KR20130075286A - Intake air cooling system for ship having turbocharger and central fresh water cooler - Google Patents

Abstract

PURPOSE: A ship intake air cooling system having a turbocharger and a central fresh water cooler are provided to cool intake air supplied to an engine of a ship using an absorbing type cooler, thereby raising engine efficiency. CONSTITUTION: A ship intake air cooling system having a turbocharger (100) and a central fresh air cooler includes the turbocharger, a cooling unit, an absorbing type cooler (200,200a), and a central fresh water cooler (700). The turbocharger compresses intake air entered from outside using part of exhaust gas generated in an engine (300) and includes a front end through which the intake air is entered and a rear end for supplying compressed intake air to the engine. The cooling unit includes a first cooling unit (510), a second cooling unit (520) and a third cooling unit (530). A first working fluid is circulated in the first cooling unit to exchange heat with the intake air discharged from the turbocharger. A second working fluid is circulated in the second cooling unit to exchange heat with the intake air. The third cooling unit is arranged between the first cooling unit and the second cooling unit. The absorbing type cooler receives a heat source from the first and second working fluids through the first and second cooling units. The center fresh water cooler supplies fresh water having a different temperature to the second cooling unit and a cooling requiring facility installed in the ship.

Description

INTAKE AIR COOLING SYSTEM FOR SHIP HAVING TURBOCHARGER AND CENTRAL FRESH WATER COOLER}

The present invention relates to a suction air cooling system of a ship equipped with a central fresh water cooling device and a supercharger.

In general ships, an internal combustion engine such as a diesel engine is installed for a number of purposes, such as the propulsion power of the ship and the power generation used in the ship.

In the case of the internal combustion engine, power is generally generated using the stroke of intake, compression, explosion and exhaust of fuel. At this time, in the intake process of the fuel, intake air (Intake Air) is introduced into the internal combustion engine with the fuel, by increasing the pressure of the intake air, the efficiency of the internal combustion engine can be increased.

Therefore, in recent years, many ships provided with the supercharger for supplying a large amount of the said suction air to the said internal combustion engine by raising the pressure of the said suction air are proposed.

The intake air compression method by the supercharger is a turbocharger driven by an exhaust turbine using a supercharger system and a exhaust gas generated in the combustion engine, by mechanically driving a cog wheel to the crankshaft of the internal combustion engine. ) There is a way.

1 shows an example of a ship provided with a supercharger for compressing intake air by a turbocharger method.

When the exhaust gas E having a predetermined pressure and temperature is discharged from the internal combustion engine of the vessel, that is, the engine 310, the exhaust gas E is supplied to the supercharger 100.

At this time, by the energy of the exhaust gas (E) supplied to the supercharger 100, a rotational force is generated in the exhaust turbine 111 of the supercharger 100, the compression turbine 112 is connected to the exhaust turbine 111 the rotational force Is passed to. In addition, the compression turbine 112 compresses the external suction air a by using the rotational force and supplies the compressed air to the engine 310.

On the other hand, in the intake air (a) compression process in the supercharger 110, the intake air (a) is compressed in accordance with the adiabatic compression process. Therefore, the temperature of the suction air (a) after compression, that is, the temperature of the rear end side suction air (a) of the supercharger 110, is the temperature of the suction air (a) before compression, that is, the front side suction air of the supercharger (110). It rises above the temperature of (a).

In this case, as the temperature of the intake air (a) supplied to the engine 310, which is generally the internal combustion engine, increases, the efficiency of the engine 310 decreases, and thus, the rear end intake air having passed through the supercharger 110 ( a) Due to the increase in temperature, a problem occurs that the efficiency of the engine 310 is reduced.

In addition, when the vessel is operated in a high temperature environment, such as the tropics, the temperature of the intake air (a) is increased from the front end side of the supercharger 110, the compressed, thereby the efficiency of the engine 310 is further The problem of degradation occurs.

In addition, the following patent document, which is the background of the invention, is provided with a main cooling facility and a sub cooling facility together, and the intake air cooled by the main cooling facility is cooled secondly by the sub cooling facility. In an environment using cooling demand equipment (hereinafter, referred to as 'cooling demand equipment'), only the relatively fresh water is supplied even when the temperature of the sea water is relatively low, thereby improving engine fuel efficiency and reducing the capacity of the absorption chiller. The situation is not planning.

Therefore, the following patent document, which is the background of the invention, can provide only high temperature fresh water to reduce the cooling capacity of the absorption chiller or the physical size of the device.

For example, the central fresh water cooling device provided in the prior art ship is provided with a separate LT (Low Temperature) cooling system for the machinery and other machinery that requires cooling, in the case of the ship, sea water temperature of 32 ℃ [Example: Seawater temperature design conditions are based on IACS M28 (1978) Tropical Condition]. When cooling fresh water, the same fresh water setting temperature (eg 36 ° C) is set to the same and the fresh water is cooled to the engine and the machinery requiring cooling. There is a problem to supply.

Patent Publication No. 10-2010-0113756

Therefore, embodiments of the present invention can increase the efficiency of the engine by additionally cooling the intake air to the engine, and when the temperature of the sea water is relatively low, the fresh water of the engine is lowered through the present embodiment. In order to provide a third cooling unit, the inlet air cooling system of a ship equipped with a central fresh water cooling system and a supercharger capable of improving engine fuel efficiency and reducing the capacity of an absorption type refrigerator is provided.

According to an aspect of an embodiment of the present invention, in the intake air cooling system of the ship, by using a portion of the exhaust gas generated in the engine to compress the intake air introduced from the outside, and the shear and the inlet air is introduced A supercharger including a rear end for supplying the intake air to the engine; Heat exchange with the intake air discharged from the supercharger to cool at least one of the intake air compressed in the supercharger and the exhaust gas passing through the supercharger, and disposed in accordance with the intake air or the flow of the exhaust gas. A first cooling unit through which the first working fluid is circulated, a second cooling unit positioned behind the first cooling unit to circulate the second working fluid to exchange heat with the intake air, and a first cooling unit and the first cooling unit. A cooling unit including a third cooling unit disposed between the two cooling units; An absorption type cooling device that receives a heat source from a working fluid circulated through the cooling unit; And a central fresh water cooling device for providing fresh water at different fresh water temperatures to the second cooling unit and the cooling demand facility provided in the ship. .

In addition, the present embodiment, the fresh water discharge passage is coupled between the outlet and the first branch point of the central fresh water cooling device, the discharge path of the first fresh water; A second supplementary valve installed in the fresh water discharge passage; A unit inlet flow passage installed between the first branch point and the inlet of the third cooling unit and serving as an inflow path of the third fresh water; A target inlet flow passage installed between the first branch point and the inlet of the cooling demand equipment and serving as an inflow path of the second fresh water; A first replenishment valve installed at the object inlet flow passage after the first branch point; A first temperature sensor installed in an object inlet flow passage to a rear end of the first supplementary valve and connected to the first supplementary valve; And a second temperature sensor installed in the unit inlet flow passage after the first branch point and connected to the second supplementary valve.

