JP7229256B2 - Freezer and heat source side unit - Google Patents

Description

The present invention relates to a refrigerating device and a heat source side unit.

Conventionally, a refrigeration system is known in which a cooling operation by an evaporator (use-side heat exchanger) and a defrosting operation for the evaporator are switched.

Japanese Patent Laying-Open No. 2006-336967 discloses a refrigeration system in which high-temperature refrigerant discharged from a compressor is supplied to a heat exchanger to be defrosted during defrosting operation.

JP-A-2006-336967

However, in the above refrigeration system, the refrigerant supplied from the compressor to the heat exchanger to be defrosted during the defrosting operation flows out of the heat exchanger and then is compressed without flowing through other heat exchangers. inhaled into the machine. Therefore, in the refrigeration system, it is necessary to limit the amount of heat supplied to the heat exchanger to be defrosted, and it is difficult to improve the defrosting efficiency.

A main object of the present invention is to provide a refrigerating apparatus with higher defrosting efficiency than a conventional refrigerating apparatus and a heat source side unit forming part of the refrigerating apparatus.

A refrigerating apparatus according to the present invention includes a refrigerant circuit through which a refrigerant circulates. A refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow switching section. In the flow path switching unit, the heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, A first state that sequentially flows through the first pressure reducing section and the first evaporator, the utilization side heat exchanger acting as the second condenser, the auxiliary heat exchanger acting as the second evaporator, and the refrigerant flowing through the compressor , the second condenser, the second depressurizing section, and the second evaporator in order.

According to the present invention, since the auxiliary heat exchanger acts as an evaporator in the second state, the refrigerating apparatus having higher defrosting efficiency than the conventional refrigerating apparatus and the heat source side unit constituting a part of the refrigerating apparatus are provided. can provide.

1 is a diagram showing a refrigerating device and a heat source side unit according to Embodiment 1; FIG. FIG. 2 is a diagram showing a first state of the refrigerating apparatus and the heat source side unit shown in FIG. 1; It is a figure which shows the refrigeration apparatus shown by FIG. 1, and the 2nd state of the heat-source side unit. FIG. 7 is a diagram showing a refrigerating device and a heat source side unit according to Embodiment 2; FIG. 5 is a diagram showing a first state of the refrigerating device and the heat source side unit shown in FIG. 4; FIG. 5 is a diagram showing a second state of the refrigerating device and the heat source side unit shown in FIG. 4; FIG. 10 is a diagram showing a refrigerating device and a heat source side unit according to Embodiment 3; FIG. 8 is a diagram showing a first state of the refrigerating device and the heat source side unit shown in FIG. 7; FIG. 8 is a diagram showing a second state of the refrigerating device and the heat source side unit shown in FIG. 7; FIG. 12 is a diagram showing a refrigerating device and a heat source side unit according to Embodiment 4; FIG. 11 is a diagram showing a first state of the refrigerating device and the heat source side unit shown in FIG. 10 ; FIG. 11 is a diagram showing a second state of the refrigerating device and the heat source side unit shown in FIG. 10 ; FIG. 12 is a diagram showing a modification of the refrigerating apparatus and the heat source side unit according to Embodiment 4; FIG. 7 is a diagram showing another modification of the refrigerating apparatus and the heat source side unit according to Embodiment 1; FIG. 9 is a diagram showing a first state of still another modified example of the refrigerating apparatus and the heat source side unit according to Embodiment 1; FIG. 16 is a diagram showing a second state of the refrigerating device and the heat source side unit shown in FIG. 15; FIG. 17 is a diagram showing a first state of a modified example of the refrigerating device and the heat source side unit shown in FIGS. 15 and 16; FIG. 9 is a diagram showing still another modification of the refrigeration system and the heat source side unit according to Embodiment 1;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated in principle.

Embodiment 1.
As shown in FIGS. 1 to 3, a refrigeration system 100 according to Embodiment 1 includes a refrigerant circuit in which refrigerant circulates. The refrigerant circuit includes a compressor 1, a heat source side heat exchanger 2, an auxiliary heat exchanger 3, a first pressure reducing section 4, a user side heat exchanger 5, a second pressure reducing section 6, a plurality of flow path switching sections, and a plurality of Includes rectifier. Refrigerating apparatus 100 further includes a first fan 7 , a second fan 8 and a third fan 9 . The refrigerant is not particularly limited, but is, for example, a refrigerant with a low global warming potential (GWP) and includes at least one selected from the group consisting of R410A, R32 and _CO2 . The refrigerant may be a mixed refrigerant containing at least one selected from the above group.

The compressor 1 has a suction port 1A through which the refrigerant is sucked and a discharge port 1B through which the refrigerant is discharged. The compressor 1 is, for example, an inverter compressor whose rotational speed is controlled by an inverter. The heat source side heat exchanger 2, the auxiliary heat exchanger 3, and the utilization side heat exchanger 5 are provided so as to perform heat exchange between, for example, refrigerant and air. The heat source side heat exchanger 2 has a first inflow/outflow portion 2A and a second inflow/outflow portion 2B through which the refrigerant flows. The auxiliary heat exchanger 3 has a third inflow/outflow portion 3A and a fourth inflow/outflow portion 3B through which the refrigerant flows. The user-side heat exchanger 5 has a fifth inflow/outflow portion 5A and a sixth inflow/outflow portion 5B through which the refrigerant flows. The first decompression section 4 and the second decompression section 6 are, for example, electronic expansion valves whose opening can be adjusted. Note that the first decompression unit 4 and the second decompression unit 6 may be capillaries whose opening cannot be adjusted.

The user-side heat exchanger 5 is arranged inside a space to be cooled by the refrigerating apparatus 100, for example, inside a freezer. The compressor 1, the heat source side heat exchanger 2, the auxiliary heat exchanger 3, the first pressure reducing section 4, and the second pressure reducing section 6 are arranged outside the space, for example, outside the freezer. The first fan 7 supplies air outside the freezer to the heat source side heat exchanger 2 . The second fan 8 supplies air outside the freezer to the auxiliary heat exchanger 3 . The third fan 9 supplies the air in the freezer to the utilization side heat exchanger 5 .

The plurality of flow path switching units are provided so as to switch between a first state and a second state, which will be described later, by switching the circulation path of the refrigerant in the refrigerant circuit. The multiple flow path switching units include, for example, a first flow path switching unit and a second flow path switching unit. 10 A of 1st flow-path switching parts have the 1st opening-and-closing valve 11, the 2nd opening-and-closing valve 12, the 5th opening-and-closing valve 15, and the 6th opening-and-closing valve 16, for example. The second flow path switching section 10B has a third on-off valve 13 and a fourth on-off valve 14, for example. Note that the first flow path switching unit may have two three-way valves instead of the four on-off valves. The second flow path switching section may have one three-way valve instead of the two on-off valves.

The refrigerant circuit includes a first flow path and a second flow path connecting between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the usage side heat exchanger 5, and a sixth flow path of the usage side heat exchanger 5. It has a third flow path and a fourth flow path that connect between the inflow/outlet portion 5B and the suction port 1A of the compressor 1 .

The first flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outflow part 5A of the heat utilization side heat exchanger 5 via the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . In the first flow path, the discharge port 1B of the compressor 1, the auxiliary heat exchanger 3, the heat source side heat exchanger 2, the first pressure reducing section 4, and the fifth inflow/outflow section 5A of the utilization side heat exchanger 5 are arranged in series in this order. Connected. A first on-off valve 11 and a fifth on-off valve 15 for opening and closing the first flow path are arranged in the first flow path. The first on-off valve 11 is arranged between the discharge port 1B of the compressor 1 and the third inflow/outflow portion 3A of the auxiliary heat exchanger 3 . The fifth opening/closing valve 15 is located between the second inflow/outflow portion 2B and the first pressure reducing portion 4 of the heat source side heat exchanger 2 and between the discharge port 1B of the compressor 1 and the first pressure reducing portion 4. are placed.

The second flow path connects between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat utilization side heat exchanger 5 without interposing the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 therebetween. In the second flow path, the discharge port 1B of the compressor 1 and the fifth inflow/outflow part 5A of the utilization side heat exchanger 5 are connected in series. A second on-off valve 12 and a sixth on-off valve 16 for opening and closing the second flow path are arranged in the second flow path. The second on-off valve 12 is arranged between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat exchanger 5 on the utilization side. The sixth on-off valve 16 is located between the second inflow/outflow portion 2B of the heat source side heat exchanger 2 and the fifth inflow/outflow portion 5A of the utilization side heat exchanger 5, and is located between the discharge port 1B of the compressor 1 and the utilization side. It is arranged between the fifth inflow/outflow part 5A of the heat exchanger 5 .

The first flow path and the second flow path have a first branch point, a second branch point, a fifth branch point, and a sixth branch point where the refrigerant splits or merges. In the first channel and the second channel, the first branch point, the second branch point, the fifth branch point, and the sixth branch point are connected in series in this order. The first branch point is arranged upstream of the third inflow/outflow part 3A of the auxiliary heat exchanger 3 in the first flow path. The second branch point is arranged downstream of the second inflow/outflow section 2B of the heat source side heat exchanger 2 and upstream of the first pressure reducing section 4 in the first flow path. The fifth branch point is arranged downstream of the second branch point and upstream of the first pressure reducing section 4 in the first flow path. The sixth branch point is arranged downstream of the first pressure reducing section 4 in the first flow path.

The first flow path and the second flow path connect the first branch point and the second branch point in parallel, and connect the fifth branch point and the sixth branch point in parallel. The first flow path and the second flow path connect the discharge port 1B of the compressor 1 and the first branch point with a common pipeline, and connect the sixth branch point and the utilization side heat exchanger 5. It connects with the 5th inflow/outlet part 5A by the common conduit line.

From a different point of view, the second flow path has a first bypass flow path and a second bypass flow path branched from the first flow path. The first bypass channel connects between the first branch point and the second branch point. The second bypass channel connects between the fifth branch point and the sixth branch point. Thereby, the first bypass flow path bypasses the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . The second bypass flow path bypasses the first pressure reducing section 4 . The first flow path switching section 10A is provided so as to switch between the first flow path and the first bypass flow path. The third flow path switching section 10C is provided to switch between the first flow path and the second bypass flow path. The second flow path is formed by closing the first flow path and opening the first bypass flow path and the second bypass flow path by the first flow switching portion 10A and the third flow switching portion 10C. be done.

As shown in FIGS. 1 to 3, the first flow channel and the second flow channel are composed of common pipes, namely, a first common flow channel C1, a second common flow channel C2, and a fifth common flow channel. has a path C5. Furthermore, the first flow path has a first non-common flow path L1 and a fifth non-common flow path L5 that are different from the second flow path. The second flow path has a second non-common flow path L2 and a sixth non-common flow path L6 which are different from the first flow path.

