration cycle in addition to the low-capacity operation mode and the high-capacity operation mode. have a mode. Hereinafter, this mode will be referred to as a "low cooling mode". Thus, the cooling operation mode of the second embodiment has a larger number of switchable modes than the cooling operation mode of the first embodiment. Hereinafter, in order to distinguish between the cooling operation mode of the first embodiment and the cooling operation mode of the second embodiment, the latter cooling operation mode may be particularly referred to as "cooling operation mode 2".

In the low temperature cooling mode, rotation of the fourth fan 4021 corresponding to the fourth heat exchanger 402 cools the third refrigerant flowing through the low temperature refrigerant circuit 300 . Note that the binary refrigerating cycle device 52 may control the rotation speed of the fourth fan 4021 based on the output value of the pressure sensor 10 in order to keep the pressure of the third refrigerant proper.

When the pressure of the third refrigerant rises beyond the proper range, the binary refrigeration cycle device 52 switches the operation mode from the low-primary cooling mode to the low-capacity operation mode. The content of the low capacity operation mode is the same as that of the first embodiment. However, in the low capacity operation mode related to Embodiment 2, the fourth heat exchanger 402 also continues to function as a condenser. Therefore, in the low capacity operation mode related to Embodiment 2, the fourth fan 4021 corresponding to the fourth heat exchanger 402 is rotating. Therefore, the low capacity operation mode according to the second embodiment has a higher maximum cooling capacity than the low capacity operation mode according to the first embodiment.

In addition, in the low-capacity operation mode related to Embodiment 2, rotation of the fourth fan 4021 corresponding to the fourth heat exchanger 402 may be stopped. Further, in the low-capacity operation mode related to Embodiment 2, control device 30 controls the rotation speed of fourth fan 4021 based on the output value of pressure sensor 10 in order to keep the pressure of the third refrigerant appropriate. good too.

When the pressure of the third refrigerant rises beyond the appropriate range in the low-capacity operation mode, the binary refrigeration cycle device 52 switches the operation mode from the low-capacity operation mode to the high-capacity operation mode. The content of the high capacity operation mode is the same as that of the first embodiment. However, in the low capacity operation mode related to Embodiment 2, the fourth heat exchanger 402 also continues to function as a condenser. Therefore, in the low capacity operation mode related to Embodiment 2, the fourth fan 4021 corresponding to the fourth heat exchanger 402 is rotating. Therefore, the high capacity operation mode according to the second embodiment has a higher maximum cooling capacity than the low capacity operation mode according to the first embodiment.

In addition, in the high-capacity operation mode related to Embodiment 2, rotation of the fourth fan 4021 corresponding to the fourth heat exchanger 402 may be stopped. Further, in the high-capacity operation mode related to Embodiment 2, control device 30 controls the rotation speed of fourth fan 4021 based on the output value of pressure sensor 10 in order to keep the pressure of the third refrigerant appropriate. good too.

<Heat transfer area ratio>
FIG. 17 is a diagram showing the ratio of the heat transfer area of the first heat exchanger 102 and the second heat exchanger 202 to the heat transfer area of the fourth heat exchanger 402. As shown in FIG. In Embodiment 2, the first heat exchanger 102 and the second heat exchanger 202 form a condenser of the high-level refrigeration cycle, and the fourth heat exchanger 402 forms a condenser of the low-level refrigeration cycle. Therefore, FIG. 17 corresponds to a diagram comparing the heat transfer areas of the condenser of the high-order refrigeration cycle and the condenser of the low-order refrigeration cycle.

Regarding the ratio of the heat transfer area of the fourth heat exchanger 402 to the total heat transfer area of the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402, pattern 1 and pattern 2 are shown in FIG. 17.

In pattern 1, the ratio of the heat transfer area of the fourth heat exchanger 402 to the total heat transfer area of the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402 is 3% to 50%. is considered to be in the range of That is, pattern 1 is an example in which the ratio of the heat transfer area of the low-order refrigeration cycle to the total heat transfer area of the condensers of the low-order refrigeration cycle and the high-order refrigeration cycle is in the range of 3% to 50%.

In pattern 2, the ratio of the heat transfer area of the fourth heat exchanger 402 to the total heat transfer area of the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402 is 8% to 30%. is considered to be in the range of That is, pattern 2 is an example in which the ratio of the heat transfer area of the low-order refrigeration cycle to the total heat transfer area of the condensers of the low-order refrigeration cycle and the high-order refrigeration cycle is in the range of 8% to 30%.

It is more desirable to adopt pattern 2 than pattern 1 as the heat transfer area ratio. For example, since pattern 2 has a higher heat transfer area ratio of the condenser of the low-order refrigeration cycle than pattern 1, pattern 2 is higher than pattern 1 in the low-order cooling mode using the fourth heat exchanger 402. It can be expected that the cooling function of

In addition, in pattern 1, any of the heat transfer ratio of the fourth heat exchanger 402 within the range of 3 to 50% may be adopted. Also, in Pattern 2, any heat transfer ratio within the range of 8 to 30% of the fourth heat exchanger 402 may be adopted.

<Integration of heat exchanger>
FIG. 18 shows a sixth heat exchanger 602 in which the first heat exchanger 102, the second heat exchanger 202 and the fourth heat exchanger 402 are integrated. The sixth heat exchanger 602 corresponds to the integrated components indicated by symbols B, C, and D in FIG. 16 .

The sixth heat exchanger 602 is divided into a first high-level refrigerant circuit 100 in which the first refrigerant flows, a second high-level refrigerant circuit 200 in which the second refrigerant flows, and a low-level refrigerant circuit 300 in which the third refrigerant flows. In addition, the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402 are integrated. A sixth fan 6021 is provided in the sixth heat exchanger 602 . However, a plurality of fans may be provided for sixth heat exchanger 602 .

By integrating the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402, the space for arranging the equipment can be effectively utilized. Also, by integrating the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402, the cost can be reduced.

FIG. 19 shows a seventh heat exchanger 702 that integrates the second heat exchanger 202 and the fourth heat exchanger 402, and the first heat exchanger 102 used in combination with the seventh heat exchanger 702. It is a diagram. A seventh heat exchanger 702 is obtained by integrating the constituent parts indicated by symbols B and C in FIG.

