KR20130032227A - Energy saving system of ship by using waste heat - Google Patents

Abstract

PURPOSE: An energy saving system using the waste heat of a ship is provided to improve the productivity of electricity as the temperature of engine cooling water is additionally increased by steam heat source wasted by a dumping condenser of a steam system. CONSTITUTION: An energy saving system using the waste heat of a ship comprises a cooling water circulating system(100), a medium and low temperature waste heat recovery device(300), a cooling water circulating system(200) for an electric heater, and an electricity producing unit(800). The cooling water circulating system has a main passage for cooling an engine. The medium and low temperature waste heat recovery device is operated by working fluid that is an organic refrigerant having a lower boiling temperature than water. The cooling circulating system for the electric heater transfers heat source provided from the cooling water circulating system to the medium and low temperature waste heat recovery device. The electricity producing unit generates electricity by using dumping steam supplied from an exhaust gas boiler of the ship.

Description

Energy saving device using waste heat of ship {ENERGY SAVING SYSTEM OF SHIP BY USING WASTE HEAT}

The present invention relates to an energy saving device using waste heat of a ship, and more particularly, to an energy saving device using waste heat of a ship capable of producing electricity using the low and low temperature waste heat of a ship.

Generally, about 50% of the thermal energy generated by combustion of fuel in a propulsion or power generation engine of a ship is used for propulsion or power generation, respectively, while the remainder is mostly used for cooling the exhaust gas or heat- And the like. The heat emitted in this form can be said to be a waste heat that can not be converted to a form useful for propulsion or power generation of an engine, and is therefore referred to as waste heat.

Therefore, if some of the waste heat discharged to the outside can be recovered and recycled as useful energy, the fuel can be saved by that much, which can contribute to the reduction of the total energy consumed by the ship.

As a result, in recent years, there is a need for a high-efficiency ship or an eco-friendly ship that can save energy by recovering some of the waste heat discharged to the outside. So-called gas turbines (or power turbines) used as direct working fluids and steam turbines using some of the steam generated by using high-temperature exhaust gas heat as operating fluids are installed to generate electricity. Waste Heat Recovery System (WHRS) is applied.

Figure 6 shows the configuration of the waste heat recovery apparatus applied to the conventional vessel. The engine 10 of the ship has a main flow passage 12 corresponding to the flow path of the cooling water for cooling. The economizer 50 is directly connected to the engine 10 to receive a high temperature exhaust gas generated after combustion of the engine 10. Waste heat recovery device 52 is a steam turbine (power turbine) receiving the steam generated from the water heated by the economizer 50 and using it as a working fluid, or the exhaust gas collecting device (Exhaust gas) of the engine 10 It is possible to produce electric power by installing a gas turbine that receives high temperature exhaust gas from the receiver and bypasses the turbo charger and uses it as a working fluid.

In this case, the steam turbine is another path (52b) connected to the path (50b) corresponding to the output side of the steam from the path (50a, 50b) for heating the water by the economizer 50 to generate steam Provided with steam, the gas turbine is configured to receive hot exhaust gas directly through another path 52a directly connected to the engine 10.

However, in recent years, many ship owners who demand to reduce fuel costs by operating the vessel at low speed, therefore, when operating the vessel at low speed, the engine output is used only about 30% to 50% of the maximum output.

When the engine is operated at such a low load, since the temperature of the exhaust gas is low, the existing waste heat recovery device 52 using high temperature heat cannot perform its role properly. That is, the gas turbine and the steam turbine of the conventional waste heat recovery device 52 can recover heat only from a heat source of about 250 degrees Celsius or more, thereby producing electrical energy, but the heat below the temperature still cannot be utilized. I have a problem that can only be abandoned.

In other words, the waste heat recovery device 52 of the conventional ship recovers a large amount of heat from the heat energy that is discarded to generate power, so that the engine 10 is driven by a high load to recover a large amount of heat to produce power. However, when the engine 10 is operated at a low load, the efficiency of power generation is lowered because the temperature of exhaust gas, that is, waste heat is relatively low.

The organic rankine cycle device 20 absorbs heat from an external heat source in the evaporator 21 (static pressure heating process), and when the working fluid is vaporized, the pressure in the cycle device 20 increases rapidly, and the increased pressure is increased. Due to the pressure, the turbine 22 installed inside the cycle rotates. At this time, power is generated by converting rotational kinetic energy of the rotating turbine 22 into electric energy (thermal insulation expansion process).

Then, the turbine 22 drives and passes the gas back into the condenser 23 and loses heat through heat exchange with an external heat source (static pressure dissipation process) and condenses (insulation compression process). The pump 24 is recycled to the evaporator 21 to continuously produce power.

The organic Rankine cycle device 20 is characterized in that the higher the temperature of the external heat source (high heat source) on the high temperature side and the lower the temperature of the external heat source (low heat source) on the low temperature side, the higher the efficiency.

Korean Patent Publication No. 2006-0134049 (United Technologies Corporation) Dec. 27, 2006

Therefore, the technical problem to be achieved by the present invention is to recover the waste heat generated in the cooling system of the ship engine and the waste heat generated in the steam system and the waste heat generated in the scavenging system, respectively, by using the same to drive the medium / low temperature waste heat recovery device It is to provide energy saving device using waste heat of ship which can not only save energy but also eco-friendly effect by producing energy.

According to an aspect of the present invention, an energy saving device using waste heat of a ship equipped with an internal combustion engine, the cooling water circulation system having a main flow path for cooling the engine; A medium / low temperature waste heat recovery apparatus operating with an organic refrigerant having a lower boiling point than water as a working fluid; An electrothermal cooling water circulation system for transferring a heat source provided from the cooling water circulation system to the medium / low temperature waste heat recovery device; And it can be provided an energy saving device using the waste heat of the ship including a power generation unit for producing power using the dumping steam supplied from the exhaust gas boiler of the ship.

The power generation unit includes a steam turbine driven by dumping steam supplied from the exhaust gas boiler; And it may further include a steam generator for producing power by driving the steam turbine.

Heat-exchanging the heat source provided from the cooling water circulation system with dumping steam delivered from the steam system of the vessel to increase the temperature of the heat source delivered to the medium / low temperature waste heat recovery device and condense the heat-exchanged dumping steam. And a dumping condenser unit, wherein the power generation unit is provided branched from a flow path connecting the exhaust gas boiler and the steam turbine, when the pressure in the flow path exceeds a preset range. The dumping condenser unit may further include a dumping induction module for inducing dumping of the dumping steam.

The dumping induction module may include: a branch line branched from a flow path connecting the exhaust gas boiler and the steam turbine to the dumping condenser unit; And a dumping valve provided at the branch line and opened when the pressure of the flow path exceeds a preset range to supply the dumping steam to the dumping condenser unit.

The dumping condenser unit may include: a first condenser module configured to increase the temperature of the heat source by mutually heat-exchanging the heat source and the dumping steam; And a second condenser module for cooling and condensing the dumping steam passed through the first condenser module, wherein the dumping steam discharged through the steam turbine is supplied to the first condenser module, and the branch line A second condenser module, wherein the dumping induction module is branched from the branch line so that the dumping steam is transferred to the first condenser module through the branch line when the steam turbine is not operated. It may further include a bridge line connected to the line connecting the condenser unit.

The coolant circulation system may include: a jacket cooler connected to the engine and the main flow path to cool a heat source having a raised temperature while passing through the engine; And a first pump connected to the jacket cooler and the main channel to pump the heat source cooled by the jacket cooler to the engine.

The medium / low temperature waste heat recovery apparatus, the evaporator for evaporating the organic refrigerant; A turbine rotating through the organic refrigerant evaporated by the evaporator; A generator for generating electric power by interlocking with the rotation of the turbine; A condenser for cooling and liquefying the organic refrigerant from the turbine; A pump for compressing the condensed organic refrigerant from the condenser and providing it to the evaporator; And a conduit for forming a circulation path of the organic refrigerant from the evaporator to the turbine, the condenser, and the pump.

The second heat source heat-exchanged in the dumping condenser unit is heat-exchanged with the scavenged air supplied from the supercharger of the engine to increase the temperature of the second heat source delivered to the medium / low temperature waste heat recovery device, and the heat exchanged It may further include an engine scavenging cooling unit for cooling the air.

The engine scavenging cooling unit may include: a first stage module configured to increase the temperature of the second heat source by heat-exchanging the second heat source and the scavenged air; And a second stage module configured to cool the scavenged air that has passed through the first stage module.

The first stage module may include a scavenging air inlet line which is an inflow passage of the scavenging air.

The second stage module may include: a second cooling water inflow line that becomes an inflow passage of cooling water for cooling the scavenged air; A second cooling water discharge line serving as a discharge passage of the cooling water heat-exchanged with the scavenging air; And a scavenging air discharge line that becomes a discharge passage of the scavenging air cooled by heat exchange with the cooling water.

In addition, according to another aspect of the present invention, an energy saving device using waste heat of a ship equipped with an internal combustion engine, comprising a medium / low temperature waste heat recovery device operating with an organic refrigerant having a lower boiling point than water as a working fluid, Apart from the medium / low temperature waste heat recovery device, it is possible to provide an energy saving device using waste heat of a ship including a power generation unit that generates power by using dumping steam supplied from an exhaust gas boiler of the ship.