In addition, the present embodiment, the unit outlet passage provided between the outlet and the confluence point of the third cooling unit discharged the third fresh water; A target outlet flow passage installed between the outlet of the third cooling unit through which the second fresh water is discharged and the confluence point; An oil mixture flow passage installed between the contention point and the inlet of the fresh water circulation pump; A fresh water inflow passage which is an inflow path of a fourth fresh water between an outlet of the fresh water circulation pump and an inlet of the central fresh water cooling device; A second branch point and a third branch point installed in the fresh water inflow passage after the fresh water circulation pump; A first supplementary flow passage installed between the second branch point of the fresh water inflow passage and the first supplementary valve; And a second replenishment flow passage installed between the third branch point of the fresh water inflow passage and the second replenishment valve.

In addition, the second fresh water may correspond to a rate at which the relatively high temperature of the fourth fresh water through the first replenishment valve and the first replenishment passage is replenished or not replenished with the first fresh water having a fresh water temperature of 21 ° C. The cooling water may be fresh water adjusted to a setting temperature of 36 ° C.

In addition, the third fresh water is the design minimum required temperature of the third cooling unit to correspond to the rate at which the fourth fresh water through the second replenishment valve and the second replenishment flow passage is supplemented or not replenished with the first fresh water. Fresh water adjusted to 21 ° C.

According to the proposed embodiment, the engine efficiency can be increased by cooling the intake air supplied to the engine of the ship by using the absorption type cooling device.

In addition, the absorption cooling device for cooling the suction air of the high temperature compressed by the supercharger is driven by obtaining a heat source from the suction air, so that a separate heat source for driving the absorption cooling device is not required. There is an advantage that the energy efficiency of the cooling system for cooling is increased.

In addition, in the process of supplying the high-temperature intake air compressed by the supercharger to the engine, the cooling air is cooled through a plurality of steps, thereby increasing the cooling efficiency of the intake air as compared with the case of cooling the intake air at once. There is an advantage.

In addition, the present embodiment can supply lower temperature fresh water to the third cooling unit on the engine side, thereby improving engine fuel efficiency and reducing the capacity of the absorption chiller, and building a realistic system in the actual vessel application of the absorption chiller. There is an advantage to this.

In addition, since the present embodiment can utilize the central fresh water cooling device installed in the ship instead of the auxiliary cooling device, bringing the weight of the entire vessel according to the secured installation location of the device and the size of the absorption type cooling device to help the propulsion efficiency of the ship Has the effect of giving.

1 is a view showing the configuration of a vessel equipped with a conventional supercharger.
2 shows the relationship between the temperature of intake air and the efficiency of the engine.
Figure 3 is a view showing the configuration of the intake air cooling system of a ship equipped with a supercharger according to a first embodiment of the present invention.
Figure 4 is a view showing the configuration of the absorption type cooling device of the intake air cooling system of FIG.
5 is a view showing the configuration of the cooling unit of the intake air cooling system according to an embodiment of the present invention.
6 is a view showing the configuration of an intake air cooling system according to a second embodiment of the present invention.
7 is a view showing the configuration of an intake air cooling system according to a third embodiment of the present invention.
8 is a view showing the configuration of an intake air cooling system according to a fourth embodiment of the present invention.
9 is a view showing the configuration of the intake air cooling system of a ship equipped with a central fresh water cooling device and a supercharger according to a fifth embodiment of the present invention.

2 shows the relationship between the temperature of the intake air and the efficiency of the engine.

Referring to FIG. 2, as the temperature of the intake air supplied to an internal combustion engine such as a diesel engine increases, the fuel consumption rate (SFOC), which shows the fuel efficiency of the internal combustion engine, also increases.

In this case, the fuel consumption rate means a daily equivalent of fuel consumption, and as the fuel consumption rate increases, the consumption of the fuel producing the same amount in the internal combustion engine increases, so that the efficiency of the internal combustion engine decreases.

That is, since the temperature of the intake air and the thermal efficiency of the internal combustion engine are inversely related, in order to increase the thermal efficiency of the internal combustion engine, a decrease in the temperature of the intake air supplied to the internal combustion engine is required.

Hereinafter, the configuration of the intake air cooling system of a ship equipped with a supercharger according to the present embodiment for reducing the temperature of the intake air supplied to the internal combustion engine will be described in detail.

Figure 3 is a view showing the configuration of the intake air cooling system of the vessel equipped with a supercharger according to a first embodiment of the present invention, Figure 4 is a view showing the configuration of the absorption type cooling device of the intake air cooling system of FIG.

First, referring to FIG. 3, the intake air cooling system 1 of a ship provided with a supercharger according to the present embodiment includes a supercharger 100, an absorption type cooling device 200, an auxiliary cooling device 400, and cooling. A portion 500 is included.

In more detail, the supercharger 100 is provided as a turbocharger type turbocharger that compresses the intake air a by using a portion E of the exhaust gas generated by the engine 300, and a portion of the exhaust gas ( E) the exhaust turbine 101 is supplied to generate a rotational force, and the compression turbine 102 connected to the exhaust turbine 101 receives the rotational force, compresses the intake air (a) of the external supply to the engine Include.

In addition, the supercharger 100 is discharged toward the engine 300 by the front of the intake air (a) is introduced from the outside and the intake air (a) compressed in the compression turbine 102 to the engine 300 on the basis of the compression turbine (102) The rear end is formed.

When the suction air (a) compressed in the supercharger (100) is supplied to the engine 300, and the engine (300) supplied with the compressed suction air (a) is supplied with the suction air (a) at atmospheric pressure. On the contrary, as the excess compressed air a is supplied, the efficiency can be increased.

On the other hand, at the time of compressing the intake air (a) in the supercharger 100, the intake air (a) is compressed according to the adiabatic compression process, the temperature is increased, the intake air (a) with the temperature rises as it is When supplied to the engine 300, a decrease in engine efficiency may occur as described above.

Therefore, between the turbocharger 100 and the engine 300 according to the present embodiment, a cooling unit 500 for cooling the intake air a compressed by the turbocharger 100 is provided.

The cooling unit 500 includes a plurality of cooling units 510, 520, and 530 disposed along the flow of intake air a, and the absorption units 200 and the auxiliary cooling unit 400 are provided in the cooling units 510, 520, and 530. The working fluids w1, w2, and w3 cooled from) are circulated to allow the intake air a to be cooled in the process of flowing into the engine 300.