The seventh heat exchanger 702 is divided into the second high-level refrigerant circuit 200 in which the second refrigerant flows and the low-level refrigerant circuit 300 in which the third refrigerant flows, and the second heat exchanger 202 and the fourth heat exchanger are divided. 402 are integrated. A seventh fan 7021 is provided in the seventh heat exchanger 702 . However, a plurality of fans may be provided for the seventh heat exchanger 702 .

By integrating the second heat exchanger 202 and the fourth heat exchanger 402, the space for arranging equipment can be effectively utilized. Also, by integrating the second heat exchanger 202 and the fourth heat exchanger 402, the cost can be reduced. Note that the first heat exchanger 102 and the fourth heat exchanger 402 may be integrated.

<Control of operation mode>
FIG. 20 is a flow chart showing the contents of the operation mode control according to the second embodiment. The control device 30 switches the operation mode between the cooling operation mode 2 and the stop operation mode by executing the processing based on this flowchart.

The control device 30 first determines whether the cooling operation has stopped (step S1000). When the operation of the low-concentration refrigerant circuit 300 is stopped due to a power failure or other circumstances, the control device 30 determines YES in step S1000, and shifts to the stop operation mode (step S2000).

The contents of the stop operation mode are the same as those in the first embodiment, so description thereof will not be repeated here. If the operation of low-concentration refrigerant circuit 300 has not stopped, control device 30 determines NO in step S1000, and shifts to cooling operation mode 2 (step S3000).

<Control of cooling operation mode 2>
FIG. 21 is a flowchart showing the contents of control in cooling operation mode 2. FIG. The control device 30 first sets the target frequency of the third compressor 301 (Comp 301) from the outside air temperature and the evaporation temperature set in the indoor unit 2 (step S90). Control device 30 identifies the outside air temperature based on the output value of temperature sensor 20 .

After step S90, the control device 30 determines whether the frequency of the third compressor 301 (Comp 301) is equal to or lower than the threshold value Y, and whether the outside air (outside air temperature) is equal to or lower than the set value (step S91). The set value of the outside air temperature is a preset value. The set value of the outside air temperature will be described later with reference to FIG. 22 . The controller 30 stores set values.

The control device 30 stores a threshold X and a threshold Y as thresholds for determining whether to switch the operation of the refrigeration cycle. A frame W20 in FIG. 21 shows the relationship between the frequency of the third compressor 301 (Comp 301) and the threshold values X and Y. As shown in FIG. First, the relationship between the frequency of the third compressor 301 (Comp 301) and the thresholds X and Y will be described with reference to the frame W20.

(1) to (3) in the frame W20 indicate the range of frequency values of the third compressor 301 (Comp 301). (1) indicates a range in which the frequency of the third compressor 301 (Comp 301) is equal to or lower than the threshold value Y; (2) indicates a range in which the frequency of the third compressor 301 (Comp 301) exceeds the threshold value Y and is less than the threshold value X; (3) indicates a range in which the frequency of the third compressor 301 (Comp 301) is equal to or higher than the threshold value X; Frequency range (2) indicates the appropriate range. Frequency range (1) indicates a range lower than the proper range. Frequency range (3) indicates a range that is higher than the proper range.

Here, with reference to FIGS. 22 and 23, the set values of the threshold X, the threshold Y, and the outside air temperature will be described in detail. FIG. 22 is a graph showing the relationship between the set value of the evaporating temperature inside the refrigerator and the cooling capacity (Embodiment 2). FIG. 23 is a graph showing the relationship between the frequency of the third compressor (Comp301) and the set value of the evaporating temperature inside the refrigerator (Embodiment 2). The threshold value X and the set value of the outside air temperature will be described with reference to FIG. 22, and the threshold value Y will be described with reference to FIG.

In the graph shown in FIG. 22, the horizontal axis indicates the condensation temperature (ET: Evaporation Temperature) set in the indoor unit 2 placed inside the refrigerator. The vertical axis indicates the compressor frequency (Hz) corresponding to the cooling capacity. As shown in FIG. 22, the required cooling capacity changes depending on the outside air temperature AT (Outside Air Temperature).

In general, the higher the outside temperature, the higher the required cooling capacity. For example, FIG. 22 shows an example in which the outside air temperature is 20.degree. C. and -15.degree. In Embodiment 2, the threshold value X is set to 60 Hz based on this graph. However, this value is only an example.

FIG. 22 further shows a region R10 where high-level operation is unnecessary. In region R10, it is not necessary to operate either the first or second high-order refrigeration cycle while the low-order refrigeration cycle is in operation. In region R10, control device 30 selects the low-level cooling mode as the operation mode. In the low temperature cooling mode, the fourth heat exchanger 402 provided in the low temperature refrigerant circuit 300 functions as a condenser to cool the third refrigerant. In the low temperature cooling mode, the high temperature refrigeration cycle does not start.

As shown in FIG. 22, the region R10 is set with the outside air temperature AT10 as the boundary. That is, the control device 30 selects the low-level cooling mode on the condition that the outside air temperature is AT10 or less. The outside air temperature AT10 is set to any value within the range of -15°C to 20°C.

In the graph shown in FIG. 23, the horizontal axis indicates the frequency of the third compressor 301 (Comp 301). The vertical axis indicates the condensing temperature (ET) set in the indoor unit 2 placed inside the refrigerator. In the graph of FIG. 23, in the relationship between the frequency of the third compressor 301 (Comp 301) and the condensing temperature (ET), a region R10 where high-level operation is unnecessary and a region R20 where high-level operation is required is shown. Region R20 is bounded by capacity equivalence lines. The higher the frequency and condensing temperature (ET) of the third compressor 301 (Comp 301), the higher the required cooling capacity.

FIG. 23 shows Y1 and Y2 as examples of values that can be used as the threshold Y. The threshold value Y1 is the maximum frequency of the third compressor 301 (Comp 301) in the region R10 where high-level operation is not required. Y1 is therefore a fixed value. The threshold Y2 is the frequency of the third compressor 301 (Comp 301) along the capacity equivalence line. Therefore, Y2 is a value that varies according to the condensation temperature (ET) set in the indoor unit 2.

In the second embodiment, either Y1 or Y2 may be used as the threshold value Y. Alternatively, two thresholds Y1 and Y2 may be stored in the memory 32 of the control device 30 in advance. The control device 30 may be configured to be able to select which of Y1 and Y2 thresholds to use.

