CN113565616A - Heat radiating device of marine diesel engine structure - Google Patents
Heat radiating device of marine diesel engine structure Download PDFInfo
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- CN113565616A CN113565616A CN202110817570.XA CN202110817570A CN113565616A CN 113565616 A CN113565616 A CN 113565616A CN 202110817570 A CN202110817570 A CN 202110817570A CN 113565616 A CN113565616 A CN 113565616A
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- end water
- water inlet
- pipe
- hot end
- inlet pipe
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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
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
- F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
- F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
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- H—ELECTRICITY
- H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N10/00—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects
- H10N10/10—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects operating with only the Peltier or Seebeck effects
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- H—ELECTRICITY
- H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
- H10N10/00—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects
- H10N10/10—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects operating with only the Peltier or Seebeck effects
- H10N10/17—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects operating with only the Peltier or Seebeck effects characterised by the structure or configuration of the cell or thermocouple forming the device
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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
Abstract
The invention discloses a heat dissipation device of a marine diesel engine structure, which comprises a plate heat exchanger. A hot end water inlet pipe and a hot end water outlet pipe are fixedly connected to the plate heat exchanger; the hot end water inlet pipe and the hot end water outlet pipe are connected with a hot end water tank, and the hot end water inlet pipe, the hot end water outlet pipe, the hot end water tank and the plate heat exchanger form a closed water path; a cold end water inlet pipe and a cold end water outlet pipe are fixedly connected to the plate heat exchanger; a gas-liquid mixer is fixedly connected to the cold end water inlet pipe; the gas-liquid mixer is respectively connected with the cold end water inlet pipe and the air compressor. The invention can quickly and stably adjust the temperature of the main engine and the auxiliary engine of the ship, remove deposited dirt in the heat exchanger, recover and utilize the excess heat energy of the ship turbine and improve the utilization efficiency.
Description
Technical Field
The invention relates to a heat dissipation device, in particular to a heat dissipation device of a marine diesel engine structure.
Background
The present case parent application number: 202010986752.5, parent patent name: a heat sink for a ship turbine structure.
As an important component of a ship power device, the working performance of a main engine and an auxiliary engine of a ship is directly influenced by the performance of a ship cooling system. The ship cooling system can reasonably cool the ship power device, reduce the abrasion of the main engine and the auxiliary engine of the ship, effectively control the low-temperature corrosion and the high-temperature corrosion of the main engine and the auxiliary engine and reduce the thermal stress. The method has the advantages that the working temperature of the main engine and the auxiliary engine of the ship is kept in the optimal temperature range, and the method has important significance for improving the dynamic property of a ship power device, reducing the generation of waste gas, reducing the fuel consumption and enhancing the working stability.
In order to ensure that the working temperatures of the main engine and the auxiliary engine of the ship are in the optimal temperature range, the prior technical scheme is mostly realized by changing the flow ratio of a high-temperature water body and a low-temperature water body in a heat dissipation system. In the case of a semi-enclosed cooling system, fresh water is typically used to cool high temperature components of the marine turbine, such as the main engine liners, and seawater is used to cool the fresh water. When the host temperature exceeds the optimal temperature range, the seawater amount flowing into the heat dissipation system is adjusted according to the change of the seawater temperature in the heat dissipation system, the temperature of the fresh water can be rapidly reduced through the adjustment, and then the heat exchange effect of the fresh water on the host cylinder sleeve is improved, so that the working temperature of the ship host is controlled.
This control of the flow of seawater is usually achieved by a seawater pump. The sea water pump is mostly arranged in an engine room of a ship, and when the flow of sea water needs to be controlled: firstly, the outlet opening of the seawater pump can be manually adjusted, and because the outlet opening of the normal seawater pump is only about 1/5 in a full-open state, the seawater pump has a larger regulation and control space; secondly, the sea water pump can be controlled in a multi-speed mode through the variable-frequency speed regulating motor, and of course, a plurality of sea water pumps with different powers can be combined according to a certain mode, so that the flow speed of the sea water can be regulated. However, the technical problem of the technical scheme is that the temperature of the main and auxiliary machines of the ship can not be adjusted quickly and stably, and meanwhile, the seawater pump is usually arranged at a position far away from a heat dissipation system, especially far away from a main heat exchange part in the heat dissipation system, so that the adjustment has certain hysteresis, the temperature overshoot is easy to occur, and the performance and the service life of the main and auxiliary machines of the ship are influenced.