One end of the first common channel C1 is connected to the discharge port 1B of the compressor 1 . The other end of the first common channel C1 is connected to the first branch point. The first common flow path C1 is arranged between the discharge port 1B of the compressor 1 and the first flow path switching section 10A.

One end of the second common channel C2 is connected to the second branch point. The other end of the second common channel C2 is connected to the fifth branch point. The second common flow path C2 is arranged between the second inflow/outflow section 2B of the heat source side heat exchanger 2 and the first pressure reducing section 4 in the first flow path.

One end of the fifth common channel C5 is connected to the sixth branch point. The other end of the fifth common flow path C5 is connected to the fifth inflow/outflow part 5A of the utilization side heat exchanger 5 . The fifth common flow path C5 is arranged between the first pressure reducing section 4 and the fifth inflow/outflow section 5A of the use side heat exchanger 5 in the first flow path.

The first non-common flow path L1 and the second non-common flow path L2 connect the first common flow path C1 and the second common flow path C2 in parallel with each other. One end of each of the first non-common flow path L1 and the second non-common flow path L2 is connected to a first branch point. The other ends of the first non-common flow path L1 and the second non-common flow path L2 are connected to a second branch point. The second non-common flow path L2 constitutes the first bypass flow path.

The fifth non-common flow path L5 and the sixth non-common flow path L6 connect the second common flow path C2 and the fifth common flow path C5 in parallel with each other. One end of each of the fifth non-common flow path L5 and the sixth non-common flow path L6 is connected to a fifth branch point. The other ends of the fifth non-common flow path L5 and the sixth non-common flow path L6 are connected to a sixth branch point. The sixth non-common flow path L6 constitutes the second bypass flow path.

In the first channel, the first common channel C1, the first non-common channel L1, the second common channel C2, the fifth non-common channel L5, and the fifth common channel C5 are connected in series. . In the second channel, the first common channel C1, the second non-common channel L2, the second common channel C2, the sixth non-common channel L6, and the fifth common channel C5 are connected in series. .

The first non-common flow path L<b>1 includes the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . The fifth non-common flow path L5 includes the first pressure reducing section 4 . That is, the first flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the heat utilization side heat exchanger 5 to the auxiliary heat exchanger 3, the heat source side heat exchanger 2, and the first pressure reducing unit. Connect via part 4. The first non-common flow path L1 further includes a first on-off valve 11 . The fifth non-common flow path L5 further includes a fifth on-off valve 15 . That is, when the first on-off valve 11 and the fifth on-off valve 15 are opened, the refrigerant flows through the first channel.

The second non-common flow path L<b>2 does not include the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . The sixth non-common flow path L6 does not include the first pressure reducing section 4 . In other words, the second flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the heat utilization side heat exchanger 5 to the auxiliary heat exchanger 3, the heat source side heat exchanger 2, and the first pressure reducing unit. Connect without going through part 4. The second non-common flow path L2 includes a second on-off valve 12 . The sixth non-common flow path L6 includes a sixth on-off valve 16 . That is, when the second on-off valve 12 and the sixth on-off valve 16 are opened, the refrigerant flows through the second flow path.

The third flow path connects the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 via the second pressure reducing portion 6 and the auxiliary heat exchanger 3 . In the third flow path, the sixth inflow/outflow section 5B of the utilization side heat exchanger 5, the second pressure reducing section 6, the auxiliary heat exchanger 3, and the suction port 1A of the compressor 1 are connected in series in this order. A third on-off valve 13 for opening and closing the third flow path is arranged in the third flow path. The third on-off valve 13 is arranged between the fourth inflow/outflow portion 3B of the auxiliary heat exchanger 3 and the suction port 1A of the compressor 1 .

The fourth flow path connects the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 without the second pressure reducing portion 6 and the auxiliary heat exchanger 3 interposed therebetween. In the fourth flow path, the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 are connected in series. A fourth on-off valve 14 that opens and closes the fourth flow path is arranged in the fourth flow path. The fourth opening/closing valve 14 is arranged between the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 .

The third flow path and the fourth flow path have a third branch point and a fourth branch point where the refrigerant splits or merges. In the third flow path and the fourth flow path, the third branch point and the fourth branch point are connected in series in order. The third branch point is arranged upstream of the second pressure reducing section 6 in the third flow path. The fourth branch point is arranged downstream of the fourth inflow/outflow part 3B of the auxiliary heat exchanger 3 in the third flow path.

The third flow path and the fourth flow path connect in parallel between the third branch point and the fourth branch point. The third flow path and the fourth flow path connect between the sixth inflow/outlet portion 5B of the utilization side heat exchanger 5 and the third branch point with a common pipeline, and the fourth branch point and the compressor 1 and the suction port 1A are connected by a common conduit.

From a different point of view, the fourth flow path has a third bypass flow path branched from the third flow path. One end of the third bypass channel is connected to the third branch point, and the other end of the third bypass channel is connected to the fourth branch point. The second flow path switching section 10B is provided so as to switch between the third flow path and the third bypass flow path. The fourth flow path is formed by closing the third flow path and opening the third bypass flow path by the second flow path switching portion 10B.

As shown in FIGS. 1 to 3, the third flow channel and the fourth flow channel have a third common flow channel C3 and a fourth common flow channel C4 configured by common pipe lines. Furthermore, the third flow path has a third non-common flow path L3 configured by a pipeline different from that of the fourth flow path. The fourth flow path has a fourth non-common flow path L4 configured by a pipeline different from that of the third flow path.

One end of the third common channel C3 is connected to the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 . That is, the third common flow path C3 is connected to the fifth common flow path C5 via the heat exchanger 5 on the user side. The other end of the third common channel C3 is connected to the third branch point. The third common channel C3 is arranged between the sixth inflow/outlet portion 5B of the utilization side heat exchanger 5 and the second pressure reducing portion 6 in the third channel.

One end of the fourth common channel C4 is connected to the fourth branch point. The other end of the fourth common flow path C4 is connected to the suction port 1A of the compressor 1. As shown in FIG. The fourth common channel C4 is arranged between the second channel switching portion 10B and the suction port 1A of the compressor 1 .

The third non-common flow path L3 and the fourth non-common flow path L4 connect the third common flow path C3 and the fourth common flow path C4 in parallel with each other. The fourth non-common flow path L4 constitutes the third bypass flow path. In the third channel, the third common channel C3, the third non-common channel L3, and the fourth common channel C4 are connected in series. In the fourth channel, the third common channel C3, the fourth non-common channel L4, and the fourth common channel C4 are connected in series.

The third non-common flow path L3 includes the second pressure reducing section 6 and the auxiliary heat exchanger 3 . The third flow path connects the sixth inflow/outflow section 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 via the second pressure reducing section 6 and the auxiliary heat exchanger 3 . The fourth non-common flow path L4 does not include the second pressure reducing section 6 and the auxiliary heat exchanger 3. The fourth flow path connects the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 without interposing the second pressure reducing portion 6 and the auxiliary heat exchanger 3 therebetween. The third non-common flow path L3 further includes a third on-off valve 13 . The fourth non-common flow path L4 further includes a fourth on-off valve 14 . That is, the refrigerant flows through the third channel when the third on-off valve 13 is opened, and the refrigerant flows through the fourth channel when the fourth on-off valve 14 is opened.

As shown in FIG. 2, in the first state, the first on-off valve 11, the fourth on-off valve 14 and the fifth on-off valve 15 are opened, and the second on-off valve 12, the third on-off valve 13 and the sixth on-off valve are opened. 16 is closed. As shown in FIG. 3, in the second state, the first on-off valve 11, the fourth on-off valve 14, and the fifth on-off valve 15 are closed, and the second on-off valve 12, the third on-off valve 13, and the sixth on-off valve 12 are closed. The on-off valve 16 is opened.

The first non-common flow path L1 of the first flow path and the third non-common flow path L3 of the third flow path include the auxiliary heat exchanger 3 in common. That is, the first non-common flow path L1 and the third non-common flow path L3 have a sixth common flow path C6 including the auxiliary heat exchanger 3.

The refrigerant circuit further includes a plurality of rectifiers that rectify the refrigerant. The multiple rectifiers have a first rectifier 17 , a second rectifier 18 , and a third rectifier 19 .

The first flow straightening section 17 is located between the second pressure reducing section 6 and the third inflow/outflow section 3A of the auxiliary heat exchanger 3 in the third non-common flow path L3. It is arranged between the channel C6. The first rectifying section 17 passes the refrigerant from the second pressure reducing section 6 toward the third inflow/outflow section 3A of the auxiliary heat exchanger 3, and restricts the flow of the refrigerant in the opposite direction.

The second rectifying section 18 is located between the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 and the first inflow/outflow section 2A of the heat source side heat exchanger 2 in the first non-common flow path L1, specifically, the sixth common flow path L1. It is arranged between the flow path C6 and the first inflow/outflow part 2A of the heat source side heat exchanger 2 . The second straightening section 18 passes the refrigerant from the fourth inflow/outlet section 3B of the auxiliary heat exchanger 3 to the first inflow/outflow section 2A of the heat source side heat exchanger 2, and restricts the flow of the refrigerant in the opposite direction.

The third straightening section 19 is arranged between the second inflow/outflow section 2B of the heat source side heat exchanger 2 and the second branch point in the first non-common flow path L1. The third rectifying portion 19 allows the refrigerant from the second inflow/outlet portion 2B of the heat source side heat exchanger 2 to flow toward the second common flow path C2, and restricts the flow of the refrigerant in the opposite direction.

The refrigeration system 100 includes a heat source side unit 200 and a decompression unit 300 arranged outside a space to be cooled, and a user side unit 400 arranged inside the space to be cooled. The heat source side unit 200 is configured separately from the decompression unit 300, for example. The heat source side unit 200 is accommodated in the first housing. The decompression unit 300 is housed in the fifth housing. The first housing forms an outer shell of the heat source side unit 200 . The fifth housing forms an outer shell of the decompression unit 300 . The first housing includes a part of the refrigerant circuit including the compressor 1, the heat source side heat exchanger 2, the auxiliary heat exchanger 3, and the second pressure reducing section 6, and the first fan 7 and the second fan 8. housed inside. The fifth housing accommodates a portion of the refrigerant circuit including the first pressure reducing section 4 inside. A portion of each of the first flow path and the second flow path, the third flow path, and the fourth flow path are arranged inside the first housing. Other parts of the first channel and the second channel are arranged inside the fifth housing.

