JP2020134127A - Freezing device - Google Patents

Abstract

To provide a freezing device that can operate without causing a freezing capacity shortage even when increasing a hot water supply temperature.SOLUTION: A freezing device includes: a compressor 11; an intercooler 23 for cooling refrigerant discharged from a low-stage discharge port 13; a main gas cooler 24 for cooling refrigerant discharged from a high-stage discharge port 15; and an auxiliary gas cooler 25 for cooling refrigerant that has passed the main gas cooler 24. Water piping 40 connects the auxiliary gas cooler 25, the intercooler 23 and the main gas cooler 24 sequentially in series in this order.SELECTED DRAWING: Figure 1

Description

The present invention relates to a freezing device, and more particularly to a freezing device capable of recovering exhaust heat by supplying hot water.

Conventionally, in large stores such as supermarkets, many freezing showcases and refrigerated showcases have been installed, and a freezing device for operating these showcases with a refrigerator is often used.

As such a refrigerating device, conventionally, for example, water pipes are connected in parallel to an intercooler and a gas cooler, and the cooling water supplied to each of them is used to heat the intercooler with the refrigerant discharged from the low-stage compression mechanism. A technique for exchanging heat with the refrigerant discharged from the high-stage compression mechanism in the gas cooler is disclosed (see, for example, Patent Document 1).

Japanese Patent No. 4947197

However, in the above-mentioned conventional technique, in order to raise the hot water supply temperature, it is necessary to reduce the flow rate of water flowing through the water pipes of the intercooler and the gas cooler. Therefore, by reducing the flow rate of water, the heat exchange performance is lowered, the heat dissipation of the refrigerant is insufficient in the intercooler and the gas cooler, the refrigerant temperature on the outlet side of the gas cooler becomes high, and as a result, the refrigerating capacity of the refrigerating device is insufficient. There was a problem of doing it.

The present invention has been made in view of the above points, and an object of the present invention is to provide a freezing device that can be operated without insufficient refrigerating capacity even when the hot water supply temperature is raised. ..

In order to achieve the above object, the present invention is a refrigerating apparatus in which the refrigerant is cooled by heat exchange between the refrigerant and water, and the water flow path of the water for cooling the refrigerant is connected by a water pipe, and the inlet of the refrigerating apparatus. A compressor that compresses the refrigerant sucked from the low-stage suction port and discharges it from the low-stage discharge port, compresses the refrigerant sucked from the high-stage suction port again, and discharges the refrigerant from the high-stage discharge port. The water is provided with an intercooler for cooling the refrigerant discharged from the low-stage discharge port, a main gas cooler for cooling the refrigerant discharged from the high-stage discharge port, and an auxiliary gas cooler for cooling the refrigerant after passing through the main gas cooler. The piping is sequentially connected in series in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler.

According to this, by flowing the water in the water pipe in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler, the water sent to the auxiliary gas cooler is supplied in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler having a low internal refrigerant temperature. Therefore, heat exchange between the refrigerant and water can be performed with high efficiency.

According to the present invention, heat exchange between the refrigerant and water can be performed with high efficiency. Therefore, even when the hot water supply temperature is raised, the amount of water flow rate reduction can be suppressed and the hot water supply temperature can be raised. it can. Further, in the intercooler and the gas cooler, sufficient heat dissipation of the refrigerant is possible, so that the temperature of the refrigerant on the outlet side of the refrigerating device is also lowered, and the refrigerating capacity of the refrigerating device can be maintained.

Refrigerant circuit diagram of the freezing device according to the first embodiment of the present invention Circuit diagram of a gas cooler unit showing a second embodiment Circuit diagram of a gas cooler unit showing a third embodiment Circuit diagram of a gas cooler unit showing a fourth embodiment Circuit diagram of a gas cooler unit showing a fifth embodiment Flow chart showing the operation of the fifth embodiment Circuit diagram of a gas cooler unit showing a sixth embodiment A flowchart showing the operation of the freezing device according to the sixth embodiment. A flowchart showing the operation of the refrigerating capacity control A of the sixth embodiment. A flowchart showing the operation of the hot water supply temperature control according to the sixth embodiment. A flowchart showing the operation of the refrigerating capacity control B according to the sixth embodiment. Circuit diagram of a gas cooler unit showing a seventh embodiment A flowchart showing the operation of the freezing device according to the seventh embodiment. A flowchart showing the operation of the refrigerating capacity control A of the seventh embodiment. A flowchart showing the operation of the hot water supply temperature control according to the seventh embodiment. A flowchart showing the operation of the refrigerating capacity control B according to the seventh embodiment. Circuit diagram of a gas cooler unit showing an eighth embodiment A flowchart showing the operation of the freezing device according to the eighth embodiment. A flowchart showing the operation of the refrigerating capacity control A according to the eighth embodiment. A flowchart showing the operation of the hot water supply temperature control according to the eighth embodiment. A flowchart showing the operation of the refrigerating capacity control B according to the eighth embodiment.

The first invention is a refrigerating apparatus in which a refrigerant is cooled by heat exchange between the refrigerant and water, and a water flow path for cooling the refrigerant is connected by a water pipe, and a low-stage suction port is provided through the inlet of the refrigerating apparatus. A compressor that compresses the refrigerant sucked from the high-stage discharge port and discharges it from the low-stage discharge port, compresses the refrigerant sucked from the high-stage suction port again and discharges it from the high-stage discharge port, and discharges from the low-stage discharge port. An intercooler for cooling the refrigerant, a main gas cooler for cooling the refrigerant discharged from the high-stage discharge port, and an auxiliary gas cooler for cooling the refrigerant after passing through the main gas cooler are provided, and the water pipe is the auxiliary gas cooler. The intercooler and the main gas cooler are connected in series in this order.

According to this, by flowing the water in the water pipe in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler, the water sent to the auxiliary gas cooler is supplied in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler having a low internal refrigerant temperature. Therefore, heat exchange between the refrigerant and water can be performed with high efficiency. Therefore, even when the hot water supply temperature is raised, the amount of water flow rate reduction can be suppressed and the hot water supply temperature can be raised. Further, since the intercooler and the gas cooler can sufficiently dissipate heat of the refrigerant, the temperature of the refrigerant on the outlet side of the refrigerating device is also lowered, and the refrigerating capacity of the refrigerating device can be maintained.

In the second invention, a branch portion is provided in the middle of the water pipe between the intercooler and the main gas cooler, a merging portion is provided in the water pipe on the upstream side of the auxiliary gas cooler, and the branch is branched at the branch portion. , A main flow path that supplies water to the main gas cooler, and a main gas cooler bypass flow path that branches at the branch portion and allows water that has flowed by bypassing the main gas cooler to pass through an external heat radiating device and then joins the merging portion. And a flow rate adjusting mechanism for adjusting the flow rate of water flowing through the main flow path and the main gas cooler bypass flow path.

According to this, the amount of heat exchange between the refrigerant and water in the main gas cooler can be adjusted by flowing a part of the water after passing through the intercooler to the main gas cooler bypass flow path by the flow rate adjusting mechanism, and the hot water supply can be performed. The temperature can be adjusted. Also, when it is necessary to adjust the flow rate of water in the main flow path in order to raise the hot water supply temperature, excess water passes through the main gas cooler bypass flow path via the flow rate adjustment mechanism and is dissipated by the external heat exchanger. Since the water is returned to the water pipe on the upstream side of the auxiliary gas cooler, the temperature of the water on the upstream side of the auxiliary gas cooler does not rise, and the auxiliary gas cooler can sufficiently exchange heat between the refrigerant and the water. As a result, insufficient heat dissipation of the refrigerant does not occur, the temperature of the refrigerant on the outlet side of the refrigerating apparatus becomes low, and the refrigerating capacity of the refrigerating apparatus can be maintained.

In the third invention, a second branch is provided in the water pipe on the downstream side of the main gas cooler, and the second branch is provided in the main gas cooler bypass flow path on the upstream side of the external heat radiating device of the main gas cooler bypass flow path. A first bypass flow path, which is provided with a merging portion and branches at the second branching portion and allows water to join the second merging portion to flow, and a first bypass flow path which branches at the second branching portion and flows water for hot water supply. The hot water supply flow path, the first bypass control valve that controls the flow rate of water flowing through the first bypass flow path on the first bypass flow path, and the flow rate of water flowing through the hot water supply flow path on the hot water supply flow path are controlled. It is equipped with a hot water supply control valve.

According to this, by adjusting the flow rate of the water flowing through the main gas cooler bypass flow path and the first bypass flow path, the amount of water flowing through the water pipe is returned to the water pipe on the upstream side of the auxiliary gas cooler via the external heat exchanger. Since the water that has passed through the main gas cooler and has undergone heat exchange can also be sent to the external radiator, the transfer for heat exchange between the refrigerant and water is more than the second invention. A larger heat area can be secured, and a more efficient refrigerating apparatus can be operated.
Further, since the refrigerant temperature on the outlet side of the refrigerating device can be lowered, the refrigerating device can be operated without causing a shortage of refrigerating capacity even when the hot water supply temperature is raised.
In addition, when the hot water supply temperature becomes high and it is necessary to adjust the flow rate of water in the hot water supply flow path, the refrigerating device can be operated by flowing water through the first bypass flow path and continuing to dissipate heat to the outside by the external heat dissipation device. You can continue.

In the fourth invention, a third branch portion is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a third confluence portion is provided upstream of the external heat dissipation device of the main gas cooler bypass flow path. A second bypass flow path for flowing water that is provided and branches at the third branching portion and merges with the third merging portion, and a flow rate of water flowing through the second bypass flow path on the second bypass flow path. It is provided with a second bypass control valve for control.

According to this, the flow rate of water flowing through each of the auxiliary gas cooler, the intercooler, and the main gas cooler can be individually adjusted by adjusting the flow rate adjusting mechanism and the second bypass control valve. Therefore, the operating conditions of the refrigeration cycle can be adjusted by individually adjusting the flow rate of water, and the refrigeration apparatus can be operated with higher efficiency.
Further, since the temperature of the refrigerant on the outlet side of the refrigerating device can be lowered, the refrigerating device can be operated without insufficient refrigerating capacity even when the hot water supply temperature is raised.
In addition, even when the hot water supply temperature becomes high and it is necessary to adjust the flow rate of water in the main flow path, the refrigerating device continues to operate by flowing water through the second bypass flow path and continuing to dissipate heat to the outside with an external heat dissipation device. Can continue to do.

In the fifth invention, the water pipe between the auxiliary gas cooler and the intercooler is provided with a fourth branch portion, and the water pipe on the upstream side of the auxiliary gas cooler is provided with the fourth confluence portion. A fourth bypass flow path that branches at a fourth branching portion, allows the branched water to pass through an external heat radiating device, and then merges with the fourth merging portion, and the fourth bypass flow path on the fourth bypass flow path. It is provided with a fourth bypass control valve that controls the flow rate of water flowing through the bypass flow path.
According to this, by controlling the fourth bypass control valve, it is possible to individually control the flow rate of the water flowing through the intercooler and the main gas cooler separately from the flow rate of the water flowing through the auxiliary gas cooler. Therefore, the hot water supply temperature can be adjusted by controlling the flow rate of the water flowing through the main gas cooler while adjusting the refrigerating capacity of the refrigerating apparatus by controlling the flow rate of the water flowing through the auxiliary gas cooler.

In the sixth invention, a fifth branch portion is provided on the downstream side of the main gas cooler, and a fifth confluence portion is provided on the fourth bypass flow path on the upstream side of the external heat radiating device of the fourth bypass flow path. Controls the flow rate of water flowing through the fifth bypass flow path on the fifth bypass flow path and the fifth bypass flow path that branches at the fifth branch portion and flows the water that joins the fifth confluence section. It is provided with a fifth bypass control valve.
According to this, the flow rate of water flowing through the fifth bypass flow path can be controlled by controlling the opening degree of the fifth bypass control valve. Then, on the downstream side of the main gas cooler, by returning the water to the external heat radiating device, the heat not used for hot water supply can be radiated by the external heat radiating device, and the refrigerating device is operated by continuing to radiate the heat to the outside. You can continue.

In the seventh invention, a sixth branch portion is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a sixth confluence portion is provided in the water pipe between the intercooler and the main gas cooler. A sixth bypass flow path for flowing water that is provided and branches at the sixth branch portion and merges with the sixth junction portion, and a flow rate of water that flows through the sixth bypass flow path on the sixth bypass flow path. It is equipped with a sixth bypass control valve for control.
According to this, the flow rate of water flowing from the auxiliary gas cooler to the sixth bypass flow path can be controlled by controlling the opening degree of the sixth bypass control valve. Then, when the flow rate of water flowing through the water flow path of the gas cooler unit equipped with the intercooler, the main gas cooler, and the auxiliary gas cooler as a unit increases, the intercooler is bypassed and the water flows to the main gas cooler to cause the gas cooler unit. The pressure loss in the water flow path can be reduced. In addition, by reducing the pressure loss in the water flow path, it is possible to operate with the input of the water supply pump small, the required hot water supply temperature changes, and the setting has changed to increase the flow rate of water. Even in this case, it is possible to operate with high efficiency.

