CN111259596A - Shell-and-tube heat exchanger full-three-dimensional coupling simulation method based on finite volume theory - Google Patents
Shell-and-tube heat exchanger full-three-dimensional coupling simulation method based on finite volume theory Download PDFInfo
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Abstract
The invention discloses a shell-and-tube heat exchanger full three-dimensional coupling simulation method based on finite volume theory, which comprises the following steps: performing geometric modeling on the shell-and-tube heat exchanger by adopting geometric modeling software; meshing the geometric model of the shell-and-tube heat exchanger by using meshing software to form a mesh model; introducing the grid model into CFD software, copying the grids of the heat transfer tube bundle area in situ as secondary tube side grids, and communicating the secondary tube side grids and the grids of the secondary side inlet and outlet areas thereof by a splicing surface method; setting user self-defined variables in CFD software, and establishing a mapping relation between primary and secondary side grids by means of a user self-defined function; calculating flow field information of a primary side and a secondary side of the heat exchanger grid control bodies, and calculating heat exchange quantity between corresponding grid control bodies; returning the heat exchange quantity to the source item of the energy equation by utilizing a user-defined function of CFD software; and finally, performing iterative computation by using CFD software. The invention can realize the coupling heat transfer calculation of the primary side and the secondary side of the shell-and-tube heat exchanger at relatively low calculation cost.
Description
Technical Field
The invention relates to the technical field of simulation of shell-and-tube heat exchangers, in particular to a full three-dimensional coupling simulation method of a shell-and-tube heat exchanger based on a finite volume theory.
Background
The heat exchanger is widely applied to engineering technical fields of energy, power, nuclear energy, petroleum, manufacture, chemical engineering, processing and the like, such as a feeding heat exchanger, an evaporator, a condenser, a reboiler, a heat regenerator and the like. The shell-and-tube heat exchanger is a dividing wall type heat exchanger which takes the wall surface of a tube bundle sealed in a shell as a heat transfer surface, has simple structure, low manufacturing cost, wider flow section and easy scale cleaning, can be used at high temperature and high pressure, accounts for about 30 percent of the whole heat exchanger market, and is one of the most widely applied heat exchanger types. The method has important significance in accurate prediction and analysis of the real-time operation performance of the shell-and-tube heat exchanger.
Such studies can be achieved by experimental means or numerical simulation methods. However, the heat exchangers involved in nuclear power systems are either exceptionally large and expensive or have extreme operating conditions and are difficult to experiment. The method of numerical simulation is of great value in performance evaluation or structural optimization design of the heat exchanger at relatively low cost. Despite the dramatic increase in computer computing power in recent years, it is still difficult to perform a fine simulation of heat exchangers based on finite volume theory.
The invention discloses a shell-and-tube heat exchanger full three-dimensional coupling simulation method based on finite volume theory, which is characterized in that models on two sides of a heat exchanger are established by a porous medium method, a grid mapping relation on two sides of the shell-and-tube heat exchanger is established by means of a user-defined function of a CFD solver, and heat exchange quantity on two sides of the heat exchanger is calculated.
Disclosure of Invention
The technical problem solved by the invention is as follows: fine numerical simulations of shell and tube heat exchangers based on finite volume theory are not acceptable at current computer computing capabilities. The invention provides a shell-and-tube heat exchanger full three-dimensional coupling simulation method based on a finite volume theory, which reasonably simplifies a heat exchange core area, allows researchers to carry out three-dimensional coupling heat transfer analysis on the shell-and-tube heat exchanger under the current computing capacity, and further realizes performance evaluation and structure optimization design of the shell-and-tube heat exchanger.