The cooling units 510, 520, and 530 are arranged as a first cooling unit 510, a second cooling unit 520, and a third cooling unit 530, and the first cooling unit 510 is closest to the supercharger 100. The second cooling unit 520 is located at the rear of the first cooling unit 510. The third cooling unit 530 is disposed between the first cooling unit 510 and the second cooling unit 520.

At this time, the first cooling unit 510 and the second cooling unit 520 are supplied and circulated with the first working fluid w1 and the second working fluid w2 cooled from the absorption chiller 200, respectively. The third working fluid w3 cooled from the auxiliary cooling device 400 is supplied and circulated to the third cooling unit 530.

Meanwhile, the absorption type cooling device 200 receives a heat source from the first working fluid w1 circulated through the first cooling unit 510 of the cooling unit 500, and circulates through the second cooling unit 520. The low temperature heat source is supplied from the second working fluid w2, and the cooling operation is performed. Detailed description of the configuration of the absorption type cooling device 200 will be described below.

In addition, the auxiliary cooling device 400 is provided separately from the absorption type cooling device 200, and installed to be heat-exchangable with the seawater circulation passage 420 and the seawater circulation passage 420 through which the auxiliary working fluid w4 is circulated. And a third working fluid circulation passage 410 through which the third working fluid w3 is circulated. In this case, the auxiliary working fluid w4 may be external sea water.

That is, in the auxiliary cooling device 400, the third working fluid w3 heated through the third cooling unit 530 may be cooled by the auxiliary working fluid w4 circulating in the seawater circulation passage 420. .

Hereinafter, the configuration of the absorption type cooling device 200 will be described in detail.

Referring to FIG. 4, the absorption type cooling device 200 is provided to cool the first working fluid w1 and the second working fluid w2 using a refrigerant, and includes an evaporator 210, an absorber 220, Regenerator 230 and condenser 240.

The evaporator 210 is provided to cool the working fluid to cool the marine fuel by using the latent heat of evaporation of the refrigerant. In the present embodiment, fresh water may be used as the refrigerant R, but is not limited thereto.

Meanwhile, a second working fluid circulation passage 251 is provided in the evaporator 210. The second working fluid w2 passing through the evaporator 210 through the second working fluid circulation path 251 is cooled by latent heat of evaporation of the refrigerant R in the evaporator 210. As the second working fluid w2, for example, various cooling media such as fresh water may be used.

In addition, a refrigerant pump 216 is provided at the lower portion of the evaporator 210 to supply the liquid refrigerant R condensed at the lower portion of the evaporator 210 to the upper portion of the evaporator 210 through the refrigerant pipe 212. do. The refrigerant R supplied to the upper portion of the evaporator 210, that is, the fresh water is sprayed toward the working fluid circulation passage 251 through the nozzle in the evaporator 210 and simultaneously evaporated.

In addition, the second working fluid w2 flowing in the second working fluid circulation passage 251 may be cooled by the latent heat of evaporation absorbed by the refrigerant R in the evaporation process of the coolant R.

At this time, the internal pressure of the evaporator 210 may be adjusted to, for example, a pressure of 6.5 mmHg, so that the internal pressure of the evaporator 210 may be adjusted, and the coolant R provided in the fresh water is at a temperature of about 5 ° C. Can be evaporated.

Meanwhile, the absorber 220 is provided to absorb the refrigerant R evaporated from the evaporator 210, and in this embodiment, fresh water, and the evaporator 210 and the absorber 220 communicate with each other by the refrigerant supply passage 211. Can be.

In more detail, if evaporation is continued in the evaporator 210, since the partial pressure of water vapor is gradually increased, the evaporation temperature is also increased, so that an adequate cooling effect cannot be obtained. Therefore, when the evaporated refrigerant R is absorbed into the absorbent liquid A stored in the absorber 220, the evaporation pressure and temperature of the refrigerant R in the evaporator 210 may be maintained constant.

In this embodiment, as the absorbent liquid A of the absorber 220, the number of lithium bromide (LiBr)

Solutions can be used, but are not limited thereto.

In addition, the auxiliary working fluid cooled from the auxiliary cooling device 400 in the absorber 220 to remove the heat of absorption generated when the absorbent liquid A in the absorber 220 absorbs the evaporated refrigerant R. An auxiliary working fluid pipe 252 through which w4 flows is provided.

On the other hand, as the aqueous lithium bromide solution as the absorbent liquid (A) continues to absorb, the concentration of the aqueous lithium bromide solution is gradually diluted, the efficiency of the absorbing action of absorbing the fresh water of the lithium bromide aqueous solution is a refrigerant (R) Progressively reduced.

Accordingly, the absorption type cooling device 200 according to the present embodiment is provided with the regenerator 230 for regeneration of the absorbent liquid A.

In addition, an absorbent liquid pump 224 is provided below the absorber 220, and the absorbent liquid pump 224 regenerates the lithium bromide aqueous solution condensed in the lower part of the absorber 220 through the first absorbent liquid circulation pipe 221. ).

The regenerator 230 heats the diluted lithium bromide aqueous solution by absorbing a coolant, that is, fresh water, thereby increasing the concentration of lithium bromide in the aqueous lithium bromide solution by evaporating the fresh water from the absorbent liquid A, that is, the aqueous lithium bromide solution. Process, that is, to perform the absorption liquid regeneration process. At this time, the first absorbent circulating pipe 221 for communicating the aqueous solution of lithium bromide diluted from the absorber 220 is communicated with the regenerator 230.

The absorbent liquid A in the regenerator 230 is heated by a heating means, and as the heating means, that is, as a heat source, while cooling the suction air a compressed in the first cooling unit 510, the first absorbed liquid A is heated. Working fluid w1 is used. At this time, the first working fluid circulating flow path 261 through which the first working fluid w1 flows passes through the regenerator 230, and the absorbent liquid A accommodated in the regenerator 230 passes through the first working fluid circulating flow path 261. Receiving heat from the), the absorption liquid regeneration process may be performed.

Meanwhile, the absorbent liquid A concentrated through the regeneration process in the regenerator 230 is circulated to the absorber 220 through the second absorbent liquid circulation pipe 231.

In this case, an absorption liquid heat exchanger 260 may be installed between the regenerator 230 and the absorber 220. The absorbent liquid heat exchanger 260 passes through a portion of the first absorbent liquid circulation pipe 221 and the second absorbent liquid circulation pipe 231, and the absorbent liquid A having low temperature and low concentration flowing in the first absorbent liquid circulation pipe 221. Heat exchange of the high temperature and high concentration of the absorbent liquid A flowing in the second absorbent liquid circulation pipe 231 is performed. Accordingly, the absorbent liquid heat exchanger 260 may serve to improve thermal efficiency by significantly reducing the amount of heating in the regenerator 230 and the amount of cooling heat in the absorber 220.

The concentrated lithium bromide aqueous solution entering the absorber 220 is absorbed again by the refrigerant R in the vapor state to become low concentration, and then circulated to the regenerator 230 to repeat the heating and condensing process continuously.

