JP7492464B2 - Cold heat recovery system and ship or floating structure equipped with cold heat recovery system - Google Patents

Description

The present disclosure relates to a cold energy recovery system for recovering cold energy from liquefied gas, and to a ship or floating body equipped with the cold energy recovery system.

Liquefied gas (e.g., liquefied natural gas) is liquefied for the purpose of transportation or storage, and when it is supplied to a destination such as a city gas or thermal power plant, it is heated and vaporized using a heat medium such as seawater. When vaporizing liquefied gas, the cold energy of the liquefied gas is sometimes recovered rather than being dumped into seawater (e.g., Patent Documents 1 and 2).

Patent Document 1 discloses a cold energy power generation cycle that recovers the cold energy of liquefied gas as electricity. Known examples of this cold energy power generation cycle include the secondary medium Rankine cycle (see Patent Document 1). The secondary medium Rankine cycle system involves heating and evaporating a secondary medium circulating in a closed loop using seawater as a heat source in an evaporator, introducing this steam into a cold energy power generation turbine to generate power, and then cooling and condensing it using liquefied natural gas.

Patent Document 2 discloses an air conditioning system for ships that uses cold energy recovered from liquefied gas as a cooling source to cool a refrigerant circulating in a refrigeration cycle, and uses the refrigerant in an air conditioner (the evaporator of the refrigeration cycle) to cool the air inside the ship.

Japanese Utility Model Application Publication No. 61-59803 JP 2015-155787 A

Meanwhile, in bulk carriers that transport bulk cargo such as unpackaged grains and ores stored in the cargo holds of the ship's hold, it is known that condensation in the cargo holds can cause damage to the cargo and the cargo holds. In the past, a method of preventing condensation in the cargo holds was to periodically open the top hatch of the cargo hold while the cargo ship was sailing in order to ventilate the cargo hold. This method entails the risk of seawater flowing in from the outside when the top hatch of the cargo hold is opened, and personnel are required to ventilate the cargo hold.

It is also possible to install a dehumidifier for ships on a cargo ship and use this dehumidifier to dehumidify the cargo hold. In this case, a lot of electricity is required to operate the dehumidifier, and the amount of power generated needs to be increased accordingly, which may result in a decrease in the fuel efficiency of the cargo ship.

In view of the above circumstances, an objective of at least one embodiment of the present disclosure is to provide a cold heat recovery system that can reduce the power consumption of a ship or float while suppressing condensation in the interior space of the ship or float, and a ship or float equipped with the cold heat recovery system.

A cold heat recovery system according to an embodiment of the present disclosure includes:
A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature below a dew point by exchanging heat between the liquefied gas or its vaporized gas and the air.

A ship or floating body according to one embodiment of the present disclosure is equipped with the above-mentioned cold heat recovery system.

According to at least one embodiment of the present disclosure, a cold heat recovery system that can reduce the power consumption of a ship or float while suppressing condensation in the interior space of the ship or float, and a ship or float equipped with the cold heat recovery system are provided.

1 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure; 1 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure; 1 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure; 1 is a schematic diagram illustrating a configuration of a dehumidifier according to an embodiment of the present disclosure. 1 is an explanatory diagram for explaining a change in air state caused by a dehumidifier according to an embodiment of the present disclosure. FIG. 1 is a schematic diagram illustrating a configuration of a dehumidifier according to an embodiment of the present disclosure. 1 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure; 1 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure; FIG. 9 is a schematic diagram illustrating the configuration of a dehumidifier and a temperature adjustment device in the embodiment shown in FIG. 8 .

Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of components described as the embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the present disclosure.
For example, expressions expressing relative or absolute configuration, such as "in a certain direction,""along a certain direction,""parallel,""orthogonal,""center,""concentric," or "coaxial," not only express such a configuration strictly, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained.
For example, expressions indicating that things are in an equal state, such as "identical,""equal," and "homogeneous," not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained.
For example, expressions describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained.
On the other hand, the expressions "comprise", "include", or "have" a certain element are not exclusive expressions excluding the presence of other elements.
In addition, the same components are denoted by the same reference numerals and the description thereof may be omitted.

(Ships, floating bodies)
Each of Figures 1 to 3 is a schematic diagram showing the configuration of a water floating structure equipped with a cold heat recovery system according to one embodiment of the present disclosure.
As shown in Figs. 1 to 3, a cold energy recovery system 1 according to some embodiments is installed on a floating structure 10 (ship 10A or float 10B) having a liquefied gas storage device (e.g., a liquefied gas tank) 11 configured to store liquefied gas. The floating structure 10 (ship 10A, float 10B) is a structure that can float on water. The ship 10A has a propulsion device (not shown) configured to drive a propeller or other thruster, and is a structure configured to be self-propelled by driving the propulsion device. The float 10B is a structure that cannot be self-propelled, unlike the ship 10A, and does not have a propulsion device for self-propulsion.

(Cold heat recovery system)
1 to 3, the cold heat recovery system 1 includes a first heat exchanger (liquefied gas vaporizer) 12 configured to vaporize a liquefied gas, a liquefied gas supply line 2 for supplying the liquefied gas from a liquefied gas storage device 11 to the heat exchanger 12, a vaporized gas supply line 3 for supplying the vaporized gas generated by vaporizing the liquefied gas in the heat exchanger 12, a cold heat recovery cycle 4 configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the heat exchanger 12, and an air conditioning cycle 5 configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle 4. The vaporized gas is sent to a supply destination 13 through the vaporized gas supply line 3.

(Liquefied gas supply line, vaporized gas supply line)
The liquefied gas supply line 2 includes a liquefied gas pipe 20 connected to the liquefied gas storage device 11 on one side and to the heat exchanger 12 on the other side, and a gas pump 21 provided on the liquefied gas supply line 2 (liquefied gas pipe 20). The vaporized gas supply line 3 includes a vaporized gas pipe 30 connected to the heat exchanger 12 on one side and to the vaporized gas supply destination 13 on the other side. Each of the liquefied gas pipe 20 and the vaporized gas pipe 30 is configured to be able to circulate liquefied gas and vaporized gas obtained by vaporizing liquefied gas. The gas pump 21 is configured to send a fluid (liquefied gas) to its downstream side. The liquefied gas stored in the liquefied gas storage device 11 is extracted by the gas pump 21 to the liquefied gas supply line 2 and sent to the heat exchanger 12 through the liquefied gas supply line 2. The vaporized gas generated by vaporizing the liquefied gas in the heat exchanger 12 is sent to the supply destination 13 through the vaporized gas supply line 3 by the gas pump 21. The supply destination 13 of the vaporized gas may be a facility provided outside the floating structure on water 10 (e.g., a power generation facility or a storage facility on land), or may be a facility mounted on the floating structure on water 10.

(Heat exchange between liquefied gas and cold heat transfer medium)
The heat exchanger 12 is configured to perform heat exchange between the liquefied gas sent from the liquefied gas supply line 2 and the cold heat medium flowing in the cold heat recovery cycle 4. The heat exchanger 12 includes a one-side heat exchange section 121 through which the liquefied gas sent from the liquefied gas supply line 2 flows, and a other-side heat exchange section 122 through which the cold heat medium provided in the cold heat recovery cycle 4 flows. Heat exchange is performed between the one-side heat exchange section 121 and the other-side heat exchange section 122, and the cold energy of the liquefied gas flowing in the one-side heat exchange section 121 is recovered by the cold heat medium flowing in the other-side heat exchange section 122. As a result, the liquefied gas flowing in the one-side heat exchange section 121 is heated, and a vaporized gas is generated. In addition, the cold heat medium flowing in the other-side heat exchange section 122 is cooled.

(Heat exchange between vaporized gas and external water)
As shown in Figs. 1 to 3, the cold heat recovery system 1 may include a vaporized gas heater 31 configured to perform heat exchange between the vaporized gas flowing through the vaporized gas supply line 3 and external water introduced from outside the cold heat recovery system 1. The vaporized gas heater 31 includes a one-side heat exchanger 311 provided in the vaporized gas supply line 3 (vaporized gas pipe 30) through which the vaporized gas flows, and a other-side heat exchanger 312 through which the external water flows. In the illustrated embodiment, the other-side heat exchanger 312 is composed of a pipe through which the external water flows, provided in the external water supply line 17 connecting the supply source 15 of the external water and the discharge destination 16 of the external water. Heat exchange is performed between the one-side heat exchanger 311 and the other-side heat exchanger 312, and the vaporized gas flowing through the one-side heat exchanger 311 is heated. By heating the vaporized gas with the vaporized gas heater 31, the temperature of the vaporized gas can be increased to a predetermined temperature required at the supply destination 13.