In order to achieve the purpose, the invention adopts the following technical scheme:
a shell-and-tube heat exchanger full three-dimensional coupling simulation method based on finite volume theory comprises a shell-and-tube heat exchanger solid modeling method, a shell-and-tube heat exchanger primary shell side and secondary tube side two-side data exchange method and a shell-and-tube heat exchanger heat exchange amount calculation method, and specifically comprises the following steps:
step 1: firstly, geometrically simplifying a heat transfer tube bundle area of a shell-and-tube heat exchanger, neglecting fine structures of dense heat transfer tube bundles, baffles and shockproof strips in the heat transfer tube bundle area of the shell-and-tube heat exchanger, adopting uniform geometric mixing treatment for the heat transfer tube bundle area, and establishing a complete and uniform simplified geometric model of the heat transfer tube bundle area by taking the inner wall surface of a primary side of a heat exchange core area of the shell-and-tube heat exchanger as a boundary; on the basis of the simplified geometric model of the heat transfer tube bundle area, performing geometric modeling on a primary side inlet area, a primary side outlet area, a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger according to a real design to form a real geometric model of the secondary side inlet and outlet areas; performing Boolean merging operation on the heat transfer tube bundle area simplified geometric model and a secondary side inlet and outlet area real geometric model to form a complete shell-and-tube heat exchanger geometric model, wherein the complete shell-and-tube heat exchanger geometric model comprises five parts, namely a primary side inlet area, a primary side outlet area, a secondary side inlet area, a secondary side outlet area and a heat transfer tube bundle area;
step 2: and (2) aiming at five parts in the complete shell-and-tube heat exchanger geometric model in the step (1), adopting a multi-domain meshing strategy to carry out meshing: firstly, carrying out grid division on a heat transfer pipe bundle area to ensure that grids of the heat transfer pipe bundle area are regular and ordered hexahedral grids; the rest part adopts hexahedron grids or tetrahedral grids as much as possible to finally form an available grid model;
and step 3: establishing a corresponding relation between grids of a primary side and a secondary side of the shell-and-tube heat exchanger, and specifically comprising the following steps of:
step 3-1: importing the available grid model in the step 2 into CFD software, wherein the grid of the heat transfer tube bundle area divided in the step 2 is used as a primary shell side grid of the shell-and-tube heat exchanger; copying a primary shell side grid in situ as a secondary tube side grid of the shell-and-tube heat exchanger, and communicating the secondary tube side grid with a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger by adopting a splicing surface method to form a complete heat exchanger secondary side model; setting two user-defined variables in CFD software, wherein the first variable is used for recording the serial number of a control body, and the second variable is used for temporarily storing the heat exchange quantity;
step 3-2: assigning a value to the first user-defined variable in the step 3-1 according to the serial number of the grid control body by adopting a user-defined function of CFD software; creating a global one-dimensional structure array in a user-defined function, wherein the length of the global one-dimensional structure array is the same as the number of primary shell side grid control bodies in a heat transfer tube bundle area; each array element in the one-dimensional structure array comprises sixteen floating point type member variables which are sequentially primary shell side temperature, primary shell side x, y and z direction speed, primary shell side density, primary shell side heat conductivity coefficient, primary shell side convective heat transfer coefficient, secondary tube side temperature, secondary tube side x, y and z direction speed, secondary tube side density, secondary tube side heat conductivity coefficient, secondary tube side convective heat transfer coefficient, two-side effective heat conductivity coefficient and two-side heat exchange quantity;
step 3-3: traversing the primary and secondary side heat transfer tube bundle zone grid control bodies in each computing node in the CFD software parallel computing, and storing the temperature, the speed in the x direction, the y direction and the z direction, the density and the heat conductivity coefficient in the grid control bodies into a structure array; in order to ensure that data of a secondary side corresponding to a control body is stored in the same array elements, a first user self-set variable value is used as a structure array index when the structure array is called; finally, according to the user-defined function of the CFD software, merging the structure array data on each computing node into a main node computed in the CFD software;
and 4, step 4: in CFD software, aiming at the shell side and tube side grids of the heat transfer tube bundle area in the step 3-1, adopting a porous medium model, and setting porous medium parameters such as permeability, viscous resistance coefficient and inertial resistance coefficient;