In addition, the excessive heat energy generated by the ship turbine is directly exchanged into the seawater or the air through the ship heat dissipation system, so that the energy is wasted.
Disclosure of Invention
The invention aims to provide a heat dissipation device of a marine diesel engine structure, which has the technical effects of quickly and stably adjusting the temperature of a main engine and an auxiliary engine of a ship, removing deposited dirt in a heat exchanger, recycling and utilizing the multi-waste heat energy of a marine turbine to realize energy conservation and improve the utilization efficiency.
The technical scheme adopted by the invention for realizing the purpose is as follows:
a heat dissipation device for a marine diesel engine structure comprises a plate heat exchanger. A hot end water inlet is formed in the plate heat exchanger and fixedly connected with a hot end water inlet pipe; a hot end water outlet is arranged on the plate heat exchanger, and a hot end water outlet pipe is fixedly connected to the hot end water outlet; the hot end water inlet pipe and the hot end water outlet pipe are connected with a hot end water tank, and the hot end water inlet pipe, the hot end water outlet pipe, the hot end water tank and the plate heat exchanger form a closed water path; a cold end water inlet is formed in the plate heat exchanger, and a cold end water inlet pipe is fixedly connected to the cold end water inlet; a cold end water outlet is formed in the plate heat exchanger, and a cold end water outlet pipe is fixedly connected to the cold end water outlet; a cold end water inlet pipe, a cold end water outlet pipe and the plate heat exchanger form a water path; the cold end water inlet pipe is fixedly connected with a gas-liquid mixer, the cold end water inlet pipe is divided into a front section and a rear section by the gas-liquid mixer, and the rear section of the cold end water inlet pipe is connected with the plate heat exchanger; the gas-liquid mixer is provided with a water inlet, an air inlet and a water outlet, the water inlet is connected with the front section of the cold-end water inlet pipe, the water outlet is connected with the rear section of the cold-end water inlet pipe, and the air inlet is connected with the air compressor.
The heat dissipation system adopted by the invention is a semi-closed cooling system, the hot end water inlet pipe, the hot end water outlet pipe, the hot end water tank and the plate heat exchanger form a closed water path, the closed water path is mainly used for cooling a high-temperature part in the ship turbine, hot end liquid is heated through heat exchange and enters the plate heat exchanger, and then heat is transferred to cold end liquid through corrugated plates of the plate heat exchanger to complete heat exchange circulation.
In addition, a gas-liquid mixer is arranged on the cold-end water inlet pipe, and the gas-liquid mixer is used for injecting gas compressed by the air compressor into the cold-end water inlet pipe and entering the plate heat exchanger along with the flow of the cold-end liquid. The gas-liquid mixer used in the invention is the prior art, and has a lot of specific designs, taking the prior art with the publication number of CN103316603B as an example, the gas-liquid mixer is provided with a water inlet, a gas inlet and a water outlet, a mixing cavity is arranged between the water inlet and the water outlet, the mixing cavity is utilized to realize the mixing of liquid and gas, and the gas concentration in water can be maintained at a certain proportion.
Air is injected into the plate heat exchanger through the cold end water inlet pipe to improve the heat transfer coefficient, and the characteristic of gas-liquid two-phase flow is mainly utilized. Specifically, gas-liquid two-phase flow has a better heat transfer coefficient than liquid single-phase flow. On one hand, based on the disturbance effect of gas, the turbulent intensity of two-phase flow can be increased, and the thickness of a thermal boundary layer on the corrugated plate can be reduced, so that the heat transfer coefficient is increased; on the other hand, when the bubble flow formed by fully mixing the gas phase and the liquid phase enters a narrow flow channel of the plate heat exchanger, the bubble space is limited, so that small bubbles are formed by bubble crushing, energy loss can be generated in the bubble crushing process, and the lost energy can impact a temperature field where the working medium is located, so that the distribution of the temperature gradient is more uniform, and the heat transfer is more facilitated. In addition, the ratio of the Reynolds number of the gas phase to the Reynolds number of the liquid phase in the flow channel can be adjusted by controlling the quantity of air injected into the plate heat exchanger by the air compressor, so that the plate heat exchanger can obtain heat transfer coefficients with different sizes, and the technical problem of cooling water temperature over-regulation is solved.
