CN106482565B - Heat exchange tube and shell-and-tube heat exchanger adopting same - Google Patents
Heat exchange tube and shell-and-tube heat exchanger adopting same Download PDFInfo
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- CN106482565B CN106482565B CN201611031481.8A CN201611031481A CN106482565B CN 106482565 B CN106482565 B CN 106482565B CN 201611031481 A CN201611031481 A CN 201611031481A CN 106482565 B CN106482565 B CN 106482565B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses a heat exchange tube and a shell-and-tube heat exchanger adopting the same, wherein the heat exchange tube comprises a round tube (2), a preposed clapboard (1) and/or a postposition clapboard (3) are/is arranged on the round tube (2), the round tube (2) is divided into two areas by taking the central axis which is perpendicular to the incoming flow direction of the heat exchange tube and passes through the round tube (2) as a reference interface, one area which is firstly contacted with the incoming flow in the two areas is taken as a preposed area, the other area is taken as a postposition area, the preposed clapboard (1) is positioned on the preposed area of the round tube (2), and the postposition clapboard (3) is positioned on the postposition area of the round tube (2). According to the invention, through setting and improving the key structures of the front clapboard, the rear clapboard and the like on the traditional heat exchange tube, the problems of vibration of the heat exchange tube and increase of resistance borne by the heat exchange tube caused by the increase of the flow velocity of fluid in the shell-and-tube heat exchanger can be effectively solved, and the resistance reduction and vibration reduction of the shell-and-tube heat exchanger are realized.
Description
Technical Field
The invention belongs to the field of engineering thermophysical heat exchangers, and particularly relates to a heat exchange tube and a shell-and-tube heat exchanger adopting the same.
Background
When fluid sweeps across the cylinder, antisymmetric vortex wake flows which periodically and alternately fall off are generated on two sides of the back of the cylinder, and the antisymmetric vortex wake flows are called karman vortex streets. The vibration of the stress on the surface of the cylinder is closely related to the vortex shedding phenomenon in the wake, and the alternate generation and shedding of the vortex can generate an exciting force which is vertical to the periodic change of the flow direction on two sides of the cylinder, so that the cylinder vibrates. With the rapid development of the fields of energy and power engineering, aerospace and nuclear engineering in recent years, the control problem of the bluff body induced vibration is attracted by wide attention and higher requirements are put forward.
In many fluid-related mechanical projects, inducing vibration is a significant safety-related problem. Once the heat exchange tube vibrates in the shell-and-tube heat exchanger, problems such as collision and abrasion between the heat exchange tube and between the heat exchange tube and the baffle plate can be caused. How to reduce the vibration in the heat exchanger to large capacity, high parameter development, simultaneously in order to strengthen heat transfer and reduce the scale formation, the fluid velocity generally improves now, seems especially important.
Disclosure of Invention
In view of the above drawbacks or needs for improvement in the prior art, an object of the present invention is to provide a heat exchange tube and a shell-and-tube heat exchanger using the same, in which the structure (especially shape parameters) and arrangement of the leading and/or trailing partition plates, which are critical in the heat exchange tube, are improved, and thus, compared with the prior art, the problems of vibration of the heat exchange tube and increase in resistance to the heat exchange tube, which are caused by an increase in fluid flow rate in the shell-and-tube heat exchanger, can be effectively solved, and resistance and vibration reduction of the shell-and-tube heat exchanger can; the heat exchange tube and the shell-and-tube heat exchanger adopting the heat exchange tube are very suitable for high-flow-rate fluid, the applicable flow rate range is more than or equal to 0.5m/s and less than or equal to 5m/s, the applicable Reynolds number Re (Reynolds number: Re is U multiplied by D/upsilon, U is the incoming flow velocity, D is the diameter (namely the outer diameter) of the heat exchange tube, and upsilon is the kinematic viscosity coefficient of the fluid) range is 103≤Re≤105。
In order to achieve the above object, according to one aspect of the present invention, there is provided a heat exchange tube, characterized in that the heat exchange tube comprises a round tube (2), a front baffle (1) and/or a rear baffle (3) are/is provided on the round tube (2), wherein the round tube (2) is divided into two regions by taking a central axis perpendicular to the incoming flow direction of the heat exchange tube and passing through the round tube (2) as a reference interface, and one of the two regions which is first contacted with the incoming flow is a front region, and the other region is a rear region, then the front baffle (1) is positioned on the front region of the round tube (2), and the plane of the front baffle (1) is parallel to the incoming flow direction; the rear clapboard (3) is positioned on the rear area of the round pipe (2), and the plane of the rear clapboard (3) is parallel to the incoming flow direction;
the outer diameter of the circular tube (2) is recorded as D, and the projection lengths of the front partition plate (3) and the rear partition plate (1) on a plane perpendicular to the central axis of the circular tube (2) are recorded as h, so that the h satisfies the following conditions: h is more than or equal to 0 and less than or equal to 0.6 multiplied by D;
as a further preferable aspect of the present invention, the front partition (1) is a flat plate having a front edge in a wavy, zigzag or trapezoidal shape; the rear baffle (3) is a flat plate with a wavy, zigzag or trapezoidal tail edge.
As a further preferable mode of the invention, the front partition (1) is a flat plate with a rectangular, triangular, trapezoidal or circular arc-shaped cross section on the end surface; the rear partition plate (3) is a flat plate with the end surface of which the cross section is rectangular, triangular, trapezoidal or circular arc.
As another arrangement scheme of the invention, the distance q1 between the contact line of the front clapboard (1) and the round tube (2) and a plane which passes through the central axis of the round tube (2) and is parallel to the incoming flow direction satisfies 0-q 1-0.2 xD; the distance q2 between the contact line between the rear clapboard (3) and the round tube (2) and the plane which passes through the central axis of the round tube (2) and is parallel to the incoming flow direction meets the condition that q2 is not less than 0 and not more than 0.2 xD.
According to another aspect of the present invention, there is provided a shell-and-tube heat exchanger using the above heat exchange tube, characterized in that the shell-and-tube heat exchanger comprises the above heat exchange tube.
Compared with the prior art, the technical scheme of the invention can improve the flow field of the heat exchange tube by-pass wake flow, reduce the resistance borne by the heat exchange tube, reduce the vibration of the heat exchange tube caused by vortex shedding, reduce the vortex shedding frequency, increase the fluid flow rate more reasonably, improve the convection heat transfer coefficient and strengthen the heat exchange of the heat exchanger. The transition of the separation shear layer at the downstream of the cylinder can be accelerated by a turbulent flow boundary layer generated when the fluid flows through the preposed partition plate, and the separation point of the shedding vortex moves downstream when the fluid flows through the cylinder, so that the width of a wake region is narrowed, and the cylinder resistance is reduced. Particularly, through the reasonable arrangement of the rear partition plate, the heat exchange tube can delay the interaction of shear layers of the wake area of the heat exchange tube to the downstream, change the static pressure distribution of the wall surface of the heat exchange tube, effectively reduce the fluctuation amplitude of the lift coefficient and efficiently reduce the induced vibration of the heat exchange tube.
The length parameter h of the partition plate is recommended to be selected from 0 to 0.6 multiplied by D, because when the length parameter h of the partition plate is smaller, the rear partition plate can block the interaction of the shear layers of the wake flow area and delay the interaction to the downstream, so that the pressure pulsation on the surface of the heat exchange tube is reduced, the purpose of reducing resistance and reducing vibration is realized, and the problem that when the length parameter h of the partition plate is too large, the trailing edge of the heat exchange tube drops and is subjected to vortex impact on the partition plate due to the overlong length of the partition plate, the vibration amplitude of the lift coefficient of the heat exchange tube is increased, and the adverse condition of reducing resistance and reducing.
The fact that the pressure distribution of the wall surface of the heat exchange tube with the rear partition plate can be measured in a wind tunnel experiment is one of the reasons, but because the fluctuation frequency of the lift coefficient caused by vortex shedding is high under high Reynolds number, an experimental instrument is difficult to capture, and the vibration reduction effect of the heat exchange tube with the rear partition plate is difficult to study. The invention accurately simulates the flowing state of the fluid under high Reynolds number through three-dimensional large vortex numerical simulation, so that the resistance and vibration reduction effects of the heat exchange tube and the rear clapboard can be accurately predicted and studied.
Specifically, the present invention can achieve the following advantageous effects:
1. the design basis of the shapes of the front clapboard and the rear clapboard adopts a rectangular flat plate (or a flat plate with the shapes of the front edge or the tail edge in different forms such as a wavy shape, a saw-tooth shape, a trapezoid shape and the like), the length parameter h of the clapboard in the invention (when the clapboard is the flat plate with the shapes of the front edge or the tail edge in different forms such as a wavy shape, a saw-tooth shape, a trapezoid shape and the like, h represents the projection length of the top end of the clapboard on a plane vertical to the central axis of a round pipe) is between 0 and 0.6 multiplied by D, the resistance and the lift force borne by a heat exchange pipe can be effectively reduced according to the corresponding simulation calculation verification, better resistance and vibration reduction effects are realized, the heat exchange pipe can be used at higher flow velocity, the increase of the flow velocity can better.
The invention can correspondingly enlarge or reduce the length parameter h of the clapboard according to the diameter D of the heat exchange tube, so that the designed rear short clapboard is more matched with the heat exchange tube.
Drawings
FIG. 1 is a schematic view of the overall structure of a heat exchange tube with a front partition and a rear partition according to the present invention;
FIG. 2 is a schematic illustration of the dimensions of a heat exchange tube with a leading and trailing baffle; in the figure, D is the diameter (namely the outer diameter) of the heat exchange tube, the lengths of the front clapboard (1) and the rear clapboard (3) are equal to each other and are h, and t is the thickness of the clapboard;
FIG. 3 is a schematic view of the installation of a heat exchange tube with only a pre-positioned baffle in a shell-and-tube heat exchanger;
FIG. 4 is a schematic illustration of the installation of a heat exchange tube with only a rear baffle in a shell and tube heat exchanger;
FIG. 5 is a schematic view of the installation of a heat exchange tube with baffles on both the front and back sides in a shell and tube heat exchanger;
FIG. 6 is a schematic view of the heat exchange tube of FIG. 1 with different types of leading and/or trailing edge separators;
FIG. 7 is a schematic view of the heat exchange tube of FIG. 1 showing the construction of the separator with different cross-sectional shapes of the end surfaces;
FIG. 8 is a schematic view of the heat exchange tube of FIG. 1 after the position of the partition has been translated;
FIG. 9 is a graph of the coefficient of mean resistance of a heat exchange tube;
FIG. 10 is a graph of a lift coefficient frequency amplitude analysis of a heat exchange tube; where, fig. 10A corresponds to Re 4 × 103Fig. 10B corresponds to Re 2 × 104Fig. 10C corresponds to Re 3.6 × 104；
The meanings of the symbols in the figure are as follows: 1 is a front baffle, 2 is a round pipe, 3 is a rear baffle, and 4 is a baffle plate in a shell-and-tube heat exchanger.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
As shown in fig. 1 and 2, the heat exchange tube of the present invention comprises a round tube (2), and a front baffle (1) and a rear baffle (3) connected to the round tube (2), wherein the round tube (2) is divided into two regions by taking a central axis passing through the round tube (2) and perpendicular to an incoming flow direction of the heat exchange tube as a reference interface, one of the two regions which is firstly contacted with the incoming flow is taken as a front region, the other region is taken as a rear region, the front baffle (1) is located on the front region of the round tube (2), and a plane of the front baffle (1) is parallel to the incoming flow direction; the rear clapboard (3) is positioned on the rear area of the round pipe (2), and the plane of the rear clapboard (3) is parallel to the incoming flow direction;
the projection lengths of the front partition plate (3) and the rear partition plate (1) on a plane vertical to the central axis of the circular tube (2) are all h, and then the h satisfies the following conditions: h is more than or equal to 0 and less than or equal to 0.6 multiplied by D;
the invention designs a novel heat exchange tube by adjusting the length parameter h (h is between 0 and 0.6 multiplied by D) of a rear clapboard (1) according to the structural parameter D of a circular tube 2 of the heat exchange tube, wherein the thickness parameter t of the rear clapboard (1) and a front clapboard (3) can be adjusted according to the practice, and the influence on the vibration reduction and the resistance reduction of the heat exchange tube is little.
FIG. 3 is a schematic view of the installation of a heat exchange tube with only a pre-positioned baffle in a shell-and-tube heat exchanger; as shown in the figure, because of the existence of the baffle plate (4), the incoming flow of the heat exchange tube is changed alternately in the upper direction and the lower direction, and if the patent is applied to a shell-and-tube heat exchanger, the structure as shown in the figure is adopted to avoid the fluid leakage at the contact part of the baffle plate and the baffle plate.
FIG. 4 is a schematic illustration of the installation of a heat exchange tube with only a rear baffle in a shell and tube heat exchanger; as shown in the figure, because of the existence of the baffle plate (4), the incoming flow of the heat exchange tube is changed alternately in the upper direction and the lower direction, and if the patent is applied to a shell-and-tube heat exchanger, the structure as shown in the figure is adopted to avoid the fluid leakage at the contact part of the baffle plate and the baffle plate.
FIG. 5 is a schematic view of the installation of a heat exchange tube with baffles on both the front and back sides in a shell and tube heat exchanger; as shown in the figure, because of the existence of the baffle plate (4), the incoming flow of the heat exchange tube is changed alternately in the upper direction and the lower direction, and if the patent is applied to a shell-and-tube heat exchanger, the structure as shown in the figure is adopted to avoid the fluid leakage at the contact part of the baffle plate and the baffle plate.
FIG. 6 is a schematic view of the heat exchange tube of FIG. 1 with different types of leading and/or trailing edge separators; wherein, figure (1) is a conventional rectangular front edge and/or tail edge clapboard, figures (2) and (3) are sawtooth-shaped front edge and/or tail edge clapboards, figures (4) and (5) are trapezoidal front edge and/or tail edge clapboards, and figures (6) and (7) are wavy front edge and/or tail edge clapboards.
FIG. 7 is a schematic view of the heat exchange tube of FIG. 1 showing the construction of the separator with different cross-sectional shapes of the end surfaces; wherein, the figure (1) is a partition board with a conventional rectangular end surface cross section, the figure (2) is a partition board with an isosceles trapezoid end surface cross section, the figure (3) is a partition board with a non-isosceles trapezoid end surface cross section, the figure (4) is a partition board with an equilateral triangle end surface cross section, the figure (5) is a partition board with a non-equilateral triangle end surface cross section, the figure (