CN109113819B - Heat energy recovery system and ship carrying same - Google Patents
Heat energy recovery system and ship carrying same Download PDFInfo
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- CN109113819B CN109113819B CN201810650516.9A CN201810650516A CN109113819B CN 109113819 B CN109113819 B CN 109113819B CN 201810650516 A CN201810650516 A CN 201810650516A CN 109113819 B CN109113819 B CN 109113819B
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- heat exchange
- working medium
- exchange unit
- flow path
- temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63J—AUXILIARIES ON VESSELS
- B63J3/00—Driving of auxiliaries
- B63J3/02—Driving of auxiliaries from propulsion power plant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K21/00—Steam engine plants not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
- F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting from exhaust energy the devices using heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T70/00—Maritime or waterways transport
- Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system
Abstract
The invention provides a heat energy recovery system capable of improving heat recovery efficiency. A thermal energy recovery system is provided with an engine (10), a supercharger (20), an air cooling device (30), a cooler (40), a 1 st circulation flow path (50), a 2 nd circulation flow path (60), a 1 st heat exchange unit (71), a 2 nd heat exchange unit (72), an expander (73), a power recovery machine (74), and a control unit (90), the control unit adjusts the inflow amount of the working medium to the 1 st heat exchange unit when the 2 nd temperature is higher than the 1 st temperature, so that the degree of superheat of the working medium flowing through a portion between the 2 nd heat exchange unit and the expander falls within a predetermined range, and when the 2 nd temperature is below the 1 st temperature, stopping the heat exchange in the 2 nd heat exchange part and adjusting the inflow amount of the working medium to the 1 st heat exchange part, the degree of superheat of the working medium flowing through a portion between the 1 st heat exchange unit and the 2 nd heat exchange unit is within a predetermined range.
Description
Technical Field
The present invention relates to a thermal energy recovery system.
Background
Conventionally, in an internal combustion engine provided with a supercharger and an engine, there is known a heat energy recovery system for recovering heat of supercharged air supplied from the supercharger to the engine and heat of cooling water after the engine is cooled. For example, patent document 1 discloses an exhaust heat recovery device (thermal energy recovery system) including: a diesel engine; a supercharger having a turbine and a compressor; an air cooler that cools the charge air discharged from the compressor with cooling water; a waste heat recovery unit; a flow path for guiding cooling water flowing out from the engine to the exhaust heat recovery unit; and a flow path for guiding the cooling water flowing out from the air cooler to the exhaust heat recovery unit.
The exhaust heat recovery unit generates electric power from heat of the engine and the charge air via the cooling water. Specifically, the exhaust heat recovery unit includes: an evaporator that evaporates a working medium by using cooling water flowing out of an engine and cooling water flowing out of an air cooler; a power turbine driven by expansion energy of the working medium flowing out of the evaporator; a generator connected to the power turbine; a condenser for condensing the working medium flowing out of the power turbine; and a circulation pump for conveying the working medium flowing out of the condenser to the evaporator.
Patent document 1: japanese patent laid-open publication No. 2016 + 142223.
In the thermal energy recovery system described in patent document 1, it is difficult to efficiently recover heat. Specifically, the temperature of the cooling water flowing out of the engine is not so high, and therefore the amount of heat that can be supplied to the evaporator is insufficient, while the temperature of the cooling water flowing out of the air cooler fluctuates greatly, and therefore the temperature of the cooling water flowing out of the air cooler may be lower than the temperature of the cooling water flowing out of the engine. In this case, the power generation amount by the generator may be reduced, or the working medium may flow into the expander in a gas-liquid two-phase state.
Disclosure of Invention
The invention aims to provide a heat energy recovery system capable of improving heat recovery efficiency and a ship carrying the heat energy recovery system.
