CN117760238A - Design method of ultra (super) critical duct type heat exchanger - Google Patents
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- 229910052734 helium Inorganic materials 0.000 description 1
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Abstract
The invention belongs to the technical field of nuclear power plant heat transfer equipment based on a fourth-generation reactor, and particularly relates to a design method of a supercritical (super) critical tunnel type heat exchanger. The heat exchange unit of the tunnel type heat exchanger is in the shape of a cylinder, a cuboid, a prism and the like, and is made of alloy materials with high temperature resistance and high pressure resistance. The diameter, height and other dimensions of the heat exchange unit of the tunnel type heat exchanger are comprehensively analyzed and set according to factors such as heat transfer capacity, occupied space and the like. The heat exchange unit of the tunnel type heat exchanger can be obtained by casting, additive manufacturing and other processes, and the primary side tunnel and the secondary side tunnel can be obtained by drilling, integral forming and other processes. The invention can safely and reliably operate in an ultra-high temperature and ultra-high pressure environment under ultra (supercritical) critical parameters, and has large heat exchange coefficient, large heat exchange area in unit volume and large heat exchange quantity.
Description
Technical Field
The invention belongs to the technical field of nuclear power plant heat transfer equipment based on a fourth-generation reactor, and particularly relates to a design method of a supercritical (super) critical duct type heat exchanger.
Background
The heat exchanger is used as important equipment in the fields of chemical industry, petroleum, energy sources, food and the like, and is used for transferring and exchanging heat. The heat exchanger exchanges heat between working media to generate power generation, industrial high-temperature steam or other products, and the heat exchange performance of the heat exchanger influences the production efficiency and the economy of the whole system. Meanwhile, the heat exchanger is used as high-temperature high-pressure equipment, and the safety of the whole system is concerned with the safe and reliable operation. And heat exchange performance and reliability are considered for heat exchange under supercritical (super) parameters. Therefore, each link of design development, manufacturing production, operation maintenance and the like of the heat exchanger is very important to the system.
Heat exchangers include plate heat exchangers, shell and tube heat exchangers, spiral coil heat exchangers, and the like. The plate heat exchanger is a heat exchanger formed by stacking a group of metal sheets with specific shapes. Narrow rectangular channels are formed between the various plates through which heat is exchanged. The heat exchange is more efficient at lower pressures and lower temperatures. The shell-and-tube heat exchanger exchanges heat between the working media of the primary loop and the secondary loop through the U-shaped tube bundles, namely exchanges heat between the working media of the primary side and the secondary side. In the shell-and-tube heat exchanger, the secondary side inlet is supercooled water, and is vaporized into a steam-water mixture after absorbing heat, so that pressure difference is generated in the U-shaped tube, and the working medium in the tube is driven to flow towards the outlet direction, so that natural circulation is formed. The shell-and-tube heat exchanger has a simpler structure and higher heat exchange efficiency, but the reliability of part of the heat exchangers is lower, and once the heat exchangers break the tubes, the safety, the reliability and the economic benefit of the system are greatly influenced. Spiral coil heat exchangers are selected for use in certain fields, such as nuclear power. The spiral coil pipe type heat exchanger spirally winds a plurality of groups of heat exchange pipes on the central circular pipe, and secondary side working media spirally rise in the heat exchange pipes. The primary side working medium passes through the heat exchange tube in a countercurrent way, and exchanges heat with the working medium in the heat exchange tube. The spiral coil type heat exchanger adopts a countercurrent heat exchange mode, so that on one hand, the heat exchange temperature difference is reduced, and the thermal stress born by the device is also reduced; on the other hand, the selection of multi-stage materials can be realized, cheaper materials are used in the low-temperature section, and alloy materials which are more resistant to high temperature but have higher manufacturing cost are only needed in the high-temperature section. The spiral coil type heat exchanger has compact structure and large heat exchange area per unit volume, but has the defects of heat exchange dead zone, insufficient pressure bearing reliability and the like.
