JP2013180625A - Exhaust heat recovery type ship propulsion device, and operation method therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an exhaust heat recovery type ship propulsion device capable of effectively utilizing exhaust heat of engine cooling water used to cool an internal combustion engine as a main engine for propulsion of a ship, and improving the exhaust heat recovery efficiency.SOLUTION: An engine cooling water circulation flow passage 61 for circulating engine cooling water, and one of a plurality of heat exchangers 22, 23 are connected to each other on the upstream side of a fresh water generator via an exhaust heat recovery flow passage 62. The engine cooling water circulation flow passage 61 and another heat exchanger separate from the one of the plurality of heat exchangers 22, 23 are connected to each other on the downstream side of the fresh water generator via another exhaust heat recovery flow passage 63 separate from the exhaust heat recovery circuit 62.

Description

  The present invention relates to an exhaust heat recovery type ship propulsion apparatus in which an exhaust heat recovery power generation apparatus is installed for exhaust heat recovery of a diesel engine (internal combustion engine) as a main engine for ship propulsion.

  On the other hand, using the exhaust heat of the jacket cooling water that has cooled the jacket of the diesel engine, the seawater taken from outside the ship is heated, and the heated seawater is evaporated in the vacuum chamber to create fresh water (flash) For example, a device disclosed in Patent Document 1 is known.

JP 2004-306807 A

  Here, conventionally, the jacket cooling water that has cooled the jacket of the diesel engine 3 has, for example, a jacket cooling water outlet temperature measured by a temperature sensor denoted by reference numeral 77 in FIG. 6 at a predetermined temperature (for example, 85 ° C.). 6 so that the inlet temperature of the jacket cooling water measured by the temperature sensor denoted by reference numeral 78 in FIG. 6 is adjusted (maintained) to a predetermined temperature (for example, 65 ° C.). The first three-way valve denoted by reference numeral 91 and the second three-way valve denoted by reference numeral 73 in FIG. 6 were switched (adjusted) as necessary.

However, in the case shown in FIG. 6, the heat of the jacket cooling water that has cooled the jacket of the diesel engine 3 is taken from outside the ship via the central cooler 93 that constitutes the jacket cooling (clean) water circulation (cooling) flow path 92. As a result, the heat of the jacket cooling water that has cooled the jacket of the diesel engine 3 is not effectively used.
In addition, the code | symbols 71, 74, and 75 in FIG. 6 have each shown the jacket cooling water circulation pump, the bypass flow path, and the fresh water generator.

  The present invention has been made to solve the above-described problems, and can effectively use exhaust heat of engine cooling water that has cooled an internal combustion engine as a main engine for propulsion of a ship, thereby improving exhaust heat recovery efficiency. It is an object of the present invention to provide an exhaust heat recovery type ship propulsion device that can be made to operate.

The present invention employs the following means in order to solve the above problems.
The exhaust heat recovery type ship propulsion device according to the first aspect of the present invention heats seawater taken from the outside of the ship using exhaust heat from the internal combustion engine of the ship and engine cooling water that cools the internal combustion engine. And a plurality of evaporative fresh water generators that evaporate heated seawater in a vacuum chamber to produce fresh water, and a plurality of heat mediums that are installed in series in the circulation path of the working medium, and that heat the working medium with different temperatures. A heat exchanger, a turbine driven by the working medium evaporated by the heat exchanger, a generator for generating electric power by the rotational output of the turbine, and a condenser for condensing the working medium that has passed through the turbine And an engine cooling water circulation passage for circulating the engine cooling water, and one of the plurality of heat exchangers is the fresh water generation device. The engine cooling water circulation flow path and a heat exchanger different from one of the plurality of heat exchangers are connected to the fresh water generation apparatus on the upstream side of the apparatus via an exhaust heat recovery flow path. It is connected to the downstream side of the apparatus via an exhaust heat recovery flow path different from the exhaust heat recovery circuit.

