WO2018047525A1 - 船舶の冷却システム - Google Patents

船舶の冷却システム Download PDF

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Publication number
WO2018047525A1
WO2018047525A1 PCT/JP2017/027867 JP2017027867W WO2018047525A1 WO 2018047525 A1 WO2018047525 A1 WO 2018047525A1 JP 2017027867 W JP2017027867 W JP 2017027867W WO 2018047525 A1 WO2018047525 A1 WO 2018047525A1
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WIPO (PCT)
Prior art keywords
fresh water
temperature
line
seawater
heat exchanger
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Application number
PCT/JP2017/027867
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
岳夫 宇井
桂介 三宅
雄輝 宍粟
Original Assignee
川崎重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Priority to CN201780053414.2A priority Critical patent/CN109642488B/zh
Priority to KR1020197008523A priority patent/KR102240300B1/ko
Publication of WO2018047525A1 publication Critical patent/WO2018047525A1/ja

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Classifications

    • 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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
    • B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/38—Apparatus or methods specially adapted for use on marine vessels, for handling power plant or unit liquids, e.g. lubricants, coolants, fuels or the like
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/14—Indicating devices; Other safety devices
    • F01P11/16—Indicating devices; Other safety devices concerning coolant temperature
    • 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
    • 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • 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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • 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
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature

Definitions

  • the present invention relates to a ship cooling system.
  • Patent Document 1 discloses a ship cooling system 100 as shown in FIG.
  • seawater is guided from the outside of the hull to the heat exchanger 110 by the first seawater line 151, and is guided from the heat exchanger 110 to the outside of the hull by the second seawater line 152.
  • a seawater pump 160 is provided in the first seawater line 151.
  • the fresh water that exchanges heat with seawater in the heat exchanger 110 is guided from the heat exchanger 110 to the main machine 120 through the first fresh water line 131, and from the main machine 120 to the heat exchanger 110 through the second fresh water line 132.
  • a bypass line 133 is connected to the first fresh water line 131 and the second fresh water line 132 so as to bypass the heat exchanger 110.
  • the ratio of the flow rate of fresh water passing through the heat exchanger 110 and the flow rate of fresh water flowing through the bypass line 133 is changed by the temperature adjustment valve 140.
  • the temperature adjustment valve 140 is controlled by the control device 170.
  • Control device 170 controls temperature adjustment valve 140 so that the temperature of fresh water supplied to main unit 120 is constant. Moreover, the control apparatus 170 controls the rotation speed of the seawater pump 160 through the inverter 175 so that the opening degree by the side of the heat exchanger 110 of the temperature control valve 140 may approach the target opening degree.
  • an object of the present invention is to provide a ship cooling system that can further improve the fuel consumption of the main engine.
  • the inventors of the present invention As a result of earnest research, when the main engine is a reciprocating engine, fresh water cools not only the main engine but also the air supplied from the supercharger to the main engine. In view of the fact that if the temperature of the fresh water supplied to the air cooler is lowered, the fuel efficiency of the main engine will be improved because it is also supplied to the air cooler, a control method has been devised. The present invention has been made from such a viewpoint.
  • a cooling system for a ship includes a heat exchanger that performs heat exchange between fresh water and seawater to cool the fresh water, and a seawater pump that guides seawater from outside the hull to the heat exchanger.
  • a first seawater line provided with a second seawater line for guiding seawater from the heat exchanger to the outside of the hull, and a main engine that is a reciprocating engine of a ship and a supercharger that supplies the main engine from the heat exchanger
  • a first fresh water line that guides fresh water to an air cooler that cools the air to be cooled, a second fresh water line that guides fresh water from the main engine and the air cooler to the heat exchanger, and the second fresh water so as to bypass the heat exchanger
  • a temperature control valve that changes a ratio between a bypass line branched from the line and joined to the first fresh water line, a flow rate of fresh water passing through the heat exchanger and a flow rate of fresh water flowing through the bypass line, and A temperature sensor after cooling fresh water that detects the temperature of fresh water flowing
  • the rotation speed of the seawater pump is controlled via an inverter so that the temperature detected by the temperature sensor after cooling with fresh water is maintained at a set temperature, and the rotation speed of the seawater pump becomes the minimum rotation speed.