In the present invention, since the waste heat of the medium / low temperature region is recovered from the heat energy discarded by the ship and electric energy can be produced through the medium, effective recycling of the waste heat of the medium / low temperature of the engine coolant, which could not be utilized in the conventional waste heat recovery system, is possible. To make it possible.

In addition, it is possible to further increase the temperature of the engine cooling water by using the steam heat source disposed through the dumping condenser of the steam system of the ship, thereby improving the production efficiency of power. In particular, since the present invention can use a heat source of a medium / low temperature independent of the existing waste heat recovery device can be applied to the vessel with the conventional waste heat recovery device, it is possible to maximize the economic effect through the reduction of energy.

As a result, the present invention makes it possible to save more energy by using waste heat of a wider range of temperature by using the existing waste heat recovery device even when the engine is operated under a high load, while operating the engine under low load. Even when the waste heat is recovered, the waste heat can be recovered through the medium / low temperature waste heat recovery system, thereby maintaining the utility of the system. In particular, in recent years, even when the slow steaming (slow steaming) that drives the engine at low load is widely used, it has a greater meaning in that a certain level of system efficiency can be obtained.

In addition, the present invention can reduce the consumption of fuel through the production of electric power using the waste heat of the medium / low temperature, and also contribute to the economical and environmentally friendly aspects by reducing the emission of carbon dioxide is expected to have significant effects in the future. It is expected.

In addition, separate operation is possible because power can be generated by using dumping steam supplied from an exhaust gas boiler of a ship separately from the medium / low temperature waste heat recovery device.

1 is a view showing the configuration of the energy saving device of a ship according to a first embodiment of the present invention.
2 is a view showing the configuration of the energy saving device of a ship according to a second embodiment of the present invention.
3 is a view showing the configuration of the energy saving device of the ship according to a third embodiment of the present invention.
4 is a diagram illustrating a multistage configuration of the turbine illustrated in FIGS. 1 to 3.
5 is a view showing a state in which the waste heat recovery apparatus of the existing vessel is added to the energy saving apparatus of the vessel according to the first embodiment of the present invention.
6 is a view showing a configuration for a waste heat recovery apparatus of the conventional vessel.
7 is a view schematically showing an energy saving apparatus of a ship according to a fourth embodiment of the present invention.
FIG. 8 is a view schematically illustrating a cooling water circulation system, a heat transfer cooling water circulation system, and a medium / low temperature waste heat recovery device in an energy saving device of a ship shown in FIG. 7.
FIG. 9 is a view schematically showing a state in which a dumping condenser unit is further added in the embodiment shown in FIG. 8.
FIG. 10 is a view schematically showing a state in which an engine scavenging cooling unit is further added in the embodiment shown in FIG. 9.
FIG. 11 is a view schematically showing a state in which a control unit is further added in the embodiment shown in FIG. 10.
12 and 13 are diagrams schematically showing a state of use of the control unit shown in FIG.
FIG. 14 is a view schematically illustrating a state in which a dry run prevention unit is further added in the embodiment shown in FIG. 11.
FIG. 15 is a view schematically illustrating a state of use of the dry run prevention unit illustrated in FIG. 14.
16 is a view schematically showing a state in which a power generation unit is further added in the embodiment shown in FIG. 10.
17 and 18 are diagrams schematically showing a state of use of the power generation unit shown in FIG.
19 is a view schematically showing a medium / low temperature waste heat recovery device and a low temperature coolant system in the energy saving device of the ship shown in FIG. 7.
20 and 21 are diagrams schematically showing a state of use of the low temperature cooling water system shown in FIG. 19.
22 and 23 are diagrams schematically showing a state of use of the energy saving device of the ship according to a fourth embodiment of the present invention.

In order to fully understand the present invention, operational advantages of the present invention, and objects achieved by the practice of the present invention, reference should be made to the accompanying drawings and the accompanying drawings which illustrate preferred embodiments of the present invention.

Hereinafter, the present invention will be described in detail with reference to the preferred embodiments of the present invention with reference to the accompanying drawings. Like reference symbols in the drawings denote like elements.

The present invention, in a ship using an internal combustion engine, such as a two-stroke diesel engine, to recover the waste heat discarded from the heat from the engine and boiler to produce energy such as electricity. 1 to 3 illustrate an energy saving apparatus using waste heat of medium / low temperature of a ship according to an embodiment of the present invention. The present invention includes a cooling water circulation system (Jacket CFW circulation system; a), a cooling water circulation system for heat transfer (b), and a medium / low temperature waste heat recovery system (c).

The cooling water circulation system (A) is an internal combustion engine mounted on a vessel as shown in FIGS. 1 to 3, and an engine 10 and a main flow passage 12 in which cooling water is circulated for cooling the engine 10. It includes. The heat transfer cooling water circulation system (b) is to transfer a heat source provided from the cooling water circulation system (a) to the medium / low temperature waste heat recovery system (c), and is illustrated in FIGS. 1 and 2. As described above, a branch passage 14 is branched from the main passage 12 at the rear end of the engine 10 and connected to the cooling water circulation system A.

The medium / low temperature waste heat recovery apparatus (C) is a turbine cycle operated using an organic refrigerant having a lower boiling point than water as a working fluid as shown in FIGS. 1 to 3, which is typically an ORC (Organic Rankine cycle). It is called a cycle device. That is, the medium / low temperature waste heat recovery apparatus (C) has a motion of the organic refrigerant evaporated by evaporating the organic refrigerant through a heat source having the cooling water of the engine 10 provided through the heat transfer cooling water circulation system (b). The energy is used to produce the electricity needed by the vessel.

The heat transfer cooling water circulation system (b) further includes a first heat transfer means for heat exchange with a dumping condenser 16 for cooling and condensing steam generated in a steam system of the ship, wherein the first heat transfer means Is the first auxiliary flow path 18 branched from the branch flow path 14 and connected to the dumping condenser 16 so as to be circulated. In this case, the dumping condenser 16 is configured in two stages in order to perform a first heat exchange with the first heat transfer means, and then perform a second heat exchange with a normal low temperature cooling water. That is, the dumping condenser 16 performs a first heat exchange with the coolant of the engine 10 through the first auxiliary passage 18, and then with the low temperature coolant through the first fresh water supply passage 20. The secondary heat exchange is performed, and the condensed water cooled by the first and second heat exchanges is finally discharged through the discharge path 16b.

Accordingly, the first heat transfer means uses the heat source of the steam introduced through the steam inflow path 16a of the dumping condenser 16 to the branch passage 14 of the heat transfer cooling water circulation system (b). By heating the cooling water flowing through the first auxiliary flow channel 18 serves to increase the amount of heat transfer provided to the medium / low temperature waste heat recovery device (C) through the branch flow path (14). In other words, the dumping condenser 16 is composed of two stages, and primarily heat exchanges with the cooling water of the cooling water circulation system (b) for heat transfer through the first heat transfer means. After the heat energy is consumed, the steam is further condensed by using fresh water corresponding to the low temperature cooling water of 50 degrees Celsius or less, which is the normal low temperature cooling water. To this end, the dumping condenser 16 forms a primary flow path for heat exchange with the first auxiliary flow path 18 of the first heat transfer means on the inlet side of the steam, and the steam outlet from the rear end of the primary flow path. A secondary flow path for heat exchange with the low temperature cooling water is integrally formed between the sides.

The heat transfer cooling water circulation system (b) further includes a second heat transfer means for heat exchange with a scavenging cooler 22 for cooling and condensing scavenging air generated in the small engine of the ship engine 10. The second heat transfer means is composed of a second auxiliary flow passage 24 branched from the branch flow passage 14 and connected to the scavenging cooler 22 so as to be circulated. In this case, the scavenging cooler 22 is configured in two stages in order to perform a second heat exchange with the second heat transfer means, and then perform a second heat exchange with a normal low temperature cooling water. That is, the scavenging cooler 22 performs a first heat exchange with the cooling water of the engine 10 through the second auxiliary passage 24, and then, with the normal low temperature cooling water through the second fresh water supply passage 26. The secondary heat exchange is performed, and the scavenged air cooled through the first and second heat exchanges is finally discharged through the discharge path 22b.

Accordingly, the second heat transfer means is connected to the branch passage 14 of the heat transfer cooling water circulating system (b) by using the heat source having the scavenging flow introduced through the scavenging inlet path 22a of the scavenging cooler 22. By further heating the cooling water flowing through the second auxiliary channel 24 serves to further increase the amount of heat transfer provided to the medium / low temperature waste heat recovery device (C) through the branch channel (14). In other words, the scavenging cooler 22 is composed of two stages, and primarily heat exchanges with the cooling water of the cooling water circulation system (b) for heat transfer through the second heat transfer means, thereby providing a desired degree of about 200 degrees Celsius. After the heat energy is consumed, the secondary air is further condensed by using fresh water corresponding to the low temperature cooling water of 50 degrees Celsius or less, which is the normal low temperature cooling water. To this end, the scavenging cooler 22 forms a primary flow passage for heat exchange with the second auxiliary flow passage 24 of the second heat transfer means on the inlet side of the scavenging air, and the scavenging outlet from the rear end of the primary flow passage. A secondary flow path for heat exchange with the low temperature cooling water is integrally formed between the sides.