In order to achieve the above object, the present invention provides a thermal energy recovery system including: an engine; a supercharger having a turbine driven by exhaust gas discharged from the engine and a compressor connected to the turbine and discharging supercharged air for supply to the engine; an air cooling device for cooling the charge air supplied to the engine; a cooler that stores cooling water for cooling the engine and the charge air and cools the cooling water; a 1 st circulation flow path for circulating the cooling water between the cooler and the engine; a 2 nd circulation flow path for circulating the cooling water between the cooler and the air cooling device; a 1 st heat exchange unit that is provided in a portion between the engine and the cooler in the 1 st circulation flow path and heats the working medium by exchanging heat between the coolant that cools the engine and the working medium; a 2 nd heat exchange unit provided in a portion between the air cooling device and the cooler in the 2 nd circulation flow path, and configured to heat the working medium by exchanging heat between the cooling water flowing out from the air cooling device and the working medium flowing out from the 1 st heat exchange unit; an expander that expands the working medium flowing out of the 2 nd heat exchange unit; a power recovery machine connected to the expander; a condenser for condensing the working medium flowing out of the expander; a pump for feeding the working medium flowing out of the condenser to the 1 st heat exchange unit; a working medium circulation flow path connecting the 1 st heat exchange unit, the 2 nd heat exchange unit, the expander, the condenser, and the pump in this order; and a control unit, a 1 st temperature of the cooling water flowing through a portion between the engine and the 1 st heat exchange unit in the 1 st circulation flow path, a 2 nd temperature of the cooling water flowing through a portion between the air cooling device and the 2 nd heat exchange unit in the 2 nd circulation flow path, wherein the control unit maintains heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit and adjusts an inflow amount of the working medium to the 1 st heat exchange unit such that a degree of superheat of the working medium flowing through a portion between the 2 nd heat exchange unit and the expander in the working medium circulation flow path is within a predetermined range when the 2 nd temperature is higher than the 1 st temperature, and stops heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit when the 2 nd temperature is lower than or equal to the 1 st temperature, and adjusting the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing through the portion between the 1 st heat exchange unit and the 2 nd heat exchange unit in the working medium circulation flow path is within the predetermined range.
In the present thermal energy recovery system, when the 2 nd temperature is higher than the 1 st temperature, the amount of the working medium flowing into the 1 st heat exchange unit is adjusted so that the degree of superheat of the working medium flowing into the expander falls within a predetermined range while maintaining the heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit. In this case, the evaporation of the working medium is mainly performed by the 2 nd heat exchange portion, and therefore, is performed by the working medium receiving heat from the cooling water having a relatively large amount of heat (the cooling water flowing out from the air cooling device). When the 2 nd temperature is equal to or lower than the 1 st temperature, that is, when the temperature of the working medium is likely to decrease in the case where the working medium is heat-exchanged with the cooling water in the 2 nd heat exchange unit, the heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit is stopped, and the inflow amount of the working medium to the 1 st heat exchange unit is adjusted so that the degree of superheat of the working medium flowing out of the 1 st heat exchange unit falls within the predetermined range. This effectively recovers the heat of the engine and the heat of the charge air, and suppresses the working medium from flowing into the expander in a gas-liquid two-phase state.
Further, "stop heat exchange between the coolant and the working medium" does not mean to block all heat transfer between the coolant and the working medium, but means a state in which heat exchange between the coolant and the working medium is not substantially performed.
In this case, it is preferable that the apparatus further comprises: a bypass flow path connected to the 2 nd circulation flow path so as to bypass the 2 nd heat exchange unit; and a switching unit that is switchable between a steady state in which the cooling water flowing out of the air cooling device flows only into the 2 nd heat exchange unit and a bypass state in which the cooling water flowing out of the air cooling device flows only into the bypass flow path; the control unit sets the switching unit to the steady state when the 2 nd temperature is higher than the 1 st temperature, and sets the switching unit to the bypass state when the 2 nd temperature is lower than or equal to the 1 st temperature.
If so, the case where the heat exchange between the cooling water and the working medium is performed in the 2 nd heat exchange unit and the case where the heat exchange between the cooling water and the working medium is stopped are effectively switched according to the relationship between the 1 st temperature and the 2 nd temperature.
In the thermal energy recovery system, when the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit may adjust the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing between the 1 st heat exchange unit and the 2 nd heat exchange unit in the working medium circulation flow path is in the predetermined range, and the degree of superheat of the working medium flowing between the 2 nd heat exchange unit and the expander in the working medium circulation flow path is in a range between an upper limit value of the predetermined range and a limit value lower than a lower limit value of the predetermined range.