In the eighth invention, a seventh branch is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a seventh confluence is provided in the water pipe on the downstream side of the main gas cooler. A seventh bypass flow path that branches at a branching portion of 7 and flows water that joins the seventh merging portion, and a seventh that controls the flow rate of water flowing through the seventh bypass flow path on the seventh bypass flow path. It is equipped with a bypass control valve.
According to this, by controlling the opening degree of the 7th bypass control valve, the flow rate of water flowing from the auxiliary gas cooler to the 7th bypass flow path can be controlled. When the flow rate of water flowing through the water flow path of the gas cooler unit increases, the pressure loss in the water flow path of the gas cooler unit can be reduced by bypassing the intercooler and flowing water through the main gas cooler. In addition, since the pressure loss in the water flow path can be reduced, the operation can be performed with the input of the water supply pump small, the required hot water supply temperature changes, and the flow rate of water flowing through the gas cooler unit increases. Highly efficient operation can be performed even when the setting is changed.

The ninth invention is a hot water supply temperature sensor that detects the temperature of water for hot water supply on the water pipe on the downstream side of the main gas cooler, and the flow rate adjusting mechanism or the flow rate adjusting mechanism based on the hot water supply temperature detected by the hot water supply temperature sensor. A control unit that controls at least one of the first bypass control valve, the fourth bypass control valve, or the fifth bypass control valve is provided, and the control unit has a temperature detected by the hot water supply temperature sensor. , The flow rate of water flowing through the main gas cooler is controlled based on the set temperature of the hot water supply.

According to this, the flow rate of water flowing through the main gas cooler can be controlled based on the difference between the set temperature and the actual water temperature, and the hot water supply temperature can be adjusted. Further, the intercooler, the main gas cooler, and the auxiliary gas cooler do not lack heat dissipation of the refrigerant, the temperature of the refrigerant on the outlet side of the refrigerating device is lowered, and the refrigerating device can be operated while maintaining the refrigerating capacity.

The tenth invention includes a water supply pump in the water flow path between the auxiliary gas cooler and the intercooler.
According to this, since the water supply pump is located in the water flow path on the downstream side of the auxiliary gas cooler, the heat generated by the water supply pump prevents the temperature of the water entering the auxiliary gas cooler from rising, and lowers the water entry temperature of the auxiliary gas cooler. It is possible to obtain a higher refrigerating capacity and use the amount of heat generated by the water supply pump to raise the temperature of water.

The eleventh invention includes a water supply pump in the water flow path between the intercooler and the main gas cooler.
According to this, since the water supply pump is located in the water flow path on the downstream side of the auxiliary gas cooler, the heat generated by the water supply pump prevents the temperature of the water entering the auxiliary gas cooler from rising, and lowers the water entry temperature of the auxiliary gas cooler. And higher freezing capacity can be obtained. Furthermore, since the water supply pump is located on the downstream side of the intercooler, the water entry temperature of the intercooler can be lowered, and the intercooler can also cool the refrigerant at a lower temperature, so that it can be operated under more efficient operating conditions. In addition, the amount of heat generated by the water supply pump can be used to raise the temperature of water.

The twelfth invention uses a carbon dioxide refrigerant as a refrigerant.
According to this, it is possible to further improve energy saving and environmental friendliness by switching between a hot water supply mode in which high temperature hot water can be supplied and a freezing mode in which the efficiency of the refrigerator is emphasized by utilizing the characteristics of the carbon dioxide refrigerant.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a circuit diagram of a refrigeration cycle showing a first embodiment of the refrigeration apparatus according to the present invention.
As shown in FIG. 1, the refrigerating device 1 is connected to a cooling device (not shown) cooled by the refrigerant sent from the refrigerating device 1, and the cooling device is, for example, a convenience store or a supermarket. It is a showcase that cools the refrigerated / frozen products that are installed in the facility and displayed.
Further, in the present embodiment, the refrigerating apparatus 1 uses carbon dioxide as a refrigerant whose high pressure side refrigerant pressure (high pressure) is equal to or higher than the critical pressure (supercritical). This carbon dioxide refrigerant is a natural refrigerant that is friendly to the global environment and is flammable and toxic.

The freezing device 1 includes a compressor unit 10 and a gas cooler unit 20.
The compressor unit 10 includes two compressors 11 arranged in parallel. In the present embodiment, the compressor 11 is an internal intermediate pressure type two-stage compression type rotary compressor provided with a two-stage compression mechanism.
The compressor 11 is provided with a low-stage suction port 12 and a low-stage discharge port 13 in the first-stage compression mechanism, and is provided with a high-stage suction port 14 and a high-stage discharge port 15 in the second-stage compression mechanism. Has been done.
A low-pressure refrigerant pipe 30 connected to the cooling device is connected to the low-stage suction port 12, and the low-pressure refrigerant sent from the cooling device via the low-pressure refrigerant pipe 30 is compressed in the first stage from the low-stage suction port 12. Send to the mechanism.

The first-stage compression mechanism of the compressor 11 compresses the low-temperature low-pressure refrigerant sucked from the low-stage suction port 12, boosts the pressure to an intermediate pressure, and discharges the refrigerant from the low-stage discharge port 13. The second-stage compression mechanism sucks the intermediate-pressure refrigerant compressed by the first-stage compression mechanism from the high-stage suction port 14, compresses it, boosts it to a high pressure, and discharges it from the high-stage discharge port 15. It is configured.

An intermediate pressure discharge pipe 31 is connected to the low-stage discharge port 13 of each compressor 11. The intermediate pressure discharge pipes 31 of the two compressors 11 merge in the middle and are connected to the gas cooler unit 20.
The gas cooler unit 20 includes an intercooler 23, a main gas cooler 24, and an auxiliary gas cooler 25.

The intermediate pressure discharge pipe 31 connected to each compressor 11 joins in the middle and is connected to the inlet side 23a of one flow path of the intercooler 23.
An intermediate pressure suction pipe 32 is connected to the outlet side 23b of one flow path of the intercooler 23, and the intermediate pressure suction pipe 32 is connected to the high-stage suction port 14 of each compressor 11.

Further, a high-pressure discharge pipe 33 is connected to the high-stage discharge port 15 of each compressor 11, and the high-pressure discharge pipe 33 joins in the middle and is connected to the inlet side 24a of one of the main gas coolers 24. Has been done.
An oil separator 26 is provided in the middle of the high-pressure discharge pipe 33. The oil separator 26 separates the oil in the refrigerant, and the oil separator 26 is connected to the intermediate pressure portion of the compressor 11 via the oil pipe 26a. An oil service valve 27 including a three-way valve and an oil adjusting electric valve 28 are provided in the middle of the oil pipe 26a.
The outlet side 24b of one flow path of the main gas cooler 24 is connected to the inlet side 25a of one flow path of the auxiliary gas cooler 25 via a refrigerant pipe 34. An intercooler 16 is connected to the outlet side 25b of one of the flow paths of the auxiliary gas cooler 25 via a refrigerant pipe 34.

A water pipe 40 is connected to the other flow path of the auxiliary gas cooler 25, the main gas cooler 24, and the intercooler 23.
The water pipe 40 is connected to the inlet side 25c of the other flow path of the auxiliary gas cooler 25, and is connected to the inlet side 23c of the other flow path of the intercooler 23 from the outlet side 25d of the other flow path of the auxiliary gas cooler 25. Has been done. The outlet side 23d of the other flow path of the intercooler 23 is connected to the inlet side 24c of the other flow path of the main gas cooler 24, and hot water is supplied from the outlet side 24d of the other flow path of the main gas cooler 24.
As described above, in the present embodiment, the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24 are configured to be connected in series. A water inlet for water supply is provided on the upstream side of the auxiliary gas cooler 25, and a check valve 41 for water supply, a suction tank 42, and a water supply pump 43 are provided in order from the water inlet.
Here, the water supply check valve 41 prevents backflow to the water inlet side, and by installing the suction tank 42 on the upstream side of the water supply pump 43, the water supply pump 43 sucks air and the water is supplied by the pump. Can be prevented from becoming unstable and water can flow stably on the water flow path.

Further, a pressure reducing electric valve 17 for reducing the pressure of the refrigerant sent from the auxiliary gas cooler 25 is provided in the middle of the refrigerant pipe 34 from the auxiliary gas cooler 25.
The inlet side 50a of the split heat exchanger 50 is connected to the refrigerant pipe 34 on the outlet side of the intercooler 16.

A branch pipe 51 branching from the refrigerant pipe 34 is connected to the refrigerant pipe 34 on the outlet side 50b of the split heat exchanger 50, and the branch pipe 51 is connected to the split heat exchanger 50 via a liquid return electric valve 52. It is connected to the other inlet side 50c of the. The refrigerant pipe 34 and the branch pipe 51 are arranged so that the flow directions of the refrigerant are opposite to each other so that the refrigerant flowing through the refrigerant pipe 34 and the refrigerant flowing through the branch pipe 51 can efficiently exchange heat. It is configured in.
A refrigerant return pipe 54 is connected to the intercooler 16 via a gas return electric valve 53, and the refrigerant return pipe 54 is connected to a branch pipe 51.

The refrigerant pipe 34 on the outlet side 50b of the split heat exchanger 50 is connected to the cooling device.
The refrigerant return pipe 54 on the outlet side 50d of the split heat exchanger 50 is connected to the outlet side of the intercooler 23.
The liquid return electric valve 52 decompresses the high-pressure refrigerant on the outlet side 50b of the split heat exchanger 50 and expands it to an intermediate pressure level, and the split heat exchanger 50 branches off from the high-pressure refrigerant flowing through the refrigerant pipe 34. It is configured to cool the high-pressure refrigerant by exchanging heat with the decompressed refrigerant flowing through the pipe 51.
The refrigerant heat exchanged by the split heat exchanger 50 merges with the refrigerant on the outlet side of the intercooler 23 and is sent to the compressor 11 from the high-stage suction port 14 to optimize the temperature of the refrigerant discharged from the compressor 11. It is designed to be.

A refrigerator inlet temperature sensor 66 that detects the temperature of the refrigerant sent from the cooling device is provided on the inlet side of the refrigerant pipe 34 of the compressor unit 1, and the temperature of the refrigerant sent to the cooling device is provided on the outlet side of the refrigerant pipe 34. The refrigerator outlet temperature sensor 67 for detecting the above is provided.
A discharge temperature sensor 68 for detecting the discharge temperature of the refrigerant is provided on the discharge side of the compressor 11, and split heat for detecting the refrigerant temperature at the outlet of the split heat exchanger 50 is provided on the outlet side of the split heat exchanger 50. An exchanger outlet temperature sensor 69 is provided.

Next, the operation of the first embodiment will be described.
First, by operating the compressor 11, the refrigerant sent from the cooling device is sucked by the low-stage suction port 12 of the compressor 11, and the sucked refrigerant is compressed to an intermediate pressure by the first-stage compression mechanism. It is discharged from the low-stage discharge port 13.

Further, the refrigerant discharged from the low-stage discharge port 13 of the compressor 11 flows into the intercooler 23 via the intermediate pressure discharge pipe 31. The inflowing refrigerant exchanges heat with water in the intercooler 23 to be cooled, and is returned to the high-stage suction port 14 of the compressor 11.
The refrigerant returned from the intercooler 23 is compressed by the compressor 11 by the second-stage compression mechanism, discharged from the high-stage discharge port 15, passes through the oil separator 26, and then sent to the main gas cooler 24.

The refrigerant sent from the compressor 11 exchanges heat with water in the main gas cooler 24, then exchanges heat in the auxiliary gas cooler 25, and is sent to the intercooler 16.
The refrigerant cooled by the intercooler 16 branches from the refrigerant pipe 34 by the split heat exchanger 50, exchanges heat with the refrigerant decompressed by the liquid return electric valve 52, is cooled, and is sent to the cooling device.

Then, the refrigerant sent to the cooling device is depressurized to a predetermined pressure by the drawing means, heat is exchanged in the evaporator, and the inside of the refrigerator is cooled to a predetermined temperature.
The refrigerant flowing out of the evaporator is returned to the compressor 11 via the low-pressure refrigerant pipe 30.

Here, in the present embodiment, the water pipe 40 is connected in series in the order of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24.
Therefore, the water flowing through the water pipe 40 first flows to the auxiliary gas cooler 25, and then flows to the intercooler 23 and the main gas cooler 24 in that order.
As a result, in the auxiliary gas cooler 25, the water sent from the water pipe 40 exchanges heat with the refrigerant to raise the temperature, and then in the intercooler 23, the water exchanges heat with the refrigerant to further raise the temperature. Finally, in the main gas cooler 24, the temperature can be further raised.
On the other hand, the refrigerant discharged from the low-stage discharge port 13 of the compressor 11 is cooled by the intercooler 23, sucked into the compressor 11 again, compressed, and then discharged from the high-stage discharge port 15 to be discharged from the high-stage discharge port 15 to the main gas cooler 24. Is cooled by water in the main gas cooler 24, and then further cooled by water in the auxiliary gas cooler 25.