In addition, as described above, the gas-liquid two-phase flow can increase the turbulence intensity, and the increase in the turbulence intensity means that the shearing force of the fluid on the scale surface is also increased, and furthermore, the breaking of the bubbles can also cause impact on the corrugated sheet, particularly, the scale attached to the sheet surface. Therefore, the peeling of the scale on the surface of the corrugated plate is realized, the scale in the plate heat exchanger can be removed while the heat exchange performance of the plate heat exchanger is improved, and the adverse effect of deposited scale on the plate heat exchanger is reduced.
Preferably, the hot end water inlet pipe and/or the hot end water outlet pipe are/is provided with at least one first pump; and the front section of the cold end water inlet pipe is provided with a second pump.
Because the end water inlet pipe, the hot end water outlet pipe, the hot end water tank and the plate heat exchanger form a closed water path together, a first pump arranged on the closed water path is used as a circulating pump, the specific installation position of the first pump can be arranged on the hot end water inlet pipe or the hot end water outlet pipe, but the direction is consistent with the water flow direction; the second pump is arranged on the cold end water inlet pipe, and liquid at the cold end is pumped into the plate heat exchanger, so that the purpose of lift is achieved, and the second pump is a high-pressure pump.
Preferably, the hot end water inlet pipe is a circular pipe, the outer side of the circular pipe is wrapped by a special pipe, and the special pipe and the hot end water inlet pipe are concentric; the cross section of the special pipe is a regular polygon; the hot end water inlet pipe is in interference fit with the special pipe; the outside of the special pipe is wrapped with a temperature difference power generation device.
The special pipe with the regular polygon shape outside the inner circle is coated outside the hot end water inlet pipe, mainly because the components for realizing thermoelectric generation mostly adopt the shape of a plate, such as the thermoelectric generation sheet used in the invention, and the round pipe is not beneficial to the coating of the plate and the transfer of heat energy. The structure of the special pipe can be solid, and the special pipe can also be provided with an inner cavity or form a closed inner cavity with the hot end water inlet pipe in an enclosing mode. When the special pipe is provided with an inner cavity or is matched to enclose a cavity, heat conducting oil can be injected inwards. Of course, no matter the solid pipe or the cavity has heat conducting oil, the heat conducting oil is used for effectively transferring the heat of the liquid in the hot-end water inlet pipe to the hot end of the thermoelectric power generation device. The thermoelectric generation device is arranged on the heat dissipation device, on one hand, the waste heat of the turbine is effectively utilized, and on the other hand, before hot-end liquid enters the plate heat exchanger, the heat absorption function of the thermoelectric generation device is used for cooling the heat exchanger in advance, so that the overall heat exchange capacity of the heat dissipation device is further improved.
Preferably, the temperature difference power generation device consists of temperature difference power generation units, and the number of the temperature difference power generation units is consistent with the number of the edges of the cross section of the special pipe; the thermoelectric power generation unit is characterized in that a hot end water inlet pipe is taken as a center, the thermoelectric power generation unit sequentially consists of thermoelectric power generation sheets, cold plates and radiating fins from inside to outside, the thermoelectric power generation sheets, the cold plates and the radiating fins are arranged in parallel, and two adjacent parts are in surface contact; the thermoelectric generation pieces in the thermoelectric generation device are all connected in series; the thermoelectric generation piece is in surface contact with the special pipe, and the hot end of the thermoelectric generation piece is close to the hot end water inlet pipe.