In the regeneration process of the absorbent liquid A, the refrigerant R in the vapor state from the absorbent liquid A, that is, water vapor, is condenser 240 through a connection pipe 232 connecting the regenerator 230 and the condenser 240. Is supplied.

Meanwhile, the condenser 240 is provided to condense the refrigerant R evaporated from the regenerator 230, that is, water vapor. In the condenser 240, an auxiliary working fluid pipe 252 passing through the absorber 220 as a heat exchanger is installed to extend the evaporated refrigerant R, that is, water vapor. Therefore, the auxiliary working fluid w4 that has passed through the absorber 220 absorbs heat from the refrigerant R in the vapor state inside the condenser 240, and the refrigerant R in the vapor state condenses in the liquid state. To be possible.

In addition, the refrigerant R condensed in a liquid state, that is, fresh water, may be supplied to the evaporator 210 through the refrigerant pipe 241. In addition, the liquid refrigerant R resupplied to the evaporator 210 repeats the circulation in the absorption type cooling device 200. In this case, an expansion valve 242 may be provided in the refrigerant pipe 241 to reduce the pressure of the refrigerant R flowing therein.

Hereinafter, in the absorption type cooling apparatus 200 of the intake air cooling system of a ship equipped with a supercharger according to an embodiment of the present invention, the flow of the refrigerant R will be described. In this case, the operation of the detailed components of the absorption type cooling device 200 has been described above, a description thereof will be omitted.

The refrigerant (R, fresh water in this embodiment) cooled by the latent heat of evaporation in the evaporator 210 of the absorption chiller 200 is absorbed by the aqueous lithium bromide solution, which is the absorbent liquid A in the absorber 220. To start. Thereafter, the absorbent liquid A whose concentration is lowered by absorbing the refrigerant R is transferred to the regenerator 230.

In the regenerator 230, from the absorbent liquid A in which the refrigerant R is excessively absorbed by the heated first working fluid w1 circulating inside the regenerator 230 through the first working fluid circulation passage 261. The refrigerant R is evaporated. In addition, the first working fluid w1 is an absorbent liquid A in which the refrigerant R is excessively absorbed by the high temperature exhaust gas E2 that receives heat from the exhaust gas in the heat exchanger 280 by the heat exchange process. From this, the refrigerant R is evaporated.

The refrigerant R is evaporated and separated, and the concentrated absorbent liquid A enters the absorber 220 again to perform the absorption function again. The refrigerant R in the vapor state from the regenerator 230 is supplied to the condenser 240, cooled and condensed by sea water, circulated to the evaporator 210, and completes a cycle of refrigerant circulation.

By repeatedly performing this circulation process, the second working fluid w1 flowing through the second working fluid circulation passage 251 in the evaporator 210 is cooled.

Hereinafter, the configuration of the cooling unit 500 to allow the intake air a to be cooled and supplied to the engine 300 in the intake air cooling system of the ship in which the supercharger is installed according to the present embodiment will be described in detail.

5 is a view showing the configuration of the cooling unit and the flow of intake air of the intake air cooling system according to an embodiment of the present invention.

3 and 5, the cooling unit 500 according to the present embodiment includes an intake air flow path 514 for flowing intake air a flowing from the supercharger 100 toward the engine 300. ) Is further formed, and further includes a cooling unit body 540 in which a plurality of cooling units 510, 520, and 53 are disposed along the intake air flow path 514.

At this time, the first cooling unit 510, the first cooling unit 510, the second cooling unit 520 and the third cooling unit 530, the first slot 541, the second slot (530) for insertion respectively 542 and a third slot 543 are formed, and the first cooling unit 510, the second cooling unit 520, and the third cooling unit 530 are detachably installed in the slots 541, 542, 543. Cartridge) type.

The first cooling unit 510, the second cooling unit 520, and the third cooling unit 530 respectively include a first working fluid w1, a second working fluid w2, and a third working fluid w3. Is flowed, the first circulation passage for heat exchange with the intake air (a) supplied to the engine 300 through the first cooling unit 510, the second cooling unit 520 and the third cooling unit 530 ( 511, a second circulation passage 521, and a third circulation passage 531 are formed.

Hereinafter, a process of cooling the intake air a by the cooling unit 500 will be described in detail.

At this time, for convenience of description, the suction air (a) flowing from the rear end of the supercharger 100 to the first cooling unit 510 side in the first state suction air (a1), the third cooling unit 510 in the third Suction air (a) flowing to the cooling unit 530 in a second state Suction air (a2), suction air (a) flowing from the third cooling unit 530 to the second cooling unit 520 in a third state The intake air a3 and the intake air a flowing from the second cooling unit 520 toward the engine 300 are referred to as a fourth state intake air a4.

First, the first state suction air a1 is the suction air a compressed in the supercharger 100 and flows into the first cooling unit 510 at a temperature of about 180 ° C.

In this case, the first working fluid 510 is cooled to a temperature of about 85 ° C. in the regenerator 230 of the absorption type cooling device 200, and is supplied to the first cooling unit 510. Heat exchanged with the one-state intake air a1, heated to a temperature of about 95 ℃, and circulated to the absorption chiller 200 again.

In the process of flowing through the first cooling unit 510, the second state suction air a2 cooled to a temperature of about 160 ° C. flows into the third cooling unit 530.

At this time, the third cooling unit 530 is supplied with a third working fluid w3 cooled by heat exchange with the sea water in the auxiliary cooling device 400 to a temperature of about 35 ° C., and the third working fluid w3 is supplied to the third cooling unit 530. Heat exchanged with the second state suction air (a2), and then heated to a temperature of about 40 ℃ to 50 ℃, it is circulated to the auxiliary cooling device (400).

In the process of flowing through the third cooling unit 530, the third state suction air a3 cooled to about 40 ° C. flows into the second cooling unit 520.

The second cooling unit 520 is supplied with a second working fluid w2 cooled at a temperature of about 7 ° C. in the evaporator 210 of the absorption type cooling device 200, and the second working fluid w2 is supplied with a second working fluid w2. Heat is exchanged with the third state suction air a3 in the cooling unit 520 and heated, and then circulated to the evaporator 210 of the absorption type cooling device 200 again.

Meanwhile, in the process of flowing through the second cooling unit 520, the fourth state intake air a4 cooled to about 10 ° C. is supplied to the engine.

At this time, the temperature of the suction air (a1, a2, a3, a4) of each state and the temperature of the first working fluid (w1), the second working fluid (w2) and the third working fluid (w3) are exemplary values. Each of the above temperatures may be set differently from the present embodiment due to various factors such as the compression ratio and the compression capacity within the range in which the absorption chiller can operate.