According to the exhaust heat recovery type ship propulsion device according to the first aspect of the present invention, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main engine for propulsion of the ship heats the working medium that passes through the evaporator. In other words, it is not thrown away into the seawater that is taken in from the outside of the ship and discharged out of the ship through the central cooler as in the prior art.
Thereby, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main propulsion engine of the ship can be effectively used, and the exhaust heat recovery efficiency can be improved.
In addition, by adjusting the flow rate of the engine cooling water flowing through the exhaust heat recovery flow path provided on the upstream side of the fresh water generator, and adjusting the temperature of the engine cooling water guided to the fresh water generator, Water production capacity [ton / day] can be easily adjusted.
Further, by adjusting the flow rate of the engine cooling water flowing through the exhaust heat recovery passage provided downstream of the fresh water generator, the temperature [° C.] of the engine cooling water returned to the internal combustion engine as the main engine for marine propulsion Can be adjusted easily.

  The exhaust heat recovery type ship propulsion device according to the second aspect of the present invention heats seawater taken from the outside of the ship by using exhaust heat from the internal combustion engine of the ship and engine cooling water that cools the internal combustion engine. And a plurality of evaporative fresh water generators that evaporate heated seawater in a vacuum chamber to produce fresh water, and a plurality of heat mediums that are installed in series in the circulation path of the working medium, and that heat the working medium with different temperatures. A heat exchanger, a turbine driven by the working medium evaporated by the heat exchanger, a generator for generating electric power by the rotational output of the turbine, and a condenser for condensing the working medium that has passed through the turbine And an engine cooling water circulation passage for circulating the engine cooling water, and one of the plurality of heat exchangers is the fresh water generation device. It is connected via the exhaust heat recovery passage upstream of the location.

According to the exhaust heat recovery type ship propulsion device according to the second aspect of the present invention, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main engine for propulsion of the ship heats the working medium that passes through the evaporator. In other words, it is not thrown away into the seawater that is taken in from the outside of the ship and discharged out of the ship through the central cooler as in the prior art.
Thereby, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main propulsion engine of the ship can be effectively used, and the exhaust heat recovery efficiency can be improved.
In addition, by adjusting the flow rate of the engine cooling water flowing through the exhaust heat recovery flow path provided on the upstream side of the fresh water generator, and adjusting the temperature of the engine cooling water guided to the fresh water generator, Water production capacity [ton / day] can be easily adjusted.

  The exhaust heat recovery type ship propulsion device according to the third aspect of the present invention heats seawater taken from the outside of the ship using exhaust heat from the internal combustion engine of the ship and engine cooling water that cools the internal combustion engine. And a plurality of evaporative fresh water generators that evaporate heated seawater in a vacuum chamber to produce fresh water, and a plurality of heat mediums that are installed in series in the circulation path of the working medium, and that heat the working medium with different temperatures. A heat exchanger, a turbine driven by the working medium evaporated by the heat exchanger, a generator for generating electric power by the rotational output of the turbine, and a condenser for condensing the working medium that has passed through the turbine And an exhaust heat recovery type marine vessel propulsion device comprising: an engine cooling water circulation passage for circulating the engine cooling water; and one of the heat exchangers of the fresh water generator. It is connected via the exhaust heat recovery channel in the flow side.

According to the exhaust heat recovery type ship propulsion device according to the third aspect of the present invention, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main engine for propulsion of the ship heats the working medium that passes through the evaporator. In other words, it is not thrown away into the seawater that is taken in from the outside of the ship and discharged out of the ship through the central cooler as in the prior art.
Thereby, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main propulsion engine of the ship can be effectively used, and the exhaust heat recovery efficiency can be improved.
Further, by adjusting the flow rate of the engine cooling water flowing through the exhaust heat recovery flow path provided on the downstream side of the fresh water generator, the temperature [° C.] of the engine cooling water returned to the internal combustion engine as the main propulsion unit for the ship Can be adjusted easily.

  A ship according to the present invention includes any one of the above-described exhaust heat recovery type ship propulsion devices.

  According to the ship according to the present invention, since any one of the above-described exhaust heat recovery type ship propulsion devices is provided, the exhaust heat recovery efficiency can be improved and the energy saving property can be improved.