The temperature difference power generation device mainly generates power through the temperature difference power generation sheet. The thermoelectric power generation sheet is a prior art which realizes the conversion between heat energy and electric energy by utilizing thermoelectric materials through a thermoelectric technology. The thermoelectric material is a functional material which realizes direct mutual conversion of electric energy and heat energy by utilizing the movement of carriers in a solid, and is divided into a P type and an N type according to the positive and negative of generated voltage. The thermoelectric device is formed by connecting P-type and N-type semiconductor materials in series and parallel in a combined manner, wherein the P-type and N-type semiconductor materials are connected in series through metal conductors to form a power generation unit, the P-type semiconductor material of one power generation unit is connected in series with the N-type semiconductor material of the adjacent power generation unit to form a minimum power generation unit group, and a plurality of power generation units are connected in series to form a complete thermoelectric device.
The principle of thermoelectric generation is that the energy of free electrons increases with increasing temperature, and if the conductor has a temperature difference, hot-side electrons will gain higher energy and faster speed than cold-side electrons. The majority carriers in the N-type semiconductor are electrons, the concentration of the electrons increases along with the rise of the temperature, and then a stream of electron flow from the hot end to the cold end is formed, and a certain potential difference is established due to the accumulation of the charges, so that a reverse electron flow is formed. Meanwhile, when the charge is accumulated to a certain degree, the reverse electron drift flow is equal to the forward electron diffusion flow, and a stable state is achieved. A stable electromotive force is formed across the semiconductor. The majority carriers in P-type semiconductors are holes rather than electrons, and compared to N-type semiconductors, the principle is the same, but the thermoelectric potentials are opposite. It is thus possible to obtain a current in the thermoelectric element composed of the P, N type semiconductor.
Preferably, the cold-end water outlet pipe is fixedly connected with a gas-liquid separator, the cold-end water outlet pipe is divided into a front section and a rear section by the gas-liquid separator, and the rear section of the cold-end water outlet pipe is connected with the plate heat exchanger; the gas-liquid separator is provided with a water inlet, a gas outlet and a water outlet, the water inlet is connected with the rear section of the cold-end water outlet pipe, and the water outlet is connected with the front section of the cold-end water outlet pipe; the air outlet of the gas-liquid separator faces the radiating fins of the temperature difference power generation device.
Gas-liquid two-phase flows through cold junction delivery port discharge plate radiator, and rethread vapour and liquid separator can be with gas and liquid separation, and the gas outlet of vapour and liquid separator is passed through to the gas outlet of separating, directly blows to thermoelectric generation device's radiating fin, and the cold junction cooling of thermoelectric generation piece has promoted the generating efficiency with higher speed. The design can realize secondary utilization of gas in the plate heat exchanger on one hand, and improves the utilization effect of the waste heat of the ship turbine on the other hand, thereby realizing comprehensive energy conservation. In addition, the gas-liquid separator is the prior art, the specific design is many, the technical effect of gas-liquid separation can be realized without electrifying part of the design, and taking the research on novel gas-liquid separator (university of northeast oil university, university research institute academic degree paper; author: gunn ocean; completion time: 2017, 5 months) as an example, a gas-liquid cyclone separator is disclosed, and gas-liquid two-phase media are separated by using centrifugal force generated by cyclone.
Preferably, the number of the thermoelectric generation pieces in the thermoelectric generation unit is at least one, and a heat conduction plate is arranged between every two adjacent thermoelectric generation pieces; the thermoelectric generation piece is in surface contact with the heat conduction plate.
Preferably, a storage battery pack is connected outside the temperature difference power generation device; and the current output end of the storage battery pack is connected with the current input end of the air compressor.
The current generated by the temperature difference power generation device is stored by the storage battery pack and can provide electric energy for the air compressor. In terms of working time, the air compressor is started only when the temperatures of the main engine and the auxiliary engine of the ship exceed the optimal temperature range, and the temperature difference power generation device can absorb and convert heat in the whole working period of the main engine and the auxiliary engine of the ship. Therefore, partial or whole power consumption requirements of the air compressor can be met through the power generation mode, the temperature difference power generation device is used as a main power source of the air compressor, and certainly, when the temperature difference power generation device cannot meet the power consumption requirements of the air compressor, power can be supplied by a power supply network of the ship. The mode is mainly used for reducing the electric load of the ship and helping to realize the energy conservation of the ship.