The external water may be water that can heat the heat exchange target as a heat medium in a heat exchanger (e.g., vaporized gas heater 31) (water that is hotter than the heat exchange target), and may be water at room temperature. The external water is preferably water that is easily available on the ship 10A or float 10B (e.g., overboard water such as seawater or engine cooling water that cools the engine of the ship 10A). In one embodiment, the external water supply source 15 is a water intake provided on the ship 10A or float 10B for introducing overboard water, and the external water discharge destination 16 is a discharge outlet provided on the ship 10A or float 10B for discharging water overboard.

The following description will be given taking liquefied natural gas (LNG) as an example of the liquefied gas supplied from the liquefied gas storage device 11 and propane as an example of the cold heat medium flowing through the cold heat recovery cycle 4, but the present disclosure can also be applied when a liquefied gas other than liquefied natural gas (liquefied petroleum gas, liquefied hydrogen, etc.) is used as the liquefied gas supplied from the liquefied gas storage device 11, and can also be applied when a heat medium other than propane (for example, an organic medium) is used as the cold heat medium flowing through the cold heat recovery cycle 4. The cold heat medium has a lower boiling point and freezing point than water.

(Heat exchange between the cold heat medium and the air conditioning heat medium)
In the embodiment shown in FIG. 1 to FIG. 3, the cold heat recovery system 1 includes a heat exchanger (cold heat evaporator, air conditioning condenser) 14. The heat exchanger 14 is configured to perform heat exchange between a cold heat medium flowing through the cold heat recovery cycle 4 and an air conditioning heat medium flowing through the air conditioning cycle 5. The heat exchanger 14 includes a cold heat side heat exchange section 141 provided in the cold heat recovery cycle 4 through which a cold heat medium flows, and an air conditioning side heat exchange section 142 provided in the air conditioning cycle 5 through which an air conditioning heat medium flows. Heat exchange is performed between the cold heat side heat exchange section 141 and the air conditioning side heat exchange section 142, and the cold energy of the cold heat medium flowing through the cold heat side heat exchange section 141 is recovered to the air conditioning heat medium flowing through the air conditioning side heat exchange section 142. As a result, the cold heat medium flowing through the cold heat side heat exchange section 141 is heated, and the air conditioning heat medium flowing through the air conditioning side heat exchange section 142 is cooled.

(Cold heat recovery cycle)
The cold heat recovery cycle 4 is configured to circulate the cold heat medium under an organic Rankine cycle. The cold heat recovery cycle 4 includes a cold heat pipe 40 for circulating the cold heat medium that has been heat exchanged with the liquefied gas, a cold heat turbine 41 configured to be driven by the cold heat energy of the cold heat medium, a cold heat pump 42 configured to compress the cold heat medium, a cold heat condenser 43 configured to cool the cold heat medium expanded by the cold heat turbine 41 by the cold heat energy of the liquefied gas, and a cold heat evaporator 44 configured to heat the cold heat medium compressed by the cold heat pump 42 by the thermal energy transferred from the air-conditioning heat medium.

The above-mentioned heat exchanger 12 functions as a cold condenser 43 in the cold heat recovery cycle 4. The cold heat recovery cycle 4 and the air conditioning cycle 5 share the heat exchanger 14. The above-mentioned heat exchanger 14 functions as a cold heat evaporator 44 in the cold heat recovery cycle 4.

The cold energy turbine 41 is located downstream of the cold energy evaporator 44 (cold energy pipe 40) (cold energy side heat exchange section 141 of heat exchanger 14) and upstream of the cold energy condenser 43 (other side heat exchange section 122 of heat exchanger 12) in the cold energy recovery cycle 4 (cold energy pipe 40). The cold energy pump 42 is located downstream of the cold energy condenser 43 and upstream of the cold energy evaporator 44 in the cold energy recovery cycle 4 (cold energy pipe 40). Here, "upstream" means the upstream side in the flow direction of the heat medium (cold energy heat medium), and "downstream" means the downstream side in the flow direction of the heat medium (cold energy heat medium).

The cold heat pump 42 is configured to send the cold heat medium downstream. By driving the cold heat pump 42, the cold heat medium circulates through the cold heat recovery cycle 4 (cold heat pipe 40). The cold heat medium cooled in the cold heat condenser 43 is compressed by the cold heat pump 42 and then guided to the cold heat evaporator 44. The cold heat medium heated to an air conditioning heat medium in the cold heat evaporator 44 is introduced into the cold heat turbine 41. The cold heat recovery cycle 4 may be configured to liquefy the cold heat medium by cooling in the cold heat condenser 43 and vaporize the cold heat medium by heating in the cold heat evaporator 44.

(Cold Heat Turbine)
The cold heat turbine 41 includes a rotating shaft 411, turbine blades 412 attached to the rotating shaft 411, and a casing 413 that rotatably houses the turbine blades 412. The cold heat turbine 41 is configured to rotate the turbine blades 412 by energy of a cold heat medium introduced into the casing 413. The cold heat medium that has passed through the turbine blades 412 is discharged to the outside of the casing 413 and then led to the cold heat condenser 43.

The cold heat recovery cycle 4 is configured to recover the rotational force of the turbine blades 412 as power. In the illustrated embodiment, the cold heat recovery cycle 4 further includes a cold heat generator 45 configured to generate power by driving the cold heat turbine 41. The cold heat generator 45 is mechanically connected to the rotating shaft 411 and configured to convert the rotational force of the turbine blades 412 into electric power. In some other embodiments, the cold heat recovery cycle 4 may recover the rotational force of the turbine blades 412 as power directly using a power transmission device (e.g., a coupling, a belt, a pulley, etc.) rather than converting it into electric power. The cold heat recovery cycle 4 may include a bypass flow path 18 that bypasses the cold heat turbine 41.

(Air conditioning cycle)
The air conditioning cycle 5 is configured to circulate the air conditioning heat medium under a refrigeration cycle having a condensation stroke (air conditioning condenser 51), an expansion stroke (air conditioning pressure reducer 52), an evaporation stroke (air conditioning evaporator 53), and a compression stroke (air conditioning compressor 54). The air conditioning cycle 5 includes an air conditioning pipe 50 for circulating the air conditioning heat medium that has been heat exchanged with the cold heat medium, the air conditioning condenser 51, the air conditioning pressure reducer 52, the air conditioning evaporator 53, and the air conditioning compressor 54. The above-mentioned heat exchanger 14 functions as the air conditioning condenser 51 in the air conditioning cycle 5.

The following description will be given using propane as a specific example of the air-conditioning heat medium that flows through the air-conditioning cycle 5, but the present disclosure is also applicable to cases where a heat medium other than propane (e.g., an organic medium) is used as the air-conditioning heat medium that flows through the air-conditioning cycle 5. Note that it is preferable for the air-conditioning heat medium to have a boiling point or freezing point lower than that of water.

The air conditioning compressor 54 is located downstream of the air conditioning evaporator 53 in the air conditioning cycle 5 (air conditioning pipe 50) and upstream of the air conditioning condenser 51 (air conditioning side heat exchange section 142 of heat exchanger 14). The air conditioning pressure reducer 52 is located downstream of the air conditioning condenser 51 in the air conditioning cycle 5 (air conditioning pipe 50) and upstream of the air conditioning evaporator 53. Here, "upstream side" means the upstream side in the flow direction of the air conditioning heat medium flowing through the air conditioning pipe 50, and "downstream side" means the downstream side in the flow direction of the air conditioning heat medium flowing through the air conditioning pipe 50.

The air conditioning compressor 54 includes a rotating shaft 541, an impeller 542 attached to the rotating shaft 541, a casing 543 that rotatably houses the impeller 542, and an electric motor 544 mechanically connected to the rotating shaft 541. The electric motor 544 is configured to convert electric power into rotational force. The impeller 542 compresses the air conditioning heat medium by rotating due to the rotational force transmitted from the electric motor 544.