The heat exchange under the supercritical parameters relates to the working environment of ultrahigh temperature and ultrahigh pressure, but the existing heat exchanger design is difficult to meet the heat exchange requirement under the ultrahigh temperature and ultrahigh pressure environment, if the existing heat exchanger design is continuously adopted, the pipe wall thickness needs to be increased for safe operation, the equipment size is increased, the manufacturing cost is increased in multiple, and the economical efficiency in the production process is seriously affected.
Aiming at the problems existing in the prior art, development of a novel heat exchanger capable of safely and reliably operating in an ultrahigh-temperature and ultrahigh-pressure working environment is urgently needed.
Disclosure of Invention
The invention mainly aims to solve the current situation that the heat exchange performance, the safety and the economy of the existing heat exchanger are poor under the application background of supercritical (supercritical) parameters such as nuclear power and the like, and provides a tunnel type heat exchanger design method suitable for the supercritical (supercritical) operation parameters.
The technical scheme adopted by the invention is as follows:
a design method of a supercritical channel type heat exchanger mainly comprises a channel type heat exchanger heat exchange unit, a primary side channel and a secondary side channel. The heat exchange unit of the tunnel type heat exchanger is in the shape of a cylinder, a cuboid, a prism and the like, and is made of alloy materials with high temperature resistance and high pressure resistance. The diameter, height and other dimensions of the heat exchange unit of the tunnel type heat exchanger are comprehensively analyzed and set according to factors such as heat transfer capacity, occupied space and the like. The primary side working medium which gives off heat flows through the primary side pore canal. The secondary side pore canal is provided with a secondary side working medium which absorbs heat to flow through. The heat exchange unit of the tunnel type heat exchanger can be obtained by casting, additive manufacturing and other processes, and the primary side tunnel and the secondary side tunnel can be obtained by drilling, integral forming and other processes.
Further, a primary side pore canal and a secondary side pore canal are processed on the pore canal type heat exchanger heat exchange unit, different working mediums flow in adjacent different pore canals, the primary side working medium flows in the primary side pore canal, the secondary side working medium flows in the secondary side pore canal, heat exchange is carried out by means of heat conduction and convection heat exchange, and the radiation heat exchange is a secondary heat exchange mode.
Because the flow velocity of the working medium in the pore canal is high, the heat exchanger adopts metal or alloy materials with good heat transfer performance, so that the overall heat exchange coefficient of the device is high, and the heat exchange performance is good. Meanwhile, a large number of pore canals can be processed according to the heat exchange quantity requirement, and the inner wall surfaces of the pore canals can be used as effective heat exchange surfaces to participate in heat exchange, so that the device has large heat exchange area and large heat exchange quantity in unit volume.
In the device, the basic structure of the heat exchanger can be a cylinder, and can also be a cuboid or a triangular prism according to the application background, and a bending structure can be added at the position of the inlet and the outlet. The heat exchanger may also be provided in a multi-stage configuration.
In the device, the number, shape, size, interval distance, arrangement angle among the pore channels and the like can be obtained after fine calculation according to actual heat exchange requirements. The heat exchange requirement comprises the requirement on heat exchange coefficient and heat exchange quantity, the heat exchange coefficient is calculated in a plurality of modes, and the heat exchange coefficient can be calculated in a mode including but not limited to heat transfer criterion number correlation. The convective heat transfer coefficient h in the pore canal can be obtained by heat transfer criterion number correlation calculation:
wherein n=0.4 when the fluid is heated and n=0.3 when the fluid is cooled.
The convection heat transfer coefficient in the pore canal can be obtained through calculation of the formula, and the required convection heat transfer coefficient is obtained through changing the shape, the size and other parameter designs of the pore canal.
The total heat exchange coefficient h' is related to the heat convection coefficient in the pore canal, and also related to the structural parameters such as the spacing distance, the arrangement angle and the like of the pore canal. The total heat exchange amount Q can be calculated by:
Q＝h`×A×Δt
wherein h' is the total heat exchange coefficient, A is the total heat exchange area, related to the number, the size and other structural parameters of the pore canal, and delta t is the average heat exchange temperature difference.