  The operation method of the exhaust heat recovery type ship propulsion device according to the present invention uses the exhaust heat of the engine cooling water for cooling the internal combustion engine of the ship and the internal combustion engine to heat seawater taken from the outside of the ship, An evaporative fresh water generator that evaporates heated seawater in a vacuum chamber to create fresh water, and a plurality of heats that are installed in series in the circulation path of the working medium and that evaporate the working medium with different heat mediums. An exchanger, a turbine driven by the working medium evaporated by the heat exchanger, a generator for generating electric power by the rotational output of the turbine, a condenser for condensing the working medium that has passed through the turbine, A method for operating an exhaust heat recovery type ship propulsion apparatus comprising: an engine coolant circulation path for circulating the engine coolant; and an exhaust heat recovery path connecting the plurality of heat exchangers. There, among the exhaust heat of the engine cooling water, in the fresh water generator, the exhaust heat other than heat necessary for the request desalination amount was so recovered in the heat exchanger.

According to the operation method of the exhaust heat recovery type ship propulsion device according to the present invention, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main propulsion unit of the ship heats the working medium passing through the evaporator. It is used and is not thrown away into the seawater that is taken in from the outside of the ship and discharged out of the ship through the central cooler as in the past.
Thereby, the exhaust heat of the engine cooling water that has cooled the internal combustion engine as the main propulsion engine of the ship can be effectively used, and the exhaust heat recovery efficiency can be improved.

  According to the exhaust heat recovery type ship propulsion device according to the present invention, exhaust heat of engine cooling water that has cooled an internal combustion engine as a main engine for ship propulsion can be effectively used, and exhaust heat recovery efficiency can be improved. There is an effect that can be done.

1 is a schematic configuration diagram of an exhaust heat recovery type ship propulsion device according to an embodiment of the present invention. It is a schematic block diagram of the engine (jacket) cooling water circulation flow path which comprises the waste heat recovery type | formula ship propulsion apparatus which concerns on one Embodiment of this invention. It is a figure which expands and shows the principal part of FIG. It is a schematic block diagram of the fresh water generator which concerns on one Embodiment of this invention. It is a graph which shows the relationship between the temperature of an engine (jacket) cooling water, and the fresh water generation capacity of a fresh water generator. It is a schematic block diagram of the conventional engine (jacket) cooling water circulation flow path.

Hereinafter, an exhaust heat recovery type ship propulsion device according to an embodiment of the present invention will be described with reference to FIGS. 1 to 5.
As shown in FIG. 1, an exhaust heat recovery type ship propulsion apparatus 1 according to the present embodiment is configured by installing an exhaust heat recovery power generation apparatus 2 for recovering exhaust heat of a diesel engine 3 as a main propulsion apparatus for a ship. is there.
The exhaust heat recovery power generation device 2 has two organic fluid paths of a first cycle 4 and a second cycle 5. The first cycle 4 includes a first circulation pump 11, a first flow rate adjustment valve (not shown), a high-pressure evaporator 12, a power turbine 13, and a condenser 14. The second cycle 5 includes a second circulation pump 21, a second flow rate adjustment valve (not shown), a low pressure evaporator 22, a low pressure heater 23, a power turbine 13, and a condenser 14. Yes. A power generator 13 is connected to the power turbine 13 via a speed reducer 24.

  The first cycle 4 and the second cycle 5 are common passages in the piping from the power turbine 13 to the condenser 14, and are separate passages in the piping from the condenser 14 to the power turbine 13. The organic fluid (working medium) existing in the first cycle 4 is circulated in the first cycle 4 by the first circulation pump 11, and the organic fluid (working medium) existing in the second cycle 5 is the second circulation pump 21. To circulate in the second cycle 5. The pressure and flow rate of the first cycle 4 are adjusted by the first flow rate adjustment valve, and the pressure and flow rate of the second cycle 5 are adjusted by the second flow rate adjustment valve.

  As the organic fluid flowing through the organic fluid path of the first cycle 4 and the second cycle 5, low molecular hydrocarbons such as isopentane, butane, propane, R134a and R245fa used as refrigerants, and the like can be used. The organic fluid existing in the first cycle 4 sequentially passes through the first circulation pump 11, the high-pressure evaporator 12, the power turbine 13, and the condenser 14 and circulates while repeating the phase change. The organic fluid existing in the second cycle 5 sequentially passes through the second circulation pump 21, the low-pressure evaporator 22, the low-pressure heater 23, the power turbine 13, and the condenser 14 and circulates while repeating the phase change.