The air conditioning heat medium circulating through the air conditioning cycle 5 (air conditioning pipe 50) passes through the air conditioning condenser 51, the air conditioning pressure reducer 52, the air conditioning evaporator 53, and the air conditioning compressor 54 in this order. The air conditioning condenser 51 is configured to cool the air conditioning heat medium compressed by the air conditioning compressor 54. The air conditioning pressure reducer 52 is configured to reduce the pressure of the air conditioning heat medium cooled by the air conditioning condenser 51. In the illustrated embodiment, the air conditioning pressure reducer 52 is an expansion valve, and the air conditioning heat medium is reduced in pressure and expanded by the expansion valve (air conditioning pressure reducer 52). The air conditioning heat medium cooled by the air conditioning condenser 51 is depressurized by the air conditioning pressure reducer 52 and then led to the air conditioning evaporator 53. The air conditioning evaporator 53 is configured to heat the air conditioning heat medium depressurized by the air conditioning pressure reducer 52. The air conditioning compressor 54 is configured to compress the air conditioning heat medium heated by the air conditioning evaporator 53. The air conditioning heat medium heated by the air conditioning evaporator 53 is compressed by the air conditioning compressor 54. The air conditioning cycle 5 may be configured to liquefy the air conditioning heat medium by cooling in the air conditioning condenser 51, and to vaporize the air conditioning heat medium by heating in the air conditioning evaporator 53.

(Dehumidifier)
Fig. 4 is a schematic diagram showing the configuration of a dehumidifier according to an embodiment of the present disclosure. As shown in Fig. 4, the cold heat recovery system 1 includes a dehumidifier 6 configured to dehumidify air taken in from an interior space 100 of a floating structure 10 (ship 10A, floating body 10B). In one embodiment, the interior space 100 is an interior space of a cargo hold for storing cargo.

In the embodiment shown in FIG. 4, the dehumidifier 6 includes an air duct 60 for sending air taken in from the shipboard space 100, a cooler 61, a heater 62, a precooler 63, and a blower 64. An air intake 101 and an air outlet 102 are formed on the wall surface forming the shipboard space 100 of the water floating structure 10 (ship 10A, float 10B). One side of the air duct 60 is connected to the air intake 101, and the other side is connected to the air outlet 102. The blower 64 includes a rotor blade 641 provided in the air duct 60, and an electric motor 642 configured to supply the rotor blade 641 with a driving force for rotating the rotor blade 641. By driving the blower 64, air is sucked from the shipboard space 100 into the air duct 60 through the air intake 101. The air sucked into the air duct 60 is sent by the blower 64 through the air duct 60 toward the downstream side (the side where the air outlet 102 is located).

The heater 62 is disposed downstream of the cooler 61 in the air duct 60. The precooler 63 is disposed upstream of the cooler 61 in the air duct 60. As shown in FIG. 4, the blower 64 may be disposed upstream of the precooler 63 and the cooler 61 in the air duct 60. Here, "upstream side" means the upstream side of the flow direction of the air flowing through the air duct 60, and "downstream side" means the downstream side of the flow direction of the air flowing through the air duct 60. The air sucked into the air duct 60 passes through the precooler 63, the cooler 61, and the heater 62 in this order, and is then returned to the interior space 100 through the air outlet 102.

Figure 5 is an explanatory diagram for explaining the change in air state caused by the dehumidifier in one embodiment of the present disclosure. In Figure 5, the state of the air taken into the dehumidifier 6 (air duct 60) from the interior space 100 is shown by a psychrometric chart. P1 in Figure 5 indicates the state value of the air taken into the air duct 60 from the interior space 100 (air before being cooled in the precooler 63), and P2 indicates the state value of the air after being cooled by the precooler 63. P3 indicates the state value of the air after being cooled by the cooler 61, and P4 indicates the state value of the air after being heated by the heater 62. Note that Figure 5 also shows an example of the dry bulb temperature and relative humidity for each of the state values P1 to P4.

The air sucked into the air duct 60 is cooled to near the dew point in the precooler 63. In state value P2, the dry-bulb temperature is lower than in state value P1, and the relative humidity is higher. The air cooled by the precooler 63 is cooled to a temperature below the dew point by the cooler 61, and the state changes from state value P2 to state value P3 along the saturation line. At this time, the amount of saturated water vapor in the air decreases, and the saturated moisture precipitates, so the air is dehumidified. In state value P3, the dry-bulb temperature is lower than in state value P2. The air cooled by the cooler 61 is heated by the heater 62, and the temperature is raised while maintaining the amount of water vapor contained in the air. In state value P4, the dry-bulb temperature is higher than in state value P3, and the relative humidity is lower. The air heated by the heater 62 is returned to the interior space 100 through the air outlet 102, and the temperature and humidity of the air in the interior space 100 are adjusted.

Figure 6 is a schematic diagram showing the configuration of a dehumidifier in one embodiment of the present disclosure. As shown in Figure 4, the dehumidifier 6 may cool the air taken in from the interior space 100 in two stages using a precooler 63 and a cooler 61, but as shown in Figure 6, the air taken in from the interior space 100 may be cooled only by the cooler 61. In this case, the state of the air changes from state value P1 to state value P2 and then to state value P3 due to cooling in the cooler 61.

As shown in Figs. 1 to 3, the cold heat recovery system 1 according to some embodiments includes the above-mentioned heat exchanger 12, the above-mentioned liquefied gas supply line 2, the above-mentioned cold heat recovery cycle 4, the above-mentioned air conditioning cycle 5, and the above-mentioned dehumidification device 6 including the cooler 61. The cooler 61 is configured to exchange heat between the liquefied gas or its vaporized gas and air taken in from the interior space 100, thereby cooling the air to a temperature below the dew point.

As shown in Figs. 1 to 4, the cooler 61 includes an air-side heat exchanger 611 through which air taken in from the inboard space 100 flows, and a refrigerant-side heat exchanger 612 through which a refrigerant for cooling the air flows. In the illustrated embodiment, the air-side heat exchanger 611 of the cooler 61 is composed of a duct through which air flows, which is provided in the air duct 60. Heat exchange is performed between the air-side heat exchanger 611 and the refrigerant-side heat exchanger 612, so that the air flowing through the air-side heat exchanger 611 is cooled to a temperature below the dew point, and the refrigerant flowing through the refrigerant-side heat exchanger 612 is heated. The refrigerant flowing through the refrigerant-side heat exchanger 612 may be the above-mentioned liquefied gas or vaporized gas, or may be a heat medium (for example, a cold medium or an intermediate heat medium described later) that has recovered cold energy from the liquefied gas or vaporized gas.

According to the above configuration, the dehumidifier 6 can reduce the amount of moisture contained in the air by cooling the air taken in from the onboard space 100 to a temperature below the dew point using the cooler 61, thereby allowing saturated moisture to precipitate from the air. The cooler 61 can reduce the amount of moisture contained in the air in the onboard space 100, thereby suppressing the occurrence of condensation in the onboard space 100. By suppressing the occurrence of condensation in the onboard space 100, damage caused by condensation to the cargo loaded in the onboard space 100 and the walls that constitute the onboard space 100 can be suppressed. The cooler 61 cools the air using the cold energy of the liquefied gas or its vaporized gas, rather than using onboard electricity, so that the consumption of onboard electricity can be suppressed. By suppressing the consumption of onboard electricity, the deterioration of the fuel efficiency of the cold energy recovery system 1 can be suppressed. In addition, the cooler 61 can raise the temperature of the heat exchange target by recovering the cold energy of the liquefied gas or its vaporized gas from the target of heat exchange with the air. In this case, the energy consumption required to raise the temperature of the heat exchange object can be reduced, improving the efficiency of the cold heat recovery system 1.

In some embodiments, as shown in FIG. 1, the cooler 61 (61A) of the dehumidifier 6 is configured to perform heat exchange between the vaporized gas flowing through the vaporized gas supply line 3 and the air taken in from the ship interior space 100. In the illustrated embodiment, the refrigerant side heat exchange section 612 (612A) of the cooler 61 (61A) is composed of a pipe through which the vaporized gas flows, which is provided upstream of the vaporized gas heater 31 in the vaporized gas supply line 3 (vaporized gas pipe 30). Heat exchange is performed between the air side heat exchange section 611 and the refrigerant side heat exchange section 612A, and the air flowing through the air side heat exchange section 611 is cooled to a temperature below the dew point, and the vaporized gas flowing through the refrigerant side heat exchange section 612A is heated.