By supplying the water in the water pipe 40 in the order of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24 having a low refrigerant temperature, heat exchange between the refrigerant and the water can be performed with high efficiency. ..
As a result, even when the hot water supply temperature is raised, the amount of water flow rate reduction can be suppressed and the hot water supply temperature can be raised. Further, since the intercooler 23 and the gas coolers 24 and 25 can sufficiently dissipate heat of the refrigerant, the temperature of the refrigerant on the outlet side of the refrigerating device 1 is also lowered, and the refrigerating capacity of the refrigerating device 1 can be maintained.

Here, when a carbon dioxide refrigerant is used, hot water can be supplied at a high temperature, but when hot water is supplied at a high temperature, the temperature difference between the water temperature on the inlet side and the water temperature on the outlet side of the water pipe 40 is increased. Conventionally, it is necessary to reduce the flow rate of water flowing through the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24. Therefore, in the intercooler 23 and the main gas cooler 24, the heat dissipation of the refrigerant is insufficient, and there is a possibility that sufficient heat exchange between the water flowing through the water pipe 40 and the refrigerant cannot be performed.
However, in the present embodiment, the water sent from the water pipe 40 is sequentially heated by the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24, so that the flow rate of the water flowing through the water pipe 40 is reduced. In addition, sufficient heat exchange can be performed in the main gas cooler 24 and the auxiliary gas cooler 25, and hot water can be supplied at a high temperature.

As described above, according to the first embodiment, the compressor 11, the intercooler 23 that cools the refrigerant discharged from the low-stage discharge port 13, and the main that cools the refrigerant discharged from the high-stage discharge port 15. A gas cooler 24 and an auxiliary gas cooler 25 for cooling the refrigerant after passing through the main gas cooler 24 are provided, and the water pipe 40 is connected in series in the order of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24.

According to this, the water in the water pipe 40 is supplied in the order of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24 having a low refrigerant temperature, so that heat exchange between the refrigerant and the water can be performed with high efficiency. Can be done. Therefore, even when the hot water supply temperature is raised, the amount of water flow rate reduction can be suppressed. Further, since the intercooler 23 and the gas cooler can sufficiently dissipate heat of the refrigerant, the temperature of the refrigerant on the outlet side of the refrigerating device 1 can be lowered, and the refrigerating capacity of the refrigerating device 1 can be maintained.

Further, in the present embodiment, a carbon dioxide refrigerant is used as the refrigerant.
According to this, by utilizing the characteristics of the carbon dioxide refrigerant and switching between the hot water supply mode in which high temperature hot water can be supplied and the freezing mode in which the efficiency of the refrigerator is emphasized, energy saving and environmental friendliness can be further improved.

Next, a second embodiment of the present invention will be described.
FIG. 2 is a circuit diagram of a gas cooler unit 20 showing a second embodiment of the present invention.
In the present embodiment, a branch portion 60 is provided in the middle of the water pipe 40 between the intercooler 23 and the main gas cooler 24. Further, a merging portion 61 is provided in the water pipe 40 on the upstream side of the auxiliary gas cooler 25.
The branch portion 60 bypasses the main flow path 63 for supplying water from the intercooler 23 to the main gas cooler 24 and the main gas cooler 24 from the intercooler 23, passes through the external heat radiating device 62, and then joins the main gas cooler 61. It branches into the bypass flow path 64.
The external heat dissipation device 62 is, for example, a cooling tower that cools the cooling water with air, a water-cooled heat exchanger that cools the cooling water with cooling water of another flow path, or the like.

In the present embodiment, the branch portion 60 is composed of, for example, a three-way valve, and the branch portion 60 can adjust the flow rate of water flowing through the main flow path 63 and the main gas cooler bypass flow path 64. It is configured to function as an adjusting mechanism 65.
Here, the flow rate adjusting mechanism 65 does not need to be installed in the branch portion 60, and the flow rate may be adjusted by installing control valves capable of adjusting the flow rate in each of the main flow path 63 and the main gas cooler bypass flow path 64.
Since other configurations are the same as those in the first embodiment, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the second embodiment will be described.
In the present embodiment, the flow rate adjusting mechanism 65 of the branch portion 60 adjusts the flow rate of water after passing through the intercooler 23, and the flow rate of water flowing through the main flow path 63 or the main gas cooler bypass flow path 64, respectively. It will be adjusted.
A part or all of the water after passing through the intercooler 23 passes through the external heat radiating device 62 through the main gas cooler bypass flow path 64, and then is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.

By allowing a part of the water after passing through the intercooler 23 to flow through the main gas cooler bypass flow path 64 by the flow rate adjusting mechanism 65 in this way, the amount of heat exchange between the refrigerant and water in the main gas cooler 24 can be adjusted. , The hot water supply temperature can be adjusted.
Then, even when it is necessary to adjust the flow rate of water in the main flow path 63 in order to raise the hot water supply temperature, excess water is sent to the external heat radiating device 62 through the main gas cooler bypass flow path 64 via the flow rate adjustment mechanism 65. Then, the water radiated by the external heat radiating device 62 is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25, so that the auxiliary gas cooler 25 can sufficiently exchange heat between the refrigerant and the water. As a result, insufficient heat dissipation of the refrigerant does not occur, the temperature of the refrigerant on the outlet side of the refrigerating apparatus 1 becomes low, and the refrigerating capacity of the refrigerating apparatus 1 can be maintained.

As described above, in the second embodiment, the branch portion 60 is provided in the middle of the water pipe 40 between the intercooler 23 and the main gas cooler 24, and the junction portion joins the water pipe 40 on the upstream side of the auxiliary gas cooler 25. 61 is provided, and the main flow path 63 that branches at the branch portion 60 and supplies water to the main gas cooler 24 and the water that branches at the branch portion 60 and flows by bypassing the main gas cooler 24 are passed through the external heat dissipation device 62. It is provided with a main gas cooler bypass flow path 64 that is later merged with the merging portion 61, and a flow rate adjusting mechanism 65 that adjusts the flow rate of water flowing through the main flow path 63 and the main gas cooler bypass flow path 64.

As a result, the amount of heat exchange between the refrigerant and water in the main gas cooler 24 can be adjusted by allowing a part of the water after passing through the intercooler 23 to flow through the main gas cooler bypass flow path 64 by the flow rate adjusting mechanism 65. , The hot water supply temperature can be adjusted. Further, even when it is necessary to adjust the flow rate of water in the main flow path 63 in order to raise the hot water supply temperature, excess water passes through the main gas cooler bypass flow path 64 via the flow rate adjustment mechanism 65 and the external heat dissipation device 62. Since the water radiated in the above is returned to the water pipe 40 on the upstream side of the auxiliary gas cooler 25, the auxiliary gas cooler 25 can sufficiently exchange heat between the refrigerant and the water. As a result, insufficient heat dissipation of the refrigerant does not occur, the temperature of the refrigerant on the outlet side of the refrigerating device 1 becomes low, and the capacity of the refrigerating device 1 can be maintained.

Next, a third embodiment of the present invention will be described.
FIG. 3 is a circuit diagram of the gas cooler unit 20 showing the third embodiment of the present invention.
In the present embodiment, the water pipe 40 on the downstream side of the main gas cooler 24 is provided with the second branch portion 70. Further, a second merging portion 71 is provided on the upstream side of the main gas cooler bypass flow path 64 with respect to the external heat radiating device 62.
One of the water pipes 40 branched at the second branch 70 serves as a hot water supply flow path 72 through which water for hot water supply flows, and the other water pipe 40 branches at the second branch 70. It becomes the first bypass flow path 73 through which the water merging into the merging portion 71 flows.

A first bypass control valve 74 that controls the flow rate of water flowing through the first bypass flow path 73 is provided in the middle of the first bypass flow path 73.
Further, a hot water supply control valve 75 for controlling the flow rate of water flowing through the hot water supply flow path 72 is provided in the middle of the hot water supply flow path 72.
Further, a check valve 44 for the main gas cooler bypass flow path is provided on the main gas cooler bypass flow path 64, and a check valve 45 for the first bypass flow path is provided on the first bypass flow path 73. Has been done.
Here, in the present embodiment, the second branch portion 70 is configured by connecting the water pipe 40, but the flow rate of water flowing through the first bypass flow path 73 is connected to the second branch portion 70. A three-way valve may be installed as the first bypass control valve 74 for controlling the above, and the flow rate of water flowing through the first bypass flow path 74 may be adjusted by the three-way valve.
Since other configurations are the same as those of the first embodiment and the second embodiment, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the third embodiment will be described.
Also in the present embodiment, as in the second embodiment, the flow rate adjusting mechanism 65 of the branch portion 60 adjusts the flow rate of water after passing through the intercooler 23, and the main flow path 63 or the main gas cooler bypass flow path. The flow rate of water flowing in each of 64 is adjusted.
As a result, a part or all of the water after passing through the intercooler 23 passes through the external heat radiating device 62 through the main gas cooler bypass flow path 64, and then is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.

The flow rate of water flowing through the first bypass flow path 73 is controlled by controlling the opening degree of the first bypass control valve 74 and the opening degree of the hot water supply control valve 75, and is one of the water after passing through the main gas cooler 24. After the part or all of the water has passed through the external heat radiating device 62 via the first bypass flow path 73, it is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.
As a result, the flow rate of water flowing through the first bypass flow path 73 is controlled by controlling the opening degree of the first bypass control valve 74 and the opening degree of the hot water supply control valve 75, and the water after passing through the main gas cooler 24. After some or all of the water has passed through the external heat radiating device 62 via the first bypass flow path 73, it is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.

Then, by adjusting the flow rate of the water flowing through the main gas cooler bypass flow path 64 and the first bypass flow path 73, the water flowing through the water pipe 40 joins the auxiliary gas cooler 25 on the upstream side via the external heat radiating device 62. The amount returned to the unit 61 can be adjusted.
Since the water that has passed through the main gas cooler 24 and has undergone heat exchange can also be sent to the external heat radiating device 62 in this way, a larger heat transfer area between the refrigerant and water is secured as compared with the second embodiment. This makes it possible to operate the refrigerating apparatus 1 with higher efficiency.

As described above, in the third embodiment, the water pipe 40 on the downstream side of the main gas cooler 24 is provided with the second branch portion 70, and the main gas cooler bypass flow path 64 on the upstream side of the external heat radiating device 62 is the second. The merging portion 71 of 2 is provided, and is branched at the second branching portion 70, and is branched at the first bypass flow path 73 for flowing the water merging into the second merging portion 71 and the second branching portion 70 for hot water supply. A hot water supply flow path 72 through which water flows, a first bypass control valve 74 that controls the flow rate of water flowing through the first bypass flow path 73 on the first bypass flow path 73, and a hot water supply flow path 72 on the hot water supply flow path 72. A hot water supply control valve 75 for controlling the flow rate of water flowing through the water heater is provided.

As a result, by adjusting the flow rate of the water flowing through the main gas cooler bypass flow path 64 and the first bypass flow path 73, the water flowing through the water pipe 40 is on the upstream side of the auxiliary gas cooler 25 via the external heat radiating device 62. Since the amount returned to the merging portion 61 can be adjusted, the water after passing through the main gas cooler 24 and exchanging heat can also be sent to the external heat radiating device 62, so that the refrigerant and water are more than those in the second embodiment. It is possible to secure a larger heat transfer area between the and, and to operate the refrigerating apparatus 1 with higher efficiency.
Further, since the refrigerant temperature on the outlet side of the freezing device 1 can be lowered, the freezing device 1 can be operated without causing a shortage of the freezing capacity even when the hot water supply temperature is raised.
Further, even when the hot water supply temperature becomes high and it is necessary to adjust the flow rate of the water in the hot water supply flow path 72, the operation of the refrigerating device 1 is continued by flowing water through the first bypass flow path 73 and continuing to dissipate heat to the outside. Can continue to do.

Next, a fourth embodiment of the present invention will be described.
FIG. 4 is a circuit diagram of the gas cooler unit 20 showing the fourth embodiment of the present invention.
In the present embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with a third branch portion 80. Further, a third merging portion 81 is provided on the upstream side of the main gas cooler bypass flow path 64 with respect to the external heat radiating device 62.
A second bypass flow path 82 that branches at the third branch portion 80 and flows water that joins the third merging portion 81 is connected to the third branch portion 80, and is connected to the second bypass flow path 82. A second bypass control valve 83 for controlling the flow rate of water flowing through the second bypass flow path 82 is provided in the middle portion.
Further, a check valve 46 for the second bypass flow path is provided on the second bypass flow path 83.
Here, in the present embodiment, the third branch portion 80 is configured by connecting the water pipe 40, but the flow rate of water flowing through the second bypass flow path 82 is connected to the third branch portion 80. A three-way valve may be installed as the second bypass control valve 83 for controlling the above, and the flow rate of water flowing through the second bypass flow path 82 may be adjusted by the three-way valve.
Since other configurations are the same as those of the first embodiment and the second embodiment, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the fourth embodiment will be described.
Also in the present embodiment, as in the second embodiment, the flow rate adjusting mechanism 65 of the branch portion 60 adjusts the flow rate of water after passing through the intercooler 23, and the main flow path 63 or the main gas cooler bypass flow path. 64. Adjust the flow rate of water flowing through each.
As a result, a part or all of the water after passing through the intercooler 23 passes through the external heat radiating device 62 through the main gas cooler bypass flow path 64, and then is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.