  • the temperature detected by the temperature sensor after cooling with fresh water becomes lower than the set temperature, the temperature detected by the temperature sensor after cooling with fresh water is kept at the lower limit temperature lower than the set temperature.
  • a control device for controlling the temperature regulating valve is controlled via an inverter so that the temperature detected by the temperature sensor after cooling with fresh water is maintained at a set temperature, and the rotation speed of the seawater pump becomes the minimum rotation speed.
  • a cooling system for a ship includes a heat exchanger that performs heat exchange between fresh water and seawater to cool the fresh water, and first guides seawater from outside the hull to the heat exchanger.
  • a first seawater line provided with a seawater pump that can be switched to either a rotational speed or a second rotational speed greater than the first rotational speed; and a second seawater line that guides the seawater from the heat exchanger to the outside of the hull.
  • a first fresh water line that guides fresh water from the heat exchanger to an air cooler that cools air supplied to the main engine from a main engine and a supercharger that are reciprocating engines of a ship, and the heat exchange from the main engine and the air cooler A second fresh water line that guides fresh water to the vessel, a bypass line that branches from the second fresh water line so as to bypass the heat exchanger and joins the first fresh water line, and fresh water that passes through the heat exchanger Flow And a temperature control valve that changes the ratio of the flow rate of fresh water flowing through the bypass line, a temperature sensor after fresh water cooling that detects the temperature of fresh water flowing through the first fresh water line at a downstream side of the junction of the bypass line, and A temperature sensor before fresh water cooling that detects the temperature of fresh water flowing through the second fresh water line, a sea water inflow temperature sensor that detects the temperature of sea water flowing through the first sea water line, a temperature sensor after fresh water cooling, and the fresh water cooling Based on the temperature detected by the pre-temperature sensor and the seawater inflow temperature
  • the temperature control valve is controlled so that water does not flow and the low-speed operation condition is satisfied, the temperature detected by the temperature sensor after the fresh water cooling when the seawater pump is switched to the first rotation speed is And a control device that controls the temperature regulating valve so as to be maintained at a lower limit temperature lower than the set temperature.
  • the heat exchanger is configured to cool fresh water to a set temperature or lower when the seawater pump reaches the second rotation speed. Therefore, according to said structure, the temperature of the fresh water supplied to a main machine and an air cooler can be changed between preset temperature and minimum temperature. That is, if the temperature of the fresh water supplied to the air cooler is lower than the set temperature, the temperature of the air supplied to the main machine is lowered. Thereby, the fuel consumption of the main engine can be improved. Moreover, in the above configuration, it is not necessary to use an inverter, so that the cost can be reduced.
  • the seawater pump is configured to be manually switched between the first rotation speed and the second rotation speed, and the control device displays whether or not the low speed operation condition is satisfied. You may display via.
  • the seawater pump is configured to be switched to either the first rotation speed or the second rotation speed by an electric signal, and the control device is configured to perform the above operation when the low-speed operation condition is not satisfied.
  • the seawater pump may be switched to the first rotational speed.
  • the control device When the seawater pump is at the second rotation speed, the control device is configured to change the heat exchanger based on temperatures detected by the temperature sensor after fresh water cooling, the temperature sensor before fresh water cooling, and the seawater inflow temperature sensor.
  • the heat exchange capacity coefficient may be calculated, and it may be determined whether or not the low speed operation condition is satisfied using the calculated heat exchange capacity coefficient. According to this configuration, it is possible to determine whether or not the low-speed operation condition is satisfied in consideration of the secular change due to dirt or the like of the heat exchanger.
  • the first fresh water line guides fresh water from the heat exchanger not only to the main engine and the air cooler but also to the EGR cooler, and the second fresh water line serves not only from the main machine and the air cooler but also from the EGR cooler. You may guide fresh water to the exchanger.
  • EGR is used only in a specific sea area.
  • the cooling system has sufficient cooling capacity during normal operation in which EGR is not used, so that the effect of improving the fuel consumption of the main engine can be obtained more remarkably.