In this case, in the heat transfer cooling water circulation system (b), the first heat transfer means and the second heat transfer means are sequentially disposed with respect to the outlet side of the branch flow passage 14 branched from the main flow passage 12. The second heat transfer means provides a heat source having a larger amount of heat than the first heat transfer means to the heat transfer cooling water circulation system (b), whereby the coolant flowing through the branch flow passage 14 is connected to the first auxiliary flow path ( 18 is primarily heated by the heat source of the steam flowing into the dumping condenser 16 through the medium, and the heat source having the scavenging air flowing into the scavenging cooler 22 through the second auxiliary passage 24. By secondary heating, the heat source of the cooling water flowing through the branch channel 14 can be increased as much as possible.

The middle / low temperature waste heat recovery apparatus (C) is an evaporator 28 for evaporating an organic refrigerant through heat exchange with the heat transfer cooling water circulation system (B), as shown in FIGS. 1 to 3, and the evaporator 28. Turbine 30 that rotates through the organic refrigerant evaporated by the medium, the generator 32 to produce power in conjunction with the rotation of the turbine 30, the organic refrigerant from the turbine 30 to cool and liquefy A condenser 34, a pump 36 for compressing the condensed organic refrigerant from the condenser 34 and providing it to the evaporator 28, and the turbine 30 and the condenser 34 from the evaporator 28. And a conduit 38 which forms a circulation path of the organic refrigerant up to the pump 36.

The medium / low temperature waste heat recovery apparatus (C) has a conduit (38) for providing organic refrigerant from the turbine (30) toward the condenser (34) and the pump (36) as shown in FIG. A regenerator 40 is added between the conduits 38 providing the organic refrigerant toward 28 so that the temperature of the organic refrigerant from the turbine 30 is higher than the temperature of the organic refrigerant from the pump 36. By allowing heat exchange of the organic refrigerant through the regenerator 40, it is desirable to minimize heat loss that may occur in the medium / low temperature waste heat recovery apparatus (C).

In this case, the turbine 30 is configured in a multi stage as shown in Figure 4, thereby increasing the rotational efficiency of the turbine 30 by the evaporated organic refrigerant of the power generated by the generator 32 The amount can be maximized. That is, by interlocking the turbine 30 and the generator 32 in multiple stages 30a, 32a, 30b, and 32b, the heat source of the evaporated organic refrigerant can be utilized to the maximum. In addition, the multi-stage configuration for the turbine 30 and the generator 32 as described above can be applied to both the energy saving device shown in Figs.

Meanwhile, as illustrated in FIG. 3, the heat transfer cooling water circulation system (b) heat-exchanges through the heat exchanger (42) with respect to the main flow passage 12 of the cooling water circulation system (a). It may be configured to include a separate independent circulation passage 44 for providing a heat source to the device (c), and a separate circulation pump 46 installed in the circulation passage 42 for the circulation of the cooling water. In this case, the cooling water flowing along the main passage 12 of the cooling water circulation system (a) and the cooling water flowing along the independent circulation passage 44 of the heat transfer cooling water circulation system (b) are respectively heat exchangers 42. Since only heat exchange by indirect contact is made by using a), it is possible to solve the problem such as contamination of the cooling water flowing through the circulation passage (42).

In addition, the independent circulation passage 44 further includes a bypass passage 44a capable of circulating without passing through the heat exchanger 42, which obtains heat from heat exchange with the main passage 12. This is in case you can't. In this case, in order to achieve the flow of the cooling water through the bypass passage 44a among the circulation passage 44, switching of the passage may be performed according to a temperature at a branch point between the circulation passage 44 and the bypass passage 44a. Thermostatic valves (not shown) should be provided.

And the energy saving device of the ship according to the present invention bar as shown in Figure 5 may be operated in combination with the conventional waste heat recovery system (WHRS: Waste Heat Recovery System, 52), the waste heat recovery device 52 Is a path 52b connected to a path 50b for generating steam among paths 50a and 50b that are heated by an economizer 50 that is directly connected to the engine 10 to receive exhaust gas and generates steam, or The steam generated through the path 52a directly connected to the engine 10 may be generated to generate electric power.

That is, the waste heat recovery device 52 uses heat of a gas turbine using a high temperature exhaust gas discharged from the engine 10 as a working fluid or a high temperature exhaust gas discharged from the engine 10. It is possible to produce electric power through a steam turbine using a portion of the steam generated as a working fluid.

Therefore, the present invention, unlike the conventional waste heat recovery device 52, a medium or lower than 250 degrees Celsius which is discarded in various forms in the vessel through the medium / low temperature waste heat recovery device (C) using an organic refrigerant having a lower boiling point than water as a working fluid Low-temperature heat sources can be used as energy sources for the production of power, further improving the efficiency of the energy used in ships. In particular, since the present invention uses a heat source in a form independent from the existing waste heat recovery device 52, simultaneously applying the medium / low temperature waste heat recovery device (C) proposed by the present invention together with the existing waste heat recovery device 52. This can maximize energy savings.

That is, the present invention can operate the medium / low temperature waste heat recovery apparatus (C) by using the cooling water flowing through the branch channel 14 branched from the main channel 12 of the cooling water circulation system (A) as a heat source. In addition, the waste heat discarded by further heating the cooling water flowing through the branch passage 14 through the dumping condenser 16 of the first heat transfer means and the scavenging cooler 22 of the second heat transfer means can be more actively utilized. And, through this it is possible to maximize the output of the power accompanying the operation of the medium / low temperature waste heat recovery (C).

In addition, the present invention is to provide the organic refrigerant from the turbine 30 to the condenser 34 in the conduit 38 of the medium / low temperature waste heat recovery apparatus (C) from the pump 36 and the pump 36 A regenerator 40 is added between the conduits 38 providing the organic refrigerant toward the evaporator 28 so that the temperature of the organic refrigerant from the turbine 30 is higher than the temperature of the organic refrigerant from the pump 36. In this case, since the heat exchange of the organic refrigerant through the regenerator 40 may be performed, waste heat may be more effectively utilized.

7 is a view schematically showing an energy saving apparatus of a ship according to a fourth embodiment of the present invention.

As shown in this figure, the energy saving device 1 of the ship according to the present embodiment, the cooling water circulation system 100 is a circulation of the cooling water for the cooling of the engine 110, and the cooling water circulation system 100 Evaporating the working fluid via the heat source delivered from the coolant circulation system 200 for transferring the coolant, that is, the heat source provided to the medium / low temperature waste heat recovery device 300, which will be described later, and the coolant circulation system for the heat transfer. Middle and low temperature waste heat recovery device 300 to produce electricity by heat exchange the heat source transferred from the cooling water circulation system 100 with the dumping steam of the heat source delivered to the medium / low temperature waste heat recovery device 300 Scavenging air supplied from the supercharger of the engine 110 to increase the temperature of the dumping condenser unit 400 for condensing the heat-exchanged dumping steam, and the temperature of the second heat source heat-exchanged in the dumping condenser unit 400 to increase the temperature. In addition to the engine scavenging cooling unit (500) for cooling the heat-exchanged scavenging air to further raise the furnace, and is provided in the cooling water circulation system 100 to supply the heat source to at least one of the cooling water circulation system 100 and the medium / low temperature waste heat recovery device (300). When the heat source provided to the control unit 600 and the heat transfer cooling water circulation system 200 to be supplied to the medium / low temperature waste heat recovery device 300 is blocked, the cooling air is supplied to the engine scavenging cooling unit 500 by supplying cooling water. Dry run prevention unit 700 to prevent a dry run (run) of the unit 500, and a power production unit 800 for producing electric power by using the dumping steam supplied from the exhaust gas boiler 810 of the ship And a low temperature cooling water system 900 for cooling the working fluid of the medium / low temperature waste heat recovery device 300.

In the present embodiment, for convenience of explanation, the cooling water discharged from the engine 110 and delivered to the dumping condenser unit 400 is called a heat source, and the cooling water that is heat-exchanged through the dumping condenser is called a second heat source. The cooling water whose temperature is increased by heat exchange through the scavenging cooling unit 500 is defined as a third heat source. In addition, the third heat source is defined as including cooling water whose temperature is lowered by heat exchange through the medium / low temperature waste heat recovery device 300.

FIG. 8 is a view schematically illustrating a cooling water circulation system, a heat transfer cooling water circulation system, and a medium / low temperature waste heat recovery device in an energy saving device of a ship shown in FIG. 7.

The cooling water circulation system 100 cools the engine 110 by circulating a heat source that is cooling water. As shown in FIG. 8, the engine 110, the engine 110, and the main flow path 120 are connected to the engine. The jacket cooler 130 for cooling the coolant that is the heat source passing through the 110 and the main cooler 120 connecting the jacket cooler 130 and the engine 110 are cooled in the jacket cooler 130. And a first pump 140 for pumping cooling water, which is a heat source, to the engine 110.

The engine 110 of the cooling water circulation system 100 may use a heat-resistant engine such as a two-stroke diesel engine and may be a main engine for driving a vessel.

The main flow path 120 of the cooling water circulation system 100 allows circulation of the cooling water, which is a heat source discharged from the engine 110, and as shown in FIGS. 7 and 8, the engine 110 and the jacket cooler ( The first main passage 121 connecting the 130, the second main passage 122 connecting the jacket cooler 130 and the first pump 140, the first pump 140 and the engine 110 It includes a third main flow path 123 for connecting.