The user unit 400 has a second housing (not shown). The second housing forms the outer shell of the user unit 400 . The second housing accommodates another part of the refrigerant circuit including the user-side heat exchanger 5 and the third fan 9 inside. A part of the refrigerant circuit arranged inside the first housing and another part of the refrigerant circuit arranged inside the second housing are connected via two pipes. .

The heat source side unit 200 includes, for example, a first unit 500 and a second unit 600, and is configured as a connection body in which each unit is detachably connected to each other. The first unit 500 includes a compressor 1, a heat source side heat exchanger 2, and a first fan 7, for example. The second unit 600 includes the auxiliary heat exchanger 3, the second fan 8, the first flow switching section 10A, the second flow switching section 10B, the first straightening section 17, the second straightening section 18, and the third straightening section. 19 included. The decompression unit 300 includes a first decompression section 4 and a third flow path switching section 10C.

The first unit 500 includes a first pipe 210A that forms part of the first common flow channel C1, a second pipe 210B and a third pipe 210C that form a part of the first non-common flow channel L1, and a fourth common flow channel. It is connected to the second unit 600 via a total of four pipes of the fourth pipe 210D forming a part of C4. The second unit 600 is connected to the decompression unit 300 via a pipe forming part of the second common channel C2. The second unit 600 is connected to the user-side unit 400 via a pipe forming part of the third common channel C3. The decompression unit 300 is connected to the user unit 400 via a pipe forming part of the fifth common channel C5. The first unit 500 and the second unit 600 are, for example, arranged adjacent to each other, but may be arranged apart from each other.

The first unit 500 further includes, for example, a third housing (not shown). The second unit 600 further includes a fourth housing (not shown). The decompression unit 300 further includes, for example, a fifth housing (not shown). The third housing accommodates the compressor 1, the heat source side heat exchanger 2, and the first fan 7 inside. The fourth housing includes the auxiliary heat exchanger 3, the second pressure reducing section 6, the second fan 8, the first flow switching section 10A, the second flow switching section 10B, the first rectifying section 17, and the second rectifying section 18. , and the third rectifying section 19 are accommodated therein. The fifth housing accommodates therein the first pressure reducing section 4 and the third flow path switching section 10C. The third housing and the fourth housing are housed inside the first housing.

<Operation of Refrigerating Device>
The refrigerating apparatus 100 performs a cooling operation for cooling a space to be cooled by the utilization side heat exchanger 5 acting as an evaporator, and a defrosting operation for melting and removing frost adhered to the utilization side heat exchanger 5 by the cooling operation. switch between When the refrigerating apparatus 100 is in cooling operation, the refrigerant circuit is in the first state shown in FIG. When the refrigerating apparatus 100 is in the defrosting operation, the refrigerant circuit is in the second state shown in FIG. Switching between the first state and the second state is performed by a plurality of channel switching units.

As shown in FIG. 2, in the first state, the first opening/closing valve 11, the fourth opening/closing valve 14, and the fifth opening/closing valve 15 are opened, and the second opening/closing valve 12, the third opening/closing valve 13, and the sixth opening/closing valve are opened. The on-off valve 16 is closed. Accordingly, in the first state, the coolant flows through the first flow path and the fourth flow path, and does not flow through the second flow path and the third flow path. That is, in the first state, the refrigerant sequentially flows through the compressor 1, the auxiliary heat exchanger 3, the heat source side heat exchanger 2, the first pressure reducing section 4, and the user side heat exchanger 5, and The auxiliary heat exchanger 3 acts as a first condenser, and the utilization side heat exchanger 5 acts as a first evaporator. As a result, the refrigeration system 100 can cool the space to be cooled when the refrigerant circuit is in the first state.

As shown in FIG. 3, in the second state, the second opening/closing valve 12, the third opening/closing valve 13, and the sixth opening/closing valve 16 are opened, and the first opening/closing valve 11, the fourth opening/closing valve 14, and the fifth opening/closing valve are opened. The on-off valve 15 is closed. Accordingly, in the second state, the coolant flows through the second and third flow paths and does not flow through the first and fourth flow paths. That is, in the second state, the refrigerant flows through the compressor 1, the utilization side heat exchanger 5, the second pressure reducing section 6, and the auxiliary heat exchanger 3 in order, and the utilization side heat exchanger 5 acts as a second condenser. , the auxiliary heat exchanger 3 acts as a second evaporator. That is, the refrigeration system 100 can defrost the user-side heat exchanger 5 when the refrigerant circuit is in the second state. The second fan 8 supplies sufficient air to the auxiliary heat exchanger 3 in the first state and the second state. On the other hand, the first fan 7 is stopped in the second state, for example. Alternatively, the rotation speed of the first fan 7 in the second state is lowered compared to that in the first state.

The third on-off valve 13 and the first straightening section 17 prevent the refrigerant discharged from the compressor 1 in the first state from flowing out from the sixth common flow path C6 to the third flow path. The second rectifying section 18 allows the high-pressure liquid-phase refrigerant upstream of the first inflow/outflow section 2A of the heat source side heat exchanger 2 to be sucked into the compressor 1 when switching from the first state to the second state. to prevent The third straightening section 19 prevents the refrigerant discharged from the compressor 1 in the second state from flowing out from the second flow path to the first non-common flow path L1.

Switching from the first state to the second state and switching from the second state to the first state are performed periodically, for example. The switching from the first state to the second state is performed, for example, when the elapsed time from the previous switching from the second state to the first state reaches a predetermined time. Also, the switching from the first state to the second state may be performed when frost adhesion is detected in the user-side heat exchanger 5 . For example, when frost formation is detected by a detection device, switching from the first state to the second state is performed by switching a plurality of flow path switching units based on a control signal output from the detection device. may be broken. For example, when frost formation is detected by an operator, switching from the first state to the second state is performed by switching a plurality of flow path switching units based on a control signal input by the operator. may

Switching from the second state to the first state is performed, for example, when the refrigerant temperature (outlet pipe temperature) of the sixth inflow/outflow portion 5B of the utilization side heat exchanger 5 reaches or exceeds a predetermined temperature.

<Effect>
The refrigeration system 100 includes a refrigerant circuit in which refrigerant circulates. The refrigerant circuit includes a compressor 1, a heat source side heat exchanger 2, an auxiliary heat exchanger 3, a first pressure reducing section 4, a user side heat exchanger 5, a second pressure reducing section 6, and a flow switching section. The channel switching unit switches between a first state and a second state. In the first state, the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 act as the first condenser, the utilization side heat exchanger 5 acts as the first evaporator, and the refrigerant flows into the compressor 1 and the first It flows through the condenser, the first depressurizing section 4 and the first evaporator in order. In the second state, the utilization side heat exchanger 5 acts as a second condenser, the auxiliary heat exchanger 3 acts as a second evaporator, and the refrigerant is the compressor 1, the second condenser, and the second decompression section 6, and the second evaporator in sequence.

When the refrigeration system 100 performs the defrosting operation, the refrigerant circuit is in the second state, and the auxiliary heat exchanger 3 acts as an evaporator. Therefore, unlike the conventional refrigerating apparatus that is provided so that the flow only flows through the heat exchanger on the user side and does not flow through the other heat exchangers during the defrosting operation, the refrigerating apparatus 100 performs the defrosting operation using the refrigerating cycle. . As a result, the defrosting operation of the refrigerating apparatus 100 is more efficient than that of the conventional refrigerating apparatus, and the defrosting operation time of the refrigerating apparatus 100 is shorter than that of the conventional refrigerating apparatus.

Furthermore, when the refrigerating apparatus 100 performs cooling operation, the refrigerant circuit is in the first state, and the auxiliary heat exchanger 3 works together with the heat source side heat exchanger 2 as a first condenser. Therefore, the amount of heat exchanged by the first condenser during the cooling operation can be increased in the refrigerating apparatus 100 as compared with a conventional refrigerating apparatus that does not include an auxiliary heat exchanger. In this case, the cooling operation of the refrigeration system 100 is more efficient than that of the conventional refrigeration system. Furthermore, the power consumption during the cooling operation of the refrigerating apparatus 100 is reduced compared to that of the conventional refrigerating apparatus.

When the refrigerating apparatus 100 is in defrosting operation, frost may adhere to the auxiliary heat exchanger 3 acting as an evaporator.

In contrast, in the first state of the refrigeration system 100, the auxiliary heat exchanger 3 is arranged upstream of the heat source side heat exchanger 2 in the refrigerant circuit. That is, in the refrigeration system 100 , the gas-phase refrigerant (hot gas) discharged from the compressor 1 is supplied to the auxiliary heat exchanger 3 in the first state. Therefore, the refrigeration system 100 can efficiently remove frost adhered to the auxiliary heat exchanger 3 during the defrosting operation during the cooling operation.

Furthermore, in the refrigeration system 100 , the refrigerant condensed in the auxiliary heat exchanger 3 is supplied to the heat source side heat exchanger 2 in the first state. Therefore, compared with the case where the refrigerant discharged from the compressor 1 is supplied to the heat source side heat exchanger 2 , the temperature rise inside the first unit 500 is suppressed in the refrigeration system 100 . As a result, in the refrigerating apparatus 100 , for example, the temperature inside the first unit 500 is prevented from rising to such an extent that the control unit that controls the rotational speed of the compressor 1 malfunctions.

Furthermore, in the refrigerating apparatus 100, the refrigerant discharged from the compressor 1 in the first state is supplied to the auxiliary heat exchanger 3, so the temperature inside the second unit 600 in the first state is relatively high. be done. Therefore, after being switched from the first state to the second state, the auxiliary heat exchanger 3 acts as an evaporator in a relatively high temperature environment. As a result, the auxiliary heat exchanger 3 can evaporate the refrigerant with relatively high efficiency.

Furthermore, since the refrigerating apparatus 100 is provided with the sixth non-common flow path L6 including the sixth on-off valve 16, compared to the refrigerating apparatus 105 shown in FIG. The degree of freedom of arrangement of the portion 4 is high. Therefore, in the refrigerating apparatus 100, the pressure loss of the refrigerant in the first state can be reduced by arranging the first pressure reducing section 4 near the utilization side heat exchanger 5. FIG.

Furthermore, in the refrigeration apparatus 100, the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 are housed inside the first housing. Therefore, when the refrigerating apparatus 100 is in cooling operation, the temperature around the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 in the first housing is relatively high. Therefore, the auxiliary heat exchanger 3 after the cooling operation of the refrigeration apparatus 100 is switched from the cooling operation to the defrosting operation acts as an evaporator under the relatively high temperature environment in the first housing. Therefore, the refrigerant evaporates efficiently in the auxiliary heat exchanger 3 . As a result, the defrosting efficiency of the refrigerating apparatus 100 is enhanced compared to that of the refrigerating apparatus 100 in which the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 are not housed in one housing.