  The high-pressure evaporator 12 is supplied from the first circulation pump 11 by the heat collected by the first air cooler 32 and the exhaust gas economizer (exhaust gas heat exchanger) 33 by the heat transfer water flowing through the first exhaust heat recovery flow path 31. It is a heat exchanger that heats the liquid organic fluid and changes the organic fluid into a gas phase. The first air cooler 32 cools the compressed air discharged from the turbocharger (supercharger) 34 of the diesel engine 3 by exchanging heat with the heat transfer water. Further, the exhaust gas economizer 33 cools the exhaust gas discharged from the diesel engine 3 by exchanging heat with the heat transfer water.

The low-pressure evaporator 22 is a heat exchanger that heats the organic fluid sent from the second circulation pump 21 by the heat of the jacket cooling water guided through the third exhaust heat recovery flow path 63.
The low-pressure heater 23 is a heat exchanger that heats the organic fluid that has passed through the low-pressure evaporator 22 by the heat of the jacket cooling water guided through the second exhaust heat recovery flow path 62.

  An organic fluid evaporated by the high-pressure evaporator 12 in the first cycle 4 and an organic fluid evaporated by the low-pressure evaporator 22 in the second cycle 5 are introduced into the power turbine 13. The power turbine 13 is rotationally driven by the heat drop (enthalpy drop) of the organic fluid evaporated by the high-pressure evaporator 12 and the heat drop (enthalpy drop) of the organic fluid evaporated by the low-pressure evaporator 22.

  The rotational power of the power turbine 13 is transmitted to the generator 25, and electric power is obtained by the generator 25. The electric power obtained by the generator 25 is supplied to the inboard system via a power line (not shown). The organic fluid that has passed through the power turbine 13 is cooled by seawater in the condenser 14 to be condensed and liquefied. The condensed and liquefied organic fluid is sent to the high-pressure evaporator 12 by the first circulation pump 11 and sent to the low-pressure evaporator 22 by the second circulation pump 21.

Next, the first exhaust heat recovery flow path 31 will be described.
The first exhaust heat recovery flow path 31 is a closed circuit, and an exhaust heat recovery pump 41 for circulating the heat transfer water is provided. The exhaust heat recovery pump 41 circulates the heat transfer water so as to exchange heat with the first air cooler 32, the exhaust gas economizer 33, and the high-pressure evaporator 12. The heat transfer water cooled by the high-pressure evaporator 12 is collected in the atmospheric pressure drain tank 42 via a pressure reducing valve (not shown). The flow rate of the heat transfer water sent from the exhaust heat recovery pump 41 to the high-pressure evaporator 12 is adjusted by a water supply control valve 43 provided in the first exhaust heat recovery flow path 31.

  The heat medium water inlet temperature of the high-pressure evaporator 12 is, for example, about 196 ° C., and the heat medium water outlet temperature is, for example, about 85 ° C. In the high pressure evaporator 12, the organic fluid is evaporated by the heat transfer water.

  A composite boiler 44 is provided on the high temperature side (exhaust gas flow upstream side) of the exhaust gas economizer 33. The composite boiler 44 includes a steam drum 45, a circulation pump 46, and an evaporator 47. The water in the steam drum 45 is sent to the evaporator 47 where it is evaporated by exchanging heat with the exhaust gas.

  The vapor evaporated in the evaporator 47 is guided to the vapor drum 45. The steam staying above the steam drum 45 is guided to an auxiliary device (oil heater, tank heating, etc.) and then collected in the atmospheric pressure drain tank 42. The water level in the steam drum 45 is adjusted by the steam drum level control valve 48, and water is supplied from the atmospheric pressure drain tank 42 to the steam drum 45 by the boiler feed pump 49.

Next, the operation of the exhaust heat recovery power generator 2 will be described.
The air compressed by the turbocharger 34 of the diesel engine 3 is cooled by the first air cooler 32 and the second air cooler 50. At this time, the heat transfer water in the first exhaust heat recovery flow path 31 flowing in the first air cooler 32 is heated by the compressed air, whereby the heat transfer water recovers heat from the compressed air. The heat transfer water temperature after heat recovery by the first air cooler 32 is, for example, about 142 ° C.