In this aspect, since the inflow amount of the working medium to the 1 st heat exchange unit is adjusted based on the degree of superheat of the working medium flowing out of the 1 st heat exchange unit, the responsiveness of adjusting the inflow amount of the working medium to the 1 st heat exchange unit is increased. Further, since the inflow amount of the working medium into the 1 st heat exchange unit is adjusted so that the degree of superheat of the working medium flowing into the expander becomes equal to or greater than the limit value, even if the degree of superheat of the working medium decreases between the inflow of the working medium into the expander after flowing out of the 1 st heat exchange unit, the inflow of the working medium into the expander in a gas-liquid two-phase state is suppressed.
Alternatively, when the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit may adjust the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing through a portion between the 1 st heat exchange unit and the 2 nd heat exchange unit in the working medium circulation flow path is in a range between an upper limit value of the predetermined range and a reference value that is larger than a lower limit value of the predetermined range and smaller than the upper limit value.
In this embodiment, the same effects as described above can be obtained.
Further, the present invention provides a ship equipped with the thermal energy recovery system.
As described above, according to the present invention, it is possible to provide a thermal energy recovery system capable of improving thermal recovery efficiency and a ship equipped with the thermal energy recovery system.
Drawings
Fig. 1 is a view schematically showing the structure of a thermal energy recovery apparatus according to an embodiment of the present invention.
Fig. 2 is a view schematically showing a modification of the thermal energy recovery unit.
Fig. 3 is a view schematically showing a modification of the thermal energy recovery unit.
Fig. 4 is a view schematically showing a modification of the thermal energy recovery unit.
Detailed Description
A thermal energy recovery system according to an embodiment of the present invention will be described with reference to fig. 1. As shown in fig. 1, the heat energy recovery system includes an engine 10, a supercharger 20, an air cooling device 30, a cooler 40, a 1 st circulation flow path 50, a 2 nd circulation flow path 60, a heat energy recovery unit 70, a switching unit 80, and a control unit 90. In the present embodiment, the thermal energy recovery system is mounted on a ship. That is, a marine engine is used as the engine 10.
The supercharger 20 has: a turbine 21 driven by exhaust gas discharged from the engine 10; and a compressor 22 connected to the turbine 21 and discharging the pressurized air for supply to the engine 10. The engine is supplied with pressurized air discharged from the compressor 22 through an intake line 11, which intake line 11 connects the compressor 22 with the engine. Exhaust gas discharged from the engine 10 is supplied to the turbine 21 through an exhaust line 12, and the exhaust line 12 connects the engine 10 and the turbine 21.
An air cooling device 30 is provided in the intake line 11. The air cooling device 30 cools the charge air supplied to the engine 10 (the charge air discharged from the compressor 22) with cooling water.
The cooler 40 stores cooling water for cooling the engine 10 and the charge air, and cools the cooling water with seawater or the like.
The 1 st circulation flow path 50 circulates the cooling water between the cooler 40 and the engine 10. A 1 st pump 51 is provided in a portion of the 1 st circulation flow path 50 downstream of the cooler 40 and upstream of the engine 10.
The 2 nd circulation flow path 60 circulates cooling water between the cooler 40 and the air cooling device 30. A 2 nd pump 61 is provided in a portion of the 2 nd circulation flow path 60 on the downstream side of the cooler 40 and on the upstream side of the air cooling device 30.
The thermal energy recovery unit 70 recovers heat of the engine 10 and heat of the charge air through the aforementioned cooling water. Specifically, the thermal energy recovery unit 70 includes a 1 st heat exchange unit 71, a 2 nd heat exchange unit 72, an expander 73, a power recovery unit 74, a condenser 75, a pump 76, and a working medium circulation flow path 77 that connects the 1 st heat exchange unit 71, the 2 nd heat exchange unit 72, the expander 73, the condenser 75, and the pump 76 in this order through the working medium circulation flow path 77.