The heat transfer cooling water circulation system 200 transfers the cooling water, which is a heat source of, for example, about 80 ° C., transmitted from the cooling water circulation system 100 to the medium / low temperature waste heat recovery device 300, as shown in FIGS. 7 and 8. Similarly, the branched flow path branched from the first main flow passage 121 in which the engine 110 of the cooling water circulation system 100 is disposed and joined to the first main flow passage 121 in which the jacket cooler 130 is disposed.

In this embodiment, the branch flow path, which is the cooling water circulation system 200 for heat transfer, is branched from the first main flow path 121 in which the engine 110 is disposed, as shown in FIG. Connected to the first branch passage 210 which is a moving passage of the cooling water, which is a heat source discharged from the engine 110, the dumping condenser unit 400 and the engine scavenging cooling unit 500 described later by connecting the dumping condenser unit ( In the engine scavenging cooling unit 500, a second branch flow passage 220 serving as a moving passage of the second heat source discharged from 400 is connected to the engine scavenging cooling unit 500 and the medium / low temperature waste heat recovery device 300. The jacket cooler 130 transmits the discharged third heat source to the middle / low temperature waste heat recovery device 300 and the third heat source after the heat transfer from the medium / low temperature waste heat recovery device 300 flows into the first main flow path 121. ) Includes a third branch channel 230 joined with the first main channel 121 disposed therein.

The medium / low temperature waste heat recovery apparatus 300 is a turbine cycle operated using an organic refrigerant having a lower boiling point than water as a working fluid, and is also commonly referred to as an organic rankine cycle (ORC).

In the present embodiment, since the medium / low temperature waste heat recovery device 300 may use an organic refrigerant having a boiling point lower than that of water, for example, R 134a, a temperature lower than a steam turbine using water as a working fluid may be operated as a heat source. Electric energy can be produced using waste heat of around 100 ℃.

In addition, in the present embodiment, since the engine cooling water (Jacket Cooling Fresh Water), which is a heat source having a lower temperature than steam used in a ship, is used as a heat source and a heat transfer material for evaporating the organic refrigerant which is a working fluid of the medium / low temperature waste heat recovery device 300, The amount of fuel can be saved, which has the advantage of reducing the total energy consumed by the ship.

Now, the medium / low temperature waste heat recovery device 300 will be described in detail. As shown in FIGS. 7 and 8, the medium / low temperature waste heat recovery device 300 is provided through heat exchange with the coolant delivered from the engine 110. An evaporator 310 for evaporating the organic refrigerant, a turbine 320 rotated through the organic refrigerant evaporated by the evaporator 310, and a generator 330 interlocked with the turbine 320 to produce power. And a condenser 340 for cooling and liquefying the organic refrigerant from the turbine 320, a pump 350 for compressing the condensed organic refrigerant from the condenser 340 to the evaporator 310, and an evaporator 310. And a conduit 360 to form a circulation path of the organic refrigerant from the turbine 320 to the condenser 340 and the pump 350.

In the present embodiment, the heat source supplied from the engine 110 has a temperature of about 80 ° C., but as will be described later in detail, the temperature is raised to a second heat source of about 86 ° C. while passing through the dumping condenser unit 400. The temperature is increased to the third heat source of about 106 ℃ while passing through the cooling unit (500). The third heat source whose temperature is raised in this manner drops to about 80 ° C. after heat exchange with the evaporator 310.

In addition, like the other turbine systems, the medium / low temperature waste heat recovery device 300 may have a higher efficiency as the temperature difference between the temperature of the high temperature portion heated in the evaporator 310 and the low temperature portion cooled in the condenser 340 increases. In other words, the higher the temperature of the high temperature portion flowing into the evaporator 310 to transfer heat to the evaporator 310 and the lower the temperature of the low temperature portion entering the condenser 340 to absorb heat from the condenser 340, the higher the efficiency.

FIG. 9 is a view schematically showing a state in which a dumping condenser unit is further added in the embodiment shown in FIG. 8.

As illustrated in FIGS. 7 and 9, the dumping condenser unit 400 heat-exchanges the heat source provided from the cooling water circulation system 100 with dumping steam delivered from the steam system of the ship to make the medium / low temperature waste heat. In addition to raising the temperature of the heat source transferred to the recovery device 300 serves to condense the heat-exchanged dumping steam.

That is, the present embodiment further increases the temperature of the heat source delivered to the evaporator 310 of the medium / low temperature waste heat recovery device 300 by the dumping condenser unit 400 to approximately 86 ° C., thereby increasing the temperature of the heat source delivered to the evaporator 310. Since the temperature can be increased, the efficiency of the medium / low temperature waste heat recovery device 300 can be improved as described above.

The dumping condenser unit 400, as shown in Figure 9, the first condenser module 410 to increase the temperature of the heat source by mutual heat exchange between the heat source supplied from the engine 110 and the dumping steam delivered from the ship's steam system And a second condenser module 420 for cooling and condensing the dumping steam exchanged through the first condenser module 410.

As illustrated in FIGS. 7 and 9, the first condenser module 410 of the dumping condenser unit 400 may be dumped so that the dumping steam generated in the steam system of the ship may be introduced into the first condenser module 410. Steam inlet line 411 is included.

In this embodiment, the dumping steam inlet line 411 of the first condenser module 410 is approximately 170 ° C. which is dumped in the exhaust gas boiler 810 of the power generation unit 800 described later, as shown in FIG. 7. A degree of dumping steam is connected to the steam turbine 820 of the power production unit 800 to be introduced into the first condenser module 410.

As illustrated in FIGS. 7 and 9, the second condenser module 420 of the dumping condenser unit 400 may be an inflow passage for cooling water that cools and condenses the dumping steam heat exchanged in the first condenser module 410. The first cooling water inlet line 421, the first cooling water discharge line 422 serving as a discharge passage of the cooling water heat-exchanged with the dumping steam, and the dumping steam discharge line 423 which becomes a discharge passage of the dumping steam condensed by heat exchange with the cooling water. ).

In the present embodiment, the cooling water condensing the dumping steam of the second condenser module 420 may use fresh water corresponding to low temperature cooling water of 50 ° C. or less.

Hereinafter, the use state of the dumping condenser unit 400 according to the present embodiment will be described with reference to FIGS. 7 and 9.

First, the dumping condenser unit 400 according to the present embodiment further increases the temperature of the heat source supplied from the cooling water circulation system 100 as described above to improve the efficiency of the medium / low temperature waste heat recovery device 300 and the ship. As the condensed dumping steam used and discarded in the steam system of, as shown in Figure 9, the heat source (approximately 80 ℃) supplied from the cooling water circulation system 100 is dumped into the dumping steam inlet line 411 Heat-exchanging with steam results in a second heat source having an elevated temperature of about 86 ° C.

Since the temperature of the dumping steam flowing into the dumping steam inlet line 411 is higher than that of the heat source supplied from the cooling water circulation system 100, the second heat source, which is a heat source that is heat-exchanged and discharged from the first condenser module 410, is The temperature rises further.

As shown in FIG. 9, the second heat source whose temperature is further increased is transferred to the evaporator 310 of the medium / low temperature waste heat recovery device 300 to be heat-exchanged with the evaporator 310 to vaporize the working fluid in a liquid state. Phase change to.

On the other hand, as shown in Figure 7, the dumping condenser unit 400 and the medium / low temperature waste heat recovery device 300 will be described in detail later, but when the engine scavenging cooling unit 500 is further provided in the dumping condenser unit 400 The discharged second heat source may be further increased in temperature through the engine scavenging cooling unit 500.

And the dumping steam heat exchanged in the first condenser module 410 is supplied to the second condenser module 420, the dumping steam supplied to the second condenser module 420, the first cooling water, as shown in FIG. It is condensed by the cooling water flowing into the inlet line 421 and discharged to the dumping steam discharge line 423.

FIG. 10 is a view schematically showing a state in which an engine scavenging cooling unit is further added in the embodiment shown in FIG. 9.

The engine scavenging cooling unit 500 is heat-exchanged in the dumping condenser unit 400 to heat-exchange the second heat source with the scavenged air supplied from the supercharger of the engine to be transferred to the medium / low temperature waste heat recovery device 300. It further increases the temperature of the heat source and serves to cool the heat exchanged scavenging air.

That is, the present embodiment further increases the temperature of the heat source delivered to the evaporator 310 of the medium / low temperature waste heat recovery device 300 by the engine scavenging cooling unit 500 to further increase the temperature of the heat source delivered to the evaporator 310. Since it can be raised to about 106 ℃ can improve the efficiency of the medium / low temperature waste heat recovery device 300 as described above.

As shown in FIGS. 7 and 10, the engine scavenging cooling unit 500 mutually heat-exchanges the second heat source whose temperature is increased through the dumping condenser unit 400 and the scavenged air supplied from the supercharger (not shown). And a first stage module 510 for raising the temperature of the second heat source, and a second stage module 520 for cooling the scavenged air passing through the first stage module 510.

The first stage module 510 of the engine scavenging cooling unit 500 includes a scavenging air inflow line 511 which is an inflow passage of scavenging air supplied from a supercharger (not shown).