In addition, the first working fluid (w1), the second working fluid (w2) and the third circulating in the first cooling unit 510, the second cooling unit 520, the third cooling unit 530 in the present embodiment The working fluid w3 may be provided with fresh water, but is not limited thereto.

Meanwhile, the first cooling unit 510 and the second cooling unit 520 are respectively operated as the heat source with respect to the absorption type cooling device 200 to cool the intake air a, and the third cooling unit 530 is By receiving the cooled working fluid from the auxiliary cooling device 400, the cooling of the first cooling unit 510, the second cooling unit 520, and the third cooling unit 530 may be performed independently of each other. That is, as each of the cooling units to perform the cooling independently of each other, even if an abnormality occurs in any one of the absorption type cooling device 200 and the auxiliary cooling device 400, intake air (a) Minimal cooling to may be performed.

According to the proposed embodiment, the absorption chiller for cooling the suction air of high temperature compressed by the supercharger is driven by obtaining a heat source from the suction air, so that a separate heat source for driving the absorption chiller is not required. In addition, the energy efficiency of the cooling system for cooling the intake air is increased.

In addition, in the process of supplying the high-temperature intake air compressed by the supercharger to the engine, the cooling air is cooled through a plurality of steps, thereby increasing the cooling efficiency of the intake air as compared with the case of cooling the intake air at once. There is an advantage.

6 is a view showing the configuration of an intake air cooling system according to a second embodiment of the present invention.

This embodiment differs only in the configuration of supplying the cooling fluid to the second cooling unit, and in other configurations is the same as the configuration of the first embodiment of FIGS. 3 to 5, the characteristic configuration of the present embodiment will be described below. The explanation is centered.

Referring to FIG. 6, the second working fluid W2 and the auxiliary working fluid w4 may be selectively circulated in the second cooling unit 520 according to the present embodiment.

More specifically, the intake air cooling system 1 according to the present embodiment further includes an auxiliary circulation passage 430 connected at one side to the second working fluid circulation passage 251 and at the other side to the seawater circulation passage 440. do.

In addition, the auxiliary circulation passage 430 includes a first auxiliary valve 431 and a first auxiliary valve 431 for introducing or blocking the auxiliary working fluid w4 from the seawater circulation passage 440 to the second working fluid circulation passage 251. And two auxiliary valves 432.

In addition, a first main valve 251a and a second main valve 251b are installed in the second working fluid circulation path 251 to selectively block the flow of the second working fluid W2.

When the absorption type cooler 200 of the intake air cooling system 1 according to the present embodiment operates normally, the first main valve 251a and the second main valve 251b are in an open state, and the first auxiliary valve ( 431 and the second auxiliary valve 432 is set to the closed state. In this case, the second working fluid w2 cooled in the absorption chiller 200 is supplied to the second cooling unit 520 along the second working fluid circulation path 251 to cool the intake air.

On the other hand, when the absorption chiller 200 does not perform a normal operation, that is, does not operate by an unexpected situation such as failure or damage, the first main valve 251a and the second main valve 251b are closed. The first auxiliary valve 431 and the second auxiliary valve 432 are set to the open state. In this case, external seawater formed at a temperature of any one of the auxiliary working fluid w4, for example, 0 ° C. to 25 ° C. flows to the second working fluid circulation path 251 and is supplied to the second cooling unit 520. Inhalation air (a) can be cooled.

In this case, an inner surface of the second working fluid cooling channel 251 may be further provided with a corrosion prevention structure for preventing the cooling channel 251 from being corroded by sea water.

That is, according to the present embodiment, even when the absorption type cooler 200 is broken, cooling of the intake air a may be performed not only in the third cooling unit 530 but also in the second cooling unit 520. At this time, the auxiliary working fluid (w4) passed through the second cooling unit 520 may be discharged to the outside of the vessel.

In the intake air cooling system 1 according to the present embodiment, any one of the second working fluid w2 and the auxiliary working fluid w4 is applied to the second cooling unit 520 according to the operating state of the absorption type cooling device 200. Although it is described as being flowed to cool the intake air, a configuration in which any one of the second working fluid w2 and the third working fluid w3 flows will also be included in the embodiment of the present invention.

7 is a view showing the configuration of an intake air cooling system according to a third embodiment of the present invention.

This embodiment differs only in the configuration in which the first cooling unit is installed, and in other configurations is the same as the configuration of the first embodiment of FIGS. do.

Referring to FIG. 7, in general, the temperature of the exhaust gas E discharged from the turbine 101 of the supercharger 100 is higher than the temperature of the suction air a compressed in the compressor 102.

Accordingly, the first cooling unit 510 of the intake air cooling system 1 according to the present embodiment is an exhaust manifold for exhausting the exhaust gas E from the turbine 101 of the supercharger 100 to the outside. Manifold).

In this case, the first cooling unit 510 may be formed as an economizer for allowing the first working fluid W1 flowing therein to be heated in the form of steam by the waste heat of the exhaust gas E.

Meanwhile, as the first cooling unit 510 is installed on the exhaust manifold, only the second cooling unit 520 and the third cooling unit 530 are installed in the cooling unit body 540 according to the present embodiment. It may be formed in a shape that is. However, the present invention is not limited thereto, and three or more cooling units may be installed in the cooling unit body 540.

That is, the absorption chiller 200 of the intake air cooling system 1 according to the present embodiment is operated by cooling the exhaust gas E discharged to the outside and obtaining a heat source therefrom.

According to this embodiment, there is an advantage that can maximize the temperature difference between the heat source to determine the cooling efficiency of the absorption type cooler (200).

8 is a view showing the configuration of an intake air cooling system according to a fourth embodiment of the present invention.

The present embodiment differs only in the configuration of the working fluid flow path and the configuration of the drain unit, and in other configurations is the same as the configuration of the first embodiment of FIGS. 3 to 5, the following description focuses on the characteristic configuration of this embodiment. Explain.

Referring to FIG. 8, the first working fluid passage 511 and the second working fluid passage 521 of the intake air cooling system 1 according to the present embodiment have a third working fluid circulation passage 410 and seawater circulation, respectively. The flow path 420 is connected.

In addition, first switching valves 512 are respectively provided at points of the first working fluid passage 511 and the second working fluid passage 521 to which the third working fluid circulation passage 410 and the seawater circulation passage 420 are connected. The second switching valve 513, the third switching valve 522, and the fourth switching valve 523 are installed.

That is, the first and second switching valves 512 and 512 connected to the upstream and downstream side flow paths of the third working fluid circulation passage 410 at the upstream and downstream points of the first working fluid passage 511. 513 is provided, and the third and fourth switching valves 522 and 4 are connected to the upstream and downstream sides of the seawater circulation passage 420 at the upstream and downstream sides of the second working fluid passage 521. 523 is installed.