According to the above configuration, the cooler 61 (61A) can cool the air taken in from the onboard space 100 using the cold energy of the vaporized gas flowing through the vaporized gas supply line 3. This can reduce the consumption of onboard electricity. The cooler 61 (61A) can also heat the vaporized gas by recovering cold energy from the vaporized gas. When the cold energy recovery system 1 is configured to heat the vaporized gas to the required temperature of the supply destination 13 using the vaporized gas heater 31, the amount of heating (amount of heat exchange) in the vaporized gas heater 31 can be reduced, thereby reducing the consumption of onboard electricity used to drive the vaporized gas heater 31.

In some embodiments, as shown in FIG. 2, the cooler 61 (61B) of the dehumidifier 6 is configured to perform heat exchange between the liquefied gas flowing through the liquefied gas supply line 2 and the air taken in from the ship interior space 100. In the illustrated embodiment, the refrigerant side heat exchanger 612 (612B) of the cooler 61 (61B) is composed of a pipeline through which the liquefied gas flows, which is provided downstream of the gas pump 21 in the liquefied gas supply line 2 (liquefied gas pipeline 20). Heat exchange is performed between the air side heat exchanger 611 and the refrigerant side heat exchanger 612B, so that the air flowing through the air side heat exchanger 611 is cooled to a temperature below the dew point, and the liquefied gas flowing through the refrigerant side heat exchanger 612B is heated.

According to the above configuration, the cooler 61 (61B) can cool the air taken in from the onboard space 100 by using the cold energy of the liquefied gas flowing through the liquefied gas supply line 2. This can reduce the consumption of onboard electricity. In addition, the cooler 61 (61B) can heat the liquefied gas by recovering cold energy from the liquefied gas. When the cold energy recovery system 1 is configured to heat the vaporized gas to the required temperature of the supply destination 13 by the vaporized gas heater 31, the amount of heating (amount of heat exchange) in the vaporized gas heater 31 can be reduced, so that the consumption of onboard electricity used to drive the vaporized gas heater 31 can be reduced.

In some embodiments, as shown in FIG. 3, the cooler 61 (61C) of the dehumidifier 6 is configured to perform heat exchange between the cold heat medium flowing between the cold heat turbine 41 and the first heat exchanger 12 in the cold heat recovery cycle 4 and the air taken in from the ship interior space 100. In the illustrated embodiment, the refrigerant side heat exchange section 612 (612C) of the cooler 61 (61C) is composed of a pipe through which the cold heat medium flows, which is provided downstream of the cold heat turbine 41 in the cold heat recovery cycle 4 (cold heat pipe 40) and upstream of the other side heat exchange section 122 of the first heat exchanger 12. Heat exchange is performed between the air side heat exchange section 611 and the refrigerant side heat exchange section 612C, and the air flowing through the air side heat exchange section 611 is cooled to a temperature below the dew point, and the liquefied gas flowing through the refrigerant side heat exchange section 612C is heated.

According to the above configuration, the cooler 61 (61C) can cool the air taken in from the shipboard space 100 by the cold energy recovered from the liquefied gas of the cold heat medium. This can reduce the consumption of electricity on board. If the cooler 61 is provided in the liquefied gas supply line 2 or the vaporized gas supply line 3, it is necessary to take sufficient measures to prevent leakage and heat radiation of the liquefied gas or vaporized gas. In contrast, if the cooler 61 is provided in the cold heat recovery cycle 4, the reliability of the cold heat recovery system 1 can be ensured without taking the above-mentioned sufficient measures. In addition, the cooler 61 (61C) can heat the cold heat medium by recovering cold energy from the cold heat medium flowing between the cold heat turbine 41 and the first heat exchanger 12 in the cold heat recovery cycle 4. By heating the cold heat medium sent to the first heat exchanger 12, the liquefied gas can be effectively heated in the first heat exchanger 12. When the cold heat recovery system 1 is configured to heat the vaporized gas to the required temperature of the supply destination 13 using the vaporized gas heater 31, the amount of heating (amount of heat exchange) in the vaporized gas heater 31 can be reduced, thereby reducing the amount of onboard electricity consumed to drive the vaporized gas heater 31.

In some embodiments, the above-mentioned dehumidifier 6 includes the above-mentioned cooler 61 and the above-mentioned heater 62, as shown in Figs. 1 to 4. The heater 62 is configured to perform heat exchange between the air-conditioning heat medium compressed by the air-conditioning compressor 54 and introduced into the air-conditioning condenser 51, and the air cooled by the cooler 61, as shown in Figs. 1 to 3.

The heater 62 includes an air-side heat exchange section 621 through which the air cooled by the cooler 61 flows, and a heat medium-side heat exchange section 622 through which a heat medium for heating the air flows. In the illustrated embodiment, the air-side heat exchange section 621 of the heater 62 is a pipe through which air flows, provided downstream of the air-side heat exchange section 611 of the cooler 61 in the air pipe 60. The heat medium-side heat exchange section 622 of the heater 62 is a pipe through which an air-conditioning heat medium flows, provided downstream of the air-conditioning compressor 54 in the air-conditioning cycle 5 (air-conditioning pipe 50) and upstream of the air-conditioning condenser 51 (air-conditioning side heat exchange section 142 of the heat exchanger 14). Heat exchange is performed between the air-side heat exchange section 621 and the heat medium-side heat exchange section 622, and the air flowing through the air-side heat exchange section 621 is heated, and the air-conditioning heat medium flowing through the heat medium-side heat exchange section 622 is cooled.

According to the above configuration, the dehumidifier 6 removes moisture from the air using the cooler 61 and heats the air cooled by the cooler 61 using the heater 62, thereby making it possible to adjust the temperature and humidity of the air. Therefore, the dehumidifier 6 can adjust the onboard space 100 to an appropriate temperature and humidity. The heater 62 is not an electric heater driven by onboard electricity, but heats the air using the compression heat of the air-conditioning heat medium compressed by the air-conditioning compressor 54, thereby reducing onboard electricity consumption.

In some embodiments, the above-mentioned dehumidifier 6 includes the above-mentioned cooler 61 and the above-mentioned precooler 63, as shown in Figs. 1 to 4. As shown in Figs. 1 to 4, the precooler 63 is configured to exchange heat between the air taken in from the interior space 100 and the air-conditioning heat medium flowing between the air-conditioning pressure reducer 52 and the air-conditioning compressor 54 in the air-conditioning cycle 5, upstream of the cooler 61 in the air flow direction. The precooler 63 functions as the air-conditioning evaporator 53 in the air-conditioning cycle 5, and is configured to heat the air-conditioning heat medium decompressed by the air-conditioning pressure reducer 52.

The precooler 63 includes an air-side heat exchanger 631 through which air flows before being cooled by the cooler 61, and a refrigerant-side heat exchanger 632 through which a refrigerant for cooling the air flows. In the illustrated embodiment, the air-side heat exchanger 631 of the precooler 63 is a pipe through which air flows, which is provided upstream of the air-side heat exchanger 611 of the cooler 61 in the air pipe 60. The refrigerant-side heat exchanger 632 of the precooler 63 is a pipe through which an air-conditioning heat medium flows, which is provided downstream of the air-conditioning pressure reducer 52 and upstream of the air-conditioning compressor 54 in the air-conditioning cycle 5 (air-conditioning pipe 50). Heat exchange is performed between the air-side heat exchanger 631 and the refrigerant-side heat exchanger 632, so that the air flowing through the air-side heat exchanger 631 is cooled, and the air-conditioning heat medium flowing through the refrigerant-side heat exchanger 632 is heated.

According to the above configuration, the pre-cooler 63 can cool the air taken in from the onboard space 100 using the cold energy of the air-conditioning heat medium recovered from the cold heat medium. This can reduce onboard electricity consumption. In addition, when the object of heat exchange with the air in the cooler 61 is a liquefied gas or a cold heat medium, the air is cooled in two stages, the pre-cooler 63 and the cooler 61, so that the amount of cold energy recovered by the cooler 61 from the cold heat medium can be reduced, thereby suppressing a decrease in the efficiency of the cold heat recovery cycle 4.