Embodiment 2.
As shown in FIGS. 4 to 6, the refrigerating device 101 according to the second embodiment basically has the same configuration as the refrigerating device 100 according to the first embodiment. The difference is that the exchanger 2 is arranged upstream of the auxiliary heat exchanger 3 in the refrigerant circuit.

The refrigerant circuit of refrigeration apparatus 101 has a fifth flow path and a sixth flow path instead of the first flow path and second flow path of refrigeration apparatus 100 . The fifth flow path and the sixth flow path connect between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the use side heat exchanger 5 . In the refrigerating device 101, the sixth inflow/outlet portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 are connected by the third flow path and the fourth flow path, as in the refrigerating device 100. .

The fifth flow path connects between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat utilization side heat exchanger 5 via the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . In the fifth flow path, the discharge port 1B of the compressor 1, the heat source side heat exchanger 2, the auxiliary heat exchanger 3, the first pressure reducing section 4, and the fifth inflow/outflow section 5A of the utilization side heat exchanger 5 are arranged in series in this order. Connected. A seventh on-off valve 21 and a fifth on-off valve 15 for opening and closing the fifth flow path are arranged in the fifth flow path. The seventh on-off valve 21 is arranged between the second inflow/outflow portion 2B of the heat source side heat exchanger 2 and the third inflow/outflow portion 3A of the auxiliary heat exchanger 3 .

The sixth flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outflow part 5A of the heat utilization side heat exchanger 5 without interposing the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 therebetween. In the sixth flow path, the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the utilization side heat exchanger 5 are connected in series. An eighth on-off valve 22 and a sixth on-off valve 16 for opening and closing the sixth flow path are arranged in the sixth flow path. The eighth on-off valve 22 is arranged between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat exchanger 5 on the utilization side.

The fifth flow path and the sixth flow path have a seventh branch point, an eighth branch point, the fifth branch point, and the sixth branch point where the refrigerant splits or merges. In the fifth flow path and the sixth flow path, the seventh branch point, the eighth branch point, the fifth branch point, and the sixth branch point are connected in series in this order. The seventh branch point is arranged on the upstream side of the first inflow/outflow part 2A of the heat source side heat exchanger 2 in the fifth flow path. The eighth branch point is arranged downstream of the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 and upstream of the first pressure reducing section 4 in the fifth flow path.

The fifth and sixth flow paths connect the seventh branch point and the eighth branch point in parallel, and connect the fifth branch point and the sixth branch point in parallel. The fifth flow path and the sixth flow path connect the discharge port 1B of the compressor 1 and the seventh branch point with a common pipe line, and connect the sixth branch point and the utilization side heat exchanger 5 It connects with the 5th inflow/outlet part 5A by the common conduit line.

From a different point of view, the sixth flow path has a fourth bypass flow path branched from the fifth flow path and the second bypass flow path. One end of the fourth bypass channel is connected to the seventh branch point. The other end of the fourth bypass channel is connected to the eighth branch point. Thereby, the fourth bypass flow path bypasses the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 . The eighth on-off valve 22 opens and closes the fourth bypass channel. As for the sixth flow path, the fifth flow path is closed by the seventh on-off valve 21 and the fifth on-off valve 15, and the fourth bypass flow path and the second bypass flow path are closed by the eighth on-off valve 22 and the sixth on-off valve 16. It is formed by being opened.

As shown in FIGS. 4 to 6, a portion of each of the fifth flow path and the sixth flow path is configured by a common conduit, and each remainder is configured by a different conduit. The fifth flow channel and the sixth flow channel have a seventh common flow channel C7, an eighth common flow channel C8, and a fifth common flow channel C5, which are configured by common pipe lines. Furthermore, the fifth flow path has a seventh non-common flow path L7 and a fifth non-common flow path L5 which are different from the sixth flow path. The sixth flow path has an eighth non-common flow path L8 and a sixth non-common flow path L6 which are different from the fifth flow path.

One end of the seventh common channel C7 is connected to the discharge port 1B of the compressor 1 . The other end of the seventh common channel C7 is connected to the seventh branch point.

One end of the eighth common channel C8 is connected to the eighth branch point. The other end of the eighth common channel C8 is connected to the fifth branch point.

The seventh non-common flow path L7 and the eighth non-common flow path L8 connect the seventh common flow path C7 and the eighth common flow path C8 in parallel with each other. The fifth non-common flow path L5 and the sixth non-common flow path L6 connect the eighth common flow path C8 and the fifth common flow path C5 in parallel with each other. In the fifth channel, the seventh common channel C7, the seventh non-common channel L7, the eighth common channel C8, the fifth non-common channel L5, and the fifth common channel C5 are connected in series. . In the sixth channel, the seventh common channel C7, the eighth non-common channel L8, the eighth common channel C8, the sixth non-common channel L6, and the fifth common channel C5 are connected in series. .

The seventh non-common flow path L7 includes the heat source side heat exchanger 2 and the auxiliary heat exchanger 3. The fifth non-common flow path L5 includes the first pressure reducing section 4 . That is, the fifth flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the heat utilization side heat exchanger 5 to the heat source side heat exchanger 2, the auxiliary heat exchanger 3, and the first pressure reducing unit. Connect via part 4. The seventh non-common flow path L7 further includes a seventh on-off valve 21 and a fifth on-off valve 15 . That is, when the seventh on-off valve 21 and the fifth on-off valve 15 are opened, the refrigerant flows through the fifth channel.

The eighth non-common flow path L8 does not include the heat source side heat exchanger 2 and the auxiliary heat exchanger 3. The eighth non-common flow path L8 constitutes the fourth bypass flow path. That is, the sixth flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the heat utilization side heat exchanger 5 to the heat source side heat exchanger 2, the auxiliary heat exchanger 3, and the first pressure reducing unit. Connect without going through part 4. The eighth non-common flow path L8 further includes an eighth on-off valve 22 and a sixth on-off valve 16 . That is, when the eighth on-off valve 22 and the sixth on-off valve 16 are opened, the refrigerant flows through the sixth flow path.

As shown in FIGS. 4 to 6, the seventh on-off valve 21, the eighth on-off valve 22, the fifth on-off valve 15, and the sixth on-off valve 16 switch between the fifth flow path and the sixth flow path. constitutes a fourth flow path switching portion 20A provided in the .

In the first state, the seventh on-off valve 21, the fifth on-off valve 15, and the fourth on-off valve 14 are opened, and the eighth on-off valve 22, the sixth on-off valve 16, and the third on-off valve 13 are closed. In the second state, the seventh on-off valve 21, the fifth on-off valve 15, and the fourth on-off valve 14 are closed, and the eighth on-off valve 22, the sixth on-off valve 16, and the third on-off valve 13 are opened.

The seventh non-common flow path L7 of the fifth flow path and the third non-common flow path L3 of the third flow path include the auxiliary heat exchanger 3 in common. That is, the seventh non-common flow path L7 and the third non-common flow path L3 have a ninth common flow path C9 including the auxiliary heat exchanger 3.

The refrigerant circuit further includes a plurality of rectifiers that rectify the refrigerant. The plurality of rectifiers has a first rectifier 17 and a fourth rectifier 23 .

The fourth rectifying section 23 is located between the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 and the eighth branch point, specifically, between the fourth common flow path C9 and the above-described eighth branch point, in the seventh non-common flow path L7. It is located between the 8 branch points. The fourth straightening section 23 allows the refrigerant from the fourth inflow/outlet section 3B of the auxiliary heat exchanger 3 to flow toward the eighth common flow path C8, and restricts the flow of the refrigerant in the opposite direction.

The third on-off valve 13, the fourth on-off valve 14, the fifth on-off valve 15, the sixth on-off valve 16, the first straightening section 17, the seventh on-off valve 21, the eighth on-off valve 22, and the fourth straightening section 23 are It is arranged inside the heat source side unit 201 , specifically inside the second unit 601 .

In the refrigerating apparatus 101, the first unit 501 and the second unit 601 are composed of the fifth pipe 210E forming the seventh non-common flow path L7, the sixth pipe 210F forming the eighth non-common flow path L8, and the fourth common flow path. It is connected via a total of three pipes of the fourth pipe 210D forming C4.

<Operation of Refrigerating Device>
As described above, the refrigeration apparatus 101 is switched between the first state shown in FIG. 5 and the second state shown in FIG. 6 by a plurality of channel switching units.

As shown in FIG. 5, in the first state, the seventh on-off valve 21, the fourth on-off valve 14, and the fifth on-off valve 15 are opened, and the eighth on-off valve 22, the third on-off valve 13, and the sixth on-off valve 13 are opened. The on-off valve 16 is closed. Thereby, the coolant flows through the fifth and fourth flow paths and does not flow through the sixth and third flow paths. That is, in the first state, the refrigerant flows through the compressor 1, the heat source side heat exchanger 2, the auxiliary heat exchanger 3, the first pressure reducing section 4, and the utilization side heat exchanger 5 in this order. The heat source side heat exchanger 2 and the auxiliary heat exchanger 3 act as a first condenser, and the utilization side heat exchanger 5 acts as a first evaporator. As a result, in the first state, the refrigerator 101 cools the space to be cooled.

As shown in FIG. 6, in the second state, the eighth on-off valve 22, the third on-off valve 13, and the sixth on-off valve 16 are opened, and the seventh on-off valve 21, the fourth on-off valve 14, and the fifth on-off valve 14 are opened. The on-off valve 15 is closed. As a result, the coolant flows through the sixth and third flow paths and does not flow through the fifth and fourth flow paths. That is, in the second state, the refrigerant flows through the compressor 1, the user-side heat exchanger 5, the second pressure reducing section 6, and the auxiliary heat exchanger 3 in this order. As a result, in the second state, the utilization side heat exchanger 5 acts as a second condenser, and the auxiliary heat exchanger 3 acts as a second evaporator. That is, the refrigeration system 101 defrosts the user-side heat exchanger 5 when the second state is realized.

The third on-off valve 13 and the first straightening section 17 prevent the refrigerant discharged from the compressor 1 in the first state from flowing out from the ninth common flow path C9 to the third flow path. The fourth straightening section 23 prevents the refrigerant discharged from the compressor 1 in the second state from flowing out from the sixth flow path to the third non-common flow path L3.

<Effect>
Since the refrigerating device 101 has basically the same configuration as the refrigerating device 100, the same effect as that of the refrigerating device 100 can be obtained.