and 5: calculating the heat exchange quantity of the primary side and the secondary side of the heat exchanger according to the data in the main node merged into the CFD software calculation in the step 3, and returning the heat exchange quantity to the corresponding control body of the heat transfer tube bundle area in each calculation node, wherein the specific steps are as follows:
step 5-1: traversing the array elements of the structure array in the step 3-2 in the main node, and respectively calculating the convection heat transfer coefficient h of the primary shell side surface of the heat exchanger according to the density, the specific heat capacity and the heat conductivity coefficientoSecondary tube side surface convection heat transfer coefficient hiCalculating the effective heat exchange coefficient k of the two sides of the heat exchanger according to a circular tube heat conduction equation; the method for calculating the convection heat transfer coefficient of the surfaces at the two sides of the heat exchanger and the effective heat transfer coefficient at the two sides comprises the following steps:
primary tube side of heat exchanger:
secondary shell side of heat exchanger:
effective heat transfer coefficient on both sides of the heat exchanger:
in the above formula, Nui、Nur、NuzRespectively tube side flow, shell side transverse sweep and shell side longitudinal sweep Knudsen cellNumber, in particular Nui＝6.0+0.006Pei、Nur＝6.0+0.006Peo、
Ur、UzThe radial flow velocity and the axial flow velocity of the shell side are respectively, and d and epsilon are respectively the outer diameter and the wall thickness of the heat exchange tube; k is a radical offThe heat transfer coefficient of the fluid is adopted, lambda is the heat transfer coefficient of the heat exchange tube bundle, and k is the effective heat transfer coefficient of two sides of the heat exchanger; peo、PeiShell side and tube side beckmai numbers, respectively, specifically,
ρ is density, CpIs a constant pressure specific heat capacity;
and finally, calculating the heat exchange quantity between the primary and secondary corresponding control bodies of the heat exchanger according to the following formula:
Q＝kAs(To-Ti) (4)
in the above formula, Q is the heat exchange amount, k is the effective heat exchange coefficient on both sides of the heat exchanger, AsFor heat exchange area density, T, of heat exchangero、TiIs the heat exchanger shell side, tube side fluid temperature;
step 5-2: sharing the structure array in the main node to each computing node: traversing the grid control bodies in the heat transfer tube bundle areas in each computing node, taking the first user-defined variable of the grid control body as a structure array index, extracting heat exchange quantity data in the structure array, and assigning values to the second user-defined variable defined in the step 3-1; when the heat exchange quantity is assigned to the primary shell side grid control body of the heat exchanger, a negative value is taken; when the value is assigned to the secondary pipe side grid control body, a positive value is taken; then assigning a second user-defined variable value to the energy equation in the user-defined source item;
step 6: solving an N-S equation in CFD software, judging calculation convergence when the change of the heat exchange amount of the heat exchanger is monitored to be less than 1%, and stopping calculation; otherwise, repeating the steps 3-3 to 6.
Advantageous effects
Compared with the common heat exchanger simulation method in the open literature, the method has the following beneficial effects:
1) the method does not need to finely model the heat exchange tube bundle region, greatly reduces the difficulty in establishing a geometric model and a grid model, and reduces the calculation amount of the heat exchanger coupling heat transfer simulation;
2) in the calculation process of the heat exchange quantity, the method adopts a basic experiment relational expression based on the flowing heat exchange of the tube bundle instead of a performance relational expression provided for a heat exchanger in a specific form. Therefore, the method is hardly influenced by the structural style of the heat exchanger, and researchers are allowed to more flexibly design and optimize the structure of the heat exchanger;
3) the method can be easily realized by means of the basic functions of the existing CFD software, and a large amount of programming development work of researchers is not needed. The CFD software functions utilized by the method are common to a plurality of CFD software, researchers can fully utilize the existing CFD software at hand, and specific software does not need to be obtained.
Drawings
FIG. 1 is a flow chart of a three-dimensional coupled shell and tube heat exchanger calculation.
FIG. 2 is a simplified sectional view of a shell-and-tube heat exchanger.
FIG. 3 is a schematic diagram showing the primary and secondary side grid mapping relationship of the shell-and-tube heat exchanger.
Detailed Description
The present invention will be described in further detail below by taking the simulation of a shell-and-tube type chinese experimental fast reactor intermediate heat exchanger as an example with reference to the flowchart shown in fig. 1, where the CFD software is Fluent and the user uses other CFD software.