  The exhaust gas discharged from the diesel engine 3 is cooled by the evaporator 47 of the composite boiler 44 and the exhaust gas economizer 33. At this time, the heat transfer water in the first exhaust heat recovery flow path 31 flowing through the exhaust gas economizer 33 is heated by the exhaust gas, so that the heat transfer water recovers heat from the exhaust gas. The heat transfer water temperature after heat recovery by the exhaust gas economizer 33 is, for example, about 196 ° C.

  The heat transfer water that has recovered the exhaust heat by the first air cooler 32 and the exhaust gas economizer 33 and has reached a high temperature is guided to the high-pressure evaporator 12, while the exhaust heat is recovered by the first air cooler 32 and the temperature is high. A part of the heat transfer water thus formed is guided to the low-pressure evaporator 22 and exchanges heat with the organic fluid circulating in the first cycle 4 and the second cycle 5. The organic fluid is heated and evaporated by the sensible heat of the heat transfer water in the high-pressure evaporator 12 and the low-pressure evaporator 22.

  The organic fluid which has evaporated and becomes high enthalpy is guided to the power turbine 13, and the power turbine 13 is rotationally driven by the heat drop. The generator 25 obtains the rotational output of the power turbine 13 and generates power. The organic fluid (gas phase) that has finished its work in the power turbine 13 is led to the condenser 14 and cooled by cooling water such as seawater to be condensed and liquefied.

  Now, in the exhaust heat recovery type ship propulsion apparatus 1 according to the present embodiment, the jacket cooling (fresh water) circulation (cooling) flow path 61 of the diesel engine 3 shown in FIG. 2 and the exhaust heat recovery power generation apparatus 2 shown in FIG. The low-pressure evaporator 22 that is configured is connected via the second exhaust heat recovery passage 62, and the jacket cooling (fresh) water circulation (cooling) passage 61 of the diesel engine 3 shown in FIG. 2 and the exhaust shown in FIG. A low-pressure heater 23 constituting the heat recovery power generation device 2 is connected via a third exhaust heat recovery flow path 63.

The jacket cooling water circulation passage 61 includes a jacket cooling water circulation pump 71, a first three-way valve 72, a second three-way valve 73, a bypass passage 74, a fresh water generator 75, and a third three-way valve 76. ing.
2 indicates a temperature sensor for measuring the outlet temperature of the jacket cooling water flowing out from the diesel engine 3, and reference numeral 78 in FIG. 2 indicates the inlet temperature of the jacket cooling water flowing into the diesel engine 3. The temperature sensor which measures is shown.

The fresh water generator 75 uses the exhaust heat of the jacket cooling water guided through the bypass channel 74, and uses the seawater supply channel 81 and the seawater supply pump (ejector pump) 82 shown in FIG. It is an evaporation type (flash type) fresh water generator that heats the seawater taken from the inside and evaporates the heated seawater in the vacuum chamber 83 to produce fresh water.
The fresh water created by the fresh water generator 75 is guided to a fresh water (miscellaneous water) tank (not shown) via the water receiving tray 84, the fresh water extraction flow path 85, and the fresh water pump 86.

The inlet end (one end) of the second exhaust heat recovery flow path 62 is connected to the first three-way valve 72 located on the downstream side of the jacket cooling water circulation pump 71, and the outlet end ( The other end is connected to a jacket cooling water circulation passage 61 located between the first three-way valve 72 and the second three-way valve 73.
The inlet end (one end) of the bypass flow path 74 is connected to the second three-way valve 73, and the outlet end (other end) of the bypass flow path 74 is between the second three-way valve 73 and the third three-way valve 76. Is connected to the jacket cooling water circulation passage 61 located at
The inlet end (one end) of the third exhaust heat recovery flow path 63 is connected to the third three-way valve 76, and the outlet end (other end) of the third exhaust heat recovery flow path 63 is connected to the third three-way valve 76. It is connected to the jacket cooling water circulation channel 61 located on the downstream side.