Furthermore, in the refrigerating apparatus 101, in the first state, the discharge port 1B of the compressor 1 and the first inflow/outflow part 2A of the heat source side heat exchanger 2 are directly connected without an on-off valve or the like. Therefore, in the refrigerating device 101 , the shortest distance on the refrigerant circuit between the discharge port 1</b>B of the compressor 1 and the condenser in the first state can be made shorter than that in the refrigerating device 100 . In this case, the length of the pipe through which the vapor-phase refrigerant flows in the refrigerating device 101 is shorter than the length of the pipe through which the vapor-phase refrigerant flows in the refrigerating device 100 . In such a refrigerating device 101, the pressure loss of the refrigerant during the cooling operation is reduced compared to that of the refrigerating device 100. FIG.

Furthermore, in the refrigerating apparatus 101, the first unit 501 and the second unit 601 are composed of the fifth pipe 210E forming the seventh non-common flow path L7, the sixth pipe 210F forming the eighth non-common flow path L8, and the fourth common flow path L8. They are connected via a total of three pipes of the fourth pipe 210D forming the flow path C4. That is, the number of pipes connecting the first unit 501 and the second unit 601 in the refrigerating device 101 is smaller than the number of pipes connecting the first unit 500 and the second unit 600 in the refrigerating device 100 . Therefore, the heat source side unit 201 is easier to assemble than the heat source side unit 200 .

Embodiment 3.
As shown in FIGS. 7 to 9, the refrigerating device 102 according to the third embodiment has basically the same configuration as the refrigerating device 100 according to the first embodiment, but the heat source side heat exchange is performed in the first state. The difference is that the vessel 2 and the auxiliary heat exchanger 3 are connected in parallel with each other.

The refrigerant circuit of refrigeration apparatus 102 has a seventh flow path and an eighth flow path instead of the first flow path and second flow path of refrigeration apparatus 100 . The seventh flow path and the eighth flow path connect between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the utilization side heat exchanger 5 . In the refrigerating device 102, the sixth inflow/outlet portion 5B of the utilization side heat exchanger 5 and the suction port 1A of the compressor 1 are connected by the third flow channel and the fourth flow channel, as in the refrigerating device 100. .

The seventh flow path connects between the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the utilization side heat exchanger 5 via the heat source side heat exchanger 2, and also via the auxiliary heat exchanger 3. is connected between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat exchanger 5 on the user side. In the seventh flow path, the discharge port 1B of the compressor 1, the heat source side heat exchanger 2, the first pressure reducing section 4, and the fifth inflow/outflow section 5A of the utilization side heat exchanger 5 are connected in series in this order, and the compressor 1 outlet 1B, the auxiliary heat exchanger 3, the first pressure reducing section 4, and the fifth inlet/outlet section 5A of the utilization side heat exchanger 5 are connected in series. In other words, in the seventh flow path, the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 are connected in parallel with each other.

A ninth on-off valve 31, a tenth on-off valve 32, and a fifth on-off valve 15 for opening and closing the seventh flow path are arranged in the seventh flow path. The ninth on-off valve 31 is arranged between the second inflow/outflow section 2B of the heat source side heat exchanger 2 and the first pressure reducing section 4 . The tenth opening/closing valve 32 is arranged between the discharge port 1B of the compressor 1 and the third inflow/outflow portion 3A of the auxiliary heat exchanger 3 .

The eighth flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outflow part 5A of the utilization side heat exchanger 5 without interposing the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 therebetween. In the eighth flow path, the discharge port 1B of the compressor 1 and the fifth inflow/outflow part 5A of the utilization side heat exchanger 5 are connected in series in this order.

An eleventh on-off valve 33 and a sixth on-off valve 16 for opening and closing the eighth flow path are arranged in the eighth flow path. The eleventh opening/closing valve 33 is arranged between the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the heat exchanger 5 on the utilization side.

The seventh flow path and the eighth flow path have a ninth branch point, a tenth branch point, a fifth branch point, an eleventh branch point, a twelfth branch point, and a sixth branch point where the refrigerant splits or merges. have. In the seventh flow path and the eighth flow path, the ninth branch point, tenth branch point, fifth branch point, and sixth branch point are connected in series in this order. In the seventh flow path, the ninth branch point, the twelfth branch point, the tenth branch point, the fifth branch point, and the sixth branch point are connected in series in this order, and the ninth branch point and the eleventh branch point , 12th branch point, 10th branch point, 5th branch point, and 6th branch point are connected in series in this order.

The ninth branch point is arranged upstream of the first inflow/outflow part 2A of the heat source side heat exchanger 2 and the third inflow/outflow part 3A of the auxiliary heat exchanger 3 in the seventh flow path. The tenth branch point is downstream of the second inflow/outflow section 2B of the heat source side heat exchanger 2 and the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 and upstream of the first pressure reducing section 4 in the seventh flow path. are placed. The eleventh branch point is arranged downstream of the ninth branch point and upstream of the third inflow/outlet portion 3A of the auxiliary heat exchanger 3 in the seventh flow path. The twelfth branch point is arranged downstream of the second inlet/outlet portion 2B of the heat source side heat exchanger 2 and the fourth inlet/outlet portion 3B of the auxiliary heat exchanger 3 and upstream of the tenth branch point in the seventh flow path. It is

From a different point of view, the eighth flow path has a seventh bypass flow path branched from the seventh flow path and the second bypass flow path. One end of the seventh bypass channel is connected to the eleventh branch point. The other end of the seventh bypass channel is connected to the tenth branch point. Thereby, the seventh bypass flow path bypasses the auxiliary heat exchanger 3 and the heat source side heat exchanger 2 . The eleventh on-off valve 33 opens and closes the seventh bypass channel. The eighth flow path is closed by the ninth on-off valve 31, the tenth on-off valve 32, and the fifth on-off valve 15, and the seventh bypass flow path by the eleventh on-off valve 33 and the sixth on-off valve 16. and the opening of the second bypass channel.

As shown in FIGS. 7 to 9, a portion of each of the seventh and eighth flow paths is configured by a common conduit, and the remaining portions are configured by different conduits. The seventh flow channel and the eighth flow channel have a tenth common flow channel C10, an eleventh common flow channel C11, a twelfth common flow channel C12, and a fifth common flow channel C5, which are configured by common pipes. are doing. Furthermore, the seventh flow path has a ninth non-common flow path L9, a tenth non-common flow path L10, and a fifth non-common flow path L5, which are different from the eighth flow path. The eighth flow path has an eleventh non-common flow path L11 and a sixth non-common flow path L6 that are different from the seventh flow path.

One end of the tenth common channel C10 is connected to the discharge port 1B of the compressor 1 . The other end of the tenth common channel C10 is connected to one end of each of the ninth non-common channel L9 and the eleventh common channel C11, that is, the ninth branch point. The tenth common flow path C10 is located between the discharge port 1B of the compressor 1 and the first inflow/outflow portion 2A of the heat source side heat exchanger 2 in the seventh flow path, and between the discharge port 1B of the compressor 1 and the auxiliary heat exchanger. 3 and the third inflow/outflow part 3A.

One end of the eleventh common channel C11 is connected to the other end of the tenth common channel C10 and the one end of the ninth non-common channel L9. The other end of the eleventh common channel C11 is connected to one end of each of the tenth non-common channel L10 and the eleventh non-common channel L11, that is, the eleventh branch point. The eleventh common flow path C11 is arranged between the discharge port 1B of the compressor 1 and the third inflow/outflow part 3A of the auxiliary heat exchanger 3 in the seventh flow path.

One end of the twelfth common channel C12 is connected to the other ends of the ninth non-common channel L9, the tenth non-common channel L10, and the eleventh non-common channel L11, that is, the tenth branch point. The other end of the twelfth common channel C12 is connected to the fifth branch point of the fifth non-common channel L5 and the sixth non-common channel L6. The twelfth common channel C12 is located between the second inlet/outlet portion 2B of the heat source side heat exchanger 2 and the first pressure reducing portion 4 in the seventh channel, and between the fourth inlet/outlet portion 3B of the auxiliary heat exchanger 3 and the first It is arranged between the decompression unit 4 and the decompression unit 4 .

The ninth non-common flow path L9, the tenth non-common flow path L10, and the eleventh non-common flow path L11 connect the tenth common flow path C10 and the twelfth common flow path C12 in parallel to each other. . Further, the tenth non-common flow path L10 and the eleventh non-common flow path L11 connect the eleventh common flow path C11 and the twelfth common flow path C12 in parallel to each other. The fifth non-common flow path L5 and the sixth non-common flow path L6 connect the twelfth common flow path C12 and the fifth common flow path C5 in parallel with each other. In the seventh channel, the tenth common channel C10, the ninth non-common channel L9, the twelfth common channel C12, the fifth non-common channel L5, and the fifth common channel C5 are connected in series. In addition, the tenth common channel C10, the eleventh common channel C11, the tenth non-common channel L10, the twelfth common channel C12, the fifth non-common channel L5, and the fifth common channel C5 are connected in series. It is In the eighth channel, a tenth common channel C10, an eleventh common channel C11, an eleventh non-common channel L11, a twelfth common channel C12, a sixth non-common channel L6, and a fifth common channel C5 are connected in series.

The ninth non-common flow path L9 includes the heat source side heat exchanger 2 . The tenth non-common flow path L10 includes the auxiliary heat exchanger 3 . That is, the seventh flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outflow portion 5A of the utilization side heat exchanger 5 via the heat source side heat exchanger 2 and the first pressure reducing portion 4. Together, they are connected via the auxiliary heat exchanger 3 and the first pressure reducing section 4 .

The eleventh non-common flow path L11 does not include the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 . The eleventh non-common flow path L11 constitutes the seventh bypass flow path. In other words, the eighth flow path connects the discharge port 1B of the compressor 1 and the fifth inflow/outlet portion 5A of the heat utilization side heat exchanger 5 to the heat source side heat exchanger 2, the auxiliary heat exchanger 3, and the first pressure reducing unit. Connect without going through part 4.

The ninth non-common flow path L9 further includes a ninth on-off valve 31 . The tenth non-common flow path L10 further includes a tenth on-off valve 32 . The eleventh non-common flow path L11 further includes an eleventh on-off valve 33 .

The ninth non-common flow path L9 and the tenth non-common flow path L10 of the seventh flow path have a thirteenth common flow path C13 configured by a common pipe line. One end of the thirteenth common channel C13 is connected to a twelfth branch point at which the ninth non-common channel L9 and the tenth non-common channel L10 join. The other end of the thirteenth common channel C13 is connected to the tenth branch point. The ninth on-off valve 31 is provided, for example, on the thirteenth common flow path C13.

As shown in FIGS. 7 to 9, the ninth on-off valve 31, the tenth on-off valve 32, the eleventh on-off valve 33, the fifth on-off valve 15, and the sixth on-off valve 16 are connected to the seventh flow path and the eighth flow path. It constitutes a fifth switching section provided to switch between the flow path.