Returning to the flowchart in FIG. 21, the explanation continues. If the determination in step S91 is NO, the control device 30 performs an operation to rotate the fourth fan 4021 of the fourth heat exchanger 402 (step S95). That is, the control device 30 starts operation in the low-level cooling mode. Thereby, the fourth heat exchanger 402 functions as a condenser. As a result, the third refrigerant in the low-concentration refrigerant circuit 300 is cooled by the fourth heat exchanger 402 .

Next, the control device 30 determines whether the frequency of the third compressor 301 (Comp 301) exceeds the threshold Y and the frequency of the third compressor 301 (Comp 301) is less than the threshold X ( step S96). That is, control device 30 determines whether or not the frequency of third compressor 301 is within proper range (2) shown in frame W20.

When determining YES in step S96, the control device 30 operates the second high-level refrigeration cycle (step S99). When the second high-order refrigeration cycle is to be operated, the control device 30 performs the same process as in step S101 already described in the second high-order refrigeration cycle (step S100). Thereby, in the second high-voltage refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary.

The control device 30 executes the low capacity operation mode after step S100. The processing of the low capacity mode of operation is disclosed in FIG. The processing of the low-capacity operation in the second embodiment is the same as the content of the control in the low-capacity operation mode of the first embodiment shown in FIG. 15, so description thereof will not be repeated here. In the second embodiment, even if the operation mode shifts to the low capacity operation mode, the operation of the fourth fan 4021 of the fourth heat exchanger 402 shown in step S95 is continued.

When determining NO in step S96, the control device 30 operates the first and second high-level refrigeration cycles (step S97).

When the first and second high-order refrigeration cycles are operated in step S97, the control device 30 performs the same processing as in step S101 already described in the first and second high-order refrigeration cycles (step S98).

As a result, in the first high-level refrigerant circuit 100, the rotational speed of the first fan 1021 of the first heat exchanger 102 and the opening degree of the first expansion valve 103 are adjusted as necessary. Also, in the second high-level refrigerant circuit 200, the rotational speed of the second fan 2021 of the second heat exchanger 202 and the opening degree of the second expansion valve 203 are adjusted as necessary.

The control device 30 executes the high capacity operation mode after step S98. The processing of the high capacity mode of operation is disclosed in FIG. The high-capacity operation processing of the second embodiment is the same as the control contents of the high-capacity operation mode of the first embodiment shown in FIG. 14, and thus description thereof will not be repeated here. In the second embodiment, even if the operation mode shifts to the high capacity operation mode, the operation of the fourth fan 4021 of the fourth heat exchanger 402 shown in step S95 is continued.

When determining YES in step S91, the control device 30 performs an operation to rotate the fourth fan 4021 of the fourth heat exchanger 402 (step S92). This process is similar to step S95 already described.

Next, the control device 30 determines whether or not the pressure P10 of the low-concentration refrigerant circuit 300 exceeds the threshold value B (step S93).

As already explained using FIG. 11, P10 indicates the pressure of the low-concentration refrigerant circuit 300. Control device 30 specifies pressure P<b>10 based on the output value of pressure sensor 10 provided in low-concentration refrigerant circuit 300 . The relationship between pressure P10 and threshold A and threshold B is shown in frame W10 in FIG.

When the pressure P10 does not exceed the threshold value B in step S93, the pressure P10 does not exceed the upper limit of the set pressure range. Therefore, if the control device 30 determines NO in step S93, the determination in step S93 is repeated until the pressure P10 exceeds the threshold value B.

When the pressure P10 exceeds the threshold value B in step S93, it can be determined that heat radiation is insufficient with the fourth heat exchanger 402 alone. Therefore, when the determination in step S93 is YES, the control device 30 operates the second high-order refrigeration cycle in order to reduce the pressure P10 to the range of (2) in the frame W10 of FIG. 11 (step S94). Thereby, the second high-level refrigerant circuit 200 is activated. When the second high-order refrigerant circuit 200 is activated, the second cascade condenser 204 cools the third refrigerant.

In this way, the control device 30 activates the second high-level refrigerant circuit 200 when the pressure P10 becomes higher than the range from the threshold value A to the threshold value B even if the fourth heat exchanger 402 is activated. , After step S94, the low capacity operation mode is executed. The details of the control in the low capacity operation mode are disclosed in FIG. The processing of the low-capacity operation in the second embodiment is the same as the content of the control in the low-capacity operation mode of the first embodiment shown in FIG. 15, so description thereof will not be repeated here. In the second embodiment, even if the operation mode shifts to the low capacity operation mode, the operation of the fourth fan 4021 of the fourth heat exchanger 402 shown in step S92 is continued.

According to the second embodiment described above, when the load on the refrigeration cycle is low, the pressure of the third refrigerant is abnormally increased by using the heat radiation function of the fourth heat exchanger 402 provided in the low-concentration refrigerant circuit 300. prevent it from rising. At this time, there is no need to operate the high-level refrigeration cycle. Therefore, it is possible to operate the refrigeration cycle with high efficiency.

In Embodiment 2, the control device 30 controls the timing of starting the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 based on the frequency set when starting the third compressor 301. do. Also in Embodiment 2, the low-capacity operation mode and the high-capacity operation mode are executed. The contents of the low-capacity operation mode and the high-capacity operation mode are as described in the first embodiment. However, in Embodiment 2, the fourth heat exchanger 402 is also activated. Therefore, the control device 30 according to the second embodiment controls the first high-order refrigerant circuit 100, the second high-order refrigerant circuit 200, and the 4 Control the heat exchanger 402 .

When the outside air temperature is low (for example, −5° C.), the control device 30 controls the rotation speed of the fourth fan 4021 without activating the high temperature refrigeration cycle so that the pressure in the low temperature refrigerant circuit 300 becomes abnormal. prevent it from rising. Especially in winter, the refrigeration cycle can be operated without activating the high-level refrigeration cycle, so the energy saving performance of the binary refrigeration cycle device 52 can be enhanced. Also, the service life of the high-order refrigeration cycle can be increased. As a result, the performance of the binary refrigeration cycle device 52 can be improved.