Preferably, the heat sink of the marine diesel engine structure further comprises a temperature sensor, and the temperature sensor is arranged on a hot end water inlet of the plate heat exchanger; the air compressor is provided with a singlechip, and the singlechip can control the air compressor to inject air into the cold-end water inlet pipe or stop injecting air; the signal output end of the temperature sensor is connected with the signal receiving end of the single chip microcomputer in a wired connection mode and/or a wireless connection mode.
Preferably, the heat exchange medium in the closed water path formed by the hot end water inlet pipe, the hot end water outlet pipe, the hot end water tank and the plate heat exchanger is fresh water; the heat exchange medium in the water channel formed by the cold end water inlet pipe, the cold end water outlet pipe and the plate heat exchanger is seawater.
Preferably, a filtering device is arranged at the inlet of the front section of the cold-end water inlet pipe.
The invention has the following beneficial effects:
1. according to the invention, the air compressor is additionally arranged at the water inlet of the plate type radiator, and the heat transfer coefficient of the plate type radiator is increased in a short time by temporarily injecting gas into the cold end water inlet pipe of the plate type radiator, so that the temperature of the main engine and the auxiliary engine of the ship can be quickly adjusted.
2. According to the invention, the number of air injected into the plate heat exchanger by the air compressor is controlled, and the ratio of the Reynolds number of a gas phase to the Reynolds number of a liquid phase in the flow channel is adjusted, so that heat transfer coefficients with different sizes are obtained, the technical problem of temperature overshoot in the prior art is solved, and the stable and accurate adjustment of the temperature of the main engine and the auxiliary engine of the ship is realized.
3. According to the invention, through injecting the gas into the cold end water inlet pipe of the plate type radiator, the heat exchange effect is improved, meanwhile, the deposited dirt in the heat exchanger is removed by utilizing the gas, and the heat radiation performance of the heat radiation device is prevented from being attenuated along with time.
4. According to the invention, the temperature difference power generation device supplies energy to the air compressor, so that the electric load of the ship can be reduced, and the energy conservation of the ship is facilitated.
5. The gas-liquid two-phase flow is separated through the gas-liquid separator, so that the separated gas is directly blown to the radiating fins of the temperature difference power generation device, the power generation efficiency is improved, the secondary utilization of the gas in the plate heat exchanger can be realized, and the utilization effect of the waste heat of the ship turbine can be improved.
Drawings
FIG. 1 is an overall schematic view of the present invention.
FIG. 2 is a schematic diagram of the connection relationship of the devices according to the present invention.
Fig. 3 is an exploded view of a thermoelectric generation device.
Fig. 4 is a structural view of the thermoelectric power generation device.
FIG. 5 is a schematic view of a thermoelectric generation chip.
Fig. 6 is a schematic diagram of a connection relationship between the thermoelectric power generation device and the battery pack.
Reference numerals: 1-a plate heat exchanger; 21 a-hot end water inlet pipe; 21 b-a shaped tube; 22-hot end water outlet pipe; 23-pump number one; 24-a hot-end water tank; 31-cold end water inlet pipe; 32 a-cold end water outlet pipe; 32 b-a gas-liquid separator; 33-pump number two; 41-gas-liquid mixer; 42-an air compressor; 5-a thermoelectric power generation device; 51-thermoelectric power generation sheet; 52-thermally conductive plate; 53-a cold plate; 54-heat dissipation fins; 6-storage battery pack; 7-seawater; a-a heat source.