The first switch valve 512, the second switch valve 513, the third switch valve 522 and the fourth switch valve 523 is formed of a 3-way valve, the first switch valve 512 and the second switching valve 513 selectively opens or shields the point so that the third working fluid W3 flows into the first working fluid passage 511. The third switching valve 522 and the fourth switching valve 523 selectively open or shield the point so that the auxiliary working fluid W4 flows into the second working fluid flow path 521.

That is, in the normal case, the first switching valve 512 and the second switching valve 513, the third switching valve 522 and the fourth switching valve 523 are the absorption type cooling device 200 and the first operation, respectively. The fluid flow path 511 and the second working fluid flow path 521 communicate with each other, and at the same time, the first working fluid flow path 511 and the third working fluid circulation flow path 410, the second working fluid flow path 521, and the seawater circulation The connection of the flow path 420 is cut off.

Meanwhile, when an abnormality occurs in the absorption type cooling device 200 and cooling of the compressed air a is not normally performed in the first cooling unit 510 and the second cooling unit 520, the first switching valve ( 512 and the second switching valve 513, the third switching valve 522 and the fourth switching valve 523 are the absorption type cooling device 200, the first working fluid flow path 511 and the second working fluid flow path, respectively. 521 disconnects the connection. The first switching valve 512 and the second switching valve 513, the third switching valve 522, and the fourth switching valve 523 include the first working fluid flow path 511 and the third working fluid circulation path. 410 and the second working fluid flow path 521 and the seawater circulation flow path 420 communicate with each other so that the cooling of the compressed air a is normally performed even when the absorption type cooling device 200 is not normally operated. can do.

In addition, in the absorption type cooling device 200 according to the present embodiment, the first working fluid W1 and the second operation supplied from the absorption type cooling device 200 to the first cooling unit 510 and the second cooling unit 520 are provided. A temperature sensor (not shown) for sensing the temperature of the fluid W2 and determining whether the absorption type cooling device is normally operated may be further provided.

Accordingly, the temperature sensor senses the temperatures of the first working fluid W1 and the second working fluid W2, so that the temperatures of the first working fluid W1 and the second working fluid W2 are respectively higher than the predetermined temperature. In the high case, the switching valves 511, 512, 521, and 522 block the supply of the first working fluid W1 and the second working fluid W2 to the first cooling unit 510 and the second cooling unit 520, and perform a third operation. The fluid W3 and the auxiliary working fluid W4 can be supplied. In the present embodiment, it is described that temperature sensors for measuring the temperature of the first working fluid (W1) and the second working fluid (W2) are included, but among the first working fluid (W1) and the second working fluid (W2) A configuration including only a temperature sensor for sensing the temperature of any one working fluid will also be included in the configuration of this embodiment.

On the other hand, the intake air cooling system 1 according to the present embodiment further includes a condensation water treatment device 600 for treating condensed water (Drain Water) generated in the cooling process of the compressed air (a).

The condensation water treatment device 600 is provided between the cooling unit 500 and the engine 300, and collects condensed water condensed in the compressed air (a) that is cooled while passing through the cooling unit 500. The compressed air (a) containing the condensation water is suppressed from being directly supplied to the engine (300).

By preventing the compressed air (a) containing excess condensed water from being supplied to the engine 300, corrosion of the engine 300 due to the condensed water can be suppressed.

9 is a view showing the configuration of the intake air cooling system of a vessel equipped with a central fresh water cooling device and a supercharger according to a fifth embodiment of the present invention.

Referring to FIG. 9, since the fifth embodiment may be configured to include the configuration of the first embodiment except for the auxiliary cooling device, a description of the same or similar configuration as that of the first embodiment may be omitted.

In general, the average temperature of seawater is known to be about 17 ℃.

Seawater may be circulated in the seawater circulation passage 420.

In addition, the central fresh water cooling apparatus 700 may make the temperature of the fresh water 21 ° C. when the sea water temperature is 17 ° C., and the temperature of the fresh water may be 36 ° C. or less when the sea water temperature is 32 ° C. or less. That is, it may be a heat exchange device for cooling the fresh water with sea water.

The central fresh water cooling device 700 may be designed by setting the design reference seawater temperature to 32 ° C.

That is, the design reference seawater temperature may be about 15 ° C. lower than the average temperature of the seawater.

The fifth embodiment of the present invention proposes a method of utilizing all of the cooling energy of the seawater through the central fresh water cooling device 700.

That is, although the average temperature of the sea water is about 17 ° C., the auxiliary cooling device of the first embodiment makes the temperature of the third working fluid (fresh water) at a temperature of about 35 ° C. through heat exchange with the fourth working fluid (sea water). After that, a third working fluid of about 35 ° C. was supplied to the third cooling unit 530. Accordingly, in the third cooling unit 530, the fresh water is heated to a temperature of about 40 ° C to 50 ° C as it is heat-exchanged with the second state suction air, and circulated to the auxiliary cooling device.

The difference between the first embodiment and the fifth embodiment further includes a central fresh water cooling device 700 instead of the auxiliary cooling device, the first supplement valve 710, the first supplement passage 730, and the first temperature sensor. By using (T1), the second fresh water (w3-2) having a fresh water temperature of 36 ℃ can be supplied to the cooling demand equipment (800).

In addition, the difference between the first embodiment and the fifth embodiment is that the temperature of 35 ° C. or less, for example, 3, using the second refill valve 720, the second refill passage 740, and the second temperature sensor T2. The third fresh water w3-3 having the minimum design temperature required for the cooling unit 530 (eg, 21 ° C. when the sea water temperature is 17 ° C.) may be supplied to the third cooling unit 530.

Through this, while supplying the second fresh water (w3-2) of the temperature required for the cooling demand equipment 800 to the cooling demand equipment 800, by maximizing the operating efficiency of the third cooling unit 530, the third cooling unit The cooling capacity or device size of the absorption type cooling device 200a for supplying the second working fluid to the second cooling unit 520 next to 530 can be reduced.

Hereinafter, the coupling relationship between components according to the fifth embodiment will be described in detail with reference to the seawater temperature of 17 ° C. for ease of description, but is not limited thereto.

The intake air cooling system 1 of a ship equipped with the central fresh water cooling device and the supercharger according to the fifth embodiment has a relatively smaller size or cooling capacity than the supercharger 100 and the absorption type cooling device 200 of the first embodiment. In addition to the absorption cooling device 200a, the cooling unit 500, the central fresh water cooling device 700, and the engine 300 may include a cooling request equipment 800 that requires cooling.

The cooling unit 500 for cooling the intake air a compressed in the supercharger 100 is installed between the supercharger 100 and the engine 300.

The third cooling unit 530 of the cooling unit 500 uses the third fresh water (w3-3) supplied from the central fresh water cooling device 700, the intake air (a) of the process flowing to the engine 300 It may play a role of cooling.