In the first state, the ninth on-off valve 31, the tenth on-off valve 32, the fifth on-off valve 15, and the third on-off valve 13 are opened, and the eleventh on-off valve 33, the sixth on-off valve 16, and the fourth on-off valve are opened. 14 is closed. In the second state, the ninth on-off valve 31, the tenth on-off valve 32, the fifth on-off valve 15, and the third on-off valve 13 are closed, and the eleventh on-off valve 33, the sixth on-off valve 16, and the fourth on-off valve are closed. 14 is released.

The ninth non-common flow path L9 of the seventh flow path and the third non-common flow path L3 of the third flow path include the auxiliary heat exchanger 3 in common. That is, the ninth non-common flow path L9 and the third non-common flow path L3 have a fourteenth common flow path C14 including the auxiliary heat exchanger 3.

The refrigerant circuit further includes a plurality of rectifiers that rectify the refrigerant. The multiple rectifiers have a first rectifier 17 , a fifth rectifier 34 , and a sixth rectifier 35 .

The fifth straightening section 34 is located between the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 and the confluence portion of the ninth non-common flow path L9 and the tenth non-common flow path L10 in the tenth non-common flow path L10. are placed in The fifth rectifying section 34 allows the refrigerant from the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 to flow toward the thirteenth common flow path C13, and restricts the flow of the refrigerant in the opposite direction.

The sixth straightening section 35 is arranged between the second inflow/outflow section 2B of the heat source side heat exchanger 2 and the eleventh branch point in the ninth non-common flow path L9. The sixth straightening section 35 passes at least the refrigerant from the second inflow/outflow section 2B of the heat source side heat exchanger 2 toward the twelfth common flow path C12, and restricts the flow of the refrigerant in the opposite direction. The sixth straightening section 35 is provided, for example, on the thirteenth common flow path C13. The sixth rectifying section 35 supplies refrigerant from the second inflow/outflow section 2B of the heat source side heat exchanger 2 to the twelfth common flow path C12, and from the fourth inflow/outflow section 3B of the auxiliary heat exchanger 3 to the twelfth common flow path C12. passes refrigerant in one direction and restricts the flow of refrigerant in each opposite direction.

Ninth on-off valve 31, tenth on-off valve 32, eleventh on-off valve 33, fifth on-off valve 15, sixth on-off valve 16, third on-off valve 13, fourth on-off valve 14, first rectifier 17, fifth The rectifying section 34 and the sixth rectifying section 35 are arranged inside the heat source side unit 202 , specifically inside the second unit 602 .

In the refrigerating apparatus 102, the first unit 502 and the second unit 602 are composed of the eighth pipe 210H forming the tenth non-common flow path L10, the ninth pipe 210I forming the ninth non-common flow path L9, and the fourth common flow path. They are connected via a total of three pipes, a tenth pipe 210J forming C4.

<Operation of Refrigerating Device>
As described above, the refrigeration apparatus 102 is switched between the first state shown in FIG. 8 and the second state shown in FIG. 9 by a plurality of channel switching units.

As shown in FIG. 8, in the first state, the ninth on-off valve 31, the tenth on-off valve 32, the fifth on-off valve 15, and the third on-off valve 13 are opened, and the eleventh on-off valve 33 and the sixth on-off valve are opened. The valve 16 and the fourth on-off valve 14 are closed. As a result, the coolant flows through the seventh and fourth flow paths and does not flow through the eighth and third flow paths. That is, in the first state, the refrigerant flows through the compressor 1, the heat source side heat exchanger 2, the first pressure reducing section 4, and the user side heat exchanger 5 in order, and also flows through the compressor 1, the auxiliary heat exchanger 3, the first It flows through the decompression unit 4 and the utilization side heat exchanger 5 in order. The heat source side heat exchanger 2 and the auxiliary heat exchanger 3 act as a third condenser, and the utilization side heat exchanger 5 acts as a third evaporator. As a result, in the first state, the refrigerator 102 cools the space to be cooled.

As shown in FIG. 9, in the second state, the ninth on-off valve 31, the tenth on-off valve 32, the fifth on-off valve 15, and the third on-off valve 13 are closed, and the eleventh on-off valve 33 and the sixth on-off valve are closed. The valve 16 and the fourth on-off valve 14 are opened. As a result, the coolant flows through the eighth and third flow paths and does not flow through the seventh and fourth flow paths. That is, in the second state, the refrigerant flows through the compressor 1, the user-side heat exchanger 5, the second pressure reducing section 6, and the auxiliary heat exchanger 3 in this order. As a result, in the second state, the utilization side heat exchanger 5 acts as a second condenser, and the auxiliary heat exchanger 3 acts as a second evaporator. That is, the refrigerating device 102 defrosts the user-side heat exchanger 5 when the second state is realized.

<Effect>
Since the refrigerating device 102 has basically the same configuration as the refrigerating device 100, the same effects as the refrigerating device 100 can be obtained.

Furthermore, in the refrigerating apparatus 102, the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 are connected in parallel to the discharge port 1B of the compressor 1 when the refrigerant circuit is in the first state. Therefore, in the refrigerating device 102, the pressure loss of the refrigerant during the cooling operation is reduced as compared with the refrigerating devices 100 and 101. FIG.

Furthermore, in the refrigerator 102, the first unit 502 and the second unit 602 are connected via three pipes. Therefore, the number of pipes connecting the first unit 502 and the second unit 602 in the refrigerating device 102 is smaller than the number of pipes connecting the first unit 500 and the second unit 600 in the refrigerating device 100 . Therefore, assemblability of the heat source side unit 202 is higher than that of the heat source side unit 200 .

Embodiment 4.
As shown in FIGS. 10 to 12, a refrigerating device 103 according to Embodiment 4 has basically the same configuration as that of refrigerating device 100 according to Embodiment 1, except for a heat medium circuit in which a heat medium circulates. and the heat source side heat exchanger 2 is provided to exchange heat between the refrigerant circulating in the refrigerant circuit and the heat medium circulating in the heat medium circuit.

The heat medium circuit is arranged inside the heat source side unit 203 , specifically inside the first unit 503 . The heat medium circulating in the heat medium circuit is, for example, a refrigerant. The refrigerating device 103 is configured as a so-called dual refrigerating device, with the refrigerant circuit forming a low temperature side circuit and the heat medium circuit forming a high temperature side circuit. The heat medium circuit includes a high temperature side compressor 51, a high temperature side condenser 52, a high temperature side pressure reducing section 53, and a heat source side heat exchanger 2 acting as a high temperature side evaporator. The heat medium flows through the high temperature side compressor 51, the high temperature side condenser 52, the high temperature side pressure reducing section 53, and the heat source side heat exchanger 2 in this order. Second unit 600 , decompression unit 300 , and usage side unit 400 each have the same configuration as second unit 600 , decompression unit 300 , and usage side unit 400 of refrigeration apparatus 100 .

The high-temperature side compressor 51 compresses and discharges the heat medium evaporated in the heat source side heat exchanger 2 . In the high temperature side condenser 52, heat exchange is performed between the heat medium discharged from the high temperature side compressor 51 and the air. Inside the first unit 503 , instead of the first fan 7 in the first unit 500 , a fourth fan 54 is arranged to supply air outside the freezer to the high temperature side condenser 52 . The high temperature side pressure reducing section 53 is, for example, an electronic expansion valve.

The heat source side heat exchanger 2 is, for example, a plate heat exchanger. The heat source side heat exchanger 2 further has a seventh inflow/outflow portion 2C and an eighth inflow/outflow portion 2D through which the heat medium flows. The seventh inflow/outflow section 2C is connected to the high temperature side condenser 52 via the high temperature side pressure reducing section 53 . The eighth inflow/outflow portion 2D is connected to the suction port of the high temperature side compressor 51 .

The first unit 503 and the second unit 600 are housed in the same housing, for example. In this case, the auxiliary heat exchanger 3 and the high temperature side condenser 52 may be provided integrally, for example. From a different point of view, a partial area of one heat exchanger may constitute the auxiliary heat exchanger 3 and another area of the one heat exchanger may constitute the high temperature side condenser 52 .

<Operation of Refrigerating Device>
In the refrigerating device 103, a first state shown in FIG. 11 and a second state shown in FIG. 12 are switched by a plurality of channel switching units. As shown in FIGS. 11 and 12 , switching between the first state and the second state in refrigerating apparatus 103 is performed in the same manner as switching between the first state and the second state in refrigerating apparatus 100 .

As shown in FIG. 11, each of the refrigerant in the refrigerant circuit and the heat medium in the heat medium circuit repeats the refrigeration cycle when the refrigerant circuit is in the first state. In the first state, the refrigerant flows through the compressor 1, the auxiliary heat exchanger 3, the heat source side heat exchanger 2, the first pressure reducing section 4, and the user side heat exchanger 5 in order, and the heat medium flows through the high temperature side compressor 51, It flows through the high temperature side condenser 52, the high temperature side pressure reducing section 53, and the heat source side heat exchanger 2 in this order. As a result, in the first state, heat is exchanged between the refrigerant and the heat medium in the heat source side heat exchanger 2, the refrigerant is condensed, and the heat medium is evaporated. As a result, in the first state, the heat source side heat exchanger 2 and the auxiliary heat exchanger 3 act as the first condenser, the utilization side heat exchanger 5 acts as the first evaporator, and the refrigerating device 103 is to be cooled. It can cool the space to be used.

As shown in FIG. 12, when the refrigerant circuit is in the second state, only the refrigerant in the refrigerant circuit circulates in the refrigerant circuit to repeat the refrigeration cycle, and the heat medium in the heat medium circuit is the heat medium. Does not circulate in the circuit and repeat the refrigeration cycle. That is, when the refrigerant circuit is in the second state, the refrigerating device 103 operates in the same manner as the refrigerating device 100 to defrost the user-side heat exchanger 5 .

<Effect>
Since the refrigerating device 103 has basically the same configuration as the refrigerating device 100, the same effect as that of the refrigerating device 100 can be obtained.

