CN112082790B - Heat exchanger performance evaluation method based on field cooperation - Google Patents

Heat exchanger performance evaluation method based on field cooperation Download PDF

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CN112082790B
CN112082790B CN202010772860.2A CN202010772860A CN112082790B CN 112082790 B CN112082790 B CN 112082790B CN 202010772860 A CN202010772860 A CN 202010772860A CN 112082790 B CN112082790 B CN 112082790B
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何雅玲
张凯
李明佳
陶文铨
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Xian Jiaotong University
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Abstract

A heat exchanger performance evaluation method based on three-field cooperation of fluid temperature, pressure and a flow field comprises the steps of selecting a reference heat exchanger, determining a criterion relation between a resistance coefficient of the reference heat exchanger and a Reynolds number under a cold working condition, obtaining a characteristic relation between heat exchange quantity ratios of the heat exchanger and the reference heat exchanger for comparison under equal pump work, equal pressure drop and equal flow conditions, representing the characteristic relation as three straight lines of a passing point (1,1) in a rectangular coordinate system under the three constraint conditions of equal pump work, equal pressure drop and equal flow conditions, dividing a working area into four parts, obtaining a performance evaluation graph, and determining the heat exchange performance of the comparison heat exchanger according to the positions of the working point in the four subareas. Through the division of four partitions, qualitative comparative analysis can be conveniently and quickly carried out on different enhanced heat exchange technologies, and whether the enhanced heat exchange technologies really save energy is quantitatively judged; the energy-saving efficiency of the heat exchange enhancement technology at different working points is visually compared with the energy-saving efficiency of different heat exchange enhancement technologies.

Description

Heat exchanger performance evaluation method based on field cooperation
Technical Field
The invention belongs to the technical field of heat transfer optimization of heat exchangers, and particularly relates to a heat exchanger performance evaluation method based on three-field cooperation of fluid temperature, pressure and a flow field.
Background
The heat exchanger is used as a common heat exchange device and widely applied to various fields in production practice, such as an economizer, a flue gas waste heat recoverer, an air conditioner condenser, an evaporator, an electronic equipment radiator, a chemical equipment heat exchanger and the like of a thermal power station. The variety, size and efficiency of heat exchangers, which are important components for industrial production, are also continuously improved with the development of the industry. Particularly, under the background of an era with large energy conservation and emission reduction, the energy consumption is reduced, the heat exchange efficiency of the heat exchanger is improved, and the heat exchanger becomes an attention focus of the industry. The thermal resistance of a commonly used heat exchanger is mainly composed of three parts: the thermal convection resistance of the fluid on the inner side of the pipe and the pipe wall, the thermal conduction resistance of the pipe wall and the thermal convection resistance of the fluid on the outer side of the pipe. Generally, the heat conduction resistance of the pipe wall is very small and is related to the properties of materials, and the heat resistance of the fluid side accounts for the most part of the total heat resistance, so that the use of the reinforced heat exchange fins and the reinforced heat exchange pipes is the most effective method for improving the overall performance of the heat exchanger. Wherein, the thermal resistance of fluid inside the pipe is relatively difficult to change under the limit of processing conditions; the thermal resistance of the fluid on the fin side outside the tube can be improved greatly simply by changing the form of the fin.
The performance of a heat exchanger includes not only thermal performance (heat transfer and resistance), but also many factors including economy, feasibility, reliability, safety, etc. should be considered in performance indexes in engineering applications. Among the numerous performance indexes of heat exchangers, the thermal performance is often the most important index for determining whether the heat exchanger can meet the production requirements. Thus, thermal performance is an index that needs to be considered first in the heat exchanger selection process. The existing heat exchanger evaluation system also usually takes the thermal performance as the standard. However, most performance evaluation indexes of the heat exchange devices are qualitative analysis of heat exchange performance and resistance, and whether the intensified heat exchange technology really achieves the purpose of energy conservation cannot be quantitatively judged.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide a heat exchanger performance evaluation method based on the synergy of the fluid temperature, the pressure and the flow field. The invention not only can quantitatively analyze the energy-saving benefit of the strengthening technology, but also can qualitatively compare the heat exchange comprehensive performance of different structures, can simply and clearly divide different strengthening technologies according to the energy-saving efficiency, and basically realizes the accurate evaluation of the comprehensive performance of the strengthening technology.