The above calculation method is only one of the calculation methods, and a suitable calculation method may be adopted in fine calculation of the structural parameters related to the design tunnel.
The arrangement mode of the primary side pore canal (2) and the secondary side pore canal (3) can be used for refining and proportioning according to the heat exchange requirement. The inside of the pore canal can also be processed into a structure with internal threads so as to strengthen the heat exchange effect.
In the device, a countercurrent heat exchange mode is adopted, the heat exchange temperature difference between working media is small, the thermal stress born by the device is small, the device is of an integrated structure, and the device is wholly pressure-bearing. When the ultrahigh pressure working medium flows through the pore canal, the accident of 'tube explosion' of the heat exchanger can not occur, and the heat exchanger can safely and reliably operate in an ultrahigh pressure environment with supercritical parameters.
In the device, the temperature distribution of different axial positions is different, the partition selection of processing materials can be performed, the low-temperature section is processed by adopting materials with good performance and low price, and the high-temperature section is processed by adopting alloy materials which can bear ultrahigh temperature and are high in price. For example, the low temperature section can be made of P93 material, the transition section between the low temperature section and the high temperature section is made of a fusion material of 740H and P93, and the high temperature section is made of 740H material. The low-temperature section is selected by material partition, so that the production and manufacturing cost is saved, the economic benefit is improved, and the device can safely and reliably operate in an ultra-high temperature environment with ultra-supercritical parameters.
The invention has the advantages that:
1 through the technical means of countercurrent heat exchange of working media in the pore canal, the technical effect of safe and reliable operation in an ultra-high temperature and ultra-high pressure environment under ultra (supercritical) critical parameters is realized.
2 through the technical means of the duct type heat exchange, the technical effects of large heat exchange coefficient, large heat exchange area in unit volume and large heat exchange amount are realized.
3, through the technical means of material partition selection, the technical effects of low cost and good economy are realized.
Drawings
FIG. 1 is a schematic diagram of the overall structure of a design method of a supercritical tunnel heat exchanger;
FIG. 2 is a schematic cross-sectional view of a supercritical tunnel heat exchanger;
FIG. 3 illustrates a supercritical channel heat exchanger channel arrangement;
fig. 4 is an embodiment of a supercritical tunnel heat exchanger.
Wherein, 1: a heat exchange unit of the tunnel type heat exchanger; 2: a primary side duct; 3: a secondary side duct; 101: a pressure-bearing housing; 102: a secondary side heat insulating layer; 103: a primary side inlet; 104: a primary side outlet; 105: a secondary side inlet; 106, a secondary side outlet; 107: a secondary side inlet header; 108: a secondary side outlet header; 109: a primary side outlet header.
Detailed Description
The invention will now be described in detail with reference to the drawings and specific examples.
As shown in fig. 1-2, the design method of the supercritical channel type heat exchanger mainly comprises a channel type heat exchanger heat exchange unit (1), a primary side channel (2) and a secondary side channel (3). The heat exchange unit (1) of the tunnel type heat exchanger is in the shape of a cylinder, a cuboid, a prism and the like, and is made of alloy materials with high temperature resistance and high pressure resistance. The diameter, height and other dimensions of the heat exchange unit (1) of the tunnel type heat exchanger are comprehensively analyzed and set according to factors such as heat transfer capacity, occupied space and the like. The primary side pore canal (2) is provided with a primary side working medium which emits heat to flow through. The secondary side working medium which absorbs heat flows through the secondary side hole (3). The heat exchange unit (1) of the tunnel type heat exchanger can be obtained by casting, additive manufacturing and other processes, and the primary side tunnel (2) and the secondary side tunnel (3) can be obtained by drilling, integral forming and other processes.