Among the cooling units 510, 520, 530, the third cooling unit 530 is disposed between the first cooling unit 510 and the second cooling unit 520.

The cooling request equipment 800 may be disposed in the ship.

The central fresh water cooling device 700 may be used to be provided in the vessel. In this case, the central fresh water cooling device 700 supplies the second fresh water (w3-2) to the machinery or the cooling demand equipment 800, which requires various types of cooling installed inside the ship, or to the third cooling unit 530. It may be responsible for supplying the third fresh water (w3-3).

In the fifth embodiment, the fresh water may be divided and defined into a first fresh water w3-1, a second fresh water w3-2, a third fresh water w3-3, and a fourth fresh water w3-4. .

The first fresh water w3-1 may mean fresh water discharged from the outlet 701 of the central fresh water cooling device 700 at a temperature of 21 ° C. cooled by heat exchange with sea water when the sea water temperature is 17 ° C.

The fourth fresh water (w3-4) is the second fresh water (w3-2) and the third fresh water (w3) respectively heated up through heat exchange in the third cooling unit (530) of the cooling demand equipment 800 and the cooling unit 500 -3) may refer to the fresh water returned to the inlet 702 of the central fresh water cooling device 700, that is, returned to the central fresh water cooling device 700.

The second fresh water w3-2 has a relatively high temperature of the fourth fresh water w3-4 through the first supplementary valve 710 and the first supplementary flow passage 730, and the first fresh water w3- having a fresh water temperature of 21 ° C. 1) may refer to fresh water adjusted to a setting temperature of 36 ° C. of the cooling demand equipment 800 to correspond to the ratio of replenishment or non-replenishment, that is, the first flow rate replenishment.

The third fresh water w3-3 is the rate at which the fourth fresh water w3-4 through the second supplementary valve 720 and the second supplementary flow passage 740 is replenished or not replenished to the first fresh water w3-1. That is, it may mean fresh water adjusted to a minimum design temperature of 21 ° C. of the third cooling unit 530 corresponding to the second flow rate replacement rate.

If the fourth fresh water w3-4 is not replenished to the first fresh water w3-1 according to the opening / closing control for each flow direction of the second supplementary valve 720, the third fresh water w3-3 The same temperature as the first fresh water w3-1 may be supplied to the third cooling unit 530 at 21 ° C.

Hereinafter, the coupling relationship between the flow path and the related configuration will be described.

At the outlet 701 of the central fresh water cooling device 700, a fresh water discharge passage 751 serving as a discharge path of the first fresh water w3-1 extends to the first branch point C1.

The fresh water discharge passage 751 is provided with a second replenishment valve 720 in the form of an electronically controllable 3-way valve.

Based on the opposite side of the fresh water discharge passage 751, the unit inlet passage 752 serving as an inflow path of the third fresh water w3-3 between the first branch point C1 and the inlet of the third cooling unit 530. Is provided, and an object inlet passage 753 is provided between the first branch point C1 and the inlet of the cooling demand device 800 to serve as an inflow path for the second fresh water w3-2.

The first replenishment valve 710 of the 3-way valve type, which is electronically controllable, is provided in the object inlet passage 753 after the first branch point C1.

A first temperature sensor T1 connected to the first supplement valve 710 is installed in the object inlet passage 753 after the first supplement valve 710.

Here, the first temperature sensor (T1) measures the temperature of the second fresh water (w3-2) flowing along the target inlet flow path (753), the temperature value required to control the valve operation of the first supplementary valve 710 To serve as a valve controller (not shown).

In addition, the valve operation of the first supplementary valve 710 means supplying or interrupting the flow, or selectively switching the flow direction so that the second fresh water w3-2 is set at a temperature of 36 ° C. of the first temperature sensor T1. It may mean a role to be adjusted to the cooling demand equipment (800).

A second temperature sensor T2 connected to the second supplementary valve 720 is installed in the unit inlet passage 752 after the first branch point C1.

Here, the second temperature sensor (T2) measures the temperature of the third fresh water (w3-3) flowing along the unit inlet flow path (752), the temperature value required to control the valve operation of the second supplementary valve 720 To serve as a valve controller (not shown).

In addition, the valve operation of the second supplementary valve 720 means supplying or interrupting the flow, or selectively switching the flow direction, so that the third fresh water w3-3 is set at the setting temperature of the second temperature sensor T2, that is, The minimum design temperature of the third cooling unit 530 may be adjusted to 21 ° C. so as to flow into the third cooling unit 530.

The unit outlet passage 754 is provided between the outlet of the third cooling unit 530 where the third fresh water w3-3, which has completed heat exchange, and the confluence point C2.

The target object outlet passage 755 is provided between the outlet of the third cooling unit 530 where the second fresh water w3-3 having completed the heat exchange and the confluence point C2 is disposed.

The oil passage 756 is provided between the joining point C2 and the inlet of the fresh water circulation pump 757.

Between the outlet of the fresh water circulation pump 757 and the inlet 702 of the central fresh water cooling apparatus 700, a fresh water inflow passage 758 serving as an inflow path of the fourth fresh water w3-4 is provided.

The second and third branch points C3 and C4 are sequentially installed in the fresh water inflow passage 758 after the fresh water circulation pump 757.

The first supplementary flow passage 730 is piped between the second branch point C3 of the fresh water inflow passage 758 and the first supplementary valve 710.

A second supplementary flow passage 740 is piped between the third branch point C4 of the fresh water inflow passage 758 and the second supplementary valve 720.

Hereinafter, the operation method of the fifth embodiment will be described.

The second supplement valve 720 may block the second supplement passage 740 and maintain the fresh water discharge passage 751 in an open state.

Accordingly, when the seawater temperature is 17 ° C, the first fresh water w3-1 may have a fresh water temperature of 21 ° C by the central fresh water cooling device 700.

The first fresh water w3-1 having a fresh water temperature of 21 ° C. is discharged from the outlet 701 of the central fresh water cooling device 700 and reaches the first branch point C1 via the second supplementary valve 720. .

The first fresh water w3-1 branched and flowing at the first branch point C1 flows along the object inlet flow path 753 to reach the first supplementary valve 710.

At this time, the first supplementary valve 710 is the first flow rate supplement ratio (the fourth relatively high temperature so that the temperature value measured by the first temperature sensor T1 of the object inlet passage 753 reaches the set temperature 36 ° C). And the fourth fresh water w3-4 is mixed with the first fresh water w3-1 so that the fresh water w3-4 is replenished with the first fresh water w3-1 having a fresh water temperature of 21 ° C. A second fresh water (w3-2) having a temperature of 36 ° C is made.

The second fresh water (w3-2) having a fresh water temperature of 36 ° C. may be supplied to the cooling demand equipment 800 along the object inlet flow path 753 and used to cool the cooling demand equipment 800.