In order to achieve the purpose, the invention adopts the technical scheme that:
a heat exchanger performance evaluation method based on cooperation of three fields of fluid temperature, pressure and a flow field comprises the following steps:
1) selecting a reference heat exchanger, and determining a criterion relation between a resistance coefficient f of the reference heat exchanger and a Reynolds number Re under a cold working condition: cRemWherein c and m are constants;
2) and obtaining a form unified characteristic relation of the heat exchange quantity ratio of the heat exchanger for comparison and the reference heat exchanger under the conditions of equal pump work, equal pressure drop and equal flow:
Figure BDA0002617300180000021
wherein, Δ peAnd Δ p0Pressure losses of the heat exchanger for comparison and the reference heat exchanger, respectively; delta TeAnd Δ T0Inlet and outlet temperature differences, k, of the heat exchanger for comparison and the reference heat exchanger, respectivelyiRepresents the constant under different constraint conditions, k under the conditions of equal pump work, equal pressure drop and equal flowiM +2, m +1 and 1, respectively;
3) in a rectangular coordinate system, by Δ p0/ΔpeAs abscissa, Δ T0/ΔTeThe characteristic relation in the step 5) is expressed as three straight lines of a passing point (1,1) in a coordinate system, namely three reference working lines, under three constraint conditions of equal pumping work condition, equal pressure drop condition and equal flow condition; wherein the intersection point of the straight line and the abscissa is a constraint point (1-k)i0), the slope of the straight line is 1/(C)Q,iki) The three straight lines divide the working area into four parts to obtain a performance evaluation graph;
4) obtaining the pressure drop ratio delta p of the reference heat exchanger and the comparison heat exchanger under the given working condition0/ΔpeAnd the ratio of inlet-outlet temperature differences DeltaT0/ΔTeTo obtain a working condition point (Δ p) in the performance evaluation chart0/Δpe，ΔT0/ΔTe) And determining and comparing the heat exchange performance of the heat exchanger according to the positions of the working points in the four subareas.
In the performance evaluation diagram, the four subareas are respectively represented by Arabic numerals 1,2,3 and 4 in the anticlockwise direction, 4 subareas represent four grades of heat exchange capacity, the higher the grade is, the better the heat exchange performance is, the part 1 is a low-efficiency area, and the heat exchange quantity is increased less than the pump work in the area; section 2 is the yield zone, which indicates that the enhanced surface has a higher amount of heat exchange than the reference surface for the same pumping power in this zone; the part 3 is a relatively high-efficiency area and shows that the heat exchange enhancement under the same pressure drop can be obtained, namely, the enhanced surface has higher heat exchange amount than the reference surface under the constraint condition of the same pressure drop; section 4 is a high efficiency zone, indicating that the increase in heat exchange capacity is greater than the increase in drag coefficient at the same flow rate.
Drawing a straight line in the performance evaluation graph, and passing the operating point and a constraint point (1-k) under a certain constraint conditioni0), the slope 1/(C) of the straight line is obtainedQ,iki) Carry-in kiAnd under the constraint condition, the heat exchange quantity lifting amplitude of the heat exchanger relative to the reference heat exchanger can be obtained.
The reference heat exchanger may be a light pipe or a straight fin.
Compared with the prior art, the invention has the beneficial effects that: by means of partitioning, an enhanced heat exchange technology meeting the energy-saving requirement can be selected conveniently; the energy-saving efficiency of different heat exchange enhancement technologies can be simply compared qualitatively and analyzed quantitatively; the purpose of visually comparing the heat exchange performances of different strengthening surfaces is realized. The performance improvement limit of the current reinforced structure and the corresponding limit working condition point can be conveniently and rapidly solved, the maximum theoretical improvement amplitude of heat exchange under a certain working condition is obtained, and a target is pointed out for the design and development of the heat exchanger.