Furthermore, since the refrigerating device 103 is configured as a dual refrigerating device, the cooling efficiency is enhanced compared to a refrigerating device operating in a single refrigerating cycle. From a different point of view, since the auxiliary heat exchanger 3 in the refrigeration system 103 acts as a condenser in the refrigerant circuit, the cooling efficiency of the refrigeration system 103 is lower than that of a conventional binary refrigeration system without the auxiliary heat exchanger 3. is elevated in comparison. Furthermore, the refrigerating device 103 has a higher defrosting efficiency than the conventional binary refrigerating device.
<Modification>
A refrigerating device 104 shown in FIG. 13 is a modification of the refrigerating device 103 shown in FIGS. The refrigerating device 104 has basically the same configuration as the refrigerating device 103, but differs in that the heat medium circulating in the heat medium circuit is water, brine, or the like. The heat medium in the refrigeration system 104 does not change phase when circulating through the heat medium circuit. The heat medium circuit has a pump 55 in place of the high temperature side compressor 51 shown in FIGS. 10 to 12 and a heat exchanger 56 in place of the high temperature side condenser 52 . The pump 55 circulates the heat medium within the heat medium circuit. The heat exchanger 56 is provided to exchange heat between the heat medium circulating in the heat medium circuit and the air outside the freezer. As described above, the auxiliary heat exchanger 3 is provided to exchange heat between the refrigerant circulating in the refrigerant circuit and the air outside the freezer. Therefore, in the refrigerating device 104 as well, as in the refrigerating device 100, the first state and the second state are realized. As a result, the refrigerating device 104 can achieve the same effects as the refrigerating device 100 .

Further, when the auxiliary heat exchanger 3 is provided to exchange heat between the refrigerant circulating in the refrigerant circuit and the refrigerant circulating in the heat medium circuit, the auxiliary heat exchanger 3 during the defrosting operation: The heat medium may exchange heat with the condensed refrigerant in the user-side heat exchanger 5 and freeze. On the other hand, in the refrigerating device 104, since the refrigerant condensed in the user-side heat exchanger 5 is not supplied to the heat source-side heat exchanger 2, freezing of the heat medium is suppressed even during the defrosting operation. In the refrigerating apparatus 104, similarly to the refrigerating apparatus 100, frost may adhere to the auxiliary heat exchanger 3 due to the defrosting operation on the utilization side heat exchanger 5, but the frost can be melted and removed by the cooling operation.

The refrigerant circuits of refrigerating devices 103 and 104 may have the same configuration as the refrigerant circuit of refrigerating device 101 or 102 . The heat medium circuit of the refrigerating devices 103 and 104 may include the heat source side heat exchanger 2 of the refrigerating device 101 or the refrigerating device 102 .

A refrigerating device 105 shown in FIG. 14 is a modification of the refrigerating device 100 shown in FIGS. In the refrigerator 105, the second flow path has only one bypass flow path, that is, only the second non-common flow path L2. From a different point of view, in the refrigeration apparatus 105, the first flow path and the second flow path do not have the second common flow path C2, the second branch point, and the fifth branch point. In this case, one end of the second non-common flow path L2 is connected to the first branch point, as in the refrigeration system 100 . The other end of the second non-common flow path L2 is connected to the first flow path downstream of the first pressure reducing section 4 and upstream of the fifth inflow/outflow section 5A of the user side heat exchanger 5 . The second non-common flow path L<b>2 is provided so as to bypass the auxiliary heat exchanger 3 , the heat source side heat exchanger 2 and the first pressure reducing section 4 . The refrigerating device 105 does not require the sixth on-off valve 16 .

Note that the refrigerating devices 101 , 102 , 103 and 104 can also adopt modifications similar to the refrigerating device 105 .

Refrigeration system 106 shown in FIGS. 15 and 16 is a modification of refrigeration system 100 shown in FIGS. 1-3. Refrigeration system 106 further includes an economizer circuit through which a refrigerant circulates. The economizer circuit includes compressor 1 , heat source side heat exchanger 2 , economizer flow path 60 , economizer heat exchanger 61 , economizer pressure reducing section 62 , fifth bypass flow path 63 , and twelfth on-off valve 64 .

The compressor 1 includes, for example, a low pressure section, a high pressure section and an intermediate pressure section located between the low pressure section and the high pressure section. The economizer flow path 60 branches off from the first flow path of the refrigerant circuit. One end of the economizer flow path 60 is connected between the second inflow/outflow portion 2B of the heat source side heat exchanger 2 and the second branch point. The other end of the economizer flow path 60 is connected to an intermediate pressure section of the compressor 1, for example. As a result, the economizer circuit causes part of the refrigerant condensed in the heat source side heat exchanger 2 to flow into the intermediate pressure section of the compressor 1 . The economizer pressure reducing unit 62 reduces the pressure of the refrigerant that has flowed into the economizer flow path after being condensed in the heat source side heat exchanger 2 . The economizer heat exchanger 61 performs heat exchange between the refrigerant decompressed by the economizer decompression unit 62 and the refrigerant condensed in the heat source side heat exchanger 2 and flowing toward the post-use side heat exchanger 5 . is provided. The economizer circuit is included in the heat source side unit 206 . Compressor 1 , heat source side heat exchanger 2 , economizer flow path 60 , economizer heat exchanger 61 , and economizer pressure reducing section 62 are included in first unit 506 .

The fifth bypass flow path 63 is provided so as to bypass the first on-off valve 11, the auxiliary heat exchanger 3 and the second straightening section 18 in the first flow path. One end of the fifth bypass channel 63 is connected between the first branch point and the first on-off valve 11 in the first non-common channel L1. The other end of the fifth bypass flow path 63 is connected between the second rectifying section 18 and the first inflow/outflow section 2A of the heat source side heat exchanger 2 in the first non-common flow path L1. The twelfth on-off valve 64 opens and closes the fifth bypass flow path 63 . The fifth bypass flow path 63 and the twelfth on-off valve 64 are included in the second unit 606 .

The economizer circuit includes a portion located between the discharge port 1B of the compressor 1 and the one end of the fifth bypass flow path 63, and a portion between the other end of the fifth bypass flow path 63 and the one end of the economizer flow path 60. An intermediate portion is shared with the first flow path of the refrigerant circuit.

From a different perspective, the refrigerant circuit of refrigeration system 106 further includes economizer flow path 60 and fifth bypass flow path 63 . When the refrigerant circuit is in the first state, the first common flow path C1, the portion of the first non-common flow path L1 located between the first branch point and the one end of the economizer flow path 60, and the economizer flow path 60 constitutes an economizer circuit. When the refrigerant circuit is in the second state, the portion of the first common flow path C1 and the first non-common flow path L1 located between the first branch point and the one end of the fifth bypass flow path 63 and the fifth bypass A portion located between the other end of the flow path 63 and the one end of the economizer flow path 60, the fifth bypass flow path 63, and the economizer flow path 60 constitute an economizer circuit. Note that the economizer circuit of the refrigerating device 106 may be configured to return part of the refrigerant condensed in the heat source side heat exchanger 2 to the compressor 1 . The other end of the economizer flow path 60 may be connected to the low pressure section of the compressor 1 or the suction port 1A. Also, the configuration of the compressor 1 in the refrigerating device 106 is not particularly limited, and may be, for example, a multi-stage compressor, or may be, for example, a single-stage compressor.

As shown in FIG. 15, when the refrigerator 106 is in cooling operation, the first on-off valve 11, the fourth on-off valve 14 and the fifth on-off valve 15 are opened, and the second on-off valve 12 and the third on-off valve 12 are opened. 13, the sixth on-off valve 16, and the 12th on-off valve 64 are closed. As a result, part of the refrigerant discharged from the compressor 1 is transferred to the heat source side heat exchanger 2 as the first condenser, the auxiliary heat exchanger 3, the first pressure reducing section 4, and the use side as the first evaporator. While sequentially flowing through the heat exchanger 5 , the rest of the refrigerant discharged from the compressor 1 flows sequentially through the heat source side heat exchanger 2 and the economizer flow path 60 . As a result, the cooling operation of the refrigerating device 106 is made more efficient than that of the conventional refrigerating device by utilizing the economizer circuit.

As shown in FIG. 16, when the refrigerating device 106 is in defrosting operation, the second on-off valve 12, the third on-off valve 13, the sixth on-off valve 16, and the twelfth on-off valve 64 are opened, and the first The on-off valve 11, the fourth on-off valve 14 and the fifth on-off valve 15 are closed. As a result, when the refrigerating device 106 is in the defrosting operation, part of the refrigerant discharged from the compressor 1 is transferred to the utilization side heat exchanger 5 as a second condenser, the second pressure reducing section 6, and the second While sequentially flowing through the auxiliary heat exchanger 3 as an evaporator, the rest of the refrigerant discharged from the compressor 1 sequentially flows through the fifth bypass flow path 63 , the heat source side heat exchanger 2 and the economizer flow path 60 . That is, when the refrigerant circuits of the refrigerating devices 100 to 105 are in the second state, the heat source side heat exchanger 2 does not act as a condenser, whereas when the refrigerant circuit of the refrigerating device 106 is in the second state, The heat source side heat exchanger 2 acts as a condenser. In the defrosting operation of the refrigerating device 106, in order to increase the amount of heat used for defrosting in the utilization side heat exchanger 5, the amount of heat exchanged in the heat source side heat exchanger 2 is less than the amount of heat exchanged in the auxiliary heat exchanger 3. It is preferably reduced relative to the amount. Therefore, the rotational speed of the first fan 7 when the refrigerating device 106 is in the defrosting operation is the rotational speed of the second fan 8 when the refrigerating device 106 is in the defrosting operation, and the rotational speed of the second fan 8 when the refrigerating device 106 is in the cooling operation. Preferably, the rotational speed of the first fan 7 when running is reduced compared to .

Refrigerant flows through the first flow path and the economizer flow path 60 when the refrigerating device 106 performs a defrosting operation. The amount of heat used for defrosting in the container 5 is sufficiently large. Also, the defrosting operation of the refrigerating apparatus 100 uses a refrigerating cycle, unlike the conventional refrigerating apparatus which is provided so that the flow only flows through the heat exchanger on the user side and not through the other heat exchangers during the defrosting operation. . As a result, the defrosting operation of the refrigerating device 106 is more efficient than that of the conventional refrigerating device.

As shown in FIG. 17 , the economizer circuit of the refrigerator 106 may include a capillary tube 65 instead of the twelfth on-off valve 64 . A capillary tube 65 is arranged in the fifth bypass channel 63 . The refrigerant pressure loss in the capillary tube 65 is higher than the refrigerant pressure loss in the auxiliary heat exchanger 3 . When the refrigerant circuit is in the first state, the capillary tube 65 is configured such that the flow rate of the refrigerant flowing through the fifth bypass flow path 63 is such that it does not affect the cooling performance of the refrigerating device 106. In other words, the flow rate of the refrigerant flowing through the fifth bypass flow path 63 is set to be less than the minimum flow rate that can affect the cooling performance of the refrigerating device 106 . In this case, the capillary tube 65 substantially blocks the flow of the refrigerant in the fifth bypass passage 63 when the first on-off valve 11 is opened, and the fifth bypass flow when the first on-off valve 11 is closed. Refrigerant is circulated in the passage 63 . Thereby, the freezing device 106 including the capillary tube 65 can achieve the same effects as the freezing device 106 including the twelfth on-off valve 64 . Note that the refrigerating devices 101 to 105 can also adopt modifications similar to the refrigerating device 106 .