Detailed Description
Example 1: referring to fig. 1 and 2, a heat dissipation device for a marine diesel engine structure comprises a plate heat exchanger 1. A hot end water inlet is formed in the plate heat exchanger 1, and a hot end water inlet pipe 21a is fixedly connected to the hot end water inlet; a hot end water outlet is arranged on the plate heat exchanger 1, and a hot end water outlet pipe 22 is fixedly connected to the hot end water outlet; the hot end water inlet pipe 21a and the hot end water outlet pipe 22 are both connected with the hot end water tank 24, and the hot end water inlet pipe 21a, the hot end water outlet pipe 22, the hot end water tank 24 and the plate heat exchanger 1 form a closed water path; a cold end water inlet is formed in the plate heat exchanger 1, and a cold end water inlet pipe 31 is fixedly connected to the cold end water inlet; a cold end water outlet is formed in the plate heat exchanger, and a cold end water outlet pipe 32a is fixedly connected to the cold end water outlet; a cold end water inlet pipe 31, a cold end water outlet pipe 32a and the plate heat exchanger 1 form a water path; the cold end water inlet pipe 31 is fixedly connected with a gas-liquid mixer 41, the cold end water inlet pipe 31 is divided into a front section and a rear section by the gas-liquid mixer 41, and the rear section of the cold end water inlet pipe 31 is connected with the plate heat exchanger 1; the gas-liquid mixer 41 is provided with a water inlet, an air inlet, and a water outlet, the water inlet is connected to the front section of the cold-end water inlet pipe 31, the water outlet is connected to the rear section of the cold-end water inlet pipe 31, and the air inlet is connected to the air compressor 42. The hot end water inlet pipe 21a and/or the hot end water outlet pipe 22 are/is provided with at least one first pump 23; a second pump 33 is mounted on the front section of the cold-end inlet pipe 31.
The heat dissipation system adopted by the invention is a semi-closed cooling system, a closed water path which is formed by a hot end water inlet pipe 21a, a hot end water outlet pipe 22, a hot end water tank 24 and the plate heat exchanger 1 is mainly used for cooling high-temperature components in the ship turbine, hot end liquid is heated through heat exchange and enters the plate heat exchanger 1, and then heat is transferred to cold end liquid through corrugated plates of the plate heat exchanger to complete heat exchange circulation.
When the temperature of the main engine and the auxiliary engine of the ship exceeds the optimal temperature range, the air compressor 42 is started, and air is injected into the plate heat exchanger 1 through the cold end water inlet pipe 31. On one hand, the turbulent intensity of two-phase flow is increased by using the disturbance effect of gas, and the thickness of a thermal boundary layer on the corrugated plate is reduced, so that the heat transfer coefficient is increased; on the other hand, bubble flow formed by fully mixing a gas phase and a liquid phase is limited in a bubble space when entering a narrow flow channel of the plate heat exchanger, so that small bubbles are formed by bubble crushing, energy loss can be generated in the bubble crushing process, and the lost energy can impact a temperature field where the working medium is located, so that the distribution of temperature gradient is more uniform, and heat transfer is more facilitated. In addition, by controlling the amount of air injected into the plate heat exchanger 1 by the air compressor 42, the ratio of the reynolds number of the gas phase to the reynolds number of the liquid phase in the flow channel can be adjusted, and the heat transfer coefficients with different sizes can be obtained. When the temperature of the main engine and the auxiliary engine of the ship exceeds the optimal temperature range, the air compressor 42 is closed, so that the temperature overshoot is avoided.
Example 2: based on embodiment 1, as shown in fig. 3 to 6, in order to reduce the power load of the ship and achieve energy saving of the ship, the thermoelectric power generation device 5 is installed on the hot-end water inlet pipe 21a, and the connection and heat transfer between the hot-end water inlet pipe and the hot-end water inlet pipe are achieved through the special pipe 21 b. The thermoelectric power generation device 5 can absorb and convert heat in the whole working period of the main engine and the auxiliary engine of the ship, and the air compressor 42 is started only when the temperature of the main engine and the auxiliary engine of the ship exceeds the optimal temperature range, so that the power consumption requirement of part or all of the air compressor 42 can be met in the power generation mode, and certainly, when the thermoelectric power generation device 5 cannot meet the power consumption requirement of the air compressor 42, the power can be supplemented by the power supply network of the ship.
Example 3: based on embodiment 2, the cold-end water outlet pipe 32a is fixedly connected with a gas-liquid separator 32b, the cold-end water outlet pipe 32a is divided into a front section and a rear section by the gas-liquid separator 32b, and the rear section of the cold-end water outlet pipe 32a is connected with the plate heat exchanger 1; the gas-liquid separator 32b is provided with a water inlet, an air outlet and a water outlet, the water inlet is connected with the rear section of the cold end water outlet pipe 32a, and the water outlet is connected with the front section of the cold end water outlet pipe 32 a; the outlet of the gas-liquid separator 32b faces the heat radiating fins 54 of the thermoelectric generation device 5.