Further, by controlling the opening degree of the second bypass control valve 83, it is possible to control the flow rate of water flowing from the third branch portion 80 on the downstream side of the auxiliary gas cooler 25 to the second bypass flow path 82, which is auxiliary. A part of the water after passing through the gas cooler 25 passes through the external heat radiating device 62 through the main gas cooler bypass flow path 64, and then is returned to the confluence portion 61 on the upstream side of the auxiliary gas cooler 25.
Thereby, by adjusting the flow rate adjusting mechanism 65 and the second bypass control valve 83, it is possible to individually adjust the flow rate of the water flowing through each of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24. Therefore, the operating conditions of the refrigeration cycle can be adjusted by individually adjusting the flow rate of water, and the refrigeration apparatus 1 can be operated with higher efficiency.

As described above, in the fourth embodiment, the third branch portion 80 is provided in the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23, and the external heat radiation device 62 of the main gas cooler bypass flow path 64 is provided. On the second bypass flow path 82 and the second bypass flow path 82, a third merging section 81 is provided on the upstream side, and the water that branches at the third branching section 80 and merges with the third merging section 81 flows. A second bypass control valve 83 for controlling the flow rate of water flowing through the second bypass flow path 82 was provided.

Thereby, by adjusting the flow rate adjusting mechanism 65 and the second bypass control valve 83, it is possible to individually adjust the flow rate of the water flowing through each of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24. Therefore, the operating conditions of the refrigeration cycle can be adjusted by individually adjusting the flow rate of water, and the refrigeration apparatus 1 can be operated with higher efficiency.
Further, since the refrigerant temperature on the outlet side of the freezing device 1 can be lowered, the freezing device 1 can be operated without causing a shortage of the freezing capacity even when the hot water supply temperature is raised.
Further, even when the hot water supply temperature becomes high and it is necessary to adjust the flow rate of the water in the main flow path 63, the operation of the refrigerating device 1 is continued by flowing the water through the second bypass flow path 82 and continuing to dissipate heat to the outside. You can continue.

Next, a fifth embodiment of the present invention will be described.
FIG. 5 is a circuit diagram of the gas cooler unit 20 showing the fifth embodiment of the present invention.
In the present embodiment, the configuration of the gas cooler unit 20 is the same as that of the second embodiment.
In the present embodiment, a hot water supply temperature sensor 90 for detecting the temperature of hot water for hot water supply is provided on the water pipe 40 on the downstream side of the main gas cooler 24.
Here, the hot water supply temperature sensor 90 may be provided either inside or outside the water pipe 40 on the downstream side of the main gas cooler 24 as long as the temperature of the water for hot water supply can be detected.
Further, in the present embodiment, the refrigerating apparatus 1 includes a control unit 91 that controls each unit in an integrated manner. The control unit 91 is configured to control the flow rate of water flowing through the main flow path 63 based on the temperature detected by the hot water supply temperature sensor 90 and the set temperature of the hot water supply.

Next, the operation of the fifth embodiment will be described.
FIG. 6 is a flowchart showing the operation of the fifth embodiment.
As shown in FIG. 6, the control unit 91 has a hot water supply temperature Tw. Acquire out (ST1).
The control unit 91 has a hot water supply temperature Tw. It is determined whether or not out is equal to or greater than the value of the set temperature T1-set temperature difference ΔT for hot water supply (ST2). Here, ΔT is set to, for example, about 5K.
The control unit 91 has a hot water supply temperature Tw. If it is determined that out is equal to or greater than the value of the hot water supply set temperature T1-set temperature difference ΔT (ST2: YES), the control unit 91 determines that the hot water supply temperature Tw. It is determined whether or not out is equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST3).

The control unit 91 has a hot water supply temperature Tw. If it is determined that out is equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST3: YES), the control unit 91 determines whether or not a stop signal has been output (ST4), and the stop signal is output. If it is not output (ST4: NO), the above operation is repeated.
Further, when the control unit 91 determines that the stop signal has been output (ST4: YES), the control unit 91 ends the control of the flow rate adjusting mechanism 65.

On the other hand, the control unit 91 has a hot water supply temperature Tw. If it is determined that out is not equal to or greater than the value of the set temperature T1-set temperature difference ΔT for hot water supply (ST2: NO), the control unit 91 adjusts the flow rate adjusting mechanism 65 to the main gas cooler bypass flow path 64 side. It is determined whether or not it is the upper limit (ST5).
Here, the adjustment amount indicates an amount adjusted by the flow rate adjusting mechanism 65, such as a valve opening degree or a flow rate adjusted by the flow rate adjusting mechanism 65.
When the control unit 91 determines that the adjustment amount of the flow rate adjusting mechanism 65 to the main gas cooler bypass flow path 64 side is the upper limit (ST5: YES), the control unit 91 determines whether or not a stop signal has been output. If the stop signal is not output (ST4: NO), the above operation is repeated.
Further, when the control unit 91 determines that the stop signal has been output (ST4: YES), the control unit 91 ends the control of the flow rate adjusting mechanism 65.

When the control unit 91 determines that the adjustment amount of the flow rate adjusting mechanism 65 toward the main gas cooler bypass flow path 64 is not the upper limit (ST5: NO), the flow rate adjusting mechanism increases the flow rate of the main gas cooler bypass flow path 64. Control 65 (ST6).
After that, the control unit 91 determines whether or not the stop signal has been output (ST4), and if the stop signal has not been output (ST4: NO), repeats the above-described operation.
Further, when the control unit 91 determines that the stop signal has been output (ST4: YES), the control unit 91 ends the control of the flow rate adjusting mechanism 65.

On the other hand, the control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST3: NO), the control unit 91 adjusts the flow rate adjusting mechanism 65 to the main gas cooler bypass flow path 64 side as the lower limit. It is determined whether or not it is (ST7).
When the control unit 91 determines that the adjustment amount of the flow rate adjusting mechanism 65 to the main gas cooler bypass flow path 64 side is the lower limit (ST7: YES), the control unit 91 determines whether or not a stop signal has been output. If the stop signal is not output (ST4: NO), the above operation is repeated.
Further, when the control unit 91 determines that the stop signal has been output (ST4: YES), the control unit 91 ends the control of the flow rate adjusting mechanism 65.

Further, when the control unit 91 determines that the adjustment amount of the flow rate adjusting mechanism 65 toward the main gas cooler bypass flow path 64 is not the lower limit (ST7: NO), the flow rate is reduced so as to reduce the flow rate of the main gas cooler bypass flow path 64. The adjustment mechanism 65 is controlled (ST8).
After that, the control unit 91 determines whether or not the stop signal has been output (ST4), and if the stop signal has not been output (ST4: NO), repeats the above-described operation.
Further, when the control unit 91 determines that the stop signal has been output (ST4: YES), the control unit 91 ends the control of the flow rate adjusting mechanism 65.

By controlling in this way, the hot water supply temperature sensor 90 detects the hot water supply temperature, and when the hot water supply temperature is lower than the set temperature, the flow rate adjusting mechanism 65 is controlled to control the flow rate of water flowing through the main gas cooler bypass flow path 64. When the temperature is increased and the hot water supply temperature is higher than the set temperature, the flow rate adjusting mechanism 65 can be controlled to reduce the flow rate of water flowing through the main gas cooler bypass flow path 64.
As a result, the flow rate of water flowing through the main flow path 63 can be controlled based on the difference between the set temperature and the actual water temperature, and the hot water supply temperature can be adjusted. Further, the intercooler 23, the main gas cooler 24, and the auxiliary gas cooler 25 do not cause insufficient heat dissipation of the refrigerant, the refrigerant temperature on the outlet side of the refrigerating device 1 can be lowered, and the operation of the refrigerating device 1 can be maintained.
Here, in the present embodiment, the flow rate of water flowing through the main flow path 63 is controlled based on the temperature detected by the hot water supply temperature sensor 90 provided in the gas cooler unit 20, but the compressor unit 10 is provided. Control may be performed by using the refrigerator inlet temperature sensor 66, the refrigerator outlet temperature sensor 67, the discharge temperature sensor 68, the split heat exchanger outlet temperature sensor 69, the pressure sensor, or the like.

As described above, in the present embodiment, based on the hot water supply temperature sensor 90 that detects the temperature of the water for hot water supply on the water pipe 40 on the downstream side of the main gas cooler 24 and the hot water supply temperature by the hot water supply temperature sensor 90. A control unit 91 for controlling the flow rate adjusting mechanism 65 is provided, and the control unit 91 controls the flow rate of water flowing through the main flow path 63 based on the temperature detected by the hot water supply temperature sensor 90 and the set temperature of the hot water supply.

As a result, the flow rate of water flowing through the main flow path 63 can be controlled based on the difference between the set temperature and the actual water temperature, and the hot water supply temperature can be adjusted. Further, the intercooler 23, the main gas cooler 24, and the auxiliary gas cooler 25 do not cause insufficient heat dissipation of the refrigerant, the refrigerant temperature on the outlet side of the refrigerating device 1 can be lowered, and the operation of the refrigerating device 1 can be maintained.

Next, the sixth embodiment of the present invention will be described.
FIG. 7 is a circuit diagram of the gas cooler unit 20 showing the sixth embodiment of the present invention.
In the present embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with a fourth branch portion 84. Further, a fourth merging portion 85 is provided in the water pipe 40 on the upstream side of the auxiliary gas cooler 25.
A fourth bypass flow path 86 that branches at the fourth branch portion 84 and flows water that joins the fourth junction portion 85 is connected to the fourth branch portion 84, and is connected to the fourth bypass flow path 86. A fourth bypass control valve 87 that controls the flow rate of water flowing through the fourth bypass flow path 86 is provided in the middle portion.
Further, a check valve 88 for the fourth bypass flow path is provided on the fourth bypass flow path 86.
Here, in the present embodiment, the fourth branch portion 84 is configured by connecting the water pipe 40, but the flow rate of water flowing through the fourth bypass flow path 86 is connected to the fourth branch portion 84. A three-way valve may be installed as the fourth bypass control valve 87 to control the above, and the flow rate of water flowing through the fourth bypass flow path 86 may be adjusted by the three-way valve.

Further, in the present embodiment, the water pipe 40 on the downstream side of the main gas cooler 24 is provided with the fifth branch portion 100. A fifth bypass flow path 102 connected to the fifth confluence 101 is connected to the fifth branch 100.
A fifth bypass control valve 103 for controlling the flow rate of water flowing through the fifth bypass flow path 102 is provided in the middle of the fifth bypass flow path 102.
A check valve 104 for the fifth bypass flow path is provided on the fifth bypass flow path 102.
Here, in the present embodiment, the fifth branch portion 100 is configured by connecting the water pipe 40, but the flow rate of water flowing through the fifth bypass flow path 102 is connected to the fifth branch portion 100. A three-way valve may be installed as the fifth bypass control valve 103 to control the above, and the flow rate of water flowing through the fifth bypass flow path 102 may be adjusted by the three-way valve.
Further, in the present embodiment, a suction tank 42 and a water supply pump 43 are provided in the water flow path between the auxiliary gas cooler 25 and the intercooler 23.
Here, also in the present embodiment, by installing the suction tank 42 on the upstream side of the water supply pump 43, the water supply becomes unstable due to the occurrence of cavitation due to the pressure drop in the element in front of the water supply pump 43. This can be prevented and water can flow stably on the water flow path.

In the present embodiment, a hot water supply temperature sensor 90 for detecting the temperature of hot water for hot water supply is provided on the water pipe 40 on the downstream side of the main gas cooler 24. The water pipe 40 on the upstream side of the auxiliary gas cooler 25 is provided with a cooling water temperature sensor 92 that detects the temperature of the cooling water to the auxiliary gas cooler 25. Further, a refrigerant outlet temperature sensor 93 for detecting the refrigerant temperature on the outlet side of the auxiliary gas cooler 25 is provided.
Further, a cooling water flow meter 94 for detecting the flow rate of the cooling water flowing through the auxiliary gas cooler 25 of the water pipe 40 is provided, and the hot water supply flow meter 95 for detecting the flow rate of the hot water supply on the downstream side of the main gas cooler 24 of the water pipe 40. Is provided.

Further, in the present embodiment, the refrigerating apparatus 1 includes a control unit 91 that controls each unit in an integrated manner. The control unit 91 controls the opening degree of each control valve based on the detected temperature by the hot water supply temperature sensor 90, the cooling water temperature sensor 92 and the refrigerant outlet temperature sensor 93, and the detected flow rate by the cooling water flow meter 94 and the hot water flow meter 95. Is configured to control the flow rate of water flowing through the main gas cooler 24 and adjust the hot water supply temperature.
Since other configurations are the same as those of the above-described embodiments, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the sixth embodiment will be described.
FIG. 8 is a flowchart showing the control of the freezing device according to the sixth embodiment.
As shown in FIG. 8, after acquiring the operation signal (ST101), the control unit 91 acquires the cooling water flow rate Vc by the cooling water flow meter 94 and the hot water supply flow rate Vh by the hot water supply flow meter 95 (ST102), respectively, and the cooling water Cooling water inlet temperature Tw by the temperature sensor 92. Acquire in (ST103).
After that, the control unit 91 acquires the mode identification signal (ST104), acquires the set temperature information (ST105), and determines whether or not the hot water supply mode signal is output (ST106).