Further, a primary side pore canal (2) and a secondary side pore canal (3) are processed on the pore canal type heat exchanger heat exchange unit (1), different working mediums flow in adjacent different pore canals, primary side working mediums flow in the primary side pore canal (2), secondary side working mediums flow in the secondary side pore canal (3), heat exchange is carried out in a heat exchange mode that heat conduction and convection heat exchange are mainly carried out, and radiation heat exchange is carried out in a secondary heat exchange mode.
Because the flow velocity of the working medium in the pore canal is high, the heat exchanger adopts metal or alloy materials with good heat transfer performance, so that the overall heat exchange coefficient of the device is high, and the heat exchange performance is good. Meanwhile, a large number of pore canals can be processed according to the heat exchange quantity requirement, and the inner wall surfaces of the pore canals can be used as effective heat exchange surfaces to participate in heat exchange, so that the device has large heat exchange area and large heat exchange quantity in unit volume.
In the device, the basic structure of the heat exchanger can be a cylinder, and can also be a cuboid or a triangular prism according to the application background, and a bending structure can be added at the position of the inlet and the outlet. The heat exchanger may also be provided in a multi-stage configuration.
In the device, the number, shape, size, interval distance, arrangement angle among the pore channels and the like can be obtained after fine calculation according to actual heat exchange requirements. The heat exchange requirement comprises the requirement on heat exchange coefficient and heat exchange quantity, the heat exchange coefficient is calculated in a plurality of modes, and the heat exchange coefficient can be calculated in a mode including but not limited to heat transfer criterion number correlation. The convective heat transfer coefficient h in the pore canal can be obtained by heat transfer criterion number correlation calculation:
wherein n=0.4 when the fluid is heated and n=0.3 when the fluid is cooled.
The convection heat transfer coefficient in the pore canal can be obtained through calculation of the formula, and the required convection heat transfer coefficient is obtained through changing the shape, the size and other parameter designs of the pore canal.
The total heat exchange coefficient h' is related to the heat convection coefficient in the pore canal, and also related to the structural parameters such as the spacing distance, the arrangement angle and the like of the pore canal. The total heat exchange amount Q can be calculated by:
Q＝h`×A×Δt
wherein h' is the total heat exchange coefficient, A is the total heat exchange area, related to the number, the size and other structural parameters of the pore canal, and delta t is the average heat exchange temperature difference.
The above calculation method is only one of the calculation methods, and a suitable calculation method may be adopted in fine calculation of the structural parameters related to the design tunnel.
The arrangement mode of the primary side pore canal (2) and the secondary side pore canal (3) can be used for refining and proportioning according to the heat exchange requirement. The inside of the pore canal can also be processed into a structure with internal threads so as to strengthen the heat exchange effect.
In the device, a countercurrent heat exchange mode is adopted, the heat exchange temperature difference between working media is small, the thermal stress born by the device is small, the device is of an integrated structure, and the device is wholly pressure-bearing. When the ultrahigh pressure working medium flows through the pore canal, the accident of 'tube explosion' of the heat exchanger can not occur, and the heat exchanger can safely and reliably operate in an ultrahigh pressure environment with supercritical parameters.
In the device, the temperature distribution of different axial positions is different, the partition selection of processing materials can be performed, the low-temperature section is processed by adopting materials with good performance and low price, and the high-temperature section is processed by adopting alloy materials which can bear ultrahigh temperature and are high in price. For example, the low temperature section can be made of P93 material, the transition section between the low temperature section and the high temperature section is made of a fusion material of 740H and P93, and the high temperature section is made of 740H material. The low-temperature section is selected by material partition, so that the production and manufacturing cost is saved, the economic benefit is improved, and the device can safely and reliably operate in an ultra-high temperature environment with ultra-supercritical parameters.
As shown in fig. 3, the primary side hole and the secondary side hole have the same diameter and the same hole pitch. The number of the primary side pore channels is the same as that of the secondary side pore channels. The different side channels are arranged in staggered manner, namely the same row is the same side channel, and the adjacent rows are different side channels. Each pore canal is closely adjacent to six pore canals, and comprises four pore canals on different sides and two pore canals on the same side, and the pore canals are arranged in a quincunx shape.