Gas-liquid two-phase flows through the cold end water outlet and is discharged out of the plate type radiator 1, gas and liquid can be separated through the gas-liquid separator 32b, the separated gas is directly blown to the radiating fins 54 of the thermoelectric generation device 5 through the gas outlet of the gas-liquid separator 32b, cooling of the cold end of the thermoelectric generation piece 51 is accelerated, and power generation efficiency is improved. According to the design, on one hand, secondary utilization of gas in the plate type heat exchanger 1 can be realized, on the other hand, the utilization effect of waste heat of the ship turbine is improved, and comprehensive energy conservation is realized.
Example 4: based on embodiment 3, in order to save labor and realize automatic temperature adjustment, a temperature sensor can be further arranged on the hot end water inlet of the plate heat exchanger 1, a single chip microcomputer is arranged on the air compressor 42, the signal output end of the temperature sensor is connected with the signal receiving end of the single chip microcomputer, and the air compressor 42 is controlled by the single chip microcomputer. Detect the hot junction temperature through temperature sensor to give the singlechip with temperature signal transmission, the singlechip judges whether need promote plate heat exchanger 1's radiating efficiency in view of the above, and air compressor 42 need inject into or stop injecting into the air to cold junction inlet tube 31 promptly. The single chip microcomputer capable of realizing the functions is the prior art, has a plurality of specific designs, and is commonly used in a ship cooling water temperature intelligent control system, such as the research and design of the ship diesel engine cooling water temperature intelligent control system (university of maritime, university of continuance, master degree paper, author: Lihaifeng; completion date: 11 months 2007).
Claims (1)
1. The heat dissipation device for the marine diesel engine structure comprises a plate heat exchanger (1) and is characterized in that a hot end water inlet is formed in the plate heat exchanger (1), and a hot end water inlet pipe (21a) is fixedly connected to the hot end water inlet; a hot end water outlet is formed in the plate heat exchanger (1), and a hot end water outlet pipe (22) is fixedly connected to the hot end water outlet; the hot end water inlet pipe (21a) and the hot end water outlet pipe (22) are connected with a hot end water tank (24), and the hot end water inlet pipe (21a), the hot end water outlet pipe (22), the hot end water tank (24) and the plate heat exchanger (1) form a closed water path; a cold end water inlet is formed in the plate heat exchanger (1), and a cold end water inlet pipe (31) is fixedly connected to the cold end water inlet; a cold end water outlet is formed in the plate heat exchanger (1), and a cold end water outlet pipe (32a) is fixedly connected to the cold end water outlet; the cold end water inlet pipe (31), the cold end water outlet pipe (32a) and the plate heat exchanger (1) form a water path; the cold end water inlet pipe (31) is fixedly connected with a gas-liquid mixer (41), the cold end water inlet pipe (31) is divided into a front section and a rear section by the gas-liquid mixer (41), and the rear section of the cold end water inlet pipe (31) is connected with the plate heat exchanger (1); the gas-liquid mixer (41) is provided with a water inlet, an air inlet and a water outlet, the water inlet is connected with the front section of the cold-end water inlet pipe (31), the water outlet is connected with the rear section of the cold-end water inlet pipe (31), and the air inlet is connected with the air compressor (42);
the hot end water inlet pipe (21a) and/or the hot end water outlet pipe (22) are/is provided with a first pump (23), and the number of the first pumps (23) is at least one; a second pump (33) is arranged on the front section of the cold end water inlet pipe (31);
the hot end water inlet pipe (21a) is a round pipe, the outer side of the round pipe is wrapped by a special pipe (21b), and the special pipe (21b) is concentric with the hot end water inlet pipe (21 a); the cross section of the special pipe (21b) is a regular polygon; the hot end water inlet pipe (21a) and the special pipe (21b) are in interference fit; the outer side of the special pipe (21b) is wrapped with a temperature difference power generation device (5);