Drawings
Fig. 1 is a graph showing the relationship between the flow rate of the heat exchanger and the amount of heat exchange and the pumping work.
Fig. 2 is a graph of the relationship between the flow rate of the heat exchanger and the amount of heat exchange and the pressure drop.
FIG. 3 is a comprehensive performance evaluation chart according to the present invention.
FIG. 4 is an experimental half-cell vortex generator fin structure.
Fig. 5 is an experimental louvered fin structure.
FIG. 6 is a performance evaluation of two structurally different tube rows in a comprehensive performance evaluation chart.
Detailed Description
The embodiments of the present invention will be described in detail below with reference to the drawings and examples.
The invention relates to a heat exchanger performance evaluation method based on three-field cooperation of fluid temperature, pressure and a flow field, and a relationship diagram of the flow rate, the heat exchange quantity and the pumping work of a heat exchanger is established as shown in figure 1. As shown in fig. 2, a graphical representation of the heat exchanger flow rate versus heat exchange capacity versus pressure drop is established. By means of mathematical derivation and graphical method, the flow rate corresponding to the strengthened surface under the same pump work or pressure drop is obtained first, then the heat exchange quantity corresponding to the flow rate is calculated, and then comparison is carried out. Namely, based on the three-field cooperativity principle, the relationship between the heat exchange quantity of the heat exchanger and the resistance loss and the flow velocity is respectively established, and a criterion relational expression of the resistance loss and the flow velocity is fitted. On the basis, a characteristic relational expression of resistance loss and heat exchange quantity under three constraint conditions of equal pump work, equal pressure drop and equal flow is obtained through mathematical processing, three straight lines corresponding to the three constraint conditions, namely reference working lines, are drawn in a rectangular coordinate system according to the relational expression, the working area is divided into four parts by the three straight lines, and a performance evaluation graph of the heat exchanger is obtained, and is shown in fig. 3. Thus, the evaluation method of the performance evaluation partition map with the aim of energy saving is obtained. Through the division of the four subareas, qualitative comparison analysis can be conveniently and quickly carried out on different enhanced heat exchange technologies, and whether the enhanced heat exchange technologies really save energy can be quantitatively judged; the energy-saving efficiency of the heat exchange technology at different working points can be visually enhanced; the energy-saving efficiency of different heat exchange enhancing technologies can be visually compared.
The specific process of the invention is as follows:
the pumping work can be expressed as
P(u)＝AcucΔp
Wherein A iscIs the smallest cross-sectional area, ucIs the average velocity at the smallest cross section.
Will be provided with
Figure BDA0002617300180000041
Substituted into the above formula to obtain
Figure BDA0002617300180000042
Wherein L is a characteristic dimension, D is a characteristic diameter (tube outer diameter), f is a resistance coefficient of the reference heat exchanger under a cold working condition, and rho is density;
similarly, the pressure drop can be expressed as
Figure BDA0002617300180000043
The flow rate can be expressed as
Qm(u)＝ρAcuc
Meanwhile, the heat exchange amount may be expressed as
Q(u)＝ρ·uc·Ac·cp·ΔT
Wherein c ispIs the heat capacity, and delta T is the inlet and outlet temperature difference;
taking pumping work P and heat exchange quantity Q as vertical coordinates and head-on wind speed ucThe pumping work P and the heat exchange quantity Q are drawn along the windward speed u in the same coordinate as the abscissacAs shown in fig. 1. In fig. 1, the curve denoted by reference numeral 1 represents the performance curve of the base structure, and the curve denoted by reference numeral 2 represents the performance curve of the reinforcing structure. Per P1(u) a point a on the curve, intersecting a parallel line P on the abscissa2(u) curve and ordinate at point b and P1Point; crossing the point a as a parallel line of the ordinate, crossing P2(u) curve at point f, parallel to abscissa and ordinate at P1Point; meanwhile, the heat exchange quantity Q corresponding to the point a and the point b is drawn in the figure1And Q2. The point a and the point b can be regarded as two structures in equal pumping work P1The working points corresponding to the conditions, namely the working points corresponding to the point a and the point b are respectively (P)1，Q1) And (P)1，Q2). As shown in fig. 1, under the condition of equal pumping work, the speed difference between two points is Δ u as can be seen in the working condition triangle corresponding to the working condition points of the two structures. By mathematical derivation, Δ u is obtained below.