A shell-and-tube heat exchanger full three-dimensional coupling simulation method based on finite volume theory comprises a shell-and-tube heat exchanger solid modeling method, a shell-and-tube heat exchanger primary shell side and secondary tube side two-side data exchange method and a shell-and-tube heat exchanger heat exchange amount calculation method, and specifically comprises the following steps:
step 1: firstly, geometrically simplifying a heat transfer tube bundle area of a shell-and-tube heat exchanger, neglecting fine structures of dense heat transfer tube bundles, baffles and shockproof strips in the heat transfer tube bundle area of the shell-and-tube heat exchanger, adopting uniform geometric mixing treatment for the heat transfer tube bundle area, and establishing a complete and uniform simplified geometric model of the heat transfer tube bundle area by taking the inner wall surface of a primary side of a heat exchange core area of the shell-and-tube heat exchanger as a boundary; on the basis of the simplified geometric model of the heat transfer tube bundle area, performing geometric modeling on a primary side inlet area, a primary side outlet area, a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger according to a real design to form a real geometric model of the secondary side inlet and outlet areas; performing Boolean merging operation on the simplified geometric model of the heat transfer tube bundle area and the real geometric model of the secondary side inlet and outlet area to form a complete geometric model of the shell-and-tube heat exchanger, wherein the complete geometric model of the shell-and-tube heat exchanger comprises five parts, namely a primary side inlet area, a primary side outlet area, a secondary side inlet area, a secondary side outlet area and the heat transfer tube bundle area, as shown in FIG. 2;
step 2: and (2) aiming at five parts in the complete shell-and-tube heat exchanger geometric model in the step (1), adopting a multi-domain meshing strategy to carry out meshing: firstly, carrying out grid division on a heat transfer pipe bundle area to ensure that grids of the heat transfer pipe bundle area are regular and ordered hexahedral grids; the rest part adopts hexahedron grids or tetrahedral grids as much as possible to finally form an available grid model;
and step 3: establishing a corresponding relation between grids of a primary side and a secondary side of the shell-and-tube heat exchanger, and specifically comprising the following steps of:
step 3-1: importing the available grid model in the step 2 into CFD software, wherein the grid of the heat transfer tube bundle area divided in the step 2 is used as a primary shell side grid of the shell-and-tube heat exchanger; copying a primary shell side grid in situ as a secondary tube side grid of the shell-and-tube heat exchanger, and communicating the secondary tube side grid with a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger by adopting a splicing surface method to form a complete heat exchanger secondary side model; setting two user-defined variables in CFD software, wherein the first variable is used for recording the serial number of a control body, and the second variable is used for temporarily storing the heat exchange quantity;
step 3-2: assigning a value to the first user-defined variable in the step 3-1 according to the grid control body serial number by adopting a user-defined function of CFD software, as shown in FIG. 3; creating a global one-dimensional structure array in a user-defined function, wherein the length of the global one-dimensional structure array is the same as the number of primary shell side grid control bodies in a heat transfer tube bundle area; each array element in the one-dimensional structure array comprises sixteen floating point type member variables which are sequentially primary shell side temperature, primary shell side x, y and z direction speed, primary shell side density, primary shell side heat conductivity coefficient, primary shell side convective heat transfer coefficient, secondary tube side temperature, secondary tube side x, y and z direction speed, secondary tube side density, secondary tube side heat conductivity coefficient, secondary tube side convective heat transfer coefficient, two-side effective heat conductivity coefficient and two-side heat exchange quantity;
step 3-3: traversing the primary and secondary side heat transfer tube bundle zone grid control bodies in each computing node in the CFD software parallel computing, and storing the temperature, the speed in the x direction, the y direction and the z direction, the density and the heat conductivity coefficient in the grid control bodies into a structure array; in order to ensure that data of a secondary side corresponding to a control body is stored in the same array elements, a first user self-set variable value is used as a structure array index when the structure array is called; finally, according to the user-defined function of the CFD software, merging the structure array data on each computing node into a main node computed in the CFD software;