the temperature difference power generation device (5) is composed of temperature difference power generation units, and the number of the temperature difference power generation units is consistent with the number of the edges of the cross section of the special pipe (21 b); the thermoelectric power generation unit is centered on a hot end water inlet pipe (21a), sequentially consists of thermoelectric power generation sheets (51), cold plates (53) and radiating fins (54) from inside to outside, and is arranged in parallel, and two adjacent parts are in surface contact with each other; the thermoelectric generation pieces (51) in the thermoelectric generation device (5) are all connected in series; the thermoelectric generation piece (51) is in surface contact with the special pipe (21b), and the hot end of the thermoelectric generation piece (51) is close to the hot end water inlet pipe (21 a);
the cold end water outlet pipe (32a) is fixedly connected with a gas-liquid separator (32b), the cold end water outlet pipe (32a) is divided into a front section and a rear section by the gas-liquid separator (32b), and the rear section of the cold end water outlet pipe (32a) is connected with the plate heat exchanger (1); the gas-liquid separator (32b) is provided with a water inlet, a gas outlet and a water outlet, the water inlet is connected with the rear section of the cold end water outlet pipe (32a), and the water outlet is connected with the front section of the cold end water outlet pipe (32 a); the air outlet of the gas-liquid separator (32b) faces to the radiating fins (54) of the thermoelectric power generation device (5);
the number of the temperature difference power generation pieces (51) in the temperature difference power generation unit is at least one, and a heat conduction plate (52) is arranged between every two adjacent temperature difference power generation pieces (51); the thermoelectric generation piece (51) is in surface contact with the heat conduction plate (52).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110817570.XA CN113565616A (en) | 2020-09-18 | 2020-09-18 | Heat radiating device of marine diesel engine structure |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110817570.XA CN113565616A (en) | 2020-09-18 | 2020-09-18 | Heat radiating device of marine diesel engine structure |
| CN202010986752.5A CN112267937B (en) | 2020-09-18 | 2020-09-18 | Heat dissipation device for ship turbine structure |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010986752.5A Division CN112267937B (en) | 2020-09-18 | 2020-09-18 | Heat dissipation device for ship turbine structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113565616A true CN113565616A (en) | 2021-10-29 |
Family
ID=74349986
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010986752.5A Active CN112267937B (en) | 2020-09-18 | 2020-09-18 | Heat dissipation device for ship turbine structure |
| CN202110817570.XA Withdrawn CN113565616A (en) | 2020-09-18 | 2020-09-18 | Heat radiating device of marine diesel engine structure |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010986752.5A Active CN112267937B (en) | 2020-09-18 | 2020-09-18 | Heat dissipation device for ship turbine structure |
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| Country | Link |
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| CN (2) | CN112267937B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11823974B2 (en) * | 2019-05-01 | 2023-11-21 | Northwestern University | Cryogenic solid state heat pump |
| CN115387896B (en) * | 2022-08-30 | 2023-09-15 | 上汽通用五菱汽车股份有限公司 | Gas-liquid hybrid cooling system, control method thereof, vehicle and readable storage medium |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010111064A2 (en) * | 2009-03-27 | 2010-09-30 | Caterpillar Inc. | Air venting arrangement |
| US9937990B2 (en) * | 2014-08-01 | 2018-04-10 | Circor Pumps North America, Llc | Intelligent sea water cooling system |
| KR101678829B1 (en) * | 2014-12-17 | 2016-11-24 | 한국해양과학기술원 | High-efficiency ocean thermal energy conversion (OTEC) applying a liquid-vapor ejector and a motive pump |
| CN209212404U (en) * | 2018-11-22 | 2019-08-06 | 湖州双快新能源科技有限公司 | A kind of alcohol hydrogen dynamic combustion surplus energy recyclable device of high stable |
| CN111336717A (en) * | 2020-02-28 | 2020-06-26 | 江苏大学 | Gas-liquid two-phase circulating cooling system for energy recovery |
-
2020
- 2020-09-18 CN CN202010986752.5A patent/CN112267937B/en active Active
- 2020-09-18 CN CN202110817570.XA patent/CN113565616A/en not_active Withdrawn
Also Published As
| Publication number | Publication date |
|---|---|
| CN112267937A (en) | 2021-01-26 |
| CN112267937B (en) | 2021-12-14 |
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Application publication date: 20211029 |
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