The pore channel arrangement mode can balance the temperature difference between the same-row and same-side pore channels, so that heat exchange is more uniform, and thermal stress is reduced.
As shown in fig. 4, the main heat exchange section of the tunnel heat exchanger adopts a tunnel heat exchange unit, and further comprises a pressure-bearing shell (101), a secondary side heat insulation layer (102), a primary side inlet (103), a primary side outlet (104), a secondary side inlet (105), a secondary side outlet (106), a secondary side inlet header (107), a secondary side outlet header (108), a primary side outlet header (109) and other structures. The pressure-bearing shell (101) is positioned at the outermost side of the whole heat exchanger, wraps other parts and serves as a boundary of the device, and is used for isolating the device from the outside and ensuring the normal operation of the device under relevant working conditions. The secondary side heat insulation layer (102) is respectively arranged at the outer wall of the pipeline of the primary side inlet (103) and the secondary side outlet (106), and the heat of the high-temperature working medium is not dissipated by adding the heat insulation layer, so that the heat exchange efficiency is improved. The primary side inlet (103) and the primary side outlet (104) are arranged at the upper part of the pressure-bearing shell (101) and are used for leading primary side working medium into and out of the heat exchanger. The secondary side inlet (105) is arranged at the lower part of the pressure-bearing shell (101) and is used for leading secondary side working medium into the heat exchanger. The secondary side outlet (106) is positioned right above the pressure-bearing shell (101) and is used for leading out the heated secondary side working medium. The secondary side inlet header (107) and the secondary side outlet header (108) are respectively arranged below and above the main heat exchange section and are used for dispersing and concentrating secondary side working media. The primary side outlet header (109) is arranged below the main heat exchange section and is used for concentrating primary side working media after heat exchange.
The application example operates under supercritical parameters, the primary side working medium is helium, the inlet temperature is 750 ℃, the outlet temperature is 250 ℃, the working pressure is 7.0MPa, and the mass flow is 96.0kg/s. The secondary side working medium is supercritical water, the inlet temperature is 205 ℃, the outlet temperature is 700 ℃, the working pressure is 28.0MPa, and the mass flow is 85.0kg/s. The heat exchange capacity was designed to be 250MW.
The heat exchange unit of the tunnel type heat exchanger in the embodiment is a cylinder, the diameter is 1460mm, and the height is 18960mm. The cross section of the pore canal is circular, the diameter of the pore canal is 10mm, the distance between the pore canals is 13mm, the pore canal on the primary side is arranged in the middle, and the number of the pore canals is 4878; the secondary side holes are arranged in the middle, and the number of the pore passages is 4900. The secondary side holes are arranged in staggered mode to obtain larger effective heat exchange area and improve the heat exchange performance of the heat exchanger.
In the application process, the embodiment has the advantages of compact structure, small occupied space and strong bearing capacity of the whole equipment due to the advantages of the tunnel type heat exchanger, and can play a good role of pressure boundary to form a safety barrier for preventing radiation. The operation stability is strong under the supercritical (super) parameter, the heat exchange performance is good, and the average heat exchange coefficient is close to 2000W/m 2 The total heat exchange capacity was 250MW at. DEG.C.