In some embodiments, the above-mentioned cold heat recovery system 1 further includes a cold heat exchanger (third heat exchanger) 46 configured to perform heat exchange between external water introduced from outside the cold heat recovery system 1 and a cold heat medium, as shown in Figs. 1 to 3. The cold heat exchanger 46 includes a one-side heat exchange section 461 provided in the cold heat recovery cycle 4 (cold heat pipe 40) through which the cold heat medium flows, and a other-side heat exchange section 462 through which the external water flows.

In the illustrated embodiment, the one-side heat exchanger 461 is a pipe through which the cold heat medium flows, which is provided downstream of the cold heat pump 42 and upstream of the cold heat turbine 41 in the cold heat recovery cycle 4 (cold heat pipe 40). The other-side heat exchanger 462 is a pipe through which the external water flows, which is provided in the external water supply line 17A connecting the external water supply source 15A and the external water discharge destination 16A. Heat exchange is performed between the one-side heat exchanger 461 and the other-side heat exchanger 462, and the cold heat medium flowing through the one-side heat exchanger 461 is heated. The external water supply source 15A may be the same as the supply source 15, and the external water discharge destination 16A may be the same as the discharge destination 16. The external water supply line 17A may be configured to share a part with the external water supply line 17.

According to the above configuration, the cold heat exchanger (third heat exchanger) 46 can heat the cold heat medium with external water, so that the temperature of the cold heat medium can be easily adjusted. This allows for a rapid response to changes in the state of the cold heat medium flowing through the cold heat recovery cycle 4, so that the cold heat recovery cycle 4 can operate stably. In addition, the cold heat exchanger 46 can heat the cold heat medium with external water, so that the cold heat recovery cycle 4 can operate regardless of whether the air conditioning cycle 5 is operating. This improves the reliability of the cold heat recovery system 1.

(Middle Cycle)
In some of the embodiments described above, the cold heat recovery system 1 is configured to perform heat exchange between the cold heat medium and the air conditioning heat medium, but the cold heat medium and the air conditioning heat medium may be configured to perform heat exchange between them via a heat medium (intermediate heat medium) therebetween.

Fig. 7 is a schematic diagram showing the configuration of a floating structure on water equipped with a cold heat recovery system according to an embodiment of the present disclosure. Fig. 8 is a schematic diagram showing the configuration of a floating structure on water equipped with a cold heat recovery system according to an embodiment of the present disclosure. Fig. 9 is a schematic diagram showing the configuration of a dehumidifier and a temperature adjustment device in the embodiment shown in Fig. 8.
As shown in Figures 7 and 8, the cold heat recovery system 1 in some embodiments includes the above-mentioned heat exchanger (first heat exchanger) 12, the above-mentioned liquefied gas supply line 2, the above-mentioned cold heat recovery cycle 4, the above-mentioned air conditioning cycle 5, the above-mentioned dehumidifier 6, the intermediate cycle 7, and an intermediate heat exchanger (second heat exchanger) 71.

The following description will be given using glycol water as an example of an intermediate heat medium flowing through the intermediate cycle 7, but the present disclosure can also be applied to cases where a heat medium other than glycol water (for example, an organic medium such as propane) is used as the intermediate heat medium flowing through the intermediate cycle 7. Note that it is preferable for the intermediate heat medium to have a lower boiling point and freezing point than water. The intermediate heat medium may be the same type of heat medium as the cold heat medium flowing through the cold heat recovery cycle 4, or it may be a different type of heat medium.

The intermediate cycle 7 is configured to circulate an intermediate heat medium that is heat exchanged between the cold heat medium flowing through the cold heat recovery cycle 4 and the air conditioning heat medium flowing through the air conditioning cycle 5. The intermediate cycle 7 includes a pipe 70 for circulating the intermediate heat medium and a circulation pump 72 for the intermediate heat medium. The circulation pump 72 is configured to send the intermediate heat medium downstream. By driving the circulation pump 72, the intermediate heat medium circulates through the intermediate cycle 7 (pipe 70). The intermediate cycle 7 may include an intermediate heat medium storage device (e.g., a buffer tank) 73 configured to store the intermediate heat medium. In the illustrated embodiment, the intermediate heat medium storage device 73 is provided upstream of the circulation pump 72 in the intermediate cycle 7 (pipe 70).

(Heat exchange between the cold heat medium, the air conditioning heat medium and the intermediate heat medium)
As shown in Fig. 7 and Fig. 8, the cold heat recovery system 1 includes a heat exchanger (air conditioning condenser) 74 configured to perform heat exchange between the air conditioning heat medium flowing in the air conditioning cycle 5 and the intermediate heat medium flowing in the intermediate cycle 7, instead of the above-mentioned heat exchanger 14, and a heat exchanger (cold heat evaporator) 75 configured to perform heat exchange between the cold heat medium flowing in the cold heat recovery cycle 4 and the intermediate heat medium flowing in the intermediate cycle 7. The air conditioning cycle 5 and the intermediate cycle 7 share the heat exchanger 74. The heat exchanger 74 functions as the air conditioning condenser 51 in the air conditioning cycle 5. The cold heat recovery cycle 4 and the intermediate cycle 7 share the heat exchanger 75. The heat exchanger 75 functions as the cold heat evaporator 44 in the cold heat recovery cycle 4.

The heat exchanger (air conditioning condenser) 74 includes an air conditioning side heat exchanger 741 through which the air conditioning heat medium flows, which is provided downstream of the heat medium side heat exchanger 622 of the heater 62 and the air conditioning compressor 54 in the air conditioning cycle 5 (air conditioning pipe 50) and upstream of the air conditioning pressure reducer 52, and an intermediate side heat exchanger 742 through which the intermediate heat medium flows, which is provided downstream of the circulation pump 72 in the intermediate cycle 7 (pipe 70). Heat exchange is performed between the air conditioning side heat exchanger 741 and the intermediate side heat exchanger 742, and the air conditioning side heat medium flowing through the air conditioning side heat exchanger 741 is cooled and the intermediate heat medium flowing through the intermediate side heat exchanger 742 is heated.

The heat exchanger (cold heat evaporator) 75 includes a cold heat side heat exchanger 751 through which the cold heat medium flows, which is provided downstream of the cold heat pump 42 and upstream of the cold heat turbine 41 in the cold heat recovery cycle 4 (cold heat pipe 40), and an intermediate side heat exchanger 752 through which the intermediate heat medium flows, which is provided downstream of the intermediate side heat exchanger 742 of the heat exchanger 74 in the intermediate cycle 7 (pipe 70). The intermediate heat medium heated in the intermediate side heat exchanger 742 is sent to the intermediate side heat exchanger 752. Heat exchange is performed between the cold side heat exchanger 751 and the intermediate side heat exchanger 752, and the cold heat medium flowing through the cold side heat exchanger 751 is heated, and the intermediate heat medium flowing through the intermediate side heat exchanger 752 is cooled.

(Heat exchange between intermediate heat medium and external water)
The intermediate heat exchanger (second heat exchanger) 71 is configured to perform heat exchange between external water introduced from outside the cold heat recovery system 1 and the intermediate heat medium that has been heat exchanged with the cold heat medium. The intermediate heat exchanger 71 includes a one-side heat exchanger 711 through which the intermediate heat medium flows, which is provided downstream of the intermediate side heat exchanger 752 of the heat exchanger 75 in the intermediate cycle 7 (pipe 70) and upstream of the circulation pump 72 and the intermediate heat medium storage device 73, and a second-side heat exchanger 712 through which the external water flows, which is provided in the external water supply line 17B connecting the external water supply source 15B and the external water discharge destination 16B. Heat exchange is performed between the one-side heat exchanger 711 and the second-side heat exchanger 712, and the intermediate heat medium flowing through the one-side heat exchanger 711 is heated. The external water supply source 15B may be the same as at least one of the supply sources 15 and 15A, and the external water discharge destination 16B may be the same as at least one of the discharge destinations 16 and 16A. The external water supply line 17B may be configured to share a portion with the external water supply line 17 or 17A.