The third refrigerant flowing from the third compressor 301 to the fourth heat exchanger 402 is superheated steam. By activating the fourth heat exchanger 402 when the high-order refrigerating cycle is operated, part of the heat of the third refrigerant before flowing into the first cascade condenser 104 can be radiated by the fourth heat exchanger 402 . Therefore, in the first cascade condenser 104, heat can be exchanged between the third refrigerant and the first refrigerant in the two-phase region having a high heat transfer coefficient. The same applies to the second cascade capacitor 204 as well.

In low-load situations, the fourth fan 4021 of the fourth heat exchanger 402 is rotated without activating the high-level refrigeration cycle. As a result, the performance of the binary refrigerating cycle device 52 can be improved while suppressing an abnormal increase in the pressure of the low-concentration refrigerant circuit 300 when starting up the refrigerating cycle. For example, when the frequency of the third compressor 301 is lower than the threshold and the outside air temperature is lower than the set value, the dual refrigeration cycle device 52 is in a low load state.

On the other hand, when the frequency of the third compressor 301 is lower than the threshold but the outside air temperature is higher than the set value, the fourth fan 4021 is rotated and the second high-order refrigeration cycle is started. Accordingly, in a situation where heat treatment cannot be performed only by the fourth heat exchanger 402, it is possible to reliably suppress an abnormal increase in the pressure of the low-concentration refrigerant circuit 300 from the start of the refrigeration cycle.

At this time, since the first high-order refrigeration cycle does not start, it is possible to suppress an increase in the pressure of the low-order refrigerant circuit 300 by starting the minimum required equipment. Therefore, the energy saving performance of the binary refrigerating cycle device 52 can be enhanced. Also, the service life of the high-order refrigeration cycle can be increased. As a result, the performance of the binary refrigeration cycle device 52 can be improved.

Furthermore, when the frequency of the third compressor 301 is higher than the threshold and the outside air temperature is higher than the set value, the fourth fan 4021 may be rotated and the first and second high-order refrigerating cycles may be activated. Accordingly, in a situation where heat treatment cannot be performed only by the fourth heat exchanger 402 and the second high-order refrigeration cycle, it is possible to reliably suppress an abnormal increase in the pressure of the low-order refrigerant circuit 300 from the start of the refrigeration cycle.

<Modified Example of Control in Cooling Operation Mode 2>
FIG. 24 is a flow chart showing a modification of cooling operation mode 2 according to the second embodiment. A modification of cooling operation mode 2 according to the second embodiment will be described with reference to FIG. 24 .

The control device 30 first sets the target frequency of the third compressor 301 (Comp 301) from the outside air temperature and the evaporation temperature set in the indoor unit 2 (step S120). The processing of step S120 is the same as the processing of step S90 in FIG.

Next, the control device 30 determines whether or not the frequency of the third compressor 301 (Comp 301) is equal to or less than the threshold value Y (step S121). If the control device 30 determines that the frequency of the third compressor 301 set in step S120 is equal to or less than the threshold value Y, it determines whether the outside air temperature is equal to or less than the set value (step S122). Here, the outside air temperature is the temperature detected by the temperature sensor 20 .

When the controller 30 determines that the outside air temperature is equal to or lower than the set value, it performs an operation to rotate the fourth fan 4021 of the fourth heat exchanger 402 (step S123). This activates the fourth heat exchanger 402 . This process is the same as step S92 in FIG. After that, the control device 30 performs the processing of steps S124 to S125. This process is the same as the process of steps S93-S94 in FIG.

When the controller 30 determines in step S122 that the outside air temperature is not equal to or lower than the set value, the controller 30 rotates the fourth fan 4021 of the fourth heat exchanger 402 and activates the second high-level refrigerant circuit 200 (step S126). ). Next, control device 30 executes the same process as already described in step S101 in the second high-level refrigerating cycle (step S127), and shifts to the low capacity operation mode.

When the control device 30 determines in step S121 that the frequency of the third compressor 301 is not equal to or lower than the threshold value Y, it determines whether the outside air temperature is equal to or lower than the set value (step S128). When the control device 30 determines that the outside air temperature is equal to or lower than the set value, the control device 30 executes the process of step S126 already described.

When the controller 30 determines in step S128 that the outside air temperature is not equal to or lower than the set value, the controller 30 rotates the fourth fan 4021 of the fourth heat exchanger 402 and rotates the first high-level refrigerant circuit 100 and the second high-level refrigerant circuit. The circuit 200 is activated (step S129). Next, control device 30 executes the same process as already described in step S101 in the second high-level refrigeration cycle (step S130), and shifts to the high capacity operation mode.

As described above, in the modified example, the control device 30 controls the first high-order refrigerant circuit 100, the It controls the timing of starting the secondary refrigerant circuit 200 and the fourth heat exchanger 402 .

Various modifications described as the first embodiment can also be applied to the second embodiment. For example, any of the modifications of the first embodiment shown in FIGS. 4 to 7 may be applied to the second embodiment. Also, all of these modifications may be applied, or one or more of those modifications may be applied.

<Other Modifications>
The binary refrigerating cycle device 51 and the binary refrigerating cycle device 52 have a configuration in which one low-order refrigerating cycle is divided into two high-order refrigerating cycles. However, the binary refrigerating cycle device 51 and the binary refrigerating cycle device 52 may have a configuration in which one low-order refrigerating cycle is divided into three high-order refrigerating cycles. For example, the binary refrigerating cycle device 51 and the binary refrigerating cycle device 52 may further include a third higher refrigerating cycle.

The third high-order refrigeration cycle may have a higher cooling capacity than the first high-order refrigeration cycle. The third higher order refrigeration cycle may have a lower cooling capacity than the second higher order refrigeration cycle. A refrigerant different from the first to third refrigerants may be used in the third high-order refrigeration cycle. Any one of the first to third refrigerants may be used in the third high-order refrigeration cycle. A common type of refrigerant may be used in the first to third high-order refrigeration cycles.

A discharge temperature sensor that detects the temperature of the high-temperature refrigerant discharged from the third compressor 301 may be provided on the discharge side of the third compressor 301 . A low pressure sensor may be provided on the suction side of the third compressor 301 to calculate the low pressure saturation temperature ET.

In cooling operation mode 2 shown in FIG. 21, controller 30 rotates fourth fan 4021 of fourth heat exchanger 402 both when YES and NO are determined in step S91. drive to let Alternatively, when determining NO in step S91, the control device 30 may proceed to the process of step S96 without rotating the fourth fan 4021 of the fourth heat exchanger 402.