The 1 st heat exchange portion 71 is provided in the 1 st circulation flow path 50 at a location between the downstream side of the engine 10 and the upstream side of the cooler 40. The 1 st heat exchange portion 71 heats the working medium by exchanging heat between the working medium and the cooling water flowing out of the engine 10. The 1 st heat exchange unit 71 includes a 1 st working medium flow path 71a through which the working medium flows, a 1 st cooling water flow path 71b through which the cooling water flows, and a 1 st housing unit 71c housing the flow paths 71a and 71 b. The cooling water flowing out of the 1 st cooling water flow path 71b flows into the cooler 40 through the 1 st circulation flow path 50.
The 2 nd heat exchange portion 72 is provided at a position including: a portion of the working medium circulation flow path 77 downstream of the 1 st heat exchange unit 71 and upstream of the expander 73, and a portion of the 2 nd circulation flow path 60 downstream of the air cooling device 30 and upstream of the cooler 40. The 2 nd heat exchange unit 72 heats the working medium by exchanging heat between the cooling water flowing out of the air cooling device 30 and the working medium flowing out of the 1 st heat exchange unit 71. The 2 nd heat exchange unit 72 includes a 2 nd working medium flow path 72a through which the working medium flows, a 2 nd cooling water flow path 72b through which the cooling water flows, and a 2 nd housing unit 72c that houses the flow paths 72a and 72 b. The 1 st housing portion 71c and the 2 nd housing portion 72c may be formed of an integral case or 2 cases independent of each other. Fig. 1 shows an example in which the 1 st housing portion 71c and the 2 nd housing portion 72c are formed by an integral housing. The cooling water flowing out of the 2 nd cooling water flow path 72b flows into the cooler 40 through the 2 nd circulation flow path 60.
The thermal energy recovery system of the present embodiment includes a bypass flow path 62 connected to the 2 nd circulation flow path 60 so as to bypass the 2 nd cooling water flow path 72b of the 2 nd heat exchange unit 72.
The expander 73 is provided in a portion of the working medium circulation flow path 77 on the downstream side of the 2 nd heat exchange unit 72. The expander 73 expands the gas-phase working medium flowing out of the 2 nd heat exchange unit 72. In the present embodiment, a positive displacement screw expander having a rotor that is rotatably driven by expansion of a gas-phase working medium is used as the expander 73.
The power recovery machine 74 is connected to the expander 73. The power recovery machine 74 recovers power from the working medium by rotating with the driving of the expander 73. In the present embodiment, a generator is used as the power recovery machine 74. Further, compressor or the like may be used as power collector 74.
The condenser 75 is provided in a portion of the working medium circulation flow path 77 on the downstream side of the expander 73. The condenser 75 condenses the working medium (seawater or the like) by exchanging heat between the working medium flowing out of the expander 73 and the cooling medium.
The pump 76 is provided in a portion of the working medium circulation flow path 77 on the downstream side of the condenser 75 (a portion between the condenser 75 and the 1 st heat exchange unit 71). The pump 76 sends the liquid-phase working medium flowing out of the condenser 75 to the 1 st heat exchange unit 71.
The switching unit 80 switches between a steady state in which the cooling water flowing out of the air-cooling device 30 flows only into the 2 nd heat exchange unit 72 and a bypass state in which the cooling water flowing out of the air-cooling device 30 flows only into the bypass flow path 62. In the present embodiment, the switching unit 80 includes: a 1 st opening/closing valve V1 provided in the 2 nd circulation flow path 60 at a position between the end of the bypass flow path 62 on the upstream side and the 2 nd heat exchange portion 72; and a 2 nd opening/closing valve V2 provided in the bypass passage 62. That is, the steady state is a state in which the 1 st opening-closing valve V1 is opened and the 2 nd opening-closing valve V2 is closed, and the bypass state is a state in which the 1 st opening-closing valve V1 is closed and the 2 nd opening-closing valve V2 is opened.