and 4, step 4: in CFD software, aiming at the shell side and tube side grids of the heat transfer tube bundle area in the step 3-1, adopting a porous medium model, and setting porous medium parameters such as permeability, viscous resistance coefficient and inertial resistance coefficient;
and 5: calculating the heat exchange quantity of the primary side and the secondary side of the heat exchanger according to the data in the main node merged into the CFD software calculation in the step 3, and returning the heat exchange quantity to the corresponding control body of the heat transfer tube bundle area in each calculation node, wherein the specific steps are as follows:
step 5-1: traversing the array elements of the structure array in the step 3-2 in the main node, and respectively calculating the convection heat transfer coefficient h of the primary shell side surface of the heat exchanger according to the density, the specific heat capacity and the heat conductivity coefficientoSecondary tube side surface convection heat transfer coefficient hiCalculating the effective heat exchange coefficient k of the two sides of the heat exchanger according to a circular tube heat conduction equation; two heat exchangersThe method for calculating the convection heat transfer coefficient of the surface of one side and the effective heat transfer coefficients of the two sides comprises the following steps:
primary tube side of heat exchanger:
secondary shell side of heat exchanger:
effective heat transfer coefficient on both sides of the heat exchanger:
in the above formula, Nui、Nur、NuzNu are the Nui＝6.0+0.006Pei、Nur＝6.0+0.006Peo、
Ur、UzThe radial flow velocity and the axial flow velocity of the shell side are respectively, and d and epsilon are respectively the outer diameter and the wall thickness of the heat exchange tube; k is a radical offThe heat transfer coefficient of the fluid is adopted, lambda is the heat transfer coefficient of the heat exchange tube bundle, and k is the effective heat transfer coefficient of two sides of the heat exchanger; peo、PeiShell side and tube side beckmai numbers, respectively, specifically,
ρ is density, CpIs a constant pressure specific heat capacity;
and finally, calculating the heat exchange quantity between the primary and secondary corresponding control bodies of the heat exchanger according to the following formula:
Q＝kAs(To-Ti) (4)
in the above formula, Q is the heat exchange amount, k is the effective heat exchange coefficient on both sides of the heat exchanger, AsFor heat exchange area density, T, of heat exchangero、TiIs the heat exchanger shell side, tube side fluid temperature;
step 5-2: sharing the structure array in the main node to each computing node: traversing the grid control bodies in the heat transfer tube bundle areas in each computing node, taking the first user-defined variable of the grid control body as a structure array index, extracting heat exchange quantity data in the structure array, and assigning values to the second user-defined variable defined in the step 3-1; when the heat exchange quantity is assigned to the primary shell side grid control body of the heat exchanger, a negative value is taken; when the value is assigned to the secondary pipe side grid control body, a positive value is taken; then assigning a second user-defined variable value to the energy equation in the user-defined source item;
step 6: solving an N-S equation in CFD software, judging calculation convergence when the change of the heat exchange amount of the heat exchanger is monitored to be less than 1%, and stopping calculation; otherwise, repeating the steps 3-3 to 6.
Claims (1)
1. A shell-and-tube heat exchanger full three-dimensional coupling simulation method based on finite volume theory is characterized in that: the method comprises a shell-and-tube heat exchanger solid modeling method, a shell-and-tube heat exchanger primary shell side and secondary tube side two-side data exchange method and a shell-and-tube heat exchanger heat exchange amount calculation method, and specifically comprises the following steps:
step 1: firstly, geometrically simplifying a heat transfer tube bundle area of a shell-and-tube heat exchanger, neglecting fine structures of dense heat transfer tube bundles, baffles and shockproof strips in the heat transfer tube bundle area of the shell-and-tube heat exchanger, adopting uniform geometric mixing treatment for the heat transfer tube bundle area, and establishing a complete and uniform simplified geometric model of the heat transfer tube bundle area by taking the inner wall surface of a primary side of a heat exchange core area of the shell-and-tube heat exchanger as a boundary; on the basis of the simplified geometric model of the heat transfer tube bundle area, performing geometric modeling on a primary side inlet area, a primary side outlet area, a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger according to a real design to form a real geometric model of the secondary side inlet and outlet areas; performing Boolean merging operation on the heat transfer tube bundle area simplified geometric model and a secondary side inlet and outlet area real geometric model to form a complete shell-and-tube heat exchanger geometric model, wherein the complete shell-and-tube heat exchanger geometric model comprises five parts, namely a primary side inlet area, a primary side outlet area, a secondary side inlet area, a secondary side outlet area and a heat transfer tube bundle area;