In the high-capacity operation mode related to Embodiment 2, control device 30 may control the rotation speed of fourth fan 4021 based on the output value of pressure sensor 10 in order to keep the pressure of the third refrigerant appropriate. . For example, when the control device 30 determines NO in step S42 of the flowchart shown in FIG. 14, the rotation speed of the fourth fan 4021 of the fourth heat exchanger 402 may be increased to the maximum speed. After that, the control device 30 may make the same determination as in step S41 before executing the process of step S44. The control device 30 may execute the process of step S44 when the pressure rise cannot be suppressed even if the rotational speed of the fourth fan 4021 of the fourth heat exchanger 402 is increased to the maximum number.

That is, based on the detection result of the pressure sensor 10, the control device 30 controls the fourth heat exchanger 402, the first high-level refrigerant circuit 100, or the second The refrigerating cycle of the two-higher refrigerant circuit 200 may be controlled.

In the low capacity operation mode related to Embodiment 2, control device 30 may control the rotation speed of fourth fan 4021 based on the output value of pressure sensor 10 in order to keep the pressure of the third refrigerant appropriate. . For example, when control device 30 determines in step S73 of the flowchart shown in FIG. 15 that the frequency of second compressor 201 (Comp 201) has reached the lower limit frequency, the fourth fan of fourth heat exchanger 402 The rotation speed of 4021 may be lowered by a certain number. After that, control device 30 may reduce the rotation speed of fourth fan 4021 and then execute the processing of steps S78 to S80. Furthermore, when the control device 30 determines NO in step S80, the rotation speed of the fourth fan 4021 may be decreased again by a certain number. Alternatively, the control device 30 may stop the fourth fan 4021 of the fourth heat exchanger 402 when determining NO in step S73.

That is, based on the detection result of the pressure sensor 10, the control device 30 adjusts the rotational speed of the fourth fan 4021 of the fourth heat exchanger 402 so that the pressure falls within the range of the first threshold to the second threshold. The refrigeration cycles of the high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 may be controlled.

As described above, according to the binary

refrigeration cycle devices

51 and 52 according to

Embodiments

1 and 2, the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 each have the maximum cooling Since the capacities are configured to differ from each other, it is possible to activate the high-level refrigeration cycle according to the cooling capacity required for the load in both the cooling operation mode and the stop operation mode. As a result, according to the binary refrigerating cycle apparatus according to the first embodiment, flexible operation corresponding to changes in the cooling capacity required for the load can be realized with a plurality of high-level refrigerating cycles.

Further, according to the binary

refrigeration cycle devices

51 and 52 according to

Embodiments

1 and 2, cooling of the high-order refrigeration cycle provided by the first high-order refrigerant circuit 100 and the second high-order refrigerant circuit 200 The capacity fluctuates based on the state of the refrigeration cycle of low-condensing refrigerant circuit 300 . For example, either the low-capacity operation mode or the high-capacity operation mode is selected according to the target frequency set for the third compressor 301 . As a result, according to the binary refrigerating cycle apparatus according to the first embodiment, flexible operation corresponding to changes in the cooling capacity required for the load can be realized with a plurality of high-level refrigerating cycles.

<Disclosure points>
Some points of this disclosure are summarized below.

(Point 1)
In the binary

refrigerating cycle devices

51 and 52 related to the present disclosure, at least the second compressor 201, the second heat exchanger 202, the second expansion valve 203, and the second cascade condenser 204 of the second higher refrigerating cycle One component has less capacity than the corresponding component of the first compressor 101, first heat exchanger 102, first expansion valve 103, and first cascade condenser 104 of the first higher order refrigeration cycle. Consists of components.

In general, if the high-level refrigeration cycle capacity is too large for the cooling capacity required for the stop operation mode, the compressor starts and stops frequently, reducing the reliability of the refrigeration cycle. However, in the present disclosure, by configuring the second high-order refrigeration cycle with smaller elements than the first high-order refrigeration cycle, the compressor of the high-order refrigeration cycle frequently starts and stops in the stop operation mode. can be suppressed.

In the binary

refrigerating cycle devices

51 and 52 related to the present disclosure, the high-level refrigerating cycle is divided into multiple units. As a result, even if a problem such as a failure occurs in some of the high-order refrigeration cycles, the other high-order refrigeration cycles can be operated. As a result, in the stop operation mode, it is possible to suppress an abnormal increase in pressure in the low-order refrigeration cycle.

In the binary

refrigerating cycle devices

51 and 52 related to the present disclosure, by using the binary refrigerating cycle, the condensation temperature of the low-order refrigerating cycle is reduced even when the high-pressure refrigerant is used in the low-order refrigerating cycle. It can be operated in this state.

In the binary

refrigerating cycle devices

51 and 52 related to the present disclosure, the pressure resistance required for the refrigerant pipes can be reduced because they are operated in a state where the condensation temperature of the lower refrigerating cycle is reduced.

The dual

refrigerating cycle devices

51 and 52 related to the present disclosure have separate refrigerating cycle circuits for the high and low levels, so they can flexibly comply with the refrigerant regulations of each country.

(Point 2)
In the dual

refrigeration cycle devices

51 and 52 related to the present disclosure, the capacity of the second high-level refrigeration cycle is less than 50% when the required high-level refrigeration cycle capacity (cooling capacity) is 100%. is preferred. Furthermore, it is more preferable that the capacity of the second high-level refrigeration cycle is 35% or less, and more preferably that the capacity of the second high-level refrigeration cycle is 20% or less. When reducing the capacity, it is preferable to reduce the size of the compressor. This is because downsizing the compressor is most effective in reducing cost and cooling capacity.

It is preferable to design the cooling capacity that can be output at the upper limit frequency of the second higher refrigeration cycle to be greater than the cooling capacity that can be output at the lower limit frequency of the first higher refrigeration cycle. The operation range can be expanded by providing a difference in the capacities of the high-level refrigeration cycles.