  Here, as shown in FIG. 5, the fresh water generation capacity [ton / day] of the fresh water generator 75 depends on the temperature [° C.] of the jacket cooling water guided to the fresh water generator 75 via the bypass flow path 74. Change. That is, when the temperature of the jacket cooling water guided to the fresh water generator 75 via the bypass flow path 74 is high, the fresh water generation capacity of the fresh water generator 75 increases and is guided to the fresh water generator 75 via the bypass flow path 74. When the temperature of the jacket cooling water is low, the fresh water generation capacity of the fresh water generator 75 is low.

In other words, as the first three-way valve 72 is switched (adjusted) and the flow rate of the jacket cooling water guided to the low-pressure evaporator 22 through the second exhaust heat recovery flow path 62 increases, the low-pressure evaporator 22 increases. In this case, the heat of the jacket cooling water taken (given) by the organic fluid flowing through the second cycle 5 increases, and the temperature of the jacket cooling water guided to the fresh water generator 75 via the bypass flow path 74 becomes lower. The water production capacity of the water device 75 is lowered.
On the other hand, as the first three-way valve 72 is switched (adjusted) and the flow rate of the jacket cooling water led to the low-pressure evaporator 22 through the second exhaust heat recovery passage 62 decreases, The heat of the jacket cooling water taken (given) by the organic fluid flowing through the second cycle 5 is reduced, and the temperature of the jacket cooling water led to the fresh water generator 75 via the bypass flow path 74 is increased, and the fresh water is generated. The water production capacity of the device 75 is increased.

For example, when the outlet temperature of the jacket cooling water measured by the temperature sensor 77 is 70 ° C. and the fresh water generation device 75 needs to produce 20 tons of fresh water per day, the second exhaust heat recovery flow path 62 is used. The jacket cooling water guided to the low-pressure evaporator 22 has a flow rate of 0 (zero), and all the jacket cooling water flowing out from the diesel engine 3 is guided to the fresh water generator 75 via the bypass flow path 74. .
Further, when all of the jacket cooling water returned to the jacket cooling water circulation passage 61 via the bypass passage 74 is returned to the diesel engine 3 without passing through the third exhaust heat recovery passage 63, the temperature When the inlet temperature of the jacket cooling water measured by the sensor 78 is higher than a predetermined temperature (for example, 65 ° C.), the third three-way valve 76 is switched (adjusted), and the third exhaust heat recovery flow path 63 is switched. The flow rate of the jacket cooling water led to the low-pressure heater 23 via the temperature is adjusted, and the temperature of the jacket cooling water returned to the diesel engine 3, that is, the inlet temperature of the jacket cooling water measured by the temperature sensor 78 is a predetermined temperature. (For example, 65 ° C.).

According to the exhaust heat recovery type ship propulsion device 1 according to the present embodiment, the exhaust heat of the jacket cooling water that has cooled the diesel engine 3 as the main engine for propulsion of the ship passes through the low-pressure evaporator 22 and the low-pressure heater 23. It is used to heat the organic fluid and is not thrown away into the seawater taken from outside the ship and discharged outside the ship via the central cooler 93 as in the prior art.
Thereby, the exhaust heat of the jacket cooling water which cooled the diesel engine 3 as a main engine for ship propulsion can be used effectively, and the exhaust heat recovery efficiency can be improved.
Further, by adjusting the flow rate of the jacket cooling water flowing through the second exhaust heat recovery flow path 62 provided on the upstream side of the fresh water generator 75, the temperature of the jacket cooling water led to the fresh water generator 75 is adjusted. The fresh water generation capacity [ton / day] in the fresh water generator 75 can be easily adjusted.
Furthermore, the jacket cooling water returned to the diesel engine 3 as the main propulsion unit of the ship is adjusted by adjusting the flow rate of the jacket cooling water flowing through the third exhaust heat recovery flow path 63 provided on the downstream side of the fresh water generator 75. The temperature [° C.] can be easily adjusted.

In addition, this invention is not limited to embodiment mentioned above, It can also implement by changing and changing suitably as needed.
For example, in the above-described embodiment, the second exhaust heat recovery flow path 62 and the third exhaust heat recovery flow path 63 are described as a specific example, but the second exhaust heat recovery flow path 62 is provided. Alternatively, only one of the third exhaust heat recovery flow paths 63 may be provided.