When the 2 nd temperature, which is the temperature of the cooling water flowing into the 2 nd heat exchange unit 72 (the cooling water flowing through the portion between the air cooling device 30 and the 2 nd heat exchange unit 72 in the 2 nd circulation flow path 60), is higher than the 1 st temperature, which is the temperature of the cooling water flowing into the 1 st heat exchange unit 71 (the cooling water flowing through the portion between the engine 10 and the 1 st heat exchange unit 71 in the 1 st circulation flow path 50), the control unit 90 maintains the switching unit 80 in the steady state and adjusts the inflow amount of the working medium into the 1 st heat exchange unit 71 so that the superheat degree of the working medium flowing into the expander 73 (the working medium flowing through the portion between the 2 nd heat exchange unit 72 and the expander 73 in the working medium circulation flow path 77) is within a predetermined range. When the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit 90 stops the heat exchange between the coolant and the working medium in the 2 nd heat exchange unit 72, and adjusts the inflow amount of the working medium into the 1 st heat exchange unit 71 so that the degree of superheat of the working medium flowing through the portion between the 1 st working medium flow path 71a and the 2 nd working medium flow path 72a in the working medium circulation flow path 77 falls within the predetermined range.
Here, the stop of the heat exchange between the cooling water and the working medium in the 2 nd heat exchange portion 72 is performed by switching the switching portion 80 from the steady state to the bypass state, that is, from the state in which the 1 st opening/closing valve V1 is open and the 2 nd opening/closing valve V2 is closed to the state in which the 1 st opening/closing valve V1 is closed and the 2 nd opening/closing valve V2 is open. The phrase "stop of heat exchange between the coolant and the working medium" in the 2 nd heat exchange unit 72 does not mean that all heat transfer between the coolant and the working medium is blocked, and means that heat exchange between the coolant and the working medium is not substantially performed.
In the present embodiment, the control unit 90 adjusts the inflow amount of the working medium to the 1 st heat exchange unit 71 by adjusting the rotation speed of the pump 76.
In addition, the aforementioned 1 st temperature is detected by a temperature sensor 91, the temperature sensor 91 being provided at a portion between the engine 10 and the 1 st heat exchange portion 71 in the 1 st circulation flow path 50. The aforementioned 2 nd temperature is detected by a temperature sensor 92, the temperature sensor 92 being provided in the 2 nd circulation flow path 60 at a location on the downstream side of the air-cooling device 30 and on the upstream side of the connection of the 2 nd circulation flow path 60 and the upstream side end of the bypass flow path 62. The degree of superheat of the working medium flowing into the expander 73 is calculated based on the detection values of a temperature sensor 93 and a pressure sensor 94, the temperature sensor 93 and the pressure sensor 94 being provided in the working medium circulation flow path 77 at a location between the 2 nd heat exchange unit 72 and the expander 73. The degree of superheat of the working medium flowing through the working medium circulation flow path 77 at a location between the 1 st working medium flow path 71a and the 2 nd working medium flow path 72a is calculated based on respective detection values of the temperature sensor 95 and the pressure sensor 96 provided at the location.
In the present embodiment, when the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit 90 adjusts the inflow amount of the working medium into the 1 st heat exchange unit 71 so that the degree of superheat of the working medium flowing out of the 1 st working medium flow path 71a (the working medium flowing between the 1 st heat exchange unit 71 and the 2 nd heat exchange unit 72 in the working medium circulation flow path 77) is within the predetermined range, and the degree of superheat of the working medium flowing into the expander 73 is within a range between the upper limit value of the predetermined range and a limit value lower than the lower limit value of the predetermined range. However, when the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit 90 may adjust the inflow amount of the working medium into the 1 st heat exchange unit 71 so that the degree of superheat of the working medium flowing through the portion between the 1 st heat exchange unit 71 and the 2 nd heat exchange unit 72 in the working medium circulation flow path 77 falls within a range between an upper limit value of the predetermined range and a reference value, the reference value being a value larger than the lower limit value of the predetermined range and smaller than the upper limit value.