The second fresh water w3-2 heated up after the use flows toward the confluence point C2 along the object outlet passage 755.

On the other hand, in the first fresh water w3-1 having reached the first branch point C1 at a fresh water temperature of 21 ° C, the second supplementary valve 720 blocks the second supplementary flow passage 740, and the fresh water discharge passage ( Since 751) is maintained in an open state, it may flow along the unit inlet flow passage 752 at the rear end of the first branch point C1 to become the third fresh water w3-3 having the same fresh water temperature of 21 ° C.

The third fresh water w3-3 having a fresh water temperature of 21 ° C. may be supplied to the third cooling unit 530 along the unit inlet passage 752 and used to cool the third cooling unit 530.

The third fresh water w3-3 heated up after the use flows along the unit outlet passage 754 toward the confluence point C2.

The third fresh water w3-3 and the second fresh water w3-2 that have reached the confluence point C2 are joined to form a high temperature fourth fresh water w3-4.

The high temperature fourth fresh water w3-4 is supplied to the fresh water circulation pump 757 along the oil mixing passage 756.

The fresh water circulation pump 757 may supply the high temperature fresh water w3-4 toward the first supplement channel 730, the second supplement channel 740, and the fresh water inlet channel 758.

That is, the high temperature fresh water w3-4 may flow along the first supplementary flow passage 730 when the first supplementary valve 710 is opened to correspond to the first flow rate replenishment ratio, and the second supplementary fresh water w3-4 may be used. When the valve 720 is opened to correspond to the second flow replenishment ratio, the valve 720 may flow along the first replenishment flow passage 730, and the remaining high temperature fourth fresh water w 3-4 may move the fresh water inflow passage 758. Accordingly, it may be recovered toward the central fresh water cooling device 700.

If the sea water temperature is 17 ° C. or less, the central fresh water cooling apparatus 700 may discharge a fresh water temperature of 21 ° C. or less toward the fresh water discharge passage 751.

In this case, the second temperature sensor T2 detects that the fresh water temperature is 21 ° C. or lower, and eventually, the second flow rate replenishment ratio of the second supplementary valve 720 (the fourth fresh water w3-4 having a relatively high temperature is fresh water temperature). The ratio of the replenishment to the first fresh water w3-1 of 21 ° C. or lower], and the fourth fresh water w3-4 is mixed with the first fresh water w3-1 and the second fresh water having a fresh water temperature of 21 ° C. ( w3-2).

The fourth fresh water w3-4 having a high temperature may be first fresh water w3-1 by heat exchange of the central fresh water cooling device 700.

This process is repeated, while cooling the cooling request equipment 800 together with the suction air (a) corresponding to the required temperature for each cooling request equipment 800 together with the suction air (a) of the ship, the relative absorption chiller (200a) Cooling capacity or device size can be reduced.

Although the above has been illustrated and described with respect to the preferred invention of the present invention, the invention is not limited to the specific embodiments described above, it is common in the art to which the invention belongs without departing from the spirit of the invention claimed in the claims. Various modifications may be made by those skilled in the art, and these modifications should not be individually understood from the technical spirit or the scope of the present invention.

100: supercharger 200, 200a: absorption chiller
210: evaporator 220: absorber
230: regenerator 240: condenser
300: engine 400: auxiliary cooling device
510: first cooling unit 520: second cooling unit
530: third cooling unit 600: condensation water treatment device
700: central fresh water cooling device 800: cooling request equipment

Claims (5)

In the intake air cooling system of a ship,
A supercharger including a front end into which the intake air is introduced and a rear end to supply the compressed intake air to the engine by using a part of the exhaust gas generated in the engine to compress the intake air;
Heat exchange with the intake air discharged from the supercharger to cool at least one of the intake air compressed in the supercharger and the exhaust gas passing through the supercharger, and disposed in accordance with the intake air or the flow of the exhaust gas. A first cooling unit through which the first working fluid is circulated, a second cooling unit positioned behind the first cooling unit to circulate the second working fluid to exchange heat with the intake air, and a first cooling unit and the first cooling unit. A cooling unit including a third cooling unit disposed between the two cooling units;
An absorption type cooling device that receives a heat source from a working fluid circulated through the cooling unit; And
And a central fresh water cooling device for providing fresh water at different fresh water temperatures to the cooling demand facilities provided in the second cooling unit and the vessel.
Intake air cooling system of ship with central fresh water cooling system and supercharger installed.
The method of claim 1,
A fresh water discharge passage coupled between the outlet of the central fresh water cooling device and the first branch point and serving as a discharge path of the first fresh water;
A second supplementary valve installed in the fresh water discharge passage;
A unit inlet flow passage installed between the first branch point and the inlet of the third cooling unit and serving as an inflow path of the third fresh water;
A target inlet flow passage installed between the first branch point and the inlet of the cooling demand equipment and serving as an inflow path of the second fresh water;
A first replenishment valve installed at the object inlet flow passage after the first branch point;
A first temperature sensor installed in an object inlet flow passage to a rear end of the first supplementary valve and connected to the first supplementary valve;
And a second temperature sensor installed in the unit inlet flow passage after the first branch point and connected to the second supplementary valve.
Intake air cooling system of ship with central fresh water cooling system and supercharger installed.
3. The method of claim 2,
A unit outlet passage installed between an outlet and a confluence point of the third cooling unit through which the third fresh water is discharged;
A target outlet flow passage installed between the outlet of the third cooling unit through which the second fresh water is discharged and the confluence point;
An oil mixture flow passage installed between the contention point and the inlet of the fresh water circulation pump;
A fresh water inflow passage which is an inflow path of a fourth fresh water between an outlet of the fresh water circulation pump and an inlet of the central fresh water cooling device;
A second branch point and a third branch point installed in the fresh water inflow passage after the fresh water circulation pump;
A first supplementary flow passage installed between the second branch point of the fresh water inflow passage and the first supplementary valve;
A second supplementary flow passage installed between the third branch point of the fresh water inflow passage and the second supplementary valve;
Intake air cooling system of ship with central fresh water cooling system and supercharger installed.
The method of claim 3, wherein
The second fresh water,
A setting temperature of 36 ° C. of the cooling demand equipment corresponding to a rate at which the relatively hot fourth fresh water through the first replenishment valve and the first replenishment flow passage is replenished or not replenished with the fresh water at a fresh water temperature of 21 ° C. It is characterized in that the fresh water adjusted to
Intake air cooling system of ship with central fresh water cooling system and supercharger installed.
The method of claim 3, wherein
The third fresh water,
The fourth fresh water through the second replenishment valve and the second replenishment passage is fresh water adjusted to a minimum design temperature 21 ° C. of the third cooling unit corresponding to a ratio of replenishing or not replenishing the first fresh water. Characterized
Intake air cooling system of ship with central fresh water cooling system and supercharger installed.

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