By deriving P (u)
Figure BDA0002617300180000051
The relationship between f and Reynolds number Re is: cRem；
Derived from f
Figure BDA0002617300180000052
Figure BDA0002617300180000053
Assuming the angle theta of the triangle under the working condition, there is
Figure BDA0002617300180000054
The increment of the constant pumping work speed Deltau can be expressed as
Figure BDA0002617300180000055
Wherein u isaIndicating pumping work P1Flow rate of the corresponding structure 1; Δ p1And Δ p2Respectively represent at the same flow rate uaNext, two configurations correspond to pressure drop.
According to the condition, the cross-sectional areas are equal, then
Figure BDA0002617300180000061
The speed variation can be expressed as
Figure BDA0002617300180000062
Then waiting for the pumping work P1The ratio of heat exchange amount under the condition is
Figure BDA0002617300180000063
Further, the ratio of the heat exchange amount under the condition of equal pump work can be obtained:
Figure BDA0002617300180000064
generally speaking, the value of delta u is very small, the sensitivity of the temperature difference between an inlet and an outlet to the flow speed is not high, and delta T can be considered1And Δ T2Were obtained at the same flow rate.
Similarly, according to fig. 2, the ratio of the heat exchange capacity under equal pressure drop conditions can be obtained:
Figure BDA0002617300180000065
ratio of heat exchange amount under equal flow rate condition:
Figure BDA0002617300180000066
defining quantitative relational expressions of heat exchange quantity ratios of the heat exchanger and the reference heat exchanger for comparison under the conditions of equal pump work, equal pressure drop and equal flow respectively as follows:
Figure BDA0002617300180000067
Figure BDA0002617300180000068
Figure BDA0002617300180000069
can obtain the product
Figure BDA00026173001800000610
Figure BDA0002617300180000071
Figure BDA0002617300180000072
The unified form is:
Figure BDA0002617300180000073
further, the characteristic relation can be obtained as
Figure BDA0002617300180000074
Wherein Q iseAnd Q0The heat exchange quantity of the heat exchanger and the reference heat exchanger used for comparison is respectively; peAnd P0The pump work of the heat exchanger for comparison and the reference heat exchanger are respectively; Δ peAnd Δ p0Pressure losses of the heat exchanger for comparison and the reference heat exchanger, respectively; delta TeAnd Δ T0Inlet and outlet temperature differences, k, of the heat exchanger for comparison and the reference heat exchanger, respectivelyiRepresents the constant under different constraint conditions, k under the conditions of equal pump work, equal pressure drop and equal flowiM +2, m +1 and 1, respectively, m being the classical correlation f-cRemIs constant in (1).