  • the first fresh water line leads fresh water from the heat exchanger not only to the main engine and the air cooler but also to special cooling equipment that requires cooling at a constant temperature
  • the second fresh water line includes only the main machine and the air cooler.
  • the cooling system is branched from the second fresh water line so as to form a circulation circuit for the special cooling equipment.
  • a reflux line may be further provided to join the two. According to this configuration, the fresh water supplied to the special cooling device can be kept at a constant temperature.
  • the fuel consumption of the main engine of the ship can be further improved.
  • FIG. 1 is a schematic configuration diagram of a ship cooling system according to a first embodiment of the present invention. It is a systematic diagram regarding the supply and exhaust of the main engine. It is a schematic block diagram of the cooling system of the ship which concerns on 2nd Embodiment of this invention. It is a schematic block diagram of the conventional ship cooling system.
  • FIG. 1 shows a cooling system 1A for a ship according to a first embodiment of the present invention.
  • This cooling system 1A is for cooling the main engine 11 and other equipment of a ship using fresh water and seawater.
  • the main machine 11 may drive a screw propeller (not shown) directly (mechanical propulsion) or may be driven via a generator and a motor (electric propulsion).
  • the main engine 11 is a reciprocating engine and has a plurality of combustion chambers formed by cylinders and pistons.
  • the main machine 11 is connected to the compressor 92 of the supercharger 91 through an air supply line 94 and is connected to the turbine 93 of the supercharger 91 through an exhaust line 95.
  • An air cooler 12 is provided in the air supply line 94. The air cooler 12 cools the air supplied from the compressor 92 of the supercharger 91 to the main engine 11.
  • an EGR (Exhaust Gas Recirculation) line 96 is branched from the exhaust line 95, and the EGR line 96 joins the air supply line 94 on the downstream side of the air cooler 12.
  • the EGR line 96 is provided with an EGR cooler 13 and a blower 97 in order from the upstream side.
  • the cooling system 1A includes a heat exchanger 21 that performs heat exchange between fresh water and seawater to cool the fresh water.
  • the cooling system 1A includes a first seawater line 31 that guides seawater from outside the hull to the heat exchanger 21 and a second seawater line 32 that guides seawater from the heat exchanger 21 to the outside of the hull.
  • the first seawater line 31 is provided with a seawater pump 33.
  • the cooling system 1A guides fresh water from the heat exchanger 21 to the main machine 11, the air cooler 12 and the EGR cooler 13, and the fresh water from the main machine 11, the air cooler 12 and the EGR cooler 13 to the heat exchanger 21.
  • 2nd fresh water line 5 is included.
  • the first fresh water line 4 guides fresh water from the heat exchanger 21 to the special cooling device 14 that requires cooling at a constant temperature
  • the second fresh water line 5 passes from the special cooling device 14 to the heat exchanger. Leads Shimizu to 21.
  • the special cooling device 14 is, for example, a power generation engine.
  • the first fresh water line 4 includes one main flow path 41 extending from the heat exchanger 21, the main flow path 41, and the above-described cooling target devices (main machine 11, air cooler 12, EGR cooler 13, and special cooling device 14). Are connected to each other.
  • the 2nd fresh water line 5 has the one main flow path 51 extended from the heat exchanger 21, and the several branch flow path 52 which each connects the main flow path 51 and a cooling object apparatus.
  • a bypass line 22 is connected to the first fresh water line 4 and the second fresh water line 5 so as to bypass the heat exchanger 110.
  • the bypass line 22 branches from the main flow path 51 of the second fresh water line 5 and merges with the main flow path 41 of the first fresh water line 4.
  • the main flow path 51 of the second fresh water line 5 is provided with a fresh water pump 23 upstream of the branch point of the bypass line 22.
  • the ratio of the flow rate of fresh water passing through the heat exchanger 21 and the flow rate of fresh water flowing through the bypass line 22 is changed by the temperature adjustment valve 24.
  • the temperature adjustment valve 24 is a three-way valve (mixing valve) provided at the junction of the bypass line 22 in the main flow path 41 of the first fresh water line 4.
  • the temperature adjustment valve 24 may be a three-way valve (distribution valve) provided at the branch point of the bypass line 22 in the main flow path 51 of the second fresh water line 5.