By designing so that the cooling capacity that can be output at the upper limit frequency of the second higher refrigeration cycle is greater than the cooling capacity that can be output at the lower limit frequency of the first higher refrigeration cycle, a boundary cooling capacity is required. It is possible to suppress frequent starting and stopping of the compressor when the

(Point 3)
In the binary

refrigerating cycle devices

51 and 52 according to the present disclosure, the first heat exchanger 102 and the second heat exchanger 202 used in the high-level refrigerating cycle are integrated into a fifth heat exchanger. 502. According to the present disclosure, the number of fans in the high-order refrigeration cycle can be reduced. As a result, space saving and cost reduction can be achieved.

(Point 4)
In the binary

refrigerating cycle devices

51 and 52 related to the present disclosure, the refrigerant used in the low refrigerating cycle is CO2. When CO2, which is a high-pressure refrigerant, is used in the low-order refrigeration cycle, the condensing pressure of the low-order refrigeration cycle can be reduced in the high-order refrigeration cycle. As a result, it is possible to apply a low withstand pressure piping and each element device to the reduced refrigeration cycle.

Because CO2 is a natural refrigerant, it can significantly reduce the total GWP of equipment. By using a non-combustible gas in the low temperature refrigeration cycle connected to the indoor unit of a warehouse or the like, the refrigerant will not burn when it leaks.

Compared to using CO in a single or double refrigeration cycle, the pressure used on the condensing side is lower compared to using CO in a single or double refrigeration cycle. The amount of refrigerant used can be reduced.

(Point 5)
By providing the uninterruptible power supply 205 in the second high-order refrigeration cycle, even if the low-order refrigeration cycle and the first high-order refrigeration cycle stop due to a power failure, the second high-order refrigeration cycle can be operated. . Thereby, the pressure rise of the low-order refrigerating cycle can be suppressed.

Since the uninterruptible power supply 205 is applied to the second high-order refrigeration cycle, which is smaller than the first high-order refrigeration cycle, the required power supply capacity can be reduced. Cost can be suppressed by reducing the required power supply capacity. Also, the size of the power supply can be reduced.

(Point 6)
In the dual

refrigerating cycle devices

51 and 52 according to the present disclosure, the refrigerant enclosed in the circuit of the second high-order refrigerating cycle is different from the refrigerant enclosed in the circuits of the low-order refrigerating cycle and the first high-order refrigerating cycle. . In particular, a second high-order refrigeration cycle having a small capacity is filled with a refrigerant having higher theoretical or practical performance than the refrigerants enclosed in the low-order refrigeration cycle and the first high-order refrigeration cycle. Thereby, the system COP can be improved. Also, reliability can be ensured.

(Point 7)
In the binary refrigerating cycle device 52 related to the present disclosure, the low refrigerating cycle transfers the heat of the high-temperature refrigerant discharged from the third compressor 301 to the air between the third compressor 301 and the first cascade condenser 104. It has a fourth heat exchanger 402 that dissipates heat. As a result, when the outside air temperature is low, it is possible to prevent the pressure of the third refrigerant in the low-level refrigerating cycle from abnormally increasing due only to heat radiation from the fourth heat exchanger 402 . In other words, the operation of the high-level refrigeration cycle is unnecessary. As a result, highly efficient operation becomes possible.

Also, in the low-order refrigeration cycle, part of the heat quantity of the third refrigerant can be radiated to the air. As a result, the superheated vapor third refrigerant is guided to the first cascade condenser 104 after being cooled by the fourth heat exchanger 402 . Therefore, in the first cascade condenser 104, heat can be exchanged between the third refrigerant and the first refrigerant in the two-phase region having a high heat transfer coefficient. The same applies to the second cascade capacitor 204 as well.

(Point 8)
In the dual refrigeration cycle device 52 according to the present disclosure, the fourth heat exchanger 402 is configured with a sixth heat exchanger 602 integrated with the first heat exchanger 102 and the second heat exchanger 202. . Also, the fourth heat exchanger 402 is composed of a seventh heat exchanger 702 integrated with the second heat exchanger 202 . According to the present disclosure, the number of fans in the high-order refrigeration cycle can be reduced. As a result, space saving and cost reduction can be achieved.

(Point 9)
The ratio of the heat transfer area of the fourth heat exchanger 402 to the total heat transfer area of the first heat exchanger 102, the second heat exchanger 202, and the fourth heat exchanger 402 is 3% or more to 50 % or in the range of 8% or more to less than 30%. By optimizing the ratio of the heat transfer area of the fourth heat exchanger 402, depending on the operating conditions of the refrigeration cycle, the low-level refrigerant circuit can be opened only by the heat radiation of the fourth heat exchanger 402 without activating the high-level refrigeration cycle. 300 pressure rise can be suppressed.

(Point 10)
In the binary

refrigeration cycle devices

51 and 52 according to the present disclosure, the gas refrigerant is fed back from the liquid receiver 304 via the check valve 305 to the inlet of the first cascade condenser 104 or the second cascade condenser 204. A refrigerant pipe 18 is provided. The return refrigerant pipe 18 is provided above the liquid receiver 304 . Therefore, only the gas refrigerant to be condensed can be returned to the first cascade condenser 104 or the second cascade condenser 204 in order to suppress the pressure rise of the refrigerant.

The liquid receiver 304 is provided at a position lower than the second cascade capacitor 204 in the vertical direction. Therefore, the liquid third refrigerant can be collected in the liquid receiver 304 by its own weight.

(Point 11)
The binary

refrigerating cycle devices

51 and 52 according to the present disclosure control the high-level refrigeration cycle to a preset threshold pressure range based on the detection result of the pressure sensor 10 provided in the condensing portion of the low-level refrigeration cycle. The rotation speed of the refrigeration cycle fans (first fan 1021, second fan 2021), the frequency of the compressors (first compressor 101, second compressor 201), and the expansion valves (first expansion valve 103, second expansion valve Controls the degree of opening of the valve 203).

The binary

refrigeration cycle devices

51 and 52 related to the present disclosure activate the high-level refrigeration cycle according to the detection result of the pressure sensor 10. When the load is large, not only the second high-order refrigeration cycle but also the first high-order refrigeration cycle are activated. Further, by controlling the rotation speed of the fan, the degree of opening of the expansion valve, and the frequency of the compressor in the high-level refrigerating cycle, the pressure rise in the low-level refrigerating cycle can be suppressed.

In particular, by controlling the number of rotations of the fans (first fan 1021, second fan 2021) (control of the condensation temperature), the pressure of the high-level refrigeration cycle is suppressed from abnormally rising, and the compression ratio is low. It is possible to reduce the rotation speed and maintain the compression ratio under various operating conditions.