In a rectangular coordinate system, by Δ p0/ΔpeAs abscissa, Δ T0/ΔTeThe characteristic relation can be expressed as three straight lines of a passing point (1,1) in a coordinate system, namely a reference working line, under three constraint conditions of equal pumping work condition, equal pressure drop condition and equal flow condition; wherein the intersection point of the straight line and the abscissa is a constraint point (1-k)i0), the slope of the straight line is 1/(C)Q, iki). The three straight lines divide the working area into four parts, and a performance evaluation diagram is obtained, as shown in fig. 3, and the comprehensive performance evaluation diagram is not limited by any other assumptions such as heat exchange area, heat exchange temperature difference and characteristic size except for the assumption that the thermal physical properties are constant and the cross-sectional area is the same. In fig. 1, four zones are respectively represented by arabic numerals 1,2,3,4 in the counterclockwise direction, and 4 zones represent four levels of heat exchange capacity, and a higher level indicates better heat exchange performance. Section 1 is referred to as the low efficiency zone, and shows that in this zone, the increase in heat exchange is less than the increase in pumping work; section 2, referred to as the yield zone, indicates that the enhanced surface has a higher amount of heat exchange than the reference surface for the same pumping work in this region; part 3 is called as a relatively high-efficiency area and shows that the heat exchange enhancement under the same pressure drop can be obtained, namely, the enhanced surface has higher heat exchange amount than the reference surface under the constraint condition of the same pressure drop; section 4, referred to as the high efficiency zone, shows that the increase in heat exchange capacity is greater than the increase in drag coefficient at the same flow rate. According to the figure, the influence of the comprehensive performance of the heat exchanger can be evaluated, and the evaluation method is irrelevant to the working condition.
During evaluation, the pressure drop ratio delta p of the reference heat exchanger and the comparative heat exchanger under a given working condition is obtained0/ΔpeAnd the ratio of inlet-outlet temperature differences DeltaT0/ΔTeTo obtain a working condition point (Δ p) in the performance evaluation chart0/Δpe，ΔT0/ΔTe) And determining and comparing the heat exchange performance of the heat exchanger according to the positions of the working points in the four subareas. Concretely, a straight line is drawn, the working point passes through the constraint point (1-k) under a certain constraint conditioni0), the slope 1/(C) of the straight line is obtainedQ,iki) Carry-in kiAnd under the constraint condition, the heat exchange quantity lifting amplitude of the heat exchanger relative to the reference heat exchanger can be obtained.
If the light pipe or the straight fin is used as the reference heat exchanger, various different heat exchangers can draw working condition points in the same performance evaluation diagram, so that the comprehensive evaluation and comparison of the performances of different heat exchangers are realized.
The constraint conditions in the performance evaluation chart of the present invention are not limited to the equal pumping power, the equal pressure drop and the equal flow rate conditions. Any constraint that limits both flow rate and pressure drop simultaneously satisfies the characteristic relation.
The horizontal and vertical coordinates (inlet and outlet temperature difference and pressure drop) of the comprehensive performance evaluation chart are physical quantities which are most concerned in engineering practice and can be directly read, so that the evaluation precision is improved, the chart is more convenient, and the using process is simpler. The performance improvement limit of the current reinforced structure and the corresponding limit working condition point can be conveniently and rapidly solved, the maximum theoretical improvement amplitude of heat exchange under a certain working condition is obtained, and a target is pointed out for the design and development of the heat exchanger.
The present invention is described below by way of an example.
Case (2): take a compact heat exchanger as an example. In the process of optimally designing the parameters of the heat exchanger, the tube spacing and the tube row number are important optimization targets due to space limitation. The heat exchange performance of the straight fins, the half-cell fins and the louver fins corresponding to different flow rates under different tube rows is contrastively analyzed by using an experimental method. As shown in fig. 4 and 5, the half-cell vortex generator and louver fin structure parameters are respectively, and the straight fin structure parameters are consistent with the half-cell vortex generator and the louver fin structure parameters. As shown in fig. 6, the operating points of two types of reinforced fins (fin pitch 2mm) at different flow rates are plotted in the engineering application performance evaluation chart (the reference heat exchanger is a flat fin). As can be seen from the figure, the experimental measurement data show that the working points of both are located substantially in zones 1 and 2. On the whole, the working point of the louver fin is closer to the abscissa, which shows that the heat exchange effect of the louver fin is better than that of a half-cell fin; from the arrangement of the working points on the partition diagram, most of the working points of the louver fins are closer to the 3 regions under the same tube row number, which shows that the comprehensive heat exchange performance of the louver fins is better than that of the half-cell fins, and the result is consistent with the conclusion obtained by experiments. As can also be seen from fig. 6, the overall heat exchange performance of the single row louver structure is the best of these six structures. In addition, the working points of the two strengthening fins under different tube rows are drawn under the same coordinate system, as can be seen from fig. 6, for the two structures, the comprehensive heat exchange performance of the four tube rows is the worst; the main reasons are as follows: with the increase of the number of the tube rows, the fluid disturbance caused by the tubes is strong, so that the heat exchange enhancement effect caused by the reinforcing structure is relatively weakened.