  • the temperature adjustment valve 24 includes a first flow rate control valve provided in a portion upstream of the junction of the bypass line 22 in the main flow channel 41 or a portion downstream of the branch point of the bypass line 22 in the main flow channel 51. You may comprise the 2nd flow control valve provided in the bypass line 22.
  • a circulation line 61 is connected to the branch passages 42 and 52 for the main machine 11 in the first and second fresh water lines 4 and 5.
  • the circulation line 61 branches from the branch flow path 52 of the second fresh water line 5 and joins the branch flow path 42 of the first fresh water line 4 so as to form a circulation circuit for the main machine 11.
  • the circulation line 61 is provided with a pump 62 for circulating fresh water in the circulation circuit for the main machine 11.
  • the pump 62 may be provided in a portion upstream of the branch point of the circulation line 61 in the branch flow path 52 or a portion downstream of the junction of the circulation line 61 in the branch flow path 42.
  • the circulation circuit for the main machine 11 is provided with a temperature adjustment valve 63 for keeping the temperature of the fresh water supplied to the main machine 11 constant.
  • the temperature adjustment valve 63 is a three-way valve (mixing valve) provided at the junction of the circulation line 61 in the branch flow path 42, but the temperature adjustment valve 63 is a branch of the circulation line 61 in the branch flow path 52. It may be a three-way valve (distribution valve) provided at the point.
  • a circulation line 64 is connected to the branch passages 42 and 52 for the special cooling device 14 in the first fresh water line 4 and the second fresh water line 5.
  • the circulation line 64 branches from the branch flow path 52 of the second fresh water line 5 and joins the branch flow path 42 of the first fresh water line 4 so as to form a circulation circuit for the special cooling device 14.
  • the circulation line 64 is provided with a pump 65 for circulating fresh water in the circulation circuit for the special cooling device 14.
  • the pump 65 may be provided at a portion upstream of the branch point of the circulation line 64 in the branch flow path 52 or a portion downstream of the junction of the circulation line 64 in the branch flow path 42.
  • the circulation circuit for the special cooling device 14 is provided with a temperature adjustment valve 66 for keeping the temperature of the fresh water supplied to the special cooling device 14 constant.
  • the temperature adjustment valve 66 is a three-way valve (mixing valve) provided at the junction of the circulation line 64 in the branch flow path 42, but the temperature adjustment valve 66 is a branch of the circulation line 61 in the branch flow path 52. It may be a three-way valve (distribution valve) provided at the point.
  • the temperature adjusting valves 24, 63, 66 described above are controlled by the control device 7. Further, the control device 7 controls the rotational speed of the seawater pump 33 described above via the inverter 8. In FIG. 1, only some signal lines are drawn for the sake of simplicity. On the other hand, the rotation speed of the fresh water pump 23 is constant.
  • the control device 7 is a computer having a memory such as a ROM or a RAM and a CPU. The control device 7 may be a single device, or may be divided into a device for controlling the seawater pump 33 and a plurality of devices for controlling the temperature control valves 24, 63, 66.
  • the control of the temperature adjustment valve 24 will be described in detail.
  • the main flow path 41 of the first fresh water line 4 is provided with a fresh water cooled temperature sensor 71 that detects the temperature of the fresh water flowing through the first fresh water line 4 on the downstream side of the junction of the bypass line 22.
  • a temperature sensor for controlling the seawater pump is used as the temperature sensor 71 after cooling with fresh water.
  • a temperature sensor for controlling the temperature regulating valve 24 may be used.
  • the control device 7 controls the temperature control valve 24 so that fresh water does not flow into the bypass line 22 in a normal state, and then inverts the temperature detected by the temperature sensor 71 after cooling with fresh water to the set temperature Td. 8 to control the rotation speed of the seawater pump 33. That is, at the normal time, the rotation speed of the seawater pump 33 is adjusted between the maximum rotation speed N1 and the minimum rotation speed N2 so that the temperature of the fresh water flowing out from the heat exchanger 21 is constant.
  • the set temperature Td is 36 ° C.
  • the maximum rotation speed N1 and the minimum rotation speed N2 are 1200 rpm and 600 rpm, respectively.