As shown in FIG. 10, the second stage module 520 of the engine scavenging cooling unit 500 includes a second cooling water inflow line 521 serving as an inflow passage for cooling water for cooling the scavenging air, and heat exchange with the scavenging air. And a second cooling water discharge line 522 serving as a discharge passage of the coolant, and a scavenging air discharge line 523 serving as a discharge passage of the scavenged air cooled by heat exchange with the second cooling water.

Hereinafter, a state of use of the engine scavenging cooling unit 500 according to the present embodiment will be described with reference to FIGS. 7 and 10.

First, the engine scavenging cooling unit 500 according to the present embodiment further increases the temperature of the second heat source supplied from the dumping condenser unit 400 to improve the efficiency of the medium / low temperature waste heat recovery device 300, and the supercharger ( As shown in FIG. 10, the second heat source (about 86 ° C.) supplied from the dumping condenser unit 400 is introduced into the scavenging air inlet line 511 as shown in FIG. 10. Heat exchanged with the scavenging air to form a third heat source having an elevated temperature of about 106 ° C.

Since the temperature of the scavenged air introduced into the scavenging air inlet line 511 is relatively higher than that of the second heat source supplied from the dumping condenser unit 400, a third heat source that is heat-exchanged by the first stage module 510 and is discharged. The heat source is further raised in temperature.

As shown in FIG. 10, the third heat source whose temperature is further increased is transferred to the evaporator 310 of the medium / low temperature waste heat recovery device 300 to exchange heat with the evaporator 310 to vaporize the working fluid in a liquid state. Phase change to.

And the scavenged air heat-exchanged in the first stage module 510 is supplied to the second stage module 520, the scavenged air supplied to the second stage module 520, the second cooling water, as shown in FIG. Cooled by the cooling water flowing into the inlet line 521 is discharged to the scavenging air discharge line 523.

Meanwhile, in the present embodiment, the engine scavenging cooling unit 500 may increase the temperature of the heat source supplied from the cooling water circulation system 100 without the dumping condenser unit 400.

FIG. 11 is a view schematically showing a state in which a control unit is further added in the embodiment shown in FIG. 10.

The control unit 600 is provided in the main flow path 120 of the cooling water circulation system 100, and a heat source is provided in the cooling water circulation system 100 or the medium / low temperature waste heat recovery device depending on whether the medium / low temperature waste heat recovery device 300 is operated. 300) to be supplied only to one, and the temperature of the third heat source when the temperature of the third heat source flowing into the cooling water circulation system 100 after the heat exchange in the medium / low temperature waste heat recovery device 300 exceeds a predetermined range It serves to control within a predetermined range.

Specifically, the control unit 600 connects the engine 110 and the jacket cooler 130 by a signal transmitted from the medium / low temperature waste heat recovery device 300 when the medium / low temperature waste heat recovery device 300 is driven. Blocking the 120 so that the heat source discharged from the engine 110 is supplied only to the medium / low temperature waste heat recovery device 300, the medium / low temperature waste heat recovery device 300 at the time of non-driving the medium / low temperature waste heat recovery device 300 By releasing the block of the main flow path 120 by the signal transmitted from) serves to circulate the heat source to the cooling water circulation system 100. That is, the control unit 600 blocks the first control valve 610 when the middle / low temperature waste heat recovery device 300 is operated, and the first control valve when the middle / low temperature waste heat recovery device 300 is not operated. 610 serves to release the block.

In addition, the control unit 600 controls the first by a signal applied from the middle / low temperature waste heat recovery apparatus, the operation of which is stopped when the temperature of the third heat source exceeds a predetermined range while the middle / low temperature waste heat recovery apparatus 300 is being driven. By releasing the blocking of the valve 610 to allow the heat source, which is the coolant, to flow in the main flow path 120 of the coolant circulation system 100, it also serves to maintain the cooling efficiency and stability of the coolant circulation system 100.

Referring now to the control unit 600 in detail, the control unit 600, as shown in Figure 11, is provided in the main flow path 120, the cooling water circulation system 100 or the medium / low temperature waste heat recovery device 300 The first control valve 610 for opening and closing the main flow path 120 so that only one of the heat sources is supplied, and the heat exchange in the medium / low temperature waste heat recovery device 300 is provided in the main flow path 120 to cool the water circulation system 100 The first temperature sensor 620 for detecting the temperature of the third heat source flowing into the first and the first to control the opening and closing of the first control valve 610 by a signal transmitted from the medium / low temperature waste heat recovery (300) And a valve controller 630.

The first control valve 610 of the control unit 600 may be an electric control valve opened and closed by an electrical signal transmitted from the first valve controller 630.

As shown in FIG. 11, the first temperature sensor 620 of the control unit 600 includes a main flow path 120 in which a main flow path 120 and a third branch flow path 230 are directly connected to the engine 110. 120 may be provided.

In the present embodiment, the first temperature sensor 620 is provided at the above-described position. The third heat source having the elevated temperature while passing through the dumping condenser unit 400 or the engine scavenging cooling unit 500 is a medium / low temperature waste heat recovery device ( After the heat exchange with the evaporator 310 of 300 to detect whether the temperature has been lowered to an appropriate level for the cooling efficiency and stability of the cooling water circulation system (100).

In addition, since the temperature of the third heat source does not fall to an appropriate level, it is to detect whether the heat source flowing into the opening of the first control valve 610 and the remaining third heat source are maintained at an appropriate level after mixing.

The first valve controller 630 of the control unit 600 blocks the first control valve 610 during the operation of the medium / low temperature waste heat recovery device 300 so that only the heat source is transferred to the medium / low temperature waste heat recovery device 300. When the medium / low temperature waste heat recovery device 300 is not operated, the first control valve 610 is opened to supply the total amount of heat to the main flow channel 120.

In addition, the first valve controller 630 when the temperature of the third heat source passing through the medium / low temperature waste heat recovery device 300 may affect the cooling efficiency and stability of the cooling water circulation system 100, that is, the medium / low temperature waste heat When the temperature of the third heat source passing through the recovery device 300 is higher than necessary, the operation of the middle / low temperature waste heat recovery device 300 is stopped, as shown in FIG. 11, the first control valve 610 is opened. Open and mix the heat source supplied from the engine 110 with the remaining third heat source serves to lower the temperature of the third heat source.

Furthermore, the first valve controller 630 senses the temperature of the remaining third heat source mixed with the heat source by the first temperature sensor 620 so that the temperature of the remaining third heat source mixed with the heat source is an appropriate temperature, thereby making the medium / low temperature waste heat. When the recovery device 300 is operated to block the first control valve 610 to block the inflow of the heat source.

12 and 13 are diagrams schematically showing a state of use of the control unit shown in FIG. FIG. 12 illustrates a state in which heat is circulated through the entire medium / low temperature waste heat recovery device 300 when the middle / low temperature waste heat recovery device 300 is operated, and FIG. 13 is a view of the medium / low temperature waste heat recovery device 300. In the non-operational state, the heat is not supplied to the middle / low temperature waste heat recovery device 300, and the heat quantity is circulated in the cooling water circulation system 100.

Hereinafter, the use state of the control unit 600 according to the present embodiment will be briefly described with reference to FIGS. 11 to 13.

As shown in FIG. 12, during the operation of the medium / low temperature waste heat recovery device 300, the heat source supplied from the cooling water circulation system 100 is a medium / low temperature waste heat recovery device 300 through the total amount of heat transfer cooling water circulation system 200. Is supplied.

That is, when the middle / low temperature waste heat recovery device 300 is operated, the first valve controller 630 of the control unit 600 blocks the first control valve 610 to allow the jacket cooler 130 to pass through the first main flow passage 121. Blocking the heat source is supplied to the heat source discharged from the engine 110 to be supplied to the total amount of medium / low temperature waste heat recovery device (300).

Next, as shown in FIG. 13, during the non-operation of the medium / low temperature waste heat recovery device, the amount of heat supplied from the cooling water circulation system 100 is entirely supplied to the jacket cooler 130 through the first main flow passage 121. The amount of heat supplied to the jacket cooler 130 is used as coolant for cooling the engine 110 while circulating the coolant circulation system 100.

That is, when the middle / low temperature waste heat recovery device 300 is not operated, the first valve controller 630 of the control unit 600 receives the first control valve 610 by a signal transmitted from the medium / low temperature waste heat recovery device 300. Open to supply the heat source discharged from the engine 110 to the jacket cooler 130 through the total amount of the first main passage 121. The heat source supplied to the jacket cooler 130 cools the engine 110 while circulating the coolant circulation system 100.

On the other hand, if the temperature of the third heat source passing through the evaporator 310 during the operation of the medium / low temperature waste heat recovery device 300 exceeds the preset range to affect the cooling efficiency and stability of the cooling water circulation system 100, / Low temperature waste heat recovery device 300 is stopped.

When the operation of the middle / low temperature waste heat recovery device 300 is stopped, the supply of the third heat source supplied through the third branch channel 230 is stopped, and the first valve controller 630 is the medium / low temperature waste heat recovery device 300. 11 by opening the first control valve 610 by the signal transmitted from the), as shown in Figure 11, the heat source is supplied to the first main flow path 121, the temperature of the coolant flowing into the jacket cooler 130 Since it can lower the cooling efficiency and stability of the cooling water circulation system 100 can be maintained.