As described above, in the present thermal energy recovery system, when the 2 nd temperature is higher than the 1 st temperature, the heat exchange between the coolant and the working medium in the 2 nd heat exchange unit 72 is maintained (the switching unit 80 is set to the steady state), and the inflow amount of the working medium to the 1 st heat exchange unit 71 (the rotation speed of the pump 76) is adjusted so that the degree of superheat of the working medium flowing into the expander 73 falls within a predetermined range. In this case, the evaporation of the working medium is mainly performed by the 2 nd heat exchange portion 72, and therefore, is performed by the working medium receiving heat from the cooling water having a relatively large amount of heat (the cooling water flowing out from the air cooling device 30). When the 2 nd temperature is equal to or lower than the 1 st temperature, that is, when the temperature of the working medium may decrease when the working medium is heat-exchanged with the cooling water in the 2 nd heat exchange unit 72, the heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit 72 is stopped (the switching unit 80 is set to the bypass state), and the inflow amount of the working medium to the 1 st heat exchange unit 71 (the rotation speed of the pump 76) is adjusted so that the degree of superheat of the working medium flowing out from the 1 st heat exchange unit 71 falls within the predetermined range. This effectively recovers the heat of the engine 10 and the heat of the supercharged air, and suppresses the working medium from flowing into the expander 73 in a gas-liquid two-phase state.
When the 2 nd temperature is equal to or lower than the 1 st temperature, the control unit 90 adjusts the inflow amount of the working medium into the 1 st heat exchange unit 71 so that the degree of superheat of the working medium flowing out of the 1 st working medium flow path 71a falls within the predetermined range, and so that the degree of superheat of the working medium flowing into the expander 73 falls within a range between the upper limit value and the limit value of the predetermined range. In this embodiment, since the inflow amount of the working medium to the 1 st heat exchange unit 71 is adjusted based on the degree of superheat of the working medium flowing out of the 1 st heat exchange unit 71, the responsiveness of adjusting the inflow amount of the working medium to the 1 st heat exchange unit 71 is increased. Further, since the inflow amount of the working medium into the 1 st heat exchange unit 71 is adjusted so that the degree of superheat of the working medium flowing into the expander 73 becomes equal to or greater than the limit value, even if the degree of superheat of the working medium decreases between the time the working medium flows out from the 1 st heat exchange unit 71 and the time the working medium flows into the expander 73, the working medium is suppressed from flowing into the expander 73 in a gas-liquid two-phase state.
The embodiments disclosed herein are illustrative in all respects and should not be considered as limiting. The scope of the present invention is defined by the claims rather than the description of the embodiments above, and includes all modifications equivalent in meaning and scope to the claims.
For example, the adjustment of the inflow amount of the working medium to the 1 st heat exchange unit 71 by the control unit 90 may be performed by adjusting the opening degree of a bypass valve V3 provided in a bypass passage 78, as shown in fig. 2, the bypass passage 78 being connected to the working medium circulation passage 77 so as to bypass the pump 76. Alternatively, the adjustment of the inflow amount may be performed by adjusting the opening degree of a flow rate adjustment valve V4 provided at a position downstream of the pump 76 in the working medium circulation flow path 77, as shown in fig. 3. In fig. 2 and 3, the signals received by the controller 90 and the signals transmitted by the controller 90 are not shown except for the signals input from the controller 90 to the bypass valve V3 and the flow rate adjustment valve V4.
In addition, instead of the bypass passage 62 connected to the 2 nd circulation passage 60 so as to bypass the 2 nd cooling water passage 72b of the 2 nd heat exchange unit 72, as shown in fig. 4, a bypass passage 79 may be provided, the bypass passage 79 being connected to the working medium circulation passage 77 so as to bypass the 2 nd working medium passage 72a of the 2 nd heat exchange unit 72. Further, a switching unit (in this example, a three-way valve) 80 may be provided at an upstream end of the bypass passage 79 (a connection portion between the 1 st and 2 nd working medium passages 71a, 72a of the working medium circulation passage 77 and the bypass passage 79). In this case, the controller 90 adjusts the opening degree of the switching unit (three-way valve) 80 to switch between the steady state in which the working medium flowing out of the 1 st working medium flow path 71a flows only into the 2 nd working medium flow path 72a and the bypass state in which the working medium flowing out of the 1 st working medium flow path 71a flows only into the bypass flow path 79.
Description of the reference numerals
10 engines
20 pressure booster
21 turbine
22 compressor
30 air cooling device
40 cooler
50 st circulation flow path
60 2 nd circulation flow path
62 bypass flow path
70 heat energy recovery unit
71 No. 1 heat exchange part
72 nd 2 nd heat exchange part
73 expansion machine
74 power recovery machine
75 condenser
76 Pump
77 working medium circulation flow path
80 switching part
90 control part
V1 first opening and closing valve
V2 No. 2 opening and closing valve.