  • the control device 7 changes the temperature from the constant temperature control to the temperature. Transition to variable control.
  • the constant temperature control is control in which the temperature of fresh water supplied to the cooling target devices (main machine 11, air cooler 12, EGR cooler 13 and special cooling device 14) is kept at the set temperature Td, and temperature variable control is the cooling target. In this control, the temperature of fresh water supplied to the device is kept lower than the set temperature Td.
  • the control device 7 controls the temperature adjustment valve 24 so that the temperature detected by the temperature sensor 71 after cooling with fresh water is maintained at the lower limit temperature Tl lower than the set temperature Td.
  • the lower limit temperature Tl is 10 ° C.
  • the temperature of seawater may be below 10 ° C.
  • the control device 7 controls the temperature adjustment valve 24 so that fresh water does not flow into the bypass line 22. .
  • the temperature of the fresh water supplied to the equipment to be cooled is left to random (precisely, the main engine 11 and the special cooling equipment 14 have the constant temperature of fresh water by the action of the temperature control valves 63 and 66. Is supplied).
  • the control device 7 causes the fresh water to flow through the bypass line 22 and the temperature detected by the fresh water cooling temperature sensor 71 is the lower limit temperature.
  • the temperature adjustment valve 24 is controlled so as to rise to Tl.
  • the temperature constant control is executed in the normal time.
  • the seawater pump 33 reaches the minimum rotation speed N2
  • the temperature of the fresh water supplied to the cooling target device is between the set temperature Td and the lower limit temperature Tl when the fresh water does not flow into the bypass line 22.
  • the lower limit temperature Tl is maintained. That is, when the seawater pump 33 reaches the minimum rotation speed N2, the temperature of fresh water supplied to the air cooler 12 can be kept lower than the set temperature Td. Thereby, the temperature of the air supplied to the main unit 11 is lowered, and the fuel consumption of the main unit 11 can be improved.
  • EGR is used only in a specific sea area. That is, since there is a margin in the cooling capacity of the cooling system 1A during normal operation in which EGR is not used, the effect of improving the fuel consumption of the main engine 11 can be obtained more remarkably.
  • the circulation circuit for the special cooling device 14 since the circulation circuit for the special cooling device 14 is formed, the fresh water supplied to the special cooling device 14 can be kept at a constant temperature.
  • FIG. 3 shows a cooling system 1B for a ship according to a second embodiment of the present invention.
  • the cooling system 1B is different from the cooling system 1A of the first embodiment in that the seawater pump 33 can be switched between the first rotation speed Na and the second rotation speed Nb that is larger than the first rotation speed Na. is there.
  • the first rotation speed Na is 600 rpm
  • the second rotation speed Nb is 1200 rpm.
  • the seawater pump 33 is configured to be manually switched between the first rotation speed Na and the second rotation speed Nb.
  • the control device 7 is connected to the display 9.
  • a fresh water cooling temperature sensor 72 is provided in the main flow path 51 of the second fresh water line 5, and a sea water inflow temperature sensor 73 is provided in the first sea water line 31.
  • the fresh water pre-cooling temperature sensor 72 detects the temperature of fresh water flowing through the main flow path 51 of the second fresh water line 5, and the seawater inflow temperature sensor 73 detects the temperature of seawater flowing through the first seawater line 31.
  • the control device 7 determines whether or not the low speed operation condition is satisfied based on the temperatures detected by the fresh water cooling temperature sensor 71, the fresh water cooling temperature sensor 72, and the seawater inflow temperature sensor 73.
  • the low-speed operation condition is a condition that the fresh water can be cooled to the set temperature Td or less by the heat exchanger 21 when the seawater pump 33 is set to the first rotation speed Na.
  • the control device 7 displays whether or not the low speed operation condition is satisfied via the display unit 9.
  • the display 9 may be a display having a screen or a simple lamp. Even when the control device 7 displays the information via the display 9, whether or not the low-speed operation condition is satisfied is displayed with the content indicating which of the first rotation speed Na and the second rotation speed Nb should be selected. Good. The ship operator looks at the display on the display 9 and switches the seawater pump 33 to the first rotation speed Na or the second rotation speed Nb.