In addition, by controlling the opening degree of the expansion valves (first expansion valve 103, second expansion valve 203) (SH control), the first compressor 101 and the second compressor on the high side are controlled according to the operating state. 201 can be made to inhale gaseous refrigerant. By causing first compressor 101 and second compressor 201 to suck gas refrigerant, the reliability of first compressor 101 and second compressor 201 can be improved.

By controlling the frequency of the compressors (first compressor 101, second compressor 201) so that the pressure becomes the set pressure, the cooling capacity of the high-level refrigerating cycle is controlled according to the load of the low-level refrigerating cycle. can do. Furthermore, by giving a range to the pressure threshold value, it is possible to suppress frequent starting and stopping of the compressor and to prevent frequent changes in the frequency of the compressor.

For example, the third compressor 301 of the low-order refrigeration cycle and the second compressor 201 of the second high-order refrigeration cycle are started. When the condensation capacity of the low-order refrigeration cycle exceeds the evaporation capacity of the high-order refrigeration cycle, the pressure of the third refrigerant increases, for example, the pressure corresponding to 3° C. or higher. In this case, the frequency of the second compressor 201 of the second high-order refrigerating cycle is increased until the pressure of the third refrigerant reaches the reference value (for example, the pressure corresponding to 0°C). When the pressure of the second compressor 201 reaches the target frequency, the operation is maintained. When the load is large, the first compressor 101 of the first high-order refrigerating cycle is started. However, if the frequency of the third compressor 301 when activated is extremely high, the first and second high-order refrigeration cycles may be activated simultaneously.

The pressure sensor 10 may be provided at any position in the section from the discharge part of the third compressor 301 to the inlet of the first cascade condenser 104, but the third compressor 301 where the third refrigerant pressure is highest is preferably provided in the ejection portion of the Among the high-order refrigeration cycles, it is preferable to start the second high-order refrigeration cycle, which basically has a small capacity, preferentially to suppress an abnormal increase in the pressure in the low-order refrigerant circuit 300 . This is because the second high-level refrigerating cycle has a smaller capacity than the first high-level refrigerating cycle, so it is possible to prevent the compressor from frequently starting and stopping. Also, when the second high-order refrigerating cycle is filled with a refrigerant with high theoretical performance, highly efficient operation is possible.

(Point 12)
The dual

refrigerating cycle devices

51 and 52 related to the present disclosure control the activation timings of the first high-level refrigerating cycle and the second high-level refrigerating cycle based on the set frequency when the third compressor 301 is started. For example, when the frequency of the third compressor 301 is lower than the threshold, only the small-capacity second high refrigeration cycle is activated, and when the frequency of the third compressor 301 is higher than the threshold, the first high refrigeration cycle is activated from the time of activation. Start the primary refrigerating cycle and the secondary refrigerating cycle.

As a result, it is possible to reliably suppress a sudden increase in pressure when the refrigeration cycle is started. Further, by not starting the first high-level refrigerating cycle when the frequency of the third compressor 301 is low, it is possible to prevent the compressor from frequently repeating starting and stopping on the high-level refrigerating cycle side. As a result, reliability can be improved. Moreover, since the cooling operation can be performed without performing unnecessary equipment operations, the performance can be improved.

(Point 13)
The binary refrigerating cycle device 52 according to the present disclosure controls the rotation speed of the fourth fan 4021 of the fourth heat exchanger 402 so that the pressure is maintained within the set range based on the detection result of the pressure sensor 10 The rotation speed of the fans (first fan 1021, second fan 2021) of the high-level refrigeration cycle, the frequency of the compressors (first compressor 101, second compressor 201), and the expansion valves (first expansion valve 103, second 2 Controls the opening of the expansion valve 203).

According to the present disclosure, by providing the fourth heat exchanger 402, when the outside air temperature is low (eg, −5° C.), the rotation speed of the fourth fan 4021 can be controlled without activating the high-level refrigeration cycle. can prevent the pressure in the low-concentration refrigerant circuit 300 from abnormally rising.

(Point 14)
The dual refrigeration cycle device 52 according to the present disclosure determines the start timing of the fan of the fourth heat exchanger 402 and the start of the first high-order refrigeration cycle based on the set frequency and the outside air temperature when the third compressor 301 is started. timing and start-up timing of the second high-order refrigeration cycle.

<Characteristics of Disclosure>
Some of the features of this disclosure are listed below.

(1) A binary refrigeration cycle device (51) according to the present disclosure includes a first high-level refrigerant circuit (100) that circulates a first refrigerant and a second high-level refrigerant circuit (200) that circulates a second refrigerant. , a low-condensing refrigerant circuit (300) for circulating the third refrigerant, a first cascade condenser (104) for exchanging heat between the first refrigerant and the third refrigerant, and between the second refrigerant and the third refrigerant. The first high-order refrigerant circuit (100) includes a first compressor (101), a first heat exchanger (102), and a first expansion valve (103), the first compressor (101), the first heat exchanger (102), the first expansion valve (103), the first cascade condenser (104), and the first compressor (101) The first refrigerant is circulated in sequence, and the second high-order refrigerant circuit (200) has a second compressor (201), a second heat exchanger (202), and a second expansion valve (203), circulating the second refrigerant in order of the second compressor (201), the second heat exchanger (202), the second expansion valve (203), the second cascade condenser (204), and the second compressor (201); The low-pressure refrigerant circuit (300) has a third compressor (301), a third heat exchanger (302), and a third expansion valve (303). The third refrigerant is circulated in the order of the heat exchanger (302) and the third compressor (301), and the first high-level refrigerant circuit (100) and the second high-level refrigerant circuit (200) each have a maximum cooling capacity of configured differently from each other (Fig. 3).

According to the present disclosure, it is possible to provide a binary refrigerating cycle device capable of realizing flexible operation with a plurality of high-order refrigerating cycles according to changes in the cooling capacity required for the load.

(2) The maximum cooling capacity of the second high-order refrigerant circuit (200) is less than 50% of the maximum cooling capacity of the first high-order refrigerant circuit (100) and the second high-order refrigerant circuit (200) (Fig. 3 ).