When the control unit 91 determines that the hot water supply mode is set (ST106: YES), the control unit 91 performs refrigerating capacity control A (ST107) and controls the hot water supply temperature (ST108).
When the control unit 91 determines that the hot water supply mode is not set (ST109), the control unit 91 determines that the refrigerating mode emphasizes the efficiency of the refrigerator and performs refrigerating capacity control B (ST1).
These refrigerating capacity control A, hot water supply temperature control, and refrigerating capacity control B are performed until a stop signal is output (ST110).

FIG. 9 is a flowchart showing the operation of the refrigerating capacity control A in the sixth embodiment.
As shown in FIG. 9, when the refrigerating capacity control A is performed, the control unit 91 sets the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. After acquiring out (ST121), it is determined whether or not the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST122).
When it is determined that the opening degree of the hot water supply control valve 75 is not equal to or greater than the set opening degree (ST122: NO), the opening degree of the hot water supply control valve 75 is controlled to be increased by n pulses (ST123). Then, the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST124), and if it is determined that the opening degree is not the lower limit (ST124: NO), the fifth bypass control valve 103 The opening degree is controlled to be lowered by n pulses (ST125).

When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST122: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the cooling set temperature T2-set temperature difference ΔT2 (ST126).
And Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST126: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the lower limit (ST127), and if it is determined that it is not the lower limit (ST127: NO). ), The opening degree of the hot water supply control valve 75 is controlled to be lowered by n pulses (ST128). When it is determined that the lower limit is reached (ST127: YES), the control of the refrigerating capacity control A is terminated.

The control unit 91 is a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST126: YES), Tr. out-Tw. It is determined whether or not in is equal to or greater than the value of T2 + ΔT2 (ST129).
And Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2 + ΔT2 (ST129: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the upper limit (ST1130), and if it is not the upper limit (ST130: NO), the hot water supply control valve The opening degree of 75 is controlled to be increased by n pulses (ST131). In the case of the upper limit (ST130: YES), the control of the refrigerating capacity control A is terminated.

Next, the hot water supply temperature control will be described.
FIG. 10 is a flowchart showing the operation of the hot water supply temperature control in the sixth embodiment.
As shown in FIG. 10, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST141).
The control unit 91 has a hot water supply temperature Tw. It is determined whether or not out is equal to or greater than the value of the set temperature T1-set temperature difference ΔT for hot water supply (ST142).

The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or greater than the value of T1-ΔT (ST142: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST143).
When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is not the lower limit (ST143: NO), the control unit 91 controls to lower the opening degree of the fifth bypass control valve 103 by n pulses (ST144). After that, the hot water supply temperature control is terminated.

When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is the lower limit (ST143: YES), the control unit 91 determines whether or not the opening degree of the fourth bypass control valve 87 is the upper limit (ST145). ).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the upper limit (ST145: NO), the control unit 91 controls to increase the opening degree of the fourth bypass control valve 87 by n pulses (ST146).
When it is determined that the opening degree of the fourth bypass control valve 87 is the upper limit (ST145: YES), the control is terminated.

The control unit 91 has a hot water supply temperature Tw. If it is determined that out is equal to or greater than the value of T1-ΔT (ST142: YES), the hot water supply temperature Tw. It is determined whether or not out is equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST147).
The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST147: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the lower limit (ST148).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the lower limit (ST148: NO), the control unit 91 controls to lower the opening degree of the fourth bypass control valve 87 by n pulses (ST149). After that, the hot water supply temperature control is terminated.

When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is the lower limit (ST148: YES), the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the upper limit (ST150). ).
When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is not the upper limit (ST150: NO), the control unit 91 controls to increase the opening degree of the fifth bypass control valve 103 by n pulses (ST151).
When it is determined that the opening degree of the fifth bypass control valve 103 is the upper limit (ST150: YES), the hot water supply temperature control is terminated.

Next, the refrigerating capacity control B will be described.
FIG. 11 is a flowchart showing the operation of the refrigerating capacity control B according to the sixth embodiment.
As shown in FIG. 11, when the refrigerating capacity control B is performed, the control unit 91 determines the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. The out is acquired (ST161), and it is determined whether or not the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST162).
When it is determined that the opening degree of the hot water supply control valve 75 is not equal to or greater than the set opening degree (ST162: NO), the opening degree of the hot water supply control valve 75 is controlled to be lowered by n pulses (ST163). Then, the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the upper limit (ST164), and if it is determined that the opening degree is not the upper limit (ST164: NO), the fifth bypass control valve 103 The opening degree is controlled to be increased by n pulses (ST165).

When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST162: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the set temperature T2-set temperature difference ΔT2 for hot water supply (ST166).
Then, the control unit 91 is subjected to Tr. out-Tw. When it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST166: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST167), and when it is determined that it is not the lower limit (ST167). : NO), the opening degree of the fifth bypass control valve 103 is controlled to be lowered by n pulses (ST168).

The control unit 91 is a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST166: YES), Tr. out-Tw. It is determined whether or not in is equal to or less than the value of T2 + ΔT2 (ST169).
And Tr. out-Tw. If it is determined that in is not less than or equal to the value of T2 + ΔT2 (ST169: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the upper limit (ST170), and if it is not the upper limit (ST170: NO), the first 5 The opening degree of the bypass control valve 103 is controlled to be increased by n pulses (ST171).

Subsequently, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST172).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the heat dissipation set temperature T3-set temperature difference ΔT3 (ST173).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or greater than the value of T3-ΔT3 (ST173: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the lower limit (ST174).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the lower limit (ST174: NO), the control unit 91 controls to lower the opening degree of the fourth bypass control valve 87 by n pulses (ST175). After that, the control of the refrigerating capacity control B is terminated.

On the other hand, the control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is equal to or greater than the value of T3-ΔT3 (ST173: YES), the hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or less than the value of the heat dissipation set temperature T3 + the set temperature difference ΔT3 (ST176).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or less than the value of T3 + ΔT3 (ST176: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the upper limit (ST177). Then, when the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the upper limit (ST177: NO), the control unit 91 controls to increase the opening degree of the fourth bypass control valve 87 by n pulses (ST178). .. When it is determined that the opening degree of the fourth bypass control valve 87 is the upper limit (ST177: YES), the control of the refrigerating capacity control B is terminated.
Here, in the control flow of the present embodiment, the opening degree at the time of controlling the opening degree of the control valve is represented by n pulses and an arbitrary opening degree, but when controlling a plurality of control valves, each control valve is used. Different opening settings may be used, or the same opening setting may be used.

In the present embodiment, by controlling the opening degree of the fourth bypass control valve 87, the flow rate of water flowing from the auxiliary gas cooler 25 to the fourth bypass flow path 86 can be controlled and passed through the auxiliary gas cooler 25. After a part of the water after passing through the external heat radiating device 62, it is returned to the water flow path upstream of the auxiliary gas cooler 25.
Thereby, by controlling the fourth bypass control valve 87, it is possible to individually control the flow rate of the water flowing through the intercooler 23 and the main gas cooler 24, in addition to the flow rate of the water flowing through the auxiliary gas cooler 25. Therefore, the hot water supply temperature can be adjusted by controlling the flow rate of the water flowing through the main gas cooler 24 while adjusting the refrigerating capacity of the refrigerating device 1 by controlling the flow rate of the water flowing through the auxiliary gas cooler 25.

Further, by controlling the opening degree of the fifth bypass control valve 103, the flow rate of water flowing through the fifth bypass flow path 102 can be controlled.
As a result, by returning the water to the external heat radiating device 62 on the downstream side of the main gas cooler 24, the heat not used for hot water supply can be radiated by the external heat radiating device 62, and the heat is continuously radiated to the outside to freeze. The operation of the device 1 can be continued.

The control unit 91 can adjust the hot water supply temperature by controlling the flow rate of the water flowing through the main gas cooler 24 based on the detection value of the hot water supply temperature sensor 90, thereby preventing the cooling device 1 from being insufficiently cooled. It is possible to continue the operation of the refrigerating device 1 while keeping the hot water supply temperature close to the set temperature without generating it.
Here, in the present embodiment, the flow rate of water flowing through the main gas cooler 94 is controlled based on the temperatures detected by the hot water supply temperature sensor 90, the cooling water temperature sensor 92, and the refrigerant outlet temperature sensor 93 provided in the gas cooler unit 20. However, control was performed using the refrigerator inlet temperature sensor 66, the refrigerator outlet temperature sensor 67, the discharge temperature sensor 68, the split heat exchanger outlet temperature sensor 69, the pressure sensor, and the like provided in the compressor unit 10. You may.

As described above, in the sixth embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with the fourth branch portion 84, and the water pipe 40 on the upstream side of the auxiliary gas cooler 25 is provided with the fourth branch portion 84. With the fourth bypass flow path 86 provided with the merging portion 85 of No. 4, branching at the fourth branching portion 84, passing the branched water through the external heat radiating device 62, and then merging with the fourth merging portion 85. A fourth bypass control valve 87 that controls the flow rate of water flowing through the fourth bypass flow path 86 on the fourth bypass flow path 86 is provided.
Thereby, by controlling the fourth bypass control valve 87, it is possible to individually control the flow rate of the water flowing through the intercooler 23 and the main gas cooler 24, in addition to the flow rate of the water flowing through the auxiliary gas cooler 25. Therefore, the hot water supply temperature can be adjusted by controlling the flow rate of the water flowing through the main gas cooler 24 while adjusting the refrigerating capacity of the refrigerating device 1 by controlling the flow rate of the water flowing through the auxiliary gas cooler 25.

Further, in the present embodiment, the fifth branch portion 100 is provided on the downstream side of the main gas cooler 24, and the fifth bypass flow path 86 on the upstream side of the external heat dissipation device 62 of the fourth bypass flow path 86 has a fifth branch. A merging portion 101 is provided, and a fifth bypass flow path 102 is provided to return the auxiliary gas cooler 25 to the upstream side after passing through the external heat radiating device 62 from the fifth branch portion 100, and the flow rate of water flowing through the fifth bypass flow path 102. A fifth bypass control valve 103 was provided to control the above.
As a result, on the downstream side of the main gas cooler 24, by returning the water to the external heat radiating device 62, the heat not used for hot water supply can be cooled by the external heat radiating device 62, and the heat is continuously dissipated to the outside for freezing. The operation of the device 1 can be continued.

Further, in the present embodiment, the water supply pump 43 is provided in the water flow path between the auxiliary gas cooler 25 and the intercooler 23.
As a result, since the water supply pump 43 is located on the downstream side of the auxiliary gas cooler 25, it is possible to prevent the temperature of the water entering the auxiliary gas cooler from rising due to the heat generated by the water supply pump and lower the water entry temperature of the auxiliary gas cooler 25. The amount of heat generated by the water supply pump 43 can be used to raise the temperature of water while obtaining a higher refrigerating capacity.

Next, a seventh embodiment of the present invention will be described.
FIG. 12 is a circuit diagram of the gas cooler unit 20 showing the seventh embodiment of the present invention.
In the present embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with a sixth branch portion 110, and the water pipe 40 between the intercooler 23 and the main gas cooler 24 is provided. Is provided with a sixth merging portion 111.
A sixth bypass flow path 112, which branches at the sixth branch portion 110 and allows water to flow into the sixth junction portion 111, is connected to the sixth branch portion 110, and is connected to the sixth bypass flow path 112. A sixth bypass control valve 113 for controlling the flow rate of water flowing through the sixth bypass flow path 112 is provided in the middle portion.
Further, a check valve 114 for the sixth bypass flow path is provided on the sixth bypass flow path 112, and the intercooler outlet check valve is stopped on the water flow path between the intercooler 23 and the sixth confluence portion 111. A valve 115 is provided.
Here, in the present embodiment, the sixth branch portion 110 is configured by connecting the water pipe 40, but the flow rate of water flowing through the sixth bypass flow path 112 to the sixth branch portion 110. A three-way valve may be installed as the sixth bypass control valve 113 for controlling the above, and the flow rate of water flowing through the sixth bypass flow path 112 may be adjusted by the three-way valve.
Further, in the present embodiment, a suction tank 42 and a water supply pump 43 are provided in the water flow path between the intercooler 23 and the main gas cooler 24.
Here, also in the present embodiment, by installing the suction tank 42 on the upstream side of the water supply pump 43, the water supply becomes unstable due to the occurrence of cavitation due to the pressure drop in the element in front of the water supply pump 43. This can be prevented and water can flow stably on the water flow path.