1 Waste heat recovery type ship propulsion device 3 Diesel engine (internal combustion engine)
5 Second cycle (circulation route)
13 Power turbine (turbine)
14 Condenser 22 Low-pressure evaporator (heat exchanger)
23 Low pressure heater (heat exchanger)
25 Generator 61 Engine cooling water circulation passage 62 Second exhaust heat recovery passage (exhaust heat recovery passage)
63 3rd exhaust heat recovery flow path (exhaust heat recovery flow path)
75 Fresh water generator 83 Vacuum chamber

Claims (5)

A ship's internal combustion engine;
An evaporative freshwater generator that heats seawater taken from outside the ship using exhaust heat of engine cooling water that cools the internal combustion engine, and evaporates the heated seawater in a vacuum chamber to create fresh water; ,
A plurality of heat exchangers installed in series in the circulation path of the working medium, each of which evaporates the working medium with a heat medium having a different temperature;
A turbine driven by the working medium evaporated by the heat exchanger;
A generator for generating electricity by the rotational output of the turbine;
A condenser for condensing the working medium that has passed through the turbine, and a waste heat recovery type ship propulsion device comprising:
The engine cooling water circulation passage for circulating the engine cooling water and one of the plurality of heat exchangers are connected via an exhaust heat recovery passage on the upstream side of the fresh water generator,
The engine cooling water circulation channel and a heat exchanger different from one of the plurality of heat exchangers are separated from the exhaust heat recovery circuit on the downstream side of the fresh water generator. An exhaust heat recovery type ship propulsion device characterized by being connected via A ship's internal combustion engine;
An evaporative freshwater generator that heats seawater taken from outside the ship using exhaust heat of engine cooling water that cools the internal combustion engine, and evaporates the heated seawater in a vacuum chamber to create fresh water; ,
A plurality of heat exchangers installed in series in the circulation path of the working medium, each of which evaporates the working medium with a heat medium having a different temperature;
A turbine driven by the working medium evaporated by the heat exchanger;
A generator for generating electricity by the rotational output of the turbine;
A condenser for condensing the working medium that has passed through the turbine, and a waste heat recovery type ship propulsion device comprising:
An engine cooling water circulation flow path for circulating the engine cooling water and one of the plurality of heat exchangers are connected via an exhaust heat recovery flow path on the upstream side of the fresh water generator. Waste heat recovery type ship propulsion device. A ship's internal combustion engine;
An evaporative freshwater generator that heats seawater taken from outside the ship using exhaust heat of engine cooling water that cools the internal combustion engine, and evaporates the heated seawater in a vacuum chamber to create fresh water; ,
A plurality of heat exchangers installed in series in the circulation path of the working medium, each of which evaporates the working medium with a heat medium having a different temperature;
A turbine driven by the working medium evaporated by the heat exchanger;
A generator for generating electricity by the rotational output of the turbine;
A condenser for condensing the working medium that has passed through the turbine, and a waste heat recovery type ship propulsion device comprising:
An engine cooling water circulation flow path for circulating the engine cooling water and one of the heat exchangers are connected to each other on the downstream side of the fresh water generator via an exhaust heat recovery flow path. Waste heat recovery type ship propulsion device.   A ship comprising the exhaust heat recovery type ship propulsion device according to any one of claims 1 to 3. A ship's internal combustion engine;
An evaporative freshwater generator that heats seawater taken from outside the ship using exhaust heat of engine cooling water that cools the internal combustion engine, and evaporates the heated seawater in a vacuum chamber to create fresh water; ,
A plurality of heat exchangers installed in series in the circulation path of the working medium, each of which evaporates the working medium with a heat medium having a different temperature;
A turbine driven by the working medium evaporated by the heat exchanger;
A generator for generating electricity by the rotational output of the turbine;
A condenser for condensing the working medium that has passed through the turbine;
An operation method of an exhaust heat recovery type ship propulsion apparatus comprising: an engine coolant circulation path that circulates the engine coolant; and an exhaust heat recovery path that connects the plurality of heat exchangers;
Of the exhaust heat of the engine cooling water, the exhaust heat recovery type ship wherein the exhaust heat other than the heat necessary for the required amount of fresh water is recovered by the heat exchanger in the fresh water generator. How to use the propulsion device.

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