Claims (5)
1. A thermal energy recovery system is characterized by comprising:
an engine;
a supercharger having a turbine driven by exhaust gas discharged from the engine and a compressor connected to the turbine and discharging supercharged air for supply to the engine;
an air cooling device for cooling the charge air supplied to the engine;
a cooler that stores cooling water for cooling the engine and the charge air and cools the cooling water;
a 1 st circulation flow path for circulating the cooling water between the cooler and the engine;
a 2 nd circulation flow path for circulating the cooling water between the cooler and the air cooling device;
a 1 st heat exchange unit that is provided in a portion between the engine and the cooler in the 1 st circulation flow path and heats the working medium by exchanging heat between the coolant that cools the engine and the working medium;
a 2 nd heat exchange unit provided in a portion between the air cooling device and the cooler in the 2 nd circulation flow path, and configured to heat the working medium by exchanging heat between the cooling water flowing out from the air cooling device and the working medium flowing out from the 1 st heat exchange unit;
an expander that expands the working medium flowing out of the 2 nd heat exchange unit;
a power recovery machine connected to the expander;
a condenser for condensing the working medium flowing out of the expander;
a pump for feeding the working medium flowing out of the condenser to the 1 st heat exchange unit;
a working medium circulation flow path connecting the 1 st heat exchange unit, the 2 nd heat exchange unit, the expander, the condenser, and the pump in this order; and
a control unit that controls a temperature of cooling water flowing through a portion between the engine and the 1 st heat exchange unit in the 1 st circulation flow path, a temperature of cooling water flowing through a portion between the air cooling device and the 2 nd heat exchange unit in the 2 nd circulation flow path, and a temperature of cooling water flowing through a portion between the 2 nd heat exchange unit and the 2 nd heat exchange unit in the 2 nd circulation flow path, wherein the control unit maintains heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit and adjusts an inflow amount of the working medium to the 1 st heat exchange unit so that a degree of superheat of the working medium flowing through a portion between the 2 nd heat exchange unit and the expander in the working medium circulation flow path becomes a predetermined range when the 2 nd temperature is higher than or equal to the 1 st temperature, and stops heat exchange between the cooling water and the working medium in the 2 nd heat exchange unit when the 2 nd temperature is lower than or equal to the 1 st temperature, and adjusting the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing through the portion between the 1 st heat exchange unit and the 2 nd heat exchange unit in the working medium circulation flow path is within the predetermined range.
2. The thermal energy recovery system of claim 1,
further comprises:
a bypass flow path connected to the 2 nd circulation flow path so as to bypass the 2 nd heat exchange unit; and
a switching unit that is switchable between a steady state in which the cooling water flowing out of the air cooling device flows only into the 2 nd heat exchange unit and a bypass state in which the cooling water flowing out of the air cooling device flows only into the bypass flow path;
the control unit sets the switching unit to the steady state when the 2 nd temperature is higher than the 1 st temperature, and sets the switching unit to the bypass state when the 2 nd temperature is lower than or equal to the 1 st temperature.
3. The thermal energy recovery system of claim 1 or 2,
the control unit adjusts the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing between the 1 st heat exchange unit and the 2 nd heat exchange unit in the working medium circulation flow path is within the predetermined range, and so that the degree of superheat of the working medium flowing between the 2 nd heat exchange unit and the expander in the working medium circulation flow path is within a range between an upper limit value and a limit value of the predetermined range, the limit value being a value lower than a lower limit value of the predetermined range, when the 2 nd temperature is equal to or lower than the 1 st temperature.
4. The thermal energy recovery system of claim 1 or 2,
the control unit adjusts the inflow amount of the working medium into the 1 st heat exchange unit so that the degree of superheat of the working medium flowing through the portion of the working medium circulation flow path between the 1 st heat exchange unit and the 2 nd heat exchange unit is in a range between an upper limit value of the predetermined range and a reference value, the reference value being a value greater than the lower limit value of the predetermined range and smaller than the upper limit value, when the 2 nd temperature is equal to or lower than the 1 st temperature.