According to the above configuration, the intermediate heat exchanger (second heat exchanger) 71 can use external water to raise the temperature of the intermediate heat medium, which has been cooled by heat exchange with the cold heat medium, making it easy to adjust the temperature of the intermediate heat medium. The intermediate heat exchanger 71 adjusts the temperature of the intermediate heat medium that is heat exchanged with the cold heat medium or the air conditioning heat medium, making it possible to quickly respond to fluctuations in either the cold heat medium flowing through the cold heat recovery cycle 4 or the air conditioning heat medium flowing through the air conditioning cycle 5. This allows the cold heat recovery cycle 4 and the air conditioning cycle 5 to operate stably, improving the reliability of the cold heat recovery system 1.

As shown in FIG. 8, the cold heat recovery system 1 according to some embodiments includes the above-mentioned heat exchanger (first heat exchanger) 12, the above-mentioned liquefied gas supply line 2, the above-mentioned cold heat recovery cycle 4, the above-mentioned air conditioning cycle 5, the above-mentioned dehumidifier 6, the intermediate cycle 7, and the intermediate heat exchanger (second heat exchanger) 71. As shown in FIG. 8, the cooler 61 (61D) of the dehumidifier 6 is configured to perform heat exchange between the intermediate heat medium that has been heat exchanged with the cold heat medium and the air taken in from the onboard space 100.

In the illustrated embodiment, the refrigerant side heat exchange section 612 (612D) of the cooler 61 (61D) is composed of a pipe through which an intermediate heat medium flows, which is provided downstream of the intermediate side heat exchange section 752 of the heat exchanger 75 in the intermediate cycle 7 (pipe 70) and upstream of the one side heat exchange section 711 of the intermediate heat exchanger 71 and the intermediate heat medium storage device 73. Heat exchange is performed between the air side heat exchange section 611 and the refrigerant side heat exchange section 612D, and the air flowing through the air side heat exchange section 611 is cooled to a temperature below the dew point, and the liquefied gas flowing through the refrigerant side heat exchange section 612D is heated.

According to the above configuration, the cooler 61 (61D) can cool the air taken in from the onboard space 100 using the cold energy of the intermediate heat medium recovered from the cold heat medium. This can reduce onboard power consumption. The intermediate heat exchanger (second heat exchanger) 71 can heat the intermediate heat medium, which has been cooled by heat exchange with the cold heat medium or air, using external water to raise the temperature, making it easy to adjust the temperature of the intermediate heat medium. This makes it possible to quickly respond to changes in the state of the air introduced into the cooler 61D. This allows the cooler 61D to operate stably, improving the reliability of the cold heat recovery system 1.

As shown in Figs. 8 and 9, the cold heat recovery system 1 according to some embodiments includes a heat exchanger (fourth heat exchanger) 81 configured to exchange heat between a medium (such as water or air) in a second interior space 110 different from the interior space 100 in which the air is dehumidified by the dehumidifier 6 of the above-mentioned floating structure 10 (ship 10A or float 10B) and an air-conditioning heat medium flowing between the air-conditioning pressure reducer 52 and the air-conditioning compressor 54 in the air-conditioning cycle 5. The medium in the second interior space 110 may be the air in the second interior space 110, or a heat medium (such as water) that exchanges heat with the air in the second interior space 110.

The heat exchanger (fourth heat exchanger) 81 functions as the air conditioning evaporator 53 in the air conditioning cycle 5, instead of the precooler 63, and is configured to heat the air conditioning heat medium decompressed by the air conditioning pressure reducer 52. In the embodiment shown in Figures 8 and 9, the dehumidifier 6 does not include a precooler 63, and the air is cooled by the cooler 61 (61D) from state value P1 to state value P3 shown in Figure 5.

In the embodiment shown in FIG. 9, the cold heat recovery system 1 includes not only the dehumidifier 6 including the cooler 61 and heater 62 described above, but also a temperature adjustment device 8. The temperature adjustment device 8 includes an air duct 80 for sending air taken in from the second interior space 110, the heat exchanger 81 described above, and a blower 82.

An air intake 111 and an air outlet 112 are formed on the wall surface forming the second interior space 110 of the floating structure 10 (ship 10A, float 10B). One side of the air duct 80 is connected to the air intake 111, and the other side is connected to the air outlet 112. The blower 82 includes a rotor blade 821 provided in the air duct 80, and an electric motor 822 configured to supply the rotor blade 821 with a driving force for rotating the rotor blade 821. By driving the blower 82, air is sucked from the second interior space 110 into the air duct 80 through the air intake 111. The air sucked into the air duct 80 is sent by the blower 82 through the air duct 80 toward the downstream side (the side where the air outlet 112 is located) of the air duct 80.

In the illustrated embodiment, the heat exchanger 81 includes an air-side heat exchange section 811 provided in the air duct 80 through which air taken in from the second inboard space 110 flows, and an air-conditioning side heat exchange section 812 provided downstream of the air-conditioning pressure reducer 52 and upstream of the air-conditioning compressor 54 in the air-conditioning cycle 5 (air-conditioning duct 50) through which the air-conditioning heat medium flows. Heat exchange is performed between the air-side heat exchange section 811 and the air-conditioning side heat exchange section 812, so that the air flowing through the air-side heat exchange section 811 is cooled and the air-conditioning heat medium flowing through the air-conditioning side heat exchange section 812 is heated.

As shown in FIG. 9, the blower 82 may be disposed upstream of the heat exchanger 81 in the air duct 80 in the air flow direction. The air drawn into the air duct 80 is cooled in the air-side heat exchange section 811 of the heat exchanger 81, and then returned to the second interior space 110 through the air outlet 112.

In the illustrated embodiment, the heat exchanger 81 cools the air in the second interior space 110 with the cold energy of the air-conditioning heat medium recovered from the cold heat medium. However, the water that exchanges heat with the air in the second interior space 110 may be cooled with the cold energy of the air-conditioning heat medium recovered from the cold heat medium. The heat exchanger 81 may include a water-side heat exchange section through which water flows that exchanges heat with the air in the second interior space 110 and which exchanges heat with the air-conditioning side heat exchange section 812 described above. Heat exchange is performed between the water-side heat exchange section and the air-conditioning side heat exchange section 812, and the water flowing through the water-side heat exchange section is cooled, and the air-conditioning heat medium flowing through the air-conditioning side heat exchange section 812 is heated. The air in the second interior space 110 is cooled by the water cooled by the water-side heat exchange section.

According to the above configuration, the heat exchanger (fourth heat exchanger) 81 can cool the medium (water, air, etc.) in the second interior space 110 using the cold energy of the air-conditioning heat medium recovered from the cold heat medium. This makes it possible to adjust the temperature of the second interior space 110 while suppressing the consumption of onboard electricity.

As shown in Figures 1 to 3, 7, and 8, the waterborne floating structure 10 (ship 10A or float 10B) in some embodiments is equipped with a cold energy recovery system 1 equipped with the above-mentioned dehumidifier 6. In this case, the ship 10A or float 10B can suppress the occurrence of condensation in the onboard space 100 while suppressing onboard power consumption by the dehumidifier 6.

The present disclosure is not limited to the above-described embodiments, but also includes variations of the above-described embodiments and appropriate combinations of these embodiments.

The contents described in the above-mentioned embodiments can be understood, for example, as follows:

1) A cold heat recovery system (1) according to at least one embodiment of the present disclosure,
A cold energy recovery system (1) installed on a ship (10A) or a floating body (10B) having a liquefied gas storage device (11) configured to store liquefied gas,
a first heat exchanger (12) configured to vaporize the liquefied gas;
a liquefied gas supply line (2) for supplying the liquefied gas from the liquefied gas storage device (11) to the first heat exchanger (12);
a cold heat recovery cycle (4) configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger (12);
an air conditioning cycle (5) configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle (4);
a dehumidification device (6) configured to dehumidify air taken in from an interior space (100) of the ship (10A) or the floating body (10B),
The dehumidifier (6) includes a cooler (61) configured to cool the air to a temperature below the dew point by exchanging heat between the liquefied gas or its vaporized gas and the air.