  • the control device 7 controls the temperature adjustment valve 24 so that fresh water does not flow into the bypass line 22 when the seawater pump 33 is switched to the second rotation speed Nb.
  • the control device 7 determines that the temperature detected by the temperature sensor 71 after cooling with fresh water when the seawater pump 33 is switched to the first rotation speed Na is lower than the set temperature Td.
  • the temperature adjustment valve 24 is controlled so as to be maintained at Tl.
  • the control device 7 controls the temperature adjustment valve 24 so that fresh water does not flow into the bypass line 22. . That is, in this case, the temperature of the fresh water supplied to the devices to be cooled (the main machine 11, the air cooler 12, the EGR cooler 13, and the special cooling device 14) depends on the situation (more precisely, the main machine 11 and the special cooling device 14).
  • the control device 7 causes the fresh water to flow through the bypass line 22 and the temperature detected by the fresh water cooling temperature sensor 71 is the lower limit temperature.
  • the temperature adjustment valve 24 is controlled so as to rise to Tl.
  • the control apparatus 7 when the seawater pump 33 is the 2nd rotation speed Nb, the control apparatus 7 is the temperature detected by the temperature sensor 71 after fresh water cooling, the temperature sensor 72 before fresh water cooling, and the seawater inflow temperature sensor 73. Based on this, the heat exchange capacity coefficient Kb of the heat exchanger 21 is calculated, and it is determined whether or not the low speed operation condition is satisfied using the calculated heat exchange capacity coefficient Kb.
  • the temperature detected by the temperature sensor 71 after cooling with fresh water becomes equal to or higher than the set temperature Tb when the low-speed operation condition is not satisfied.
  • the control device 7 first calculates the heat exchange amount Q from the following Equation 1.
  • Q (Tf1 ⁇ Tf2) ⁇ cf ⁇ df ⁇ Ff (Formula 1)
  • Tf1 Temperature detected by temperature sensor 72 before fresh water cooling
  • Tf2 Temperature detected by temperature sensor 71 after cooling fresh water
  • cf Specific heat of fresh water
  • df Specific gravity of fresh water
  • Ff Flow rate of fresh water (converted from the number of rotations of fresh water pump 23) )
  • the control apparatus 7 calculates seawater outflow temperature Ts2b from the following formula 2.
  • Ts2b Ts1 + Q / (cs ⁇ ds ⁇ Fsb) (Formula 2)
  • Ts1 Temperature detected by the seawater inflow temperature sensor 73
  • cs Specific heat of seawater ds: Specific gravity of seawater
  • Fsb Flow rate of seawater at the second rotation speed Nb
  • the control device 7 calculates the logarithmic average temperature difference LMTDb at the second rotation speed Nb from the following Expression 3.
  • LMTDb (TD1b ⁇ TD2b) / ln (TD1b / TD2b) ...
  • TD1b Fresh water inlet side temperature difference (Tf1-Ts2b)
  • TD2b Fresh water outlet side temperature difference (Tf2-Ts1)
  • control device 7 calculates the heat exchange capacity coefficient Kb from the following equation 4.
  • Kb Q / LMTDb (Formula 4)
  • control device 7 calculates a virtual heat exchange capacity coefficient Ka at which the fresh water outflow temperature becomes the set temperature Td when the seawater pump 33 is set to the first rotation speed Na.
  • the control device 7 calculates the fresh water cooling pre-cooling temperature Tf1a from the following Equation 5.
  • Tf1a Td + Q / (cf ⁇ df ⁇ Ff) (Formula 5)
  • the control device 7 calculates the seawater outflow temperature Ts2a from the following Expression 6.
  • Ts2a Ts1 + Q / (cs ⁇ ds ⁇ Fsa) (Formula 6)
  • Fsa Flow rate of seawater at the first rotation speed Na
  • the control device 7 calculates the logarithmic average temperature difference LMTDa at the first rotation speed Na from the following Expression 7.
  • LMTDa (TD1a ⁇ TD2a) / ln (TD1a / TD2a) ...