FIG. 14 is a view schematically illustrating a state in which a dry run prevention unit is further added in the embodiment shown in FIG. 11.

The dry run prevention unit 700 is provided in the heat transfer cooling water circulation system 200 and supplies coolant to the engine scavenging cooling unit 500 when the heat source supplied to the medium / low temperature waste heat recovery device 300 is blocked. It serves to prevent a dry run (run-run) of the cooling unit (500).

That is, when the medium / low temperature waste heat recovery device 300 does not operate, the engine scavenging cooling unit 500 is operated without the coolant because the coolant as the second heat source is not supplied to the engine scavenging cooling unit 500, that is, dry running. do.

In this case, the temperature of the cooling water, which is the second heat source stagnant in the first stage module 510 of the engine scavenging cooling unit 500, is continuously raised by the high-temperature compressed scavenging air supplied through the supercharger (not shown) to provide a boiling point. When the steam is generated, the pressure in the branch flow path, which is the cooling water circulation system 200 for heat transfer, may increase.

Of course, there is a safety valve (not shown) for pressure relief is installed, the pressure does not rise above a certain pressure, but it is not preferable if the safety valve designed to operate in an emergency is operated from time to time.

In addition, since the cooling of the scavenging air is not performed in the first stage module 510 of the engine scavenging cooling unit 500, a burden may be placed on the second stage module 520 cooling the scavenging air. May not affect the engine performance as much as desired.

Therefore, in the present embodiment, even when the medium / low temperature waste heat recovery device 300 is not operated by the dry run prevention unit 700, a separate coolant is supplied to the engine scavenging cooling unit 500 to provide the engine scavenging cooling unit 500. There is an advantage that can be secured by preventing the draft run.

Referring now to the dry run prevention unit 700 in detail, the drain run prevention unit, as shown in Figure 14, the second branch which is a flow path between the dumping condenser unit 400 and the engine scavenging cooling unit 500 A third valve that is provided in the flow path 220 to supply the coolant to the engine scavenging cooling unit 500, and a third flow path between the engine scavenging cooling unit 500 and the medium / low temperature waste heat recovery device 300. The second valve module 720 provided in the branch flow path 230 to discharge the cooling water supplied to the engine scavenging cooling unit 500 and the first valve module 710 according to whether the medium / low temperature waste heat recovery device 300 is operated. And a second valve controller (not shown) for selectively controlling the second valve module 720.

As shown in FIG. 14, the first valve module 710 of the dry run prevention unit 700 includes a third coolant inflow line 711 through which coolant is introduced, and an inlet line of the engine scavenging cooling unit 500. It is provided but is connected to the third cooling water inlet line 711 includes a first three-way valve 712 for introducing the cooling water into the engine scavenging cooling unit (500).

In this embodiment, as shown in FIG. 14, the third cooling water inflow line 711 is branched from the second cooling water inflow line 521 of the engine scavenging cooling unit 500 to be connected to the first three-way valve 712. Can be.

As shown in FIG. 14, the second valve module 720 of the dry run prevention unit 700 includes a second three-way valve 721 provided in the discharge line of the engine scavenging cooling unit 500, and a second three-way valve. And a third coolant discharge line 722 connected to the valve 721 to become a discharge passage of the coolant supplied to the engine scavenging cooling unit 500.

In the present embodiment, as shown in FIG. 14, the third coolant discharge line 722 may be joined to the second coolant discharge line 522 of the engine scavenging cooling unit 500.

The second valve controller (not shown) of the dry run prevention unit 700 includes the inlet and the coolant of the first three-way valve 712 through which the coolant flows when the heat source is supplied to the medium / low temperature waste heat recovery device 300. Blocking the outlet of the second three-way valve 721 is discharged so that the second heat source is supplied to the medium / low temperature waste heat recovery device 300, the first when the heat source is not supplied to the medium / low temperature waste heat recovery device 300 The three-way valve 712 is opened to allow the coolant to be supplied to the first stage module 510 of the engine scavenging cooling unit 500, and the coolant discharged from the first stage module 510 is a medium / low temperature waste heat recovery device. It blocks the outlet of the second three-way valve 721 connected to the medium / low temperature waste heat recovery device 300 to be discharged without entering the 300.

FIG. 15 is a view schematically illustrating a state of use of the dry run prevention unit illustrated in FIG. 14. FIG. 15 illustrates a state in which the dry run prevention unit 700 does not operate when the middle / low temperature waste heat recovery apparatus 300 is operated. For reference, FIG. 14 illustrates a state in which the middle / low temperature waste heat recovery apparatus 300 is not operated. In order to prevent the dry running of the engine scavenging cooling unit 500 is shown a state in which the dry run prevention unit 700 is automatically.

Hereinafter, the use state of the dry run prevention unit 700 according to the present embodiment will be briefly described with reference to FIGS. 14 and 15.

First, when the medium / low temperature waste heat recovery device 300 is not operated, cooling water, which is a second heat source, is not supplied to the first stage module 510 of the engine scavenging cooling unit 500, and the high-temperature and high-pressure scavenging is performed in a supercharger (not shown). Since only air is supplied, the pressure of the first stage module 510 is increased abnormally, which may impair the stability of the present embodiment.

Therefore, when the middle / low temperature waste heat recovery apparatus 300 is not operated, as shown in FIG. 14, the first stage module 510 is separately provided through the first valve module 710 of the dry run prevention unit 700. By supplying the cooling water and heat exchange with the scavenging air of high temperature and high pressure supplied from the supercharger, it is possible to prevent the dry run of the first stage module 510.

Meanwhile, the separate cooling water exchanged through the first stage module 510 is discharged through the third cooling water discharge line 722 by the control of the second valve controller.

And, as shown in Figure 15, during operation of the medium / low temperature waste heat recovery device 300, the second valve controller controls the first three-way valve 712 to separate the cooling water to the third cooling water inlet line 711 Is not introduced, and the third three-way valve 721 is controlled so that the third heat source is not discharged to the third cooling water discharge line 722 and is supplied to the middle / low temperature waste heat recovery device 300.

16 is a view schematically showing a state in which a power generation unit is further added in the embodiment shown in FIG. 10.

Steam generated from the exhaust gas boiler 810 during the operation of the ship is supplied to the elements that require some steam and the remaining steam is condensed through the dumping condenser is discarded without using thermal energy, this embodiment is the power generation The dumping steam is supplied to the separate turbine by the unit 800, and thus, additional electric energy may be produced.

The electric power generating unit 800 generates electric power by driving the steam turbine 820 driven by the dumping steam supplied from the exhaust gas boiler 810 and the steam turbine 820, as shown in FIG. 16. The steam generator 830 is branched from the flow path connecting the exhaust gas boiler 810 and the steam turbine 820, the dumping condenser unit through the steam generator 830 when the pressure of the flow path exceeds a preset range Apart from the dumping steam dumped into 400, a dumping induction module 840 for inducing the dumping of the dumping steam into the dumping condenser unit 400.

The dumping induction module 840 of the power generation unit 800 is branched in the flow path connecting the exhaust gas boiler 810 and the steam turbine 820, as shown in FIG. 16, to remove the dumping condenser unit 400. The branch line 841 connected to the first condenser module 410 and the second condenser module 420 of the dumping condenser unit 400 are opened when the pressure of the flow path is provided in the branch line 841 and exceeds the preset range. The dumping valve 842 for supplying the low dumping steam and the dumping steam supplied from the exhaust gas boiler 810 during the non-operation of the steam turbine 820 are transferred to the first condenser module 410 through the branch line 841. And a bridge line 843 branched from the branch line 841 to be connected to the dumping steam branch line 841.

17 and 18 are diagrams schematically showing a state of use of the power generation unit shown in FIG. FIG. 17 illustrates the steam turbine 820 for generating dumping steam, which is supplied to an element requiring some of the steam supplied from the exhaust gas boiler 810 and the remaining steam, and FIG. 18. When not driving 820 illustrates the state of supplying the remaining remaining dumping steam to the dumping condenser module.

Hereinafter, a state of use of the power generation unit 800 according to the present embodiment will be briefly described with reference to FIGS. 17 and 18.

First, as shown in FIG. 17, some of the steam produced in the exhaust gas boiler 810 is supplied to an element that requires steam, and the remaining steam, which is dumping steam, is passed through a steam turbine 820. Supplied to the first condenser module 410. The steam turbine 820 is rotated by the dumping steam supplied to the steam turbine 820, and the rotational force of the steam turbine 820 is transmitted to the steam generator 830 to produce power. In the present embodiment, the power production unit 800 may be operated separately from the medium / low temperature waste heat recovery device 300, or may be operated according to the power required when the ship is operated.

On the other hand, if there is more steam produced in the exhaust gas boiler 810 than steam to be used in the vessel, it is necessary to discard the dumping steam separately from the dumping steam supplied to the steam turbine 820 to prevent the pressure rise in the flow path. This is done by the dumping induction module 840 as shown in FIG. 18.

Specifically, when the steam produced in the exhaust gas boiler 810 is produced more than necessary, the pressure is increased, and in order to lower the increased pressure, the dumping valve 842 is opened by an applied signal, and the dumping steam is branched. It is supplied to the first condenser module 410 and the second condenser module 420 of the dumping condenser unit 400 through the line 841 or the bridge line 843.