According to the configuration of 1) above, the dehumidifier (6) can reduce the amount of moisture contained in the air by cooling the air taken in from the onboard space (100) to a temperature below the dew point using the cooler (61), thereby allowing saturated moisture to precipitate from the air. The cooler (61) can reduce the amount of moisture contained in the air in the onboard space (100), thereby preventing condensation from occurring in the onboard space (100). The cooler (61) cools the air using cold energy from the liquefied gas or its vaporized gas, rather than using onboard electricity, thereby reducing the consumption of onboard electricity. In addition, the cooler (61) can recover the cold energy from the liquefied gas or its vaporized gas from a heat exchange target with the air, thereby raising the temperature of the heat exchange target. In this case, the energy consumption required to raise the temperature of the heat exchange target can be reduced, thereby improving the efficiency of the cold heat recovery system (1).

2) In some embodiments, the cold heat recovery system (1) described above in 1),
The air conditioning cycle (5) comprises:
an air conditioning compressor (54) configured to compress the air conditioning heat medium;
an air conditioning condenser (51) configured to condense the air conditioning heat medium downstream of the air conditioning compressor (54) in the air conditioning cycle (5),
The dehumidifier (6) further includes a heater (62) configured to perform heat exchange between the air-conditioning heat medium compressed by the air-conditioning compressor (54) and introduced into the air-conditioning condenser (51) and the air cooled by the cooler (61).

According to the configuration of 2) above, the dehumidifier (6) removes moisture from the air using the cooler (61) and heats the air cooled by the cooler (61) using the heater (62), thereby making it possible to adjust the temperature and humidity of the air. Therefore, the dehumidifier (6) can adjust the onboard space (100) to an appropriate temperature and humidity. The heater (62) heats the air not with an electric heater driven by onboard electricity, but with the compression heat of the air-conditioning heat medium compressed by the air-conditioning compressor (54), thereby reducing onboard electricity consumption.

3) In some embodiments, the cold heat recovery system (1) according to 1) or 2) above,
The system further includes a vaporized gas supply line (3) for supplying the vaporized gas produced by vaporizing the liquefied gas in the first heat exchanger (12),
The cooler (61A) is configured to perform heat exchange between the vaporized gas flowing through the vaporized gas supply line (3) and the air taken in from the interior space (100).

According to the configuration of 3) above, the cooler (61A) can cool the air taken in from the onboard space (100) using the cold energy of the vaporized gas flowing through the vaporized gas supply line (3). This can reduce the consumption of onboard electricity. The cooler (61A) can also heat the vaporized gas by recovering cold energy from the vaporized gas. When the cold energy recovery system (1) is configured to heat the vaporized gas to the required temperature of the supply destination (13) using the vaporized gas heater (31), the amount of heating (amount of heat exchange) in the vaporized gas heater (31) can be reduced, thereby reducing the consumption of onboard electricity used to drive the vaporized gas heater (31).

4) In some embodiments, the cold heat recovery system (1) described in 1) or 2) above,
The cooler (61B) is configured to perform heat exchange between the liquefied gas flowing through the liquefied gas supply line (2) and the air taken in from the interior space (100).

According to the configuration of 4) above, the cooler (61B) can cool the air taken in from the onboard space (100) by using the cold energy of the liquefied gas flowing through the liquefied gas supply line (2). This can reduce the consumption of onboard electricity. In addition, the cooler (61B) can heat the liquefied gas by recovering cold energy from the liquefied gas. When the cold energy recovery system (1) is configured to heat the vaporized gas to the required temperature of the supply destination (13) by the vaporized gas heater (31), the amount of heating (amount of heat exchange) in the vaporized gas heater (31) can be reduced, so that the consumption of onboard electricity used to drive the vaporized gas heater (31) can be reduced.

5) In some embodiments, the cold heat recovery system (1) according to 1) or 2) above,
The cold energy recovery cycle (4) includes a cold energy turbine (41) configured to be driven by cold energy of the cold energy medium,
The cooler (61C) is configured to perform heat exchange between the cold heat medium flowing between the cold heat turbine (41) and the first heat exchanger (12) in the cold heat recovery cycle (4) and the air taken in from the onboard space (100).

According to the configuration of 5) above, the cooler (61C) can cool the air taken in from the onboard space (100) using the cold energy of the cold heat medium that has recovered the cold energy of the liquefied gas. This can reduce the consumption of electricity on board. In addition, when the cooler (61) is provided in the liquefied gas supply line (2) or the vaporized gas supply line (3), it is necessary to take sufficient measures to prevent gas leakage and heat radiation from these lines (2, 3). In contrast, when the cooler (61C) is provided in the cold recovery cycle (4), the reliability of the cold recovery system (1) can be ensured without taking the above measures.

6) In some embodiments, the cold heat recovery system (1) according to any one of 1) to 5) above,
an intermediate cycle (7) configured to circulate an intermediate heat medium having a lower freezing point than water, the intermediate heat medium being heat-exchanged between the cold heat medium flowing through the cold heat recovery cycle (4) and the air conditioning heat medium flowing through the air conditioning cycle (5);
The cold heat recovery system (1) further includes a second heat exchanger (intermediate heat exchanger 71) configured to perform heat exchange between external water introduced from outside the cold heat recovery system (1) and the intermediate heat medium that has been heat exchanged with the cold heat medium.

According to the configuration of 6) above, the intermediate heat medium, whose temperature has been reduced by heat exchange with the cold heat medium in the second heat exchanger (71), can be heated by external water, making it easy to adjust the temperature of the intermediate heat medium. By adjusting the temperature of the intermediate heat medium that is heat exchanged with the cold heat medium or the air conditioning heat medium in the second heat exchanger (71), it is possible to quickly respond to fluctuations in either the cold heat medium flowing through the cold heat recovery cycle (4) or the air conditioning heat medium flowing through the air conditioning cycle (5). This allows the cold heat recovery cycle (4) and the air conditioning cycle (5) to operate stably, improving the reliability of the cold heat recovery system (1).

7) In some embodiments, the cold heat recovery system (1) according to any one of 1) to 5) above,
The cold heat recovery system (1) further includes a third heat exchanger (cold heat exchanger 46) configured to exchange heat between external water introduced from outside the cold heat recovery system (1) and the cold heat medium.

According to the configuration of 7) above, the third heat exchanger (46) allows the cold heat medium to be heated by external water, so that the temperature of the cold heat medium can be easily adjusted. This allows the cold heat recovery cycle (4) to operate stably because it can quickly respond to changes in the state of the cold heat medium flowing through the cold heat recovery cycle (4). In addition, the third heat exchanger (46) allows the cold heat medium to be heated by external water, so that the cold heat recovery cycle (4) can operate regardless of whether the air conditioning cycle (5) is operating. This improves the reliability of the cold heat recovery system (1).

8) In some embodiments, the cold heat recovery system (1) described in 1) or 2) above,
an intermediate cycle (7) configured to circulate an intermediate heat medium having a lower freezing point than water, the intermediate heat medium being heat-exchanged between the cold heat medium flowing through the cold heat recovery cycle (4) and the air conditioning heat medium flowing through the air conditioning cycle (5);
The cold heat recovery system (1) further includes a second heat exchanger (intermediate heat exchanger 71) configured to perform heat exchange between external water introduced from outside the cold heat recovery system (1) and the intermediate heat medium that has been heat exchanged with the cold heat medium,
The cooler (61D) is configured to perform heat exchange between the intermediate heat medium that has been heat exchanged with the cold heat medium and the air taken in from the interior space (100).

According to the configuration of 8) above, the cooler (61D) can cool the air taken in from the onboard space (100) using the cold energy of the intermediate heat medium recovered from the cold heat medium. This can reduce the consumption of onboard electricity. The second heat exchanger (71) can heat the intermediate heat medium, whose temperature has been reduced by heat exchange with the cold heat medium or air, using external water, making it easy to adjust the temperature of the intermediate heat medium. This makes it possible to quickly respond to changes in the state of the air introduced into the cooler (61D). This allows the cooler (61D) to operate stably, improving the reliability of the cold heat recovery system (1).

9) In some embodiments, the cold heat recovery system (1) according to any one of 1) to 8) above,
The air conditioning cycle (5) comprises:
an air conditioning compressor (54) configured to compress the air conditioning heat medium;
an air conditioning pressure reducer (52) configured to reduce the pressure of the air conditioning heat medium upstream of the air conditioning compressor (54) in the air conditioning cycle,
The cold heat recovery system (1) comprises:
The air conditioning system further includes a precooler (63) configured to perform heat exchange between the air taken in from the interior space (100) and the air conditioning heat medium flowing between the air conditioning pressure reducer (52) and the air conditioning compressor (54) in the air conditioning cycle (5), upstream of the cooler (61) in the air flow direction.