A refrigerating device 107 shown in FIG. 18 is a modification of the refrigerating device 100 shown in FIGS. In the refrigerating device 107, a plurality of compressors 1 are connected in parallel in the first channel and the second channel. Furthermore, a plurality of heat source side heat exchangers 2 are connected in parallel with each other in the first flow path. Since such a refrigerating device 107 has basically the same configuration as that of the refrigerating device 100, the same effect as that of the refrigerating device 100 can be obtained. Note that the refrigerating devices 101 to 106 can also adopt modifications similar to the refrigerating device 107 .

In the refrigerators 100 to 107, the decompression unit 300 may be arranged outside the first housing. The decompression unit 300 may be arranged, for example, together with the user unit 400 in the space to be cooled. Also, the decompression unit 300 may be configured integrally with the user unit 400 .

Further, in the refrigerating apparatuses 100 to 107, the heat source side units 200 to 207 may be provided with the decompression unit 300. FIG. The decompression unit 300 is configured, for example, integrally or separately from the first units 500 to 507 and the second units 600 to 605 in the heat source side units 200 to 207, and is arranged inside the first housing.

Although the embodiment of the present invention has been described as above, it is also possible to modify the above-described embodiment in various ways. Also, the scope of the present invention is not limited to the above-described embodiments. The scope of the present invention is indicated by the scope of claims, and is intended to include all changes within the meaning and scope of equivalence to the scope of the claims.

Reference Signs List 1 compressor, 1A suction port, 1B discharge port, 2 heat source side heat exchanger, 2A first inflow/outflow section, 2B second inflow/outflow section, 2C seventh inflow/outflow section, 2D eighth inflow/outflow section, 3 auxiliary heat exchanger, 3A 3rd inflow/outlet part 3B 4th inflow/outlet part 4 1st decompression part 5 utilization side heat exchanger 5A 5th inflow/outlet part 5B 6th inflow/outlet part 6 second decompression part 7 first fan 8 second second Fan 9 Third fan 10A First flow switching section 10B Second flow switching section 10C Third flow switching section 11 First on-off valve 12 Second on-off valve 13 Third on-off valve 14 4th on-off valve 15 5th on-off valve 16 6th on-off valve 17 1st straightening section 18 2nd straightening section 19 3rd straightening section 20A 4th flow switching section 21 7th on-off valve 22 8th on-off valve, 23 4th straightening section, 31 9th on-off valve, 32 10th on-off valve, 33 11th on-off valve, 34 5th rectifying section, 35 6th rectifying section, 51 high temperature side compressor, 52 high temperature side Condenser, 53 high-temperature side decompression section, 54 fourth fan, 55 pump, 56 heat exchanger, 60 economizer flow path, 61 economizer heat exchanger, 62 economizer decompression section, 63 fifth bypass flow path, 64 twelfth on-off valve , 65 capillary tube 100, 101, 102, 103, 104, 105, 106, 107 refrigerator 200, 201, 202 heat source side unit 210A first pipe, 210B second pipe, 210C third pipe, 210D fourth Piping, 210E 5th pipe, 210F 6th pipe, 210H 8th pipe, 210I 9th pipe, 210J 10th pipe, 300 decompression unit, 400 user side unit, 500, 501, 502, 503 1st unit, 600 2nd unit.

Claims (10)

Equipped with a refrigerant circuit in which the refrigerant circulates,
The refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow path switching section,
The compressor, the heat source side heat exchanger, and the auxiliary heat exchanger are included in a heat source side unit,
The flow path switching unit is
The heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, the a first state in which the first decompression unit and the first evaporator are sequentially flowed;
Only the utilization side heat exchanger acts as a second condenser, the auxiliary heat exchanger acts as a second evaporator, and the refrigerant is the compressor, the second condenser, the second pressure reducing section, and provided to switch between a second state in which the second evaporator is sequentially flowed,
A refrigerating apparatus, wherein a direction of flow of refrigerant flowing through the utilization side heat exchanger is constant regardless of the first state and the second state. Equipped with a refrigerant circuit in which the refrigerant circulates,
The refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow path switching section,
The compressor, the heat source side heat exchanger, and the auxiliary heat exchanger are included in a heat source side unit,
The flow path switching unit is
The heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, the a first state in which the first decompression unit and the first evaporator are sequentially flowed;
The utilization side heat exchanger acts as a second condenser, the auxiliary heat exchanger acts as a second evaporator, and the refrigerant is the compressor, the second condenser, the second pressure reducing section, and the provided to switch between a second state of sequentially flowing through the second evaporator,
the flow direction of the refrigerant flowing through the utilization side heat exchanger is constant regardless of the first state and the second state;
The refrigeration system, wherein in the first state, the auxiliary heat exchanger is arranged upstream of the heat source side heat exchanger in the refrigerant circuit. The refrigerant circuit is
a first flow path connecting a discharge port of the compressor and the utilization side heat exchanger via the auxiliary heat exchanger, the heat source side heat exchanger, and the first pressure reducing unit;
a second flow path connecting a discharge port of the compressor and the utilization side heat exchanger without passing through the auxiliary heat exchanger, the heat source side heat exchanger, and the first pressure reducing unit;
a third flow path connecting the utilization side heat exchanger and the suction port of the compressor via the second pressure reducing section and the auxiliary heat exchanger; and
a fourth flow path that connects between the utilization-side heat exchanger and the suction port of the compressor without passing through the second pressure reducing section and the auxiliary heat exchanger;
The flow path switching unit is
A first flow path switching unit for switching between the first flow path and the second flow path and a second flow path switching unit for switching between the third flow path and the fourth flow path,
The first flow path switching section forms the first flow path in the first state and forms the second flow path in the second state,
3. The refrigeration apparatus according to claim 2, wherein said second flow path switching section forms said fourth flow path in said first state and forms said third flow path in said second state. 2. The refrigeration system according to claim 1, wherein in said first state, said heat source side heat exchanger is arranged upstream of said auxiliary heat exchanger in said refrigerant circuit. Equipped with a refrigerant circuit in which the refrigerant circulates,
The refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow path switching section,
The compressor, the heat source side heat exchanger, and the auxiliary heat exchanger are included in a heat source side unit,
The flow path switching unit is
The heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, the a first state in which the first decompression unit and the first evaporator are sequentially flowed;
The utilization side heat exchanger acts as a second condenser, the auxiliary heat exchanger acts as a second evaporator, and the refrigerant is the compressor, the second condenser, the second pressure reducing section, and the provided to switch between a second state of sequentially flowing through the second evaporator,
the flow direction of the refrigerant flowing through the utilization side heat exchanger is constant regardless of the first state and the second state;
The refrigeration system, wherein the heat source side heat exchanger and the auxiliary heat exchanger are connected in parallel in the first state. Equipped with a refrigerant circuit in which the refrigerant circulates,
The refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow path switching section,
The compressor, the heat source side heat exchanger, and the auxiliary heat exchanger are included in a heat source side unit,
The flow path switching unit is
The heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, the a first state in which the first decompression unit and the first evaporator are sequentially flowed;
The utilization side heat exchanger acts as a second condenser, the auxiliary heat exchanger acts as a second evaporator, and the refrigerant is the compressor, the second condenser, the second pressure reducing section, and the provided to switch between a second state of sequentially flowing through the second evaporator,
the flow direction of the refrigerant flowing through the utilization side heat exchanger is constant regardless of the first state and the second state;
further comprising a heat medium circuit in which the heat medium circulates,
The refrigeration apparatus, wherein the heat source side heat exchanger is provided to exchange heat between a refrigerant circulating in the refrigerant circuit and a heat medium circulating in the heat medium circuit. Equipped with a refrigerant circuit in which the refrigerant circulates,
The refrigerant circuit includes a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow switching section,
The compressor, the heat source side heat exchanger, and the auxiliary heat exchanger are included in a heat source side unit,
The flow path switching unit is
The heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, the utilization side heat exchanger acts as a first evaporator, and the refrigerant is the compressor, the first condenser, the a first state in which the first decompression unit and the first evaporator are sequentially flowed;
The utilization side heat exchanger acts as a second condenser, the auxiliary heat exchanger acts as a second evaporator, and the refrigerant is the compressor, the second condenser, the second pressure reducing section, and the provided to switch between a second state of sequentially flowing through the second evaporator,
the flow direction of the refrigerant flowing through the utilization side heat exchanger is constant regardless of the first state and the second state;
It further comprises an economizer circuit in which the refrigerant circulates,
the economizer circuit includes the compressor and the heat source side heat exchanger;
The economizer circuit further includes an economizer flow path for returning part of the refrigerant condensed in the heat source side heat exchanger to the compressor,
In the second state, the heat source side heat exchanger and the utilization side heat exchanger act as the second condenser,
A refrigeration system further comprising a first fan that blows air to the heat source side heat exchanger and a second fan that blows air to the auxiliary heat exchanger. 8. The refrigeration system according to any one of claims 1 to 7, further comprising a first housing housing said heat source side heat exchanger and said auxiliary heat exchanger therein. The first housing further houses therein the compressor, the first decompression unit and the second decompression unit,
9. The refrigeration system according to claim 8, further comprising a second housing that accommodates said utilization side heat exchanger therein. One type of refrigeration apparatus comprising a refrigerant circuit in which refrigerant circulates, including a compressor, a heat source side heat exchanger, a first pressure reducing section, a user side heat exchanger, a second pressure reducing section, an auxiliary heat exchanger, and a flow path switching section. A heat source side unit constituting a part,
part of the refrigerant circuit including the compressor, the heat source side heat exchanger, the auxiliary heat exchanger, the second pressure reducing section, and the flow path switching section;
an outflow port that flows out from a part of the refrigerant circuit to another part of the refrigerant circuit;
an inflow port that flows into a part of the refrigerant circuit from another part of the refrigerant circuit,
The flow path switching unit is
a first state in which the heat source side heat exchanger and the auxiliary heat exchanger act as a first condenser, and refrigerant sequentially flows through the inlet, the compressor, the first condenser, and the outlet;
Switching between a second state in which the auxiliary heat exchanger acts as a first evaporator and refrigerant flows through the inlet, the second pressure reducing section, the first evaporator, the compressor, and the outlet in order. ,
The heat source side unit, wherein the direction of circulation of the refrigerant flowing through the auxiliary heat exchanger is constant regardless of the first state and the second state.

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