5. A marine vessel, characterized in that,
a thermal energy recovery system according to any one of claims 1 to 4 is mounted thereon.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017122000A JP6761380B2 (en) | 2017-06-22 | 2017-06-22 | Thermal energy recovery system and ships equipped with it |
| JP2017-122000 | 2017-06-22 |
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| CN109113819A CN109113819A (en) | 2019-01-01 |
| CN109113819B true CN109113819B (en) | 2021-03-16 |
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| JP (1) | JP6761380B2 (en) |
| KR (1) | KR101990247B1 (en) |
| CN (1) | CN109113819B (en) |
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| JP7201562B2 (en) | 2019-09-27 | 2023-01-10 | 株式会社神戸製鋼所 | GENERATING DEVICE AND CONTROL METHOD OF GENERATING DEVICE |
| CN111022183A (en) * | 2019-12-18 | 2020-04-17 | 周旭龙 | Cogeneration system |
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| JP2013160132A (en) * | 2012-02-03 | 2013-08-19 | Mitsubishi Heavy Ind Ltd | Exhaust-heat recovery and utilization system |
| CN104975894A (en) * | 2014-04-04 | 2015-10-14 | 株式会社神户制钢所 | Waste heat recovery system and waste heat recovery method |
| JP2016142223A (en) * | 2015-02-04 | 2016-08-08 | 三菱重工業株式会社 | Exhaust heat recovery device, exhaust heat recovery type ship propulsion device and exhaust heat recovery method |
| CN106555624A (en) * | 2015-09-29 | 2017-04-05 | 株式会社神户制钢所 | Heat reclaiming system |
| JP2019007378A (en) * | 2017-06-22 | 2019-01-17 | 株式会社神戸製鋼所 | Thermal energy recovery system and ship equipped with the same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6986251B2 (en) * | 2003-06-17 | 2006-01-17 | Utc Power, Llc | Organic rankine cycle system for use with a reciprocating engine |
| JP2011149332A (en) * | 2010-01-21 | 2011-08-04 | Mitsubishi Heavy Ind Ltd | Exhaust heat recovery power generating device and ship with the same |
| JP2011231636A (en) * | 2010-04-26 | 2011-11-17 | Mitsubishi Heavy Ind Ltd | Exhaust heat recovery power generator and ship provided with exhaust heat recovery power generator |
| JP6214252B2 (en) * | 2013-07-12 | 2017-10-18 | 日立造船株式会社 | Boiler system |
| JP6223886B2 (en) * | 2014-03-28 | 2017-11-01 | 株式会社神戸製鋼所 | Power generator |
| JP5801449B1 (en) * | 2014-06-10 | 2015-10-28 | サムソン ヘビー インダストリーズ カンパニー，リミテッド | Marine waste heat recovery system |
| KR101614605B1 (en) * | 2014-08-01 | 2016-04-22 | 현대중공업 주식회사 | Supercritical Carbon Dioxide Power Generation System and Ship having the same |
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- 2018-06-11 KR KR1020180066645A patent/KR101990247B1/en active IP Right Grant
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013160132A (en) * | 2012-02-03 | 2013-08-19 | Mitsubishi Heavy Ind Ltd | Exhaust-heat recovery and utilization system |
| CN104975894A (en) * | 2014-04-04 | 2015-10-14 | 株式会社神户制钢所 | Waste heat recovery system and waste heat recovery method |
| JP2016142223A (en) * | 2015-02-04 | 2016-08-08 | 三菱重工業株式会社 | Exhaust heat recovery device, exhaust heat recovery type ship propulsion device and exhaust heat recovery method |
| CN106555624A (en) * | 2015-09-29 | 2017-04-05 | 株式会社神户制钢所 | Heat reclaiming system |
| JP2019007378A (en) * | 2017-06-22 | 2019-01-17 | 株式会社神戸製鋼所 | Thermal energy recovery system and ship equipped with the same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109113819A (en) | 2019-01-01 |
| JP6761380B2 (en) | 2020-09-23 |
| KR101990247B1 (en) | 2019-06-17 |
| KR20190000292A (en) | 2019-01-02 |
| JP2019007379A (en) | 2019-01-17 |
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