Also in this embodiment, the control unit 91 controls the flow rate of the water flowing through the main gas cooler 24 based on the temperature detected by the hot water supply temperature sensor 90 and the set temperature of the hot water supply, and adjusts the hot water supply temperature. It is configured in.
Since other configurations are the same as those of the above-described embodiments, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the seventh embodiment will be described.
FIG. 13 is a flowchart showing the control of the freezing device according to the seventh embodiment.
After acquiring the operation signal (ST201), the control unit 91 acquires the cooling water flow rate Vc by the cooling water flow meter 94 and the hot water supply flow rate Vh by the hot water supply flow meter 95 (ST202), and the cooling water by the cooling water temperature sensor 92. Inlet temperature Tw. Acquire in (ST203).
After that, the control unit 91 acquires the mode identification signal (ST204), acquires the set temperature information (ST205), and T1-Tw. The set opening degree P6set of the sixth bypass control valve 113 is set based on the value of in (ST206).

The control unit 91 determines whether or not the hot water supply mode signal is output (ST207), and when the control unit 91 determines that the hot water supply mode is in (ST207: YES), the refrigerating capacity control A is performed. (ST208), the hot water supply temperature is controlled (ST209).
When the control unit 91 determines that the hot water supply mode is not set (ST207: NO), the control unit 91 determines that the refrigerating mode emphasizes the efficiency of the refrigerator and performs refrigerating capacity control B (ST210).
These refrigerating capacity control A, hot water supply temperature control, and refrigerating capacity control B are performed until a stop signal is output (ST211).

FIG. 14 is a flowchart showing the operation of the refrigerating capacity control A according to the seventh embodiment.
As shown in FIG. 14, when the refrigerating capacity control A is performed, the control unit 91 sets the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. The out is acquired (ST221), and it is determined whether or not the opening degree of the sixth bypass control valve 113 is equal to the set opening degree (ST222).
If the control unit 91 determines that the opening degree of the sixth bypass control valve 113 is not equal to the set opening degree (ST222: NO), is the opening degree P6 of the sixth bypass control valve 113 larger than the set opening degree P6set? It is determined whether or not (ST223).

When the control unit 91 determines that the opening degree P6 of the sixth bypass control valve 113 is smaller than the set opening degree P6set (ST223: NO), the control unit 91 controls to increase the opening degree of the sixth bypass control valve 113 by n pulses. (ST224).
When the control unit 91 determines that the opening degree P6 of the sixth bypass control valve 113 is larger than the set opening degree P6set (ST223: YES), the control unit 91 controls to lower the opening degree of the sixth bypass control valve 113 by n pulses. (ST225).

When the control unit 91 determines that the opening degree of the sixth bypass control valve 113 is equal to the set opening degree (ST222: YES), the control unit 91 determines whether or not the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree. (ST226).
When it is determined that the opening degree of the hot water supply control valve 75 is not equal to or greater than the set opening degree (ST226: NO), the opening degree of the hot water supply control valve 75 is controlled to be increased by n pulses (ST227). Then, the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST228), and if it is determined that the opening degree is not the lower limit (ST228: NO), the fifth bypass control valve 103 The opening degree is controlled to be lowered by n pulses (ST229).

If it is determined that the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST226: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the set temperature T2-set temperature difference ΔT2 for hot water supply (ST230).
Then, the control unit 91 is subjected to Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST230: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the lower limit (ST231), and if it is determined that it is not the lower limit (ST2311: NO). ), The opening degree of the hot water supply control valve 75 is controlled to be lowered by n pulses (ST232). In the case of the lower limit, the control of the refrigerating capacity control A is terminated.

Further, the control unit 91 has a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST230: YES), Tr. out-Tw. It is determined whether or not in is equal to or greater than the value of T2 + ΔT2 (ST233).
And Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2 + ΔT2 (ST233: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the upper limit (ST234), and if it is not the upper limit (ST234: NO), the hot water supply control valve The opening degree of 75 is controlled to be increased by n pulses (ST235). When it is determined that the opening degree of the hot water supply control valve 75 is the upper limit, the control of the refrigerating capacity control A is terminated.

Next, the hot water supply temperature control will be described.
FIG. 15 is a flowchart showing the operation of the hot water supply temperature control in the seventh embodiment.
As shown in FIG. 15, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST241).
The control unit 91 has a hot water supply temperature Tw. It is determined whether or not out is equal to or greater than the value of the set temperature T1-set temperature difference ΔT for hot water supply (ST242).

The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or greater than the value of T1-ΔT (ST242: NO), it is determined whether or not the opening degree of the first bypass control valve 74 is the lower limit (ST243).
When the control unit 91 determines that the opening degree of the first bypass control valve 74 is not the lower limit (ST243: NO), the control unit 91 controls to lower the opening degree of the first bypass control valve 74 by n pulses (ST244). After that, the hot water supply temperature control is terminated.
When the control unit 91 determines that the opening degree of the first bypass control valve 74 is the lower limit (ST243: YES), the control unit 91 determines whether or not the opening degree of the flow rate adjusting mechanism 65 is the upper limit (ST245).
When the control unit 91 determines that the opening degree of the flow rate adjusting mechanism 65 is not the upper limit (ST245: NO), the control unit 91 controls to increase the opening degree of the flow rate adjusting mechanism 65 by n pulses (ST246).
When it is determined that the opening degree of the flow rate adjusting mechanism 65 is the upper limit (ST245: YES), the control is terminated.

The control unit 91 has a hot water supply temperature Tw. If it is determined that out is equal to or greater than the value of T1-ΔT (ST242: YES), the hot water supply temperature Tw. It is determined whether or not out is equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST247).
The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST247: NO), it is determined whether or not the opening degree of the flow rate adjusting mechanism 65 is the lower limit (ST248).
When the control unit 91 determines that the opening degree of the flow rate adjusting mechanism 65 is not the lower limit (ST248: NO), the control unit 91 controls to lower the opening degree of the flow rate adjusting mechanism 65 by n pulses (ST249). After that, the hot water supply temperature control is terminated.

When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is the lower limit (ST248: YES), the control unit 91 determines whether or not the opening degree of the first bypass control valve 74 is the upper limit (ST250). ).
When the control unit 91 determines that the opening degree of the first bypass control valve 74 is not the upper limit (ST250: NO), the control unit 91 controls to increase the opening degree of the first bypass control valve 74 by n pulses (ST251).
When it is determined that the opening degree of the first bypass control valve 74 is the upper limit (ST250: YES), the hot water supply temperature control is terminated.

Next, the refrigerating capacity control B will be described.
FIG. 16 is a flowchart showing the operation of the refrigerating capacity control B in the seventh embodiment.
As shown in FIG. 16, when the refrigerating capacity control B is performed, the control unit 91 sets the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. The out is acquired (ST261), and it is determined whether or not the opening degree of the sixth bypass control valve 113 is equal to the set opening degree (ST262).
When it is determined that the opening degree of the sixth bypass control valve 113 is not equal to the set opening degree (ST262: NO), it is determined whether or not the opening degree P6 of the sixth bypass control valve 113 is larger than the set opening degree P6set. (ST263).
When the control unit 91 determines that the opening degree P6 of the sixth bypass control valve 113 is smaller than the set opening degree P6set (ST263: NO), the control unit 91 controls to increase the opening degree of the sixth bypass control valve 113 by n pulses. (ST264).
When the control unit 91 determines that the opening degree P6 of the sixth bypass control valve 113 is larger than the set opening degree P6set (ST263: YES), the control unit 91 controls to lower the opening degree of the sixth bypass control valve 113 by n pulses. (ST265).

When the control unit 91 determines that the opening degree of the sixth bypass control valve 113 is equal to the set opening degree (ST262: YES), the control unit 91 determines whether or not the opening degree of the hot water supply control valve 75 is the lower limit (ST266). ).
When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is not the lower limit (ST266: NO), the control unit 91 controls to lower the opening degree of the hot water supply control valve 75 by n pulses (ST267). Then, the control unit 91 determines whether or not the opening degree of the first bypass control valve 74 is the lower limit (ST268), and if it is determined that the opening degree is not the lower limit (ST268: NO), the control unit 91 of the first bypass control valve 74. The opening degree is controlled to be lowered by n pulses (ST269).

When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is the lower limit (ST266: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the cooling set temperature T2-set temperature difference ΔT2 (ST270).
And Tr. out-Tw. When it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST270: NO), it is determined whether or not the opening degree of the first bypass control valve 74 is the lower limit (ST271), and when it is determined that it is not the lower limit (ST271). : NO), the opening degree of the first bypass control valve 74 is controlled to be lowered by n pulses (ST272).

The control unit 91 is a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST270: YES), Tr. out-Tw. It is determined whether or not in is equal to or greater than the value of T2 + ΔT2 (ST273).
And Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2 + ΔT2 (ST273: NO), it is determined whether or not the opening degree of the first bypass control valve 74 is the upper limit (ST274), and if it is not the upper limit (ST274: NO), the first 1 The opening degree of the bypass control valve 74 is controlled to be increased by n pulses (ST275).

Subsequently, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST276).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the heat dissipation set temperature T3-set temperature difference ΔT3 (ST277).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or greater than the value of T3-ΔT3 (ST277: NO), it is determined whether or not the opening degree of the flow rate adjusting mechanism 65 is the lower limit (ST278).
When the control unit 91 determines that the opening degree of the flow rate adjusting mechanism 65 is not the lower limit (ST278: NO), the control unit 91 controls to lower the opening degree of the flow rate adjusting mechanism 65 by n pulses (ST279). After that, the control of the refrigerating capacity control B is terminated.

On the other hand, the control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is equal to or greater than the value of T3-ΔT3 (ST277: YES), the hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or less than the value of the set temperature T3 for hot water supply + the set temperature difference ΔT3 (ST280).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or less than the value of T3 + ΔT3 (ST280: NO), it is determined whether or not the opening degree of the flow rate adjusting mechanism 65 is the upper limit (ST281). Then, when the control unit 91 determines that the opening degree of the flow rate adjusting mechanism 65 is not the upper limit (ST281: NO), the control unit 91 controls to increase the opening degree of the flow rate adjusting mechanism valve 65 by n pulses (ST282). When it is determined that the opening degree of the flow rate adjusting mechanism 65 is the upper limit (ST281: YES), the control of the refrigerating capacity control B is terminated.
Here, in the control flow of the present embodiment, the opening degree at the time of controlling the opening degree of the control valve is represented by n pulses and an arbitrary opening degree, but when controlling a plurality of control valves, it differs for each control valve. The opening degree may be set, or the same opening degree may be set.

In the present embodiment, the flow rate of water flowing from the auxiliary gas cooler 25 to the sixth bypass flow path 112 can be controlled by controlling the opening degree of the sixth bypass control valve 113.
As a result, when the flow rate of water flowing through the water flow path of the gas cooler unit 20 increases, the pressure loss in the water flow path of the gas cooler unit 20 is reduced by bypassing the intercooler 23 and flowing water through the main gas cooler 24. be able to. Further, since the pressure loss in the water flow path can be reduced, the operation can be performed in a state where the input of the water supply pump 43 is small, and even when the required hot water supply temperature changes and the flow rate setting changes. It is possible to operate with high efficiency.

Further, the control unit 91 can control the flow rate of water flowing through the main gas cooler 24 based on the detection value of the hot water supply temperature sensor 90 and adjust the hot water supply temperature, thereby preventing the refrigerating apparatus 1 from being insufficiently cooled. It is possible to continue the operation of the refrigerating device 1 while keeping the hot water supply temperature close to the set temperature without generating it.
Here, in the present embodiment, the flow rate of water flowing through the main gas cooler 94 is controlled based on the temperatures detected by the hot water supply temperature sensor 90, the cooling water temperature sensor 92, and the refrigerant outlet temperature sensor 93 provided in the gas cooler unit 20. However, control was performed using the refrigerator inlet temperature sensor 66, the refrigerator outlet temperature sensor 67, the discharge temperature sensor 68, the split heat exchanger outlet temperature sensor 69, the pressure sensor, and the like provided in the compressor unit 10. You may.

As described above, in the present embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with the sixth branch 110, and the water pipe between the intercooler 23 and the main gas cooler 24 is provided. A sixth merging section 111 is provided in 40, and a sixth bypass flow path 112 for flowing water that branches at the sixth branching section 110 and merges with the sixth merging section 111 and water flowing through the sixth bypass flow path 112. A sixth bypass control valve 113 for controlling the flow rate of the water is provided.
As a result, when the flow rate of water flowing through the water pipe 40 increases, the pressure loss of the entire water flow path can be reduced by bypassing the intercooler 23 and flowing the water. Further, since the pressure loss in the water flow path can be reduced, the operation can be performed in a state where the input of the water supply pump 43 is small, and even when the required hot water supply temperature changes and the flow rate setting changes. It is possible to operate with high efficiency.