(3) At least one component of the second compressor (201), the second heat exchanger (202), the second expansion valve (203), and the second cascade condenser (204) (101), first heat exchanger (102), first expansion valve (103) and first cascade condenser (104).

(4) The maximum cooling capacity of the first high-order refrigerant circuit (100) is greater than the maximum cooling capacity of the second high-order refrigerant circuit (200), and is within the range of the cooling capacity of the first high-order refrigerant circuit (100). , the upper limit of the cooling capacity of the second high-order refrigerant circuit (200) (FIGS. 8 and 9).

(5) The first heat exchanger (102) and the second heat exchanger (202) are composed of an integrated heat exchanger (502).

(6) The third refrigerant is carbon dioxide (Fig. 3).
(7) The second high-voltage refrigerant circuit (200) is connected to an uninterruptible power supply (205) (Figs. 6 and 7).

(8) The first refrigerant (R1234yf, etc.) is a different type of refrigerant from the second refrigerant (R32, etc.).

(9) A low-level refrigerant circuit (300) comprises a liquid receiver (304) arranged between a second cascade condenser (204) and a third expansion valve (303), and from the second cascade condenser (204) a return route (route of return refrigerant pipe 18) for returning the third refrigerant that has flowed into the liquid receiver (304) to the first cascade condenser (104) or the second cascade condenser (204); A check valve (305) is provided to block the flow of the third refrigerant in the direction of the liquid receiver (304).

(10) The return path is connected to the top of the liquid receiver (304) (Fig. 2).
(11) The liquid receiver (304) is placed vertically lower than the position of the second cascade capacitor (204) (Fig. 2).

The embodiments disclosed this time should be considered illustrative in all respects and not restrictive. The scope of the present disclosure is indicated by the scope of the claims rather than the description of the above-described embodiments, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

1 outdoor unit, 2 indoor unit, 10 pressure sensor, 15 extension pipe, 16 first refrigerant pipe, 17 second refrigerant pipe, 18 return refrigerant pipe, 20 temperature sensor, 30 control device, 31 processor, 32 memory, 51, 52 Binary refrigerating cycle device, 100 first high-level refrigerant circuit, 101 first compressor, 102 first heat exchanger, 103 first expansion valve, 104 first cascade condenser, 200 second high-level refrigerant circuit, 201 second compressor, 202 second heat exchanger, 203 second expansion valve, 204 second cascade condenser, 205 uninterruptible power supply, 300 low-level refrigerant circuit, 301 third compressor, 302 third heat exchanger, 303 third Expansion valve, 304 receiver, 305 check valve, 402 fourth heat exchanger, 502 fifth heat exchanger, 602 sixth heat exchanger, 702 seventh heat exchanger, 1021 first fan, 2021 second fan , 3021 3rd fan, 4021 4th fan, 5021 5th fan, 6021 6th fan, 7021 7th fan, AT10 outside air temperature, R10 area where high temperature operation is not required, R20 high temperature operation is required Area, W10, W20 frames.

Claims

A binary refrigeration cycle device,
a first high-level refrigerant circuit that circulates the first refrigerant;
a second high-level refrigerant circuit that circulates the second refrigerant;
a low-concentration refrigerant circuit that circulates the third refrigerant;
a first cascade condenser for exchanging heat between the first refrigerant and the third refrigerant;
a second cascade condenser for exchanging heat between the second refrigerant and the third refrigerant;
The first high-level refrigerant circuit has a first compressor, a first heat exchanger, and a first expansion valve, and the first compressor, the first heat exchanger, the first expansion valve, circulating the first refrigerant in the order of the first cascade condenser and the first compressor;
The second high-level refrigerant circuit has a second compressor, a second heat exchanger, and a second expansion valve, and the second compressor, the second heat exchanger, the second expansion valve, circulating the second refrigerant in the order of the second cascade condenser and the second compressor;
The low-pressure refrigerant circuit has a third compressor, a third heat exchanger, and a third expansion valve, and comprises the third compressor, the first cascade condenser, the second cascade condenser, the third circulating the third refrigerant in the order of the expansion valve, the third heat exchanger, and the third compressor;
A binary refrigeration cycle apparatus, wherein the first high-level refrigerant circuit and the second high-level refrigerant circuit are configured to have different maximum cooling capacities.
2. The dual refrigeration of claim 1, wherein the maximum cooling capacity of the second higher order refrigerant circuit is less than 50% of the maximum cooling capacity of the first higher order refrigerant circuit and the second higher order refrigerant circuit. cycle equipment.
At least one component of the second compressor, the second heat exchanger, the second expansion valve, and the second cascade condenser comprises the first compressor, the first heat exchanger, the first 3. The binary refrigerating cycle apparatus according to claim 1, wherein the refrigerating cycle apparatus is configured by a component having a capacity smaller than that of the corresponding component of the one expansion valve and the first cascade condenser.
The maximum cooling capacity of the first high-order refrigerant circuit is greater than the maximum cooling capacity of the second high-order refrigerant circuit,
The binary refrigeration cycle according to any one of claims 1 to 3, wherein the range of the cooling capacity of the first high-order refrigerant circuit includes an upper limit value of the cooling capacity of the second high-order refrigerant circuit. Device.
The binary refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the first heat exchanger and the second heat exchanger are configured as an integrated heat exchanger.
The binary refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the third refrigerant is carbon dioxide.
The binary refrigeration cycle apparatus according to any one of claims 1 to 6, wherein the second high-order refrigerant circuit is connected to an uninterruptible power supply.
The binary refrigerating cycle apparatus according to any one of claims 1 to 7, wherein the first refrigerant is a different kind of refrigerant from the second refrigerant.
The low-concentration refrigerant circuit is
a liquid receiver disposed between the second cascade condenser and the third expansion valve;
a feedback path for returning the third refrigerant that has flowed into the liquid receiver from the second cascade condenser to the first cascade condenser or the second cascade condenser;
The binary refrigeration cycle according to any one of claims 1 to 8, wherein the return path is provided with a check valve that prevents the third refrigerant from flowing in the direction of the liquid receiver. Device.
The binary refrigeration cycle apparatus according to claim 9, wherein said return path is connected to the upper part of said liquid receiver.
The binary refrigerating cycle apparatus according to claim 9 or 10, wherein the liquid receiver is arranged at a position lower in the vertical direction than the position of the second cascade condenser.