Claims (10)
1. A design method of a supercritical (super) critical tunnel type heat exchanger is characterized in that: the main heat exchange section of the tunnel type heat exchanger adopts a tunnel type heat exchanger heat exchange unit (1); the main heat exchange section of the duct type heat exchanger comprises a pressure-bearing shell (101), a secondary side heat insulation layer (102), a primary side inlet (103), a primary side outlet (104), a secondary side inlet (105), a secondary side outlet (106), a secondary side inlet header (107), a secondary side outlet header (108) and a primary side outlet header (109); the pressure-bearing shell (101) is positioned at the outermost side of the whole heat exchanger, and the secondary side heat insulation layer (102) is respectively arranged at the outer wall of the pipeline of the primary side inlet (103) and the secondary side outlet (106); the primary side inlet (103) and the primary side outlet (104) are arranged at the upper part of the pressure-bearing shell (101); the secondary side inlet (105) is arranged at the lower part of the pressure-bearing shell (101); the secondary side outlet (106) is positioned right above the pressure-bearing shell (101); the secondary side inlet header (107) and the secondary side outlet header (108) are respectively arranged below and above the main heat exchange section; the primary side outlet header (109) is arranged below the main heat exchange section.
2. The design method of the ultra (supercritical) channel type heat exchanger according to claim 1, wherein the design method comprises the following steps: a primary side pore canal (2) and a secondary side pore canal (3) are processed on the pore canal type heat exchanger heat exchange unit (1); different working mediums flow in adjacent different pore channels, a primary side working medium which emits heat flows through a primary side pore channel (2), and a secondary side working medium which absorbs heat flows through a secondary side pore channel (3); the heat exchange unit (1) of the duct type heat exchanger is one of a cylinder, a cuboid and a prism.
3. The design method of the ultra (supercritical) critical aperture type heat exchanger according to claim 2, wherein the design method comprises the following steps: the heat exchange unit (1) of the tunnel type heat exchanger is made of alloy materials with high temperature resistance and high pressure resistance; the diameter, height and other dimensions of the heat exchange unit (1) of the tunnel type heat exchanger are comprehensively analyzed and set according to factors such as heat transfer capacity, occupied space and the like.
4. A method for designing a supercritical tunnel heat exchanger according to claim 3, wherein: the processing mode of the heat exchange unit (1) of the tunnel type heat exchanger comprises, but is not limited to, casting and additive manufacturing; the processing modes of the primary side pore canal (2) and the secondary side pore canal (3) include, but are not limited to, drilling and integral molding.
5. The design method of the ultra (supercritical) critical pore path heat exchanger according to claim 4, wherein the design method comprises the following steps: the heat exchange unit (1) of the duct type heat exchanger can adopt a P93 material at a low temperature section, a transition section between the low temperature section and a high temperature section adopts a fusion material of 740H and P93, and the high temperature section adopts a 740H material.
6. The design method of the ultra (supercritical) critical aperture type heat exchanger according to claim 5, wherein the design method comprises the following steps: the heat exchange unit (1) of the tunnel type heat exchanger is provided with a bending structure at the inlet and outlet positions.
7. The design method of the ultra (supercritical) critical aperture type heat exchanger according to claim 6, wherein the design method comprises the following steps: the heat exchange unit (1) of the tunnel type heat exchanger is of a multi-section structure.
8. The design method of the ultra (supercritical) critical aperture type heat exchanger according to claim 7, wherein: the number, shape and size of the pore channels, the interval distance and the arrangement angle between the pore channels are calculated according to the heat exchange requirement; the heat exchange requirement is calculated by the following modes including but not limited to heat transfer criterion number correlation type convective heat exchange coefficient h in the pore canal:
wherein n=0.4 when the fluid is heated and n=0.3 when the fluid is cooled.
9. The design method of the ultra (supercritical) channel type heat exchanger according to claim 8, wherein the design method comprises the following steps: the inside of the pore canal is processed into a structure with internal threads so as to strengthen the heat exchange effect.
10. The method for designing the ultra (supercritical) tunnel type heat exchanger according to claim 9, wherein: the diameters of the primary side pore canal and the secondary side pore canal are the same, the pore spaces are the same, and the number of the primary side pore canal is the same as that of the secondary side pore canal; the different side channels are arranged in staggered manner, namely the same row is the same side channel, and the adjacent row is different side channel; each pore canal is closely adjacent to six pore canals, and comprises four pore canals on different sides and two pore canals on the same side, and the pore canals are arranged in a quincunx shape.
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