Further, in the present embodiment, the water supply pump 43 is provided in the water flow path between the intercooler 23 and the main gas cooler 24.
Here, also in the present embodiment, by installing the suction tank 42 on the upstream side of the water supply pump 43, the water supply becomes unstable due to the occurrence of cavitation due to the pressure drop in the element in front of the water supply pump 43. This can be prevented and water can flow stably on the water flow path.
As a result, since the water supply pump 43 is located in the water flow path on the downstream side of the auxiliary gas cooler 25, the heat generated by the water supply pump prevents the temperature of the water entering the auxiliary gas cooler from rising, and lowers the water entry temperature of the auxiliary gas cooler 25. It is possible to obtain a higher freezing capacity. Further, since the water supply pump 43 is located on the downstream side of the intercooler 23, the water entry temperature of the intercooler 23 can be lowered, and the intercooler 23 can also cool the refrigerant at a lower temperature, so that the operating conditions are more efficient. It can be operated, and the amount of heat generated by the water supply pump 43 can be used to raise the temperature of water.

Next, an eighth embodiment of the present invention will be described.
FIG. 17 is a circuit diagram of the gas cooler unit 20 showing the eighth embodiment of the present invention.
In the present embodiment, as in the sixth embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with a fourth branch portion 84. Further, a fourth merging portion 85 is provided on the upstream side of the main gas cooler bypass flow path 64 with respect to the external heat radiating device 62.
A fourth bypass flow path 86 that branches at the fourth branch portion 84 and flows water that joins the fourth junction portion 85 is connected to the fourth branch portion 84, and is connected to the fourth bypass flow path 86. A fourth bypass control valve 87 that controls the flow rate of water flowing through the fourth bypass flow path 86 is provided in the middle portion.

The water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with a seventh branch portion 120, and a seventh confluence portion 121 is provided on the downstream side of the main gas cooler 24. Here, the fourth branch portion 84 and the seventh branch portion 120 may be shared as shown in FIG. 17, or may be provided individually.
A seventh bypass flow path 122 that branches at the seventh branch portion 120 and flows water that merges with the seventh junction portion 121 is connected to the seventh branch portion 120, and is connected to the seventh bypass flow path 122. A seventh bypass control valve 123 for controlling the flow rate of water flowing through the seventh bypass flow path 122 is provided in the middle portion.
Further, a check valve 124 for the 7th bypass flow path is provided on the 7th bypass flow path 122, and the main gas cooler outlet check valve is stopped on the water flow path between the main gas cooler 24 and the 7th confluence portion 121. A valve 125 is provided.

Here, in the present embodiment, the seventh branch portion 120 is configured by connecting the water pipe 40, but after providing the fourth branch portion 84 and the seventh branch portion 170 separately. , A three-way valve is installed in the seventh branch 170 as a seventh bypass control valve 123 for controlling the flow rate of water flowing through the seventh bypass flow path 122, and the flow rate of water flowing through the seventh bypass flow path 122 by the three-way valve. It may be configured to adjust.
In the present embodiment, a hot water supply temperature sensor 90 for detecting the temperature of hot water for hot water supply is provided on the water pipe 40 on the downstream side of the main gas cooler 24 and on the downstream side of the seventh confluence 121. In this way, by providing the hot water supply temperature sensor 90 in the water pipe 40 on the downstream side of the main gas cooler 24 and on the downstream side of the seventh confluence portion 121, the water flowing through the seventh bypass flow path 122 and merging is mixed. The temperature of the water discharged from the gas cooler unit 20 can be grasped.

Also in this embodiment, the control unit 91 controls the flow rate of the water flowing through the main gas cooler 24 based on the temperature detected by the hot water supply temperature sensor 90 and the set temperature of the hot water supply, and adjusts the hot water supply temperature. It is configured in.
Since other configurations are the same as those of the above-described embodiments, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Next, the operation of the eighth embodiment will be described.
FIG. 18 is a flowchart showing the control of the freezing device according to the eighth embodiment.
As shown in FIG. 18, when the control unit 91 acquires the operation signal (ST301), it acquires the cooling water flow rate Vc by the cooling water flow meter 94 and the hot water supply flow rate Vh by the hot water supply flow meter 95 (ST302), and cools the water. Cooling water inlet temperature Tw by the water temperature sensor 92. Acquire in (ST303).
After that, the control unit 91 acquires the mode identification signal (ST304), acquires the set temperature information (ST305), and T1-Tw. The set opening P7set of the 7th bypass control valve 123 is set based on the value of in (ST306).

The control unit 91 determines whether or not a hot water supply mode signal is output (ST307), and when the control unit 91 determines that the hot water supply mode is in (ST307: YES), the control unit 91 performs refrigerating capacity control A and at the same time. (ST308), the hot water supply temperature is controlled (ST309).
When the control unit 91 determines that the hot water supply mode is not set (ST307: NO), the control unit 91 determines that the refrigerating mode emphasizes the efficiency of the refrigerator and performs refrigerating capacity control B (ST310).
These refrigerating capacity control A, hot water supply temperature control, and refrigerating capacity control B are performed until a stop signal is output (ST311).

FIG. 19 is a flowchart showing the operation of the refrigerating capacity control A according to the eighth embodiment.
As shown in FIG. 19, when the refrigerating capacity control A is performed, the control unit 91 determines the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. The out is acquired (ST321), and it is determined whether or not the opening degree of the 7th bypass control valve 123 is equal to the set opening degree (ST322).
If the control unit 91 determines that the opening degree of the 7th bypass control valve 123 is not equal to the set opening degree (ST322: NO), is the opening degree P7 of the 7th bypass control valve 123 larger than the set opening degree P7set? It is determined whether or not (ST323).

When the control unit 91 determines that the opening degree P7 of the 7th bypass control valve 123 is smaller than the set opening degree P7set (ST323: NO), the control unit 91 controls to increase the opening degree of the 7th bypass control valve 123 by n pulses. (ST324).
When the control unit 91 determines that the opening degree P7 of the 7th bypass control valve 123 is larger than the set opening degree P7set (ST323: YES), the control unit 91 controls to lower the opening degree of the 7th bypass control valve 123 by n pulses. (ST325).

When the control unit 91 determines that the opening degree of the 7th bypass control valve 123 is equal to the set opening degree (ST322: YES), the control unit 91 determines whether or not the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree. (ST326).
When it is determined that the opening degree of the hot water supply control valve 75 is not equal to or greater than the set opening degree (ST326: NO), the opening degree of the hot water supply control valve 75 is controlled to be increased by n pulses (ST327). Then, the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST328), and if it is determined that the opening degree is not the lower limit (ST328: NO), the fifth bypass control valve 103 The opening degree is controlled to be lowered by n pulses (ST329).

If it is determined that the opening degree of the hot water supply control valve 75 is equal to or greater than the set opening degree (ST326: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the cooling set temperature T2-set temperature difference ΔT2 (ST330).
And Tr. out-Tw. If it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST330: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the lower limit (ST331), and if it is determined that it is not the lower limit (ST331: NO). ), The opening degree of the hot water supply control valve 75 is controlled to be lowered by n pulses (ST332). In the case of the lower limit, the control of the refrigerating capacity control A is terminated.

Further, the control unit 91 has a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST330: YES), Tr. out-Tw. It is determined whether or not in is equal to or less than the value of T2 + ΔT2 (ST333).
And Tr. out-Tw. If it is determined that in is not less than or equal to the value of T2 + ΔT2 (ST333: NO), it is determined whether or not the opening degree of the hot water supply control valve 75 is the upper limit (ST334), and if it is not the upper limit (ST334: NO), the hot water supply control valve The opening degree of 75 is controlled to be increased by n pulses (ST335). When it is determined that the opening degree of the hot water supply control valve 75 is the upper limit (ST334: YES), the control of the refrigerating capacity control A is terminated.

Next, the hot water supply temperature control will be described.
FIG. 20 is a flowchart showing the operation of the hot water supply temperature control in the eighth embodiment.
As shown in FIG. 20, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST341).
The control unit 91 has a hot water supply temperature Tw. It is determined whether or not out is equal to or greater than the value of the set temperature T1-set temperature difference ΔT for hot water supply (ST342).

The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or greater than the value of T1-ΔT (ST342: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST343).
When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is not the lower limit (ST343: NO), the control unit 91 controls to lower the opening degree of the fifth bypass control valve 103 by n pulses (ST344). After that, the hot water supply temperature control is terminated.
When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is the lower limit (ST343: YES), the control unit 91 determines whether or not the opening degree of the fourth bypass control valve 87 is the upper limit (ST345). ).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the upper limit (ST345: NO), the control unit 91 controls to increase the opening degree of the fourth bypass control valve 87 by n pulses (ST346).
When it is determined that the opening degree of the fourth bypass control valve 87 is the upper limit (ST345: YES), the hot water supply temperature control is terminated.

The control unit 91 has a hot water supply temperature Tw. If it is determined that out is equal to or greater than the value of T1-ΔT (ST342: YES), the hot water supply temperature Tw. It is determined whether or not out is equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT (ST347).
The control unit 91 has a hot water supply temperature Tw. When it is determined that out is not equal to or less than the value of the set temperature T1 for hot water supply + the set temperature difference ΔT1 (ST347: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the lower limit (ST348).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the lower limit (ST348: NO), the control unit 91 controls to lower the opening degree of the fourth bypass control valve 87 by n pulses (ST349). After that, the hot water supply temperature control is terminated.

When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is the lower limit (ST348: YES), the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the upper limit (ST350). ).
When the control unit 91 determines that the opening degree of the fifth bypass control valve 103 is not the upper limit (ST350: NO), the control unit 91 controls to increase the opening degree of the fifth bypass control valve 103 by n pulses (ST351).
When it is determined that the opening degree of the fifth bypass control valve 103 is the upper limit (ST350: YES), the hot water supply temperature control is terminated.

Next, the refrigerating capacity control B will be described.
FIG. 21 is a flowchart showing the operation of the refrigerating capacity control B in the eighth embodiment.
As shown in FIG. 21, when the refrigerating capacity control B is performed, the control unit 91 determines the refrigerant outlet temperature Tr of the auxiliary gas cooler 25 by the refrigerant outlet temperature sensor 93. The out is acquired (ST361), and it is determined whether or not the opening degree of the 7th bypass control valve 123 is equal to the set opening degree (ST362).
When it is determined that the opening degree of the 7th bypass control valve 123 is not equal to the set opening degree (ST362: NO), it is determined whether or not the opening degree P7 of the 6th bypass control valve 113 is larger than the set opening degree P7set. (ST363).

When the control unit 91 determines that the opening degree P7 of the 7th bypass control valve 123 is smaller than the set opening degree P7set (ST363: NO), the control unit 91 controls to increase the opening degree of the 7th bypass control valve 123 by n pulses. (ST364).
When the control unit 91 determines that the opening degree P6 of the 7th bypass control valve 123 is larger than the set opening degree P6set (ST363: YES), the control unit 91 controls to lower the opening degree of the 7th bypass control valve 123 by n pulses. (ST365).

When the control unit 91 determines that the opening degree of the sixth bypass control valve 113 is equal to the set opening degree (ST362: YES), the control unit 91 determines whether or not the opening degree of the hot water supply control valve 75 is the lower limit (ST366). ).
When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is not the lower limit (ST366: NO), the control unit 91 controls to lower the opening degree of the hot water supply control valve 75 by n pulses (ST367). Then, the control unit 91 determines whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST368), and if it is determined that the opening degree is not the lower limit (ST368: NO), the fifth bypass control valve 103 The opening degree is controlled to be lowered by n pulses (ST369).

When the control unit 91 determines that the opening degree of the hot water supply control valve 75 is the lower limit (ST366: YES), the refrigerant outlet temperature Tr. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the cooling set temperature T2-set temperature difference ΔT2 (ST370).
And Tr. out-Tw. When it is determined that in is not equal to or greater than the value of T2-ΔT2 (ST370: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the lower limit (ST371), and when it is determined that it is not the lower limit (ST371). : NO), the opening degree of the fifth bypass control valve 103 is controlled to be lowered by n pulses (ST372).

The control unit 91 is a Tr. out-Tw. If it is determined that in is equal to or greater than the value of T2-ΔT2 (ST370: YES), Tr. out-Tw. It is determined whether or not in is equal to or less than the value of T2 + ΔT2 (ST373).
And Tr. out-Tw. If it is determined that in is not less than or equal to the value of T2 + ΔT2 (ST373: NO), it is determined whether or not the opening degree of the fifth bypass control valve 103 is the upper limit (ST374), and if it is not the upper limit (ST374: NO), the first 5 The opening degree of the bypass control valve 103 is controlled to be increased by n pulses (ST375).

Subsequently, the control unit 91 uses the hot water supply temperature sensor 90 to determine the hot water supply temperature Tw. Acquire out (ST376).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or greater than the value of the heat dissipation set temperature T3-set temperature difference ΔT3 (ST377).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or greater than the value of T3-ΔT3 (ST377: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the lower limit (ST378).
When the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the lower limit (ST378: NO), the control unit 91 controls to lower the opening degree of the fourth bypass control valve 87 by n pulses (ST379). After that, the control of the refrigerating capacity control B is terminated.