step 2: and (2) aiming at five parts in the complete shell-and-tube heat exchanger geometric model in the step (1), adopting a multi-domain meshing strategy to carry out meshing: firstly, carrying out grid division on a heat transfer pipe bundle area to ensure that grids of the heat transfer pipe bundle area are regular and ordered hexahedral grids; the rest part adopts hexahedron grids or tetrahedral grids as much as possible to finally form an available grid model;
and step 3: establishing a corresponding relation between grids of a primary side and a secondary side of the shell-and-tube heat exchanger, and specifically comprising the following steps of:
step 3-1: importing the available grid model in the step 2 into CFD software, wherein the grid of the heat transfer tube bundle area divided in the step 2 is used as a primary shell side grid of the shell-and-tube heat exchanger; copying a primary shell side grid in situ as a secondary tube side grid of the shell-and-tube heat exchanger, and communicating the secondary tube side grid with a secondary side inlet area and a secondary side outlet area of the shell-and-tube heat exchanger by adopting a splicing surface method to form a complete heat exchanger secondary side model; setting two user-defined variables in CFD software, wherein the first variable is used for recording the serial number of a control body, and the second variable is used for temporarily storing the heat exchange quantity;
step 3-2: assigning a value to the first user-defined variable in the step 3-1 according to the serial number of the grid control body by adopting a user-defined function of CFD software; creating a global one-dimensional structure array in a user-defined function, wherein the length of the global one-dimensional structure array is the same as the number of primary shell side grid control bodies in a heat transfer tube bundle area; each array element in the one-dimensional structure array comprises sixteen floating point type member variables which are sequentially primary shell side temperature, primary shell side x, y and z direction speed, primary shell side density, primary shell side heat conductivity coefficient, primary shell side convective heat transfer coefficient, secondary tube side temperature, secondary tube side x, y and z direction speed, secondary tube side density, secondary tube side heat conductivity coefficient, secondary tube side convective heat transfer coefficient, two-side effective heat conductivity coefficient and two-side heat exchange quantity;
step 3-3: traversing the primary and secondary side heat transfer tube bundle zone grid control bodies in each computing node in the CFD software parallel computing, and storing the temperature, the speed in the x direction, the y direction and the z direction, the density and the heat conductivity coefficient in the grid control bodies into a structure array; in order to ensure that data of a secondary side corresponding to a control body is stored in the same array elements, a first user self-set variable value is used as a structure array index when the structure array is called; finally, according to the user-defined function of the CFD software, merging the structure array data on each computing node into a main node computed in the CFD software;
and 4, step 4: in CFD software, aiming at the shell side and tube side grids of the heat transfer tube bundle area in the step 3-1, adopting a porous medium model, and setting porous medium parameters such as permeability, viscous resistance coefficient and inertial resistance coefficient;
and 5: calculating the heat exchange quantity of the primary side and the secondary side of the heat exchanger according to the data in the main node merged into the CFD software calculation in the step 3, and returning the heat exchange quantity to the corresponding control body of the heat transfer tube bundle area in each calculation node, wherein the specific steps are as follows:
step 5-1: traversing the array elements of the structure array in the step 3-2 in the main node, and respectively calculating the convection heat transfer coefficient h of the primary shell side surface of the heat exchanger according to the density, the specific heat capacity and the heat conductivity coefficientoSecondary tube side surface convection heat transfer coefficient hiCalculating the effective heat exchange coefficient k of the two sides of the heat exchanger according to a circular tube heat conduction equation; the method for calculating the convection heat transfer coefficient of the surfaces at the two sides of the heat exchanger and the effective heat transfer coefficient at the two sides comprises the following steps:
primary tube side of heat exchanger:
secondary shell side of heat exchanger:
effective heat transfer coefficient on both sides of the heat exchanger:
in the above formula, Nui、Nur、NuzNu are the Nui＝6.0+0.006Pei、Nur＝6.0+0.006Peo、
Ur、UzThe radial flow velocity and the axial flow velocity of the shell side are respectively, and d and epsilon are respectively the outer diameter and the wall thickness of the heat exchange tube; k is a radical offThe heat transfer coefficient of the fluid is adopted, lambda is the heat transfer coefficient of the heat exchange tube bundle, and k is the effective heat transfer coefficient of two sides of the heat exchanger; peo、PeiShell side and tube side beckmai numbers, respectively, specifically,
Pei＝ρCp(d-2. epsilon.)/k, p is density, CpIs a constant pressure specific heat capacity;
and finally, calculating the heat exchange quantity between the primary and secondary corresponding control bodies of the heat exchanger according to the following formula:
Q＝kAs(To-Ti) (4)
in the above formula, Q is the heat exchange amount, k is the effective heat exchange coefficient on both sides of the heat exchanger, AsFor heat exchange area density, T, of heat exchangero、TiIs the heat exchanger shell side, tube side fluid temperature;
step 5-2: sharing the structure array in the main node to each computing node: traversing the grid control bodies in the heat transfer tube bundle areas in each computing node, taking the first user-defined variable of the grid control body as a structure array index, extracting heat exchange quantity data in the structure array, and assigning values to the second user-defined variable defined in the step 3-1; when the heat exchange quantity is assigned to the primary shell side grid control body of the heat exchanger, a negative value is taken; when the value is assigned to the secondary pipe side grid control body, a positive value is taken; then assigning a second user-defined variable value to the energy equation in the user-defined source item;
step 6: solving an N-S equation in CFD software, judging calculation convergence when the change of the heat exchange amount of the heat exchanger is monitored to be less than 1%, and stopping calculation; otherwise, repeating the steps 3-3 to 6.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112560359A (en) * | 2020-12-09 | 2021-03-26 | 华南理工大学 | Simulation method for heat transfer characteristics of shell-and-tube heat exchanger in scaling state |
| WO2022011726A1 (en) * | 2020-07-17 | 2022-01-20 | 天华化工机械及自动化研究设计院有限公司 | Ansys-based heat exchanger tube bundle modal analysis method in liquid filling state |
| CN116362159A (en) * | 2023-04-04 | 2023-06-30 | 西安交通大学 | Full three-dimensional coupling calculation and optimization method for liquid metal spiral tube steam generator |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040083012A1 (en) * | 2002-10-28 | 2004-04-29 | Miller John P. | Method of modeling and sizing a heat exchanger |
| CN102788813A (en) * | 2012-08-10 | 2012-11-21 | 甘肃蓝科石化高新装备股份有限公司 | Measurement method for amount of saved energy of enhanced heat-transferring shell-and-tube exchanger |
| CN108170998A (en) * | 2018-02-13 | 2018-06-15 | 上海市特种设备监督检验技术研究院 | A kind of shell-and-tube exchanger efficiency evaluation method |
| CN109657372A (en) * | 2018-12-24 | 2019-04-19 | 成都安世亚太科技有限公司 | A kind of novel shell-and-tube heat exchanger multi-scale coupling collaboration heat exchange analogy method |
-
2020
- 2020-02-20 CN CN202010103669.9A patent/CN111259596B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040083012A1 (en) * | 2002-10-28 | 2004-04-29 | Miller John P. | Method of modeling and sizing a heat exchanger |
| CN102788813A (en) * | 2012-08-10 | 2012-11-21 | 甘肃蓝科石化高新装备股份有限公司 | Measurement method for amount of saved energy of enhanced heat-transferring shell-and-tube exchanger |
| CN108170998A (en) * | 2018-02-13 | 2018-06-15 | 上海市特种设备监督检验技术研究院 | A kind of shell-and-tube exchanger efficiency evaluation method |
| CN109657372A (en) * | 2018-12-24 | 2019-04-19 | 成都安世亚太科技有限公司 | A kind of novel shell-and-tube heat exchanger multi-scale coupling collaboration heat exchange analogy method |
Non-Patent Citations (2)
| Title |
|---|
| 孙鑫: "基于热流固耦合的管壳式换热器数值模拟", 《中国优秀博硕士学位论文全文数据库（硕士） 工程科技II辑》 * |
| 罗再祥: "管壳式换热器传热对比研究与数值模拟", 《中国优秀博硕士学位论文全文数据库（硕士） 工程科技I辑》 * |
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| WO2022011726A1 (en) * | 2020-07-17 | 2022-01-20 | 天华化工机械及自动化研究设计院有限公司 | Ansys-based heat exchanger tube bundle modal analysis method in liquid filling state |
| CN112560359A (en) * | 2020-12-09 | 2021-03-26 | 华南理工大学 | Simulation method for heat transfer characteristics of shell-and-tube heat exchanger in scaling state |
| CN112560359B (en) * | 2020-12-09 | 2022-04-22 | 华南理工大学 | Simulation method for heat transfer characteristics of shell-and-tube heat exchanger in scaling state |
| CN116362159A (en) * | 2023-04-04 | 2023-06-30 | 西安交通大学 | Full three-dimensional coupling calculation and optimization method for liquid metal spiral tube steam generator |
| CN116362159B (en) * | 2023-04-04 | 2024-01-09 | 西安交通大学 | Full three-dimensional coupling calculation and optimization method for liquid metal spiral tube steam generator |
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