  • TD1a fresh water inlet side temperature difference
  • Tf1a-Ts2a fresh water outlet side temperature difference
  • Td-Ts1 fresh water outlet side temperature difference
  • control device 7 calculates the heat exchange capacity coefficient Ka from the following Expression 8.
  • Ka Q / LMTDa (Formula 8)
  • the control device 7 After calculating both the heat exchange capacity coefficient Kb at the second rotation speed Nb and the virtual heat exchange capacity coefficient Ka at the first rotation speed Na, the control device 7 compares them, and Kb> Ka If there is, it is determined that the low speed operation condition is satisfied, and if Kb ⁇ Ka, it is determined that the low speed operation condition is not satisfied.
  • the heat exchanger 21 is configured to cool the fresh water to a set temperature Td or less when the seawater pump 33 reaches the second rotation speed Nb. Therefore, if it is control like this embodiment, the temperature of the fresh water supplied to a cooling object apparatus can be changed between preset temperature Td and lower limit temperature Tl. That is, if the temperature of the fresh water supplied to the air cooler 12 is lower than the set temperature Td, the temperature of the air supplied to the main machine 11 is lowered. Thereby, the fuel consumption of the main engine 11 can be improved. Moreover, in the above configuration, it is not necessary to use the inverter 8 (see FIG. 1), so that the cost can be reduced.
  • the heat exchange capacity coefficient K at the time of design is stored in the control device 7 in advance, It may be determined whether or not the low-speed operation condition is satisfied using the heat exchange capacity coefficient K.
  • the heat exchange capacity coefficient Kb of the heat exchanger 21 is calculated as in the above embodiment, it is possible to determine whether or not the low speed operation condition is satisfied in consideration of the secular change due to contamination of the heat exchanger 21 or the like. it can.
  • the low-speed operation condition when the change of the heat exchange capability when the flow rate of seawater is changed is known as a characteristic of the heat exchanger 21, it may be determined whether or not the low-speed operation condition is satisfied by taking this effect into consideration. . For example, if the heat exchange capacity is reduced by 20% when the flow rate of seawater is reduced, the low speed operation condition may be determined as Kb ⁇ 0.8> Ka.
  • the seawater pump 33 may be configured to be switched to either the first rotation speed Na or the second rotation speed Nb by an electric signal.
  • the control device 7 switches the seawater pump 33 to the second rotation speed Nb when the low speed operation condition is not satisfied, and switches the seawater pump 33 to the first rotation speed Na when the low speed operation condition is satisfied.
  • a seawater outflow temperature sensor may be provided in the second seawater line 32, and the temperature directly detected by this temperature sensor may be used as the seawater outflow temperature Ts2b.
  • the EGR line 96 and the EGR cooler 13 may not be provided. 1 and 3, not only the EGR cooler 13 but also the special cooling device 14 may be employed, and the first fresh water line 4 may guide fresh water from the heat exchanger 21 only to the main machine 11 and the air cooler 12.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Ocean & Marine Engineering (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Heat Treatment Of Water, Waste Water Or Sewage (AREA)
PCT/JP2017/027867 2016-09-06 2017-08-01 船舶の冷却システム WO2018047525A1 (ja)

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CN109736931A (zh) * 2019-03-01 2019-05-10 广西玉柴机器股份有限公司 汽车模拟水箱装置

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CN110745229A (zh) * 2019-11-26 2020-02-04 南通旭日船用机械有限公司 一种板式冷却器海水变频控制方法及系统
KR102336108B1 (ko) * 2021-06-01 2021-12-10 (주) 대경엔지니어링 충전케이블 안전구조를 포함하는 전기선박 충전시스템
CN114109577A (zh) * 2021-11-10 2022-03-01 中国重汽集团济南动力有限公司 一种发动机余热管理系统及其使用方法
CN114572372A (zh) * 2022-02-18 2022-06-03 中国船舶重工集团公司第七一九研究所 船舶定频泵冷却系统及其控制方法、电子设备和存储介质
CN115434833B (zh) * 2022-09-30 2023-07-25 南通中远海运川崎船舶工程有限公司 一种新型egr主机的冷却水系统

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KR20190040058A (ko) 2019-04-16
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CN109642488B (zh) 2021-05-07
JP6788440B2 (ja) 2020-11-25

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