On the other hand, the control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is equal to or greater than the value of T3-ΔT3 (ST377: YES), the hot water supply temperature Tw. out and cooling water inlet temperature Tw. It is determined whether or not the difference from in is equal to or less than the value of the set temperature T3 for hot water supply + the set temperature difference ΔT3 (ST380).
The control unit 91 has a hot water supply temperature Tw. out and cooling water inlet temperature Tw. When it is determined that the difference from in is not equal to or less than the value of T3 + ΔT3 (ST380: NO), it is determined whether or not the opening degree of the fourth bypass control valve 87 is the upper limit (ST381). Then, when the control unit 91 determines that the opening degree of the fourth bypass control valve 87 is not the upper limit (ST381: NO), the control unit 91 controls to increase the opening degree of the fourth bypass control valve 87 by n pulses (ST382). .. When it is determined that the opening degree of the fourth bypass control valve 87 is the upper limit (ST381: YES), the control of the refrigerating capacity control B is terminated.
Here, in the control flow of the present embodiment, the opening degree at the time of controlling the opening degree of the control valve is represented by n pulses and an arbitrary opening degree, but when controlling a plurality of control valves, it differs for each control valve. The opening degree may be set, or the same opening degree may be set.

In the present embodiment, by controlling the opening degree of the fourth bypass control valve 87, the flow rate of water flowing from the auxiliary gas cooler 25 to the fourth bypass flow path 86 can be controlled and passed through the auxiliary gas cooler 25. After a part of the water after passing through the external heat radiating device 62, it is returned to the water flow path upstream of the auxiliary gas cooler 25.
Thereby, by controlling the fourth bypass control valve 87, it is possible to individually control the flow rate of the water flowing through each of the auxiliary gas cooler 25, the intercooler 23, and the main gas cooler 24. Therefore, the hot water supply temperature can be adjusted by controlling the flow rate of the water flowing through the main gas cooler 24 while adjusting the refrigerating capacity of the refrigerating device 1 by controlling the flow rate of the water flowing through the auxiliary gas cooler 25.

Further, by controlling the opening degree of the 7th bypass control valve 123, the flow rate of water flowing from the auxiliary gas cooler 25 to the 7th bypass flow path 122 can be controlled.
As a result, when the flow rate of water flowing through the water pipe 40 increases, the pressure loss in the water flow path of the gas cooler unit can be reduced by bypassing the intercooler 23 and flowing water through the main gas cooler 24. Further, since the pressure loss in the water flow path can be reduced, the operation can be performed in a state where the input of the water supply pump 43 is small, and even when the required hot water supply temperature changes and the flow rate setting changes. It is possible to operate with high efficiency.

Further, the control unit 91 can control the flow rate of water flowing through the main gas cooler 24 based on the detection value of the hot water supply temperature sensor 90 and adjust the hot water supply temperature, thereby preventing the refrigerating apparatus 1 from being insufficiently cooled. It is possible to continue the operation of the refrigerating device 1 while keeping the hot water supply temperature close to the set temperature without generating it.
Here, in the present embodiment, the flow rate of water flowing through the main gas cooler 94 is controlled based on the temperatures detected by the hot water supply temperature sensor 90, the cooling water temperature sensor 92, and the refrigerant outlet temperature sensor 93 provided in the gas cooler unit 20. However, control was performed using the refrigerator inlet temperature sensor 66, the refrigerator outlet temperature sensor 67, the discharge temperature sensor 68, the split heat exchanger outlet temperature sensor 69, the pressure sensor, and the like provided in the compressor unit 10. You may.

As described above, in the present embodiment, the water pipe 40 between the auxiliary gas cooler 25 and the intercooler 23 is provided with the seventh branch portion 120, and the water pipe 40 on the downstream side of the main gas cooler 24 is provided with the seventh branch portion 120. The 7th bypass flow path 122, which branches at the 7th branching section 120 and flows the water merging into the 7th merging section 121, and the flow rate of the water flowing through the 7th bypass flow path 122 are controlled. A seventh bypass control valve 123 is provided.
As a result, by controlling the opening degree of the 7th bypass control valve 123, the flow rate of water flowing from the auxiliary gas cooler 25 to the 7th bypass flow path 122 can be controlled, and the flow rate of water flowing through the water pipe 40 is large. In this case, the pressure loss in the water flow path of the gas cooler unit can be reduced by bypassing the intercooler 23 and flowing water through the main gas cooler 24. Further, since the pressure loss in the water flow path can be reduced, the operation can be performed in a state where the input of the water supply pump 43 is small, the required hot water supply temperature changes, and the flow rate of water flowing through the gas cooler unit is large. It is possible to operate with high efficiency even when the setting is changed to.

The present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.

As described above, the freezing device according to the present invention can suppress the amount of reducing the flow rate of water even when the hot water supply temperature is raised, and the intercooler and the gas cooler can sufficiently dissipate the refrigerant. The refrigerant temperature on the outlet side of the device can also be lowered, and it can be suitably used for a freezing device capable of maintaining the freezing capacity of the freezing device. Further, the refrigerating apparatus according to the present invention exchanges heat between the refrigerant and water, and is suitably used for hot water supply using hot water generated by the heat exchange, hot water supply used for hot water heating, and hot water heating equipment. It is possible.

1 Refrigerator 10 Compressor unit 11 Compressor 12 Low-stage suction port 13 Low-stage suction port 14 High-stage suction port 15 High-stage discharge port 16 Intermediate cooler 17 Decompression electric valve 20 Gas cooler unit 23 Intercooler 23a One of the intercoolers Inlet side of the flow path 23b Outlet side of one flow path of the intercooler 23c Inlet side of the other flow path of the intercooler 23d Outlet side of the other flow path of the intercooler 24 Main gas cooler 24a Of one flow path of the main gas cooler Inlet side 24b Outlet side of one flow path of main gas cooler 24c Inlet side of the other flow path of main gas cooler 24d Outlet side of the other flow path of main gas cooler 25 Auxiliary gas cooler 25a Inlet side of one flow path of auxiliary gas cooler 25b Outlet side of one flow path of auxiliary gas cooler 25c Inlet side of the other flow path of auxiliary gas cooler 25d Outlet side of other flow path of auxiliary gas cooler 26 Oil separator 26a Oil pipe 27 Oil service valve 28 Oil adjustment electric valve 30 Low pressure refrigerant Piping 31 Intermediate pressure discharge piping 32 Intermediate pressure suction piping 33 High pressure discharge piping 34 Refrigerator piping 40 Water piping 41 Water supply check valve 42 Suction tank 43 Water supply pump 44 Main gas cooler Pipe pass flow path check valve 45 First bypass flow path Check valve 46 Check valve for 2nd bypass flow path 50 Split heat exchanger 50a Inlet side of one flow path of split heat exchanger 50b Outlet side of one flow path of split heat exchanger 50c Split heat exchanger 50d Outlet side of the other flow path of the split heat exchanger 51 Branch pipe 52 Liquid return electric valve 53 Gas return electric valve 54 Coolant return pipe 60 Branch part 61 Confluence part 62 External heat dissipation device 63 Mainstream Road 64 Main gas cooler bypass flow path 65 Flow adjustment mechanism 66 Refrigerator inlet temperature sensor 67 Refrigerator outlet temperature sensor 68 Discharge temperature sensor 69 Split heat exchanger outlet temperature sensor 70 Second branch 71 Second confluence 72 Hot water supply flow Road 73 1st bypass flow path 74 1st bypass control valve 75 Hot water supply control valve 80 3rd branch part 81 3rd merging part 82 2nd bypass flow path 83 2nd bypass control valve 84 4th branch part 85 4th 86 4th bypass flow path 87 4th bypass control valve 88 Check valve for 4th bypass flow path 90 Hot water supply temperature sensor 91 Control unit 92 Cooling water temperature sensor 93 Coolant outlet temperature sensor 94 Cooling water flow meter 95 Hot water supply flow meter 100 5th branch 101 5th confluence 102 5th bypass flow path 103 5th bypass control valve 104 Check valve for 5th bypass flow path 110 6th branch part 111 6th merging part 112 6th bypass flow path 113 6th bypass control valve 114 Check valve for 6th bypass flow path 115 Intercooler outlet check valve Valve 120 7th branch 121 7th confluence 122 7th bypass flow path 123 7th bypass control valve 124 Check valve for 7th bypass flow path 125 Main gas cooler outlet check valve

Claims (12)

A refrigeration system in which the refrigerant is cooled by heat exchange between the refrigerant and water, and the water flow path for cooling the refrigerant is connected by a water pipe.
A compressor that compresses the refrigerant sucked from the low-stage suction port through the inlet of the freezing device and discharges it from the low-stage discharge port, and again compresses the refrigerant sucked from the high-stage suction port and discharges it from the high-stage discharge port. When,
An intercooler that cools the refrigerant discharged from the low-stage discharge port, and
A main gas cooler that cools the refrigerant discharged from the high-stage discharge port,
An auxiliary gas cooler for cooling the refrigerant after passing through the main gas cooler is provided.
A refrigerating apparatus characterized in that the water pipes are sequentially connected in series in the order of the auxiliary gas cooler, the intercooler, and the main gas cooler. A branch portion is provided in the middle of the water pipe between the intercooler and the main gas cooler, and a confluence portion is provided in the water pipe on the upstream side of the auxiliary gas cooler.
A main flow path that branches at the branch and supplies water to the main gas cooler,
A main gas cooler bypass flow path that branches at the branch portion, allows water that has flowed by bypassing the main gas cooler to pass through an external heat radiating device, and then merges with the confluence portion.
The refrigerating apparatus according to claim 1, further comprising a flow rate adjusting mechanism for adjusting the flow rate of water flowing through the main flow path and the main gas cooler bypass flow path. A second branch is provided in the water pipe on the downstream side of the main gas cooler.
A second confluence is provided in the main gas cooler bypass flow path on the upstream side of the external heat dissipation device of the main gas cooler bypass flow path.
A first bypass flow path for flowing water that branches at the second branch and joins the second confluence.
A hot water supply flow path that branches at the second branch and allows hot water to flow.
A first bypass control valve that controls the flow rate of water flowing through the first bypass flow path on the first bypass flow path,
The refrigerating apparatus according to claim 2, further comprising a hot water supply control valve for controlling the flow rate of water flowing through the hot water supply flow path on the hot water supply flow path. A third branch is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a third confluence is provided on the upstream side of the main gas cooler bypass flow path from the external heat radiating device.
A second bypass flow path for flowing water that branches at the third branch and joins the third confluence.
The refrigerating apparatus according to claim 2, further comprising a second bypass control valve for controlling the flow rate of water flowing through the second bypass flow path on the second bypass flow path. A fourth branch is provided in the water pipe between the auxiliary gas cooler and the intercooler.
A fourth confluence is provided in the water pipe on the upstream side of the auxiliary gas cooler.
A fourth bypass flow path that branches at the fourth branching portion, allows the branched water to pass through an external heat radiating device, and then merges with the fourth merging portion.
The refrigerating apparatus according to claim 1, further comprising a fourth bypass control valve for controlling the flow rate of water flowing through the fourth bypass flow path on the fourth bypass flow path. A fifth branch is provided on the downstream side of the main gas cooler, and a fifth confluence is provided on the fourth bypass flow path on the upstream side of the external heat radiating device of the fourth bypass flow path.
A fifth bypass flow path for flowing water that branches at the fifth branch and joins the fifth junction.
The refrigerating apparatus according to claim 5, further comprising a fifth bypass control valve for controlling the flow rate of water flowing through the fifth bypass flow path on the fifth bypass flow path. A sixth branch is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a sixth confluence is provided in the water pipe between the intercooler and the main gas cooler.
A sixth bypass flow path for flowing water that branches at the sixth branch and joins the sixth junction.
The invention according to any one of claims 1 to 6, wherein the sixth bypass control valve for controlling the flow rate of water flowing through the sixth bypass flow path is provided on the sixth bypass flow path. Refrigeration equipment. A seventh branch is provided in the water pipe between the auxiliary gas cooler and the intercooler, and a seventh confluence is provided in the water pipe on the downstream side of the main gas cooler.
A seventh bypass flow path that branches at the seventh branch and allows water to flow into the seventh confluence.
The invention according to any one of claims 1 to 5, wherein the seventh bypass control valve for controlling the flow rate of water flowing through the seventh bypass flow path is provided on the seventh bypass flow path. Refrigeration equipment. A hot water supply temperature sensor that detects the temperature of hot water for hot water supply on the water pipe on the downstream side of the main gas cooler, and the flow rate adjusting mechanism or the first bypass control based on the hot water supply temperature detected by the hot water supply temperature sensor. A valve or a control unit that controls at least one of the fourth bypass control valve or the fifth bypass control valve is provided.
Any one of claims 2 to 8, wherein the control unit controls the flow rate of water flowing through the main gas cooler based on the temperature detected by the hot water supply temperature sensor and the hot water supply temperature. Refrigeration equipment described in. The freezing device according to any one of claims 1 to 9, wherein a water supply pump is provided in the water flow path between the auxiliary gas cooler and the intercooler. The refrigerating apparatus according to any one of claims 1 to 9, wherein a water supply pump is provided in the water flow path between the intercooler and the main gas cooler. The refrigerating apparatus according to any one of claims 1 to 11, wherein a carbon dioxide refrigerant is used as the refrigerant.

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