According to the configuration of 9) above, the pre-cooler (63) can cool the air taken in from the onboard space (100) using the cold energy of the air-conditioning heat medium recovered from the cold heat medium. This can reduce the consumption of electricity on board. In addition, when the object of heat exchange with the air in the cooler (61) is liquefied gas or a cold heat medium, the air is cooled in two stages, the pre-cooler (63) and the cooler (61), so that the amount of cold energy recovered by the cooler (61) from the cold heat medium can be reduced, thereby suppressing a decrease in the efficiency of the cold heat recovery cycle (4).

10) In some embodiments, the cold heat recovery system (1) according to any one of 1) to 8) above,
The air conditioning cycle (5) comprises:
an air conditioning compressor (54) configured to compress the air conditioning heat medium;
an air conditioning pressure reducer (52) configured to reduce the pressure of the air conditioning heat medium upstream of the air conditioning compressor (54) in the air conditioning cycle,
The cold heat recovery system (1) comprises:
The ship (10A) or the float (10B) further includes a fourth heat exchanger (81) configured to exchange heat between a medium in a second onboard space (110) different from the onboard space (100) in which the air is dehumidified by the dehumidifier (6) of the ship (10A) or the float (10B) and the air-conditioning heat medium flowing between the air-conditioning pressure reducer (52) and the air-conditioning compressor (54) in the air-conditioning cycle (5).

According to the configuration of 10) above, the fourth heat exchanger (81) can cool the medium (water, air, etc.) in the second interior space (110) using the cold energy of the air-conditioning heat medium recovered from the cold heat medium. This makes it possible to adjust the temperature of the second interior space (110) while suppressing the consumption of onboard electricity.

11) A ship (10A) or a floating body (10B) according to at least one embodiment of the present disclosure,
The present invention is equipped with a cold heat recovery system (1) according to any one of 1) to 10) above.

According to the configuration of 11) above, the ship (10A) or the floating body (10B) can suppress the occurrence of condensation in the onboard space (100) while suppressing the consumption of onboard electricity by the dehumidifier (6).

1 Cold heat recovery system 2 Liquefied gas supply line 3 Vaporized gas supply line 4 Cold heat recovery cycle 5 Air conditioning cycle 6 Dehumidifier 7 Intermediate cycle 8 Temperature adjustment device 10 Water floating structure 10A Ship 10B Floating body 11 Liquefied gas storage device 12, 14 Heat exchanger 13 Supply destination 15, 15A, 15B Supply source 16, 16A, 16B Discharge destination 17, 17A, 17B External water supply line 18 Bypass flow path 20 Liquefied gas pipeline 21 Gas pump 30 Vaporized gas pipeline 31 Vaporized gas heater 40 Cold heat pipe 41 Cold heat turbine 42 Cold heat pump 43 Cold heat condenser 44 Cold heat evaporator 45 Generator 46 Cold heat heat exchanger 50 Air conditioning pipeline 51 Air conditioning condenser 52 Air conditioning pressure reducer 53 Air conditioning evaporator 54 Air conditioning compressor 60, 80 Air pipe 61, 61A to 61D Cooler 62 Heater 63 Precooler 64, 82 Blower 70 Pipe 71 Intermediate heat exchanger 72 Circulation pump 73 Intermediate heat medium storage device 74, 75, 81 Heat exchanger 100, 110 Inboard space 101, 111 Air intake 102, 112 Air outlet P1, P2, P3, P4 Status value

Claims (11)

A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The cold heat recovery cycle includes a cold heat turbine configured to be driven by cold energy of the cold heat medium, the cold heat medium being introduced into the cold heat recovery cycle and being heat exchanged with the air-conditioning heat medium flowing through the air-conditioning cycle,
Cold and heat recovery system. The air conditioning cycle comprises:
an air conditioning compressor configured to compress the air conditioning heat medium;
an air conditioning condenser configured to condense the air conditioning heat medium downstream of the air conditioning compressor in the air conditioning cycle,
The dehumidifier further includes a heater configured to perform heat exchange between the air-conditioning heat medium compressed by the air-conditioning compressor and introduced into the air-conditioning condenser and the air cooled by the cooler.
The cold heat recovery system according to claim 1 . The apparatus further includes a vaporized gas supply line for supplying the vaporized gas generated by vaporizing the liquefied gas in the first heat exchanger,
The cooler is configured to perform heat exchange between the vaporized gas flowing through the vaporized gas supply line and the air taken in from the interior space of the vessel.
The cold heat recovery system according to claim 1 . The cooler is configured to perform heat exchange between the liquefied gas flowing through the liquefied gas supply line and the air taken in from the interior space of the ship.
The cold heat recovery system according to claim 1 . A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The cold energy recovery cycle includes a cold energy turbine configured to be driven by cold energy of the cold energy medium,
The cooler is configured to perform heat exchange between the cold heat medium flowing between the cold heat turbine and the first heat exchanger in the cold heat recovery cycle and the air taken in from the inboard space .
Cold and heat recovery system. A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The cold heat recovery system includes:
an intermediate cycle configured to circulate an intermediate heat medium having a lower freezing point than water, the intermediate heat medium being heat-exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium flowing through the air conditioning cycle;
The system further includes a second heat exchanger configured to perform heat exchange between external water introduced from outside the cold heat recovery system and the intermediate heat medium that has been heat exchanged with the cold heat medium .
Cold and heat recovery system. Further comprising a third heat exchanger configured to perform heat exchange between external water introduced from outside the cold heat recovery system and the cold heat medium.
The cold heat recovery system according to claim 1 . A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The cold heat recovery system includes:
an intermediate cycle configured to circulate an intermediate heat medium having a lower freezing point than water, the intermediate heat medium being heat-exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium flowing through the air conditioning cycle;
A second heat exchanger configured to perform heat exchange between external water introduced from outside the cold heat recovery system and the intermediate heat medium that has been heat exchanged with the cold heat medium,
The cooler is configured to perform heat exchange between the intermediate heat medium that has been heat exchanged with the cold heat medium and the air taken in from the inboard space .
Cold and heat recovery system. A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The air conditioning cycle comprises:
an air conditioning compressor configured to compress the air conditioning heat medium;
an air conditioning pressure reducer configured to reduce the pressure of the air conditioning heat medium upstream of the air conditioning compressor in the air conditioning cycle,
The cold heat recovery system includes:
a precooler configured to perform heat exchange between the air taken in from the interior space and the air conditioning heat medium flowing between the air conditioning pressure reducer and the air conditioning compressor in the air conditioning cycle, the precooler being disposed upstream of the cooler in the air flow direction,
Cold and heat recovery system. A cold energy recovery system installed on a ship or a floating body having a liquefied gas storage device configured to store liquefied gas,
a first heat exchanger configured to vaporize the liquefied gas;
a liquefied gas supply line for supplying the liquefied gas from the liquefied gas storage device to the first heat exchanger;
a cold heat recovery cycle configured to circulate a cold heat medium that has been heat exchanged with the liquefied gas in the first heat exchanger;
an air conditioning cycle configured to circulate an air conditioning heat medium that has been heat exchanged between the cold heat medium flowing through the cold heat recovery cycle and the air conditioning heat medium;
and a dehumidification device configured to dehumidify air taken in from an interior space of the ship or the floating body,
The dehumidification device includes a cooler configured to cool the air to a temperature equal to or lower than a dew point by performing heat exchange between the liquefied gas or the vaporized gas thereof and the air,
The air conditioning cycle comprises:
an air conditioning compressor configured to compress the air conditioning heat medium;
an air conditioning pressure reducer configured to reduce the pressure of the air conditioning heat medium upstream of the air conditioning compressor in the air conditioning cycle,
The cold heat recovery system includes:
a fourth heat exchanger configured to exchange heat between a medium in a second onboard space different from the onboard space from which the air is dehumidified by the dehumidifier of the ship or the float, and the air-conditioning heat medium flowing between the air-conditioning compressor and the air-conditioning pressure reducer in the air-conditioning cycle ;
Cold and heat recovery system. A ship or a floating body comprising the cold heat recovery system according to any one of claims 1 to 10 .

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