Claims (4)

1. A heat exchanger performance evaluation method based on cooperation of three fields of fluid temperature, pressure and a flow field is characterized by comprising the following steps:
1) selecting a reference heat exchanger, and determining a criterion relation between a resistance coefficient f of the reference heat exchanger and a Reynolds number Re under a cold working condition: cRemWherein c and m are constants;
2) and obtaining a form unified characteristic relation of the heat exchange quantity ratio of the comparison heat exchanger and the reference heat exchanger for comparison under the conditions of equal pump work, equal pressure drop and equal flow:
Figure FDA0003021751470000011
wherein, Δ peAnd Δ p0Pressure drops of the reference heat exchanger and the reference heat exchanger are respectively measured; delta TeAnd Δ T0The inlet and outlet temperature difference k of the comparison heat exchanger and the reference heat exchangeriRepresents the constant under different constraint conditions, k under the conditions of equal pump work, equal pressure drop and equal flowiM +2, m +1 and 1, respectively;
3) in a rectangular coordinate system, by Δ p0/ΔpeAs abscissa, Δ T0/ΔTeThe characteristic relation in the step 2) is expressed as three straight lines of a passing point (1,1) in a coordinate system, namely three reference working lines, under three constraint conditions of equal pumping work condition, equal pressure drop condition and equal flow condition; wherein the intersection point of the straight line and the abscissa is a constraint point (1-k)i0), the slope of the straight line is 1/(C)Q，iki) The three straight lines divide the working area into four parts to obtain a performance evaluation graph;
4) obtaining the pressure drop ratio delta p of the reference heat exchanger and the comparison heat exchanger under the given working condition0/ΔpeAnd the ratio of inlet-outlet temperature differences DeltaT0/ΔTeTo obtain a performance evaluationOperating Point (Δ p) in the figure0/Δpe，ΔT0/ΔTe) And determining and comparing the heat exchange performance of the heat exchanger according to the positions of the working points in the four subareas.
2. The method for evaluating the performance of the heat exchanger based on the cooperation of the fluid temperature, the fluid pressure and the fluid field in the three fields is characterized in that in the performance evaluation chart, the four subareas are respectively represented by Arabic numerals 1,2,3 and 4 in the counterclockwise direction, the 4 subareas represent four grades of heat exchange capacity, the higher the grade is, the better the heat exchange performance is indicated, the part 1 is a low-efficiency area, and the increase of the heat exchange quantity in the area is smaller than the increase of the pump work; section 2 is the yield zone, which indicates that the enhanced surface has a higher amount of heat exchange than the reference surface for the same pumping power in this zone; the part 3 is a relatively high-efficiency area and shows that the heat exchange enhancement under the same pressure drop can be obtained, namely, the enhanced surface has higher heat exchange amount than the reference surface under the constraint condition of the same pressure drop; section 4 is a high efficiency zone, indicating that the increase in heat exchange capacity is greater than the increase in drag coefficient at the same flow rate.
3. The heat exchanger performance evaluation method based on the cooperation of the fluid temperature, the fluid pressure and the flow field according to claim 1, wherein a straight line is drawn in a performance evaluation graph, the operating point is passed through, and the constraint point (1-k) under a certain constraint condition is passed throughi0), the slope 1/(C) of the straight line is obtainedQ，iki) Carry-in kiAnd under the constraint condition, the heat exchange quantity lifting amplitude of the heat exchanger relative to the reference heat exchanger can be obtained.
4. The method for evaluating the performance of the heat exchanger based on the cooperation of the fluid temperature, the fluid pressure and the fluid field according to claim 1, wherein the reference heat exchanger is a light pipe or a straight fin.
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