In addition, since the dumping steam may not be supplied through the steam turbine 820 when the steam turbine 820 is not operated, the dumping steam may be supplied to the dumping condenser unit 400 through the dumping induction module 840.

19 is a view schematically showing a medium / low temperature waste heat recovery device and a low temperature coolant system in the energy saving device of the ship shown in FIG. 7.

The middle / low temperature waste heat recovery apparatus 300 which generates electricity using a turbine has higher efficiency as the temperature difference between the temperature of the high temperature portion heated in the evaporator 310 and the low temperature portion cooled in the condenser 340, like other turbine systems, increases. You can get it. Therefore, the present embodiment may improve the efficiency of the medium / low temperature waste heat recovery device 300 by lowering the temperature of the coolant flowing into the condenser 340 using the low temperature coolant system 900.

The low temperature coolant system 900, as shown in Figure 19, the low temperature coolant cooling unit 910 for cooling the coolant used in the equipment (M) that requires cooling to maintain the temperature of the coolant in a predetermined range And a working fluid cooling unit 920 for cooling the working fluid of the medium / low temperature waste heat recovery device 300 by using the cooling water cooled by the low temperature cooling water cooling unit 910.

The low temperature coolant cooling unit 910 of the low temperature coolant system 900 may include a low temperature coolant cooler 911 and a low temperature coolant cooler 911 that cools the low temperature coolant used in the equipment M as shown in FIG. 19. ) And a second pump 912 provided in the flow path between the equipment M and the low temperature coolant circulation path from the low temperature coolant cooler 911 to the second pump 912 and the equipment M. A third three-way valve 914 provided in the first cooling channel 913 between the first cooling channel 913, the low temperature cooling water cooler 911, and the second pump 912, and the equipment M; Branch flow passage 915 which is branched from the first cooling passage 913 between the low temperature cooling water cooler 911 and transferring the low temperature cooling water discharged from the equipment M to the third three way valve 914, and the third three way valve. The temperature of the low-temperature cooling water provided in the first cooling passage 913 between the 914 and the second pump 912 and discharged from the third three-way valve 914. A second temperature sensor 916 for sensing.

In addition, the low temperature cooling water cooling unit 910, as shown in Figure 19, by adjusting the opening and closing degree of the third three-way valve 914 low temperature cooling water supplied from the low temperature cooling water cooler 911 to the third three-way valve 914. And a third three-way valve controller 917 for controlling a mixing temperature of the low temperature cooling water supplied to the third three-way valve 914 through the branch passage 915.

The working fluid cooling unit 920 of the low temperature coolant system 900 is branched from the first cooling channel 913 between the low temperature coolant cooler 911 and the third three-way valve 914 to form a medium / low temperature waste heat recovery device 300. After passing through), the second cooling passage 921 connected to the first cooling passage 913 between the third three-way valve 914 and the second pump 912, the low-temperature cooling water cooler 911 and the medium / low temperature A second control valve 922 provided in the second cooling flow path 921 connecting the waste heat recovery device 300, and a second control valve 922 and the second / low temperature waste heat recovery device 300. And a third pump 923 provided in the cooling passage 921.

In the present embodiment, branching of the second cooling channel 921 from the first cooling channel 913 between the low temperature cooling water cooler 911 and the third three-way valve 914 is the efficiency of the medium / low temperature waste heat recovery device 300. In order to increase the temperature, after the heat exchange in the condenser 340, so that the low temperature cooling water does not affect the low temperature cooling water cooling unit 910.

In the present embodiment, the third pump 923 is a medium / low temperature waste heat recovery device such that a large amount of low temperature coolant is supplied to the medium / low temperature waste heat recovery device 300 so as not to affect the low temperature cooling water cooling unit 910. It may be a variable displacement pump capable of supplying a variable flow rate according to the operating conditions of 300).

And the working fluid cooling unit 920 of the low temperature cooling water system 900, as shown in Figure 19, during the operation of the medium / low temperature waste heat recovery device 300 by opening the second control valve 922 to the second The low-temperature cooling water is supplied to the medium / low temperature waste heat recovery device 300 through the refrigerant flow path, and when the medium / low temperature waste heat recovery device 300 is not operated, the second control valve 922 is blocked to prevent the second coolant from being supplied. It further includes a third valve controller (not shown) for blocking the low-temperature cooling water supplied to the medium / low temperature waste heat recovery device (300).

20 and 21 are diagrams schematically showing a state of use of the low temperature cooling water system shown in FIG. 19. FIG. 20 illustrates a state in which the working fluid cooling unit 920 is not operated and only the low temperature cooling water cooling unit 910 is operated when the medium / low temperature waste heat recovery device 300 is not operated. FIG. 21 is a middle / low temperature waste heat. The recovery apparatus 300, the low temperature cooling water cooling unit 910 and the working fluid cooling unit 920 are all shown to operate.

20 and 21, the use state of the low temperature cooling water system 900 according to the present embodiment will be briefly described.

First, as shown in FIG. 20, when the medium / low temperature waste heat recovery device 300 is not operated, it is not necessary to cool the working fluid of the medium / low temperature waste heat recovery device 300 only the low temperature cooling water cooling unit 910. It works.

The low temperature coolant that performs the cooling operation while passing through the equipment M may flow directly into the low temperature coolant cooler 911 or directly through the branch flow passage 915 without passing through the low temperature coolant cooler 911. Flows into.

The low temperature coolant cooled by the low temperature coolant cooler 911 is introduced into the third three-way valve 914 and mixed with the low temperature coolant introduced through the branch flow passage 915. At this time, the third three-way valve controller 917 opens and closes the third three-way valve 914 by a second temperature sensor 916 which senses a temperature of the low temperature cooling water discharged through the third three-way valve 914 and transmits a signal. Adjust the degree.

That is, when the temperature of the low temperature coolant discharged through the third three-way valve 914 is too low, the inlet of the third three-way valve 914 connected to the branch flow passage 915 into which the relatively high temperature low-temperature coolant is introduced may be further opened. When the temperature of the low temperature coolant discharged through the third three-way valve 914 is increased, and the temperature of the low temperature coolant discharged through the third three-way valve 914 is too high, the low temperature coolant cooler 911 discharging the relatively low temperature coolant 911. ) May further open the inlet of the third three-way valve 914 to lower the temperature of the low temperature cooling water.

Next, as shown in Figure 20, during the operation of the medium / low temperature waste heat recovery device 300, the low temperature low temperature by the working fluid cooling unit 920 to increase the efficiency of the medium / low temperature waste heat recovery device 300 Cooling water is supplied to the medium / low temperature waste heat recovery device (300).

Specifically, when the middle / low temperature waste heat recovery device 300 is operated, the third valve controller (not shown) opens the second control valve 922 to directly pump the low temperature coolant cooled by the low temperature coolant cooler 911. (923).

The third pump 923 supplies the low-temperature cooling water supplied to the medium / low temperature waste heat recovery device 300 to exchange heat with the condenser 340. As described above, the medium / low temperature waste heat recovery apparatus 300 has a higher efficiency as the temperature difference between the temperature of the high temperature portion heated in the evaporator 310 and the low temperature portion cooled in the condenser 340 increases, so that the working fluid is cooled in the present embodiment. Since the unit 920 may lower the temperature of the low temperature portion cooled in the condenser 340, there is an advantage of improving the efficiency of the medium / low temperature waste heat recovery device 300.

In this embodiment, since the third pump 923 may variably supply the low temperature cooling water according to the operating conditions of the medium / low temperature waste heat recovery device 300, the third pump 923 does not affect the cooling performance of the low temperature cooling water cooling unit 910.

22 and 23 are diagrams schematically showing a state of use of the energy saving device of the ship according to a fourth embodiment of the present invention. 22 is a view showing a state of use when the medium / low temperature waste heat recovery device 300 is operated, Figure 23 is a view showing a state of use when the medium / low temperature waste heat recovery device 300 is not operated. .

Hereinafter, a state of use of the energy saving device 1 of the ship according to the fourth embodiment of the present invention will be briefly described with reference to FIGS. 22 and 23.

First, as shown in FIG. 22, the heat source discharged from the engine 110 during the operation of the medium / low temperature waste heat recovery device 300 is dumped through the first branch flow path 210 of the cooling water circulation system 200 for the total amount of heat transfer. Flows into the unit 400. The heat source introduced into the dumping condenser unit 400 is heat-exchanged with the dumping steam introduced into the dumping steam inlet line from the first condenser module 410 of the dumping condenser unit 400 to increase the temperature, and the temperature is increased. The heat source, which is a higher heat source, becomes a second heat source and is delivered to the engine scavenging cooling unit 500.

The second heat source transferred to the engine scavenging cooling unit 500 is heat exchanged with the high temperature and high pressure scavenging air supplied from a supercharger (not shown) in the first stage module 510 of the engine scavenging cooling unit 500 to provide a higher heat source. The third heat source is introduced into the evaporator 310 of the medium / low temperature waste heat recovery device 300.

As described above, the efficiency of the medium / low temperature waste heat recovery device 300 may be increased as the temperature difference between the temperature of the high temperature portion heated in the evaporator 310 and the low temperature portion cooled in the condenser 340 increases as in other turbine systems. .

Although the present embodiment may use the cooling water as the heat source discharged from the engine 110 by itself, the heat source is introduced into the evaporator 310 by additional heat exchange in the dumping condenser unit 400 and the engine scavenging cooling unit 500. Since the temperature of the third heat source can be increased, there is an advantage of improving the efficiency of the medium / low temperature waste heat recovery device 300.

The third heat source that has passed through the medium / low temperature waste heat recovery device 300 is transferred to the jacket cooler 130, cooled, flowed back into the engine 110, and then circulated in the above-described process.

When the temperature of the third heat source discharged from the medium / low temperature waste heat recovery device 300 and introduced into the jacket cooler 130 exceeds the preset range, the cooling performance and safety of the cooling water circulation system 100 may be affected. , Control unit 600 controls this.

That is, the first valve controller 630 of the control unit 600 opens the first control valve 610 when the temperature of the third heat source flowing into the jacket cooler 130 exceeds a preset range, so that the engine is relatively low in temperature. The heat source discharged from the 110 may be mixed with the third heat source to lower the temperature of the third heat source introduced into the jacket cooler 130 to a predetermined range to ensure cooling efficiency and stability of the cooling water circulation system 100.

Meanwhile, the efficiency of the medium / low temperature waste heat recovery device 300 increases as the temperature of the low temperature portion cooled in the condenser 340 is lower, so in the present embodiment, the low temperature portion cooled in the condenser 340 using the low temperature cooling water system 900. By lowering the temperature of the medium / low temperature waste heat recovery device 300 can increase the efficiency

Specifically, the low-temperature cooling water discharged from the low-temperature cooling water cooler 911 of the low-temperature cooling water cooling unit 910 is directly supplied to the medium / low temperature waste heat recovery device 300 to provide a condenser 340 of the medium / low temperature waste heat recovery device 300. It is possible to lower the temperature of the cold part to be cooled.

In particular, the present embodiment can produce electrical energy by using the dumping steam dumped in the exhaust gas boiler 810 separately from the medium / low temperature waste heat recovery device 300, so that the driving is performed separately according to the required power during operation of the ship. This has a possible advantage.

Next, the coolant, which is a heat source discharged from the engine 110 when the middle / low temperature waste heat recovery device 300 is not operated, is supplied to the jacket cooler 130 through the first main flow passage 121 in total and is supplied to the coolant circulation system 100. The engine 110 is cooled while circulating.

In this state, since the heat source is not supplied to the engine scavenging cooling unit 500 and the first stage module 510 of the engine scavenging cooling unit 500 is supplied with the scavenging gas of high temperature and high pressure from the supercharger, the first stage module 510 is provided. The second heat source remaining in the is heated by the scavenging gas of high temperature and high pressure so that the pressure may be abnormally raised.

In the present embodiment, such a phenomenon may be prevented by the dry run prevention unit 700. That is, when the middle / low temperature waste heat recovery device 300 is not operated, the first stage module may be supplied to the first stage module 510 of the engine scavenging cooling unit 500 by the dry run prevention unit 700. Abnormal pressure and temperature rise due to heating of 510 may be prevented.

In addition, the low-temperature cooling water cooling unit 910 may be operated separately to cool the equipment (M) when the medium / low temperature waste heat recovery device 300 is not operated. Can produce.

As described above, the present invention is not limited to the described embodiments, and various modifications and changes can be made without departing from the spirit and scope of the present invention, which will be apparent to those skilled in the art. Accordingly, such modifications or variations are intended to fall within the scope of the appended claims.

Cooling water circulation system Cooling water circulation system for heat transfer
Multi-medium / cold waste heat recovery device
10-engine 12-main euro
14-branch euro 16-dump condenser
18-First Auxiliary Euro 20-First Fresh Water Supply Euro
22-Scavenger Chiller 24-Secondary Aqueous
26-Second fresh water supply 28-Evaporator
30-turbine 32-generator
34-condenser 36-pump
38-pipe 40-player
42-heat exchanger 44-independent circulation passage
46-circulating pump
1: Energy saving device using waste heat of ship
100: coolant circulation system 110: engine
120: main euro 130: jacket cooler
140: first pump 200: cooling water circulation system for heat transfer
300: medium / low temperature waste heat recovery device 310: evaporator
320 turbine 330 generator
340: condenser 350: pump
360: pipeline 400: dumping condenser unit
410: first capacitor module 420: second capacitor module
500: engine scavenging cooling unit 510: first stage module
520: second stage module 600: control unit
610: first control valve 620: first temperature sensor
630: first valve controller 700: dry run prevention unit
710: first valve module 720: second valve module
800: power production unit 810: exhaust gas boiler
820: Steam Turbine 830: Steam Generator
840 dumping induction module 900 low temperature cooling water system
910: low temperature cooling water cooling unit 920: working fluid cooling unit
M: Equipment

Claims (12)

Energy saving device using waste heat of a ship equipped with an internal combustion engine,
A coolant circulation system having a main flow path for cooling the engine;
A medium / low temperature waste heat recovery apparatus operating with an organic refrigerant having a lower boiling point than water as a working fluid;
An electrothermal cooling water circulation system for transferring a heat source provided from the cooling water circulation system to the medium / low temperature waste heat recovery device; And
Energy saving device using the waste heat of the ship comprising a power generation unit for producing electric power by using the dumping steam supplied from the exhaust gas boiler of the vessel. The method according to claim 1,
The power production unit,
A steam turbine driven by dumping steam supplied from the exhaust gas boiler; And
Energy saving device using the waste heat of the ship further comprising a steam generator for producing electric power by driving the steam turbine. The method according to claim 2,
The heat source provided from the cooling water circulation system is heat-exchanged with dumping steam delivered from the steam system of the vessel to increase the temperature of the heat source delivered to the medium / low temperature waste heat recovery device and condense the heat-exchanged dumping steam. Further comprising a dumping condenser unit,
The power production unit,
It is provided branched from the flow path connecting the exhaust gas boiler and the steam turbine, and if the pressure of the flow path exceeds a preset range further comprises a dumping induction module for inducing the dumping (dumpimg) of the dumping steam to the dumping condenser unit Energy saving device using waste heat of the ship including. The method according to claim 3,
The dumping induction module,
A branch line branched from a flow path connecting the exhaust gas boiler and the steam turbine to the dumping condenser unit; And
And a dumping valve provided in the branch line and opened when the pressure of the flow path exceeds a preset range to supply the dumping steam to the dumping condenser unit. The method of claim 4,
The dumping condenser unit,
A first condenser module for raising a temperature of the heat source by mutually exchanging the heat source and the dumping steam; And
A second condenser module for cooling and condensing the dumping steam passing through the first condenser module,
The dumping steam discharged through the steam turbine is supplied to the first condenser module, the branch line is connected to the second condenser module,
The dumping induction module,
And a bridge line branched from the branch line and connected to a line connecting the steam turbine and the dumping condenser unit so that the dumping steam is delivered to the first condenser module through the branch line when the steam turbine is not operated. Energy saving device using the waste heat of the ship. The method according to claim 1,
The cooling water circulation system,
A jacket cooler connected to the engine and the main channel to cool a heat source having a raised temperature while passing through the engine; And
And a first pump connected to the jacket cooler and the main channel to pump the heat source cooled by the jacket cooler to the engine. The method according to claim 1,
The medium / low temperature waste heat recovery device,
An evaporator for evaporating the organic refrigerant through heat exchange with a heat source having a raised temperature in the dumping condenser unit;
A turbine rotating through the organic refrigerant evaporated by the evaporator;
A generator for generating electric power by interlocking with the rotation of the turbine;
A condenser for cooling and liquefying the organic refrigerant from the turbine;
A pump for compressing the condensed organic refrigerant from the condenser and providing it to the evaporator; And
Energy saving device using the waste heat of the ship comprising a conduit for forming a circulation path of the organic refrigerant from the evaporator to the turbine, the condenser and the pump. The method according to claim 3,
The second heat source heat-exchanged in the dumping condenser unit is heat-exchanged with the scavenged air supplied from the supercharger of the engine to increase the temperature of the second heat source delivered to the medium / low temperature waste heat recovery device, and the heat exchanged Energy saving device using the waste heat of the ship further comprises an engine scavenging cooling unit for cooling the air. The method according to claim 8,
The engine scavenging cooling unit,
A first stage module configured to increase the temperature of the second heat source by mutually exchanging the second heat source and the scavenged air; And
Energy saving device using the waste heat of the ship comprising a second stage module for cooling the scavenging air passing through the first stage module. The method according to claim 9,
The first stage module is an energy saving device using the waste heat of the ship comprising a scavenging air inlet line to be the inlet passage of the scavenging air. The method according to claim 9,
The second stage module,
A second cooling water inflow line serving as an inflow passage of the cooling water for cooling the scavenging air;
A second cooling water discharge line serving as a discharge passage of the cooling water heat-exchanged with the scavenging air; And
Energy-saving device using the waste heat of the ship comprising a scavenging air discharge line that becomes the discharge passage of the scavenging air cooled by heat exchange with the cooling water. Energy saving device using waste heat of a ship equipped with an internal combustion engine,
A medium / low temperature waste heat recovery device operating with an organic refrigerant having a lower boiling point than water as a working fluid, and generates electric power by using dumping steam supplied from an exhaust gas boiler of the ship separately from the medium / low temperature waste heat recovery device. Energy saving device using the waste heat of the ship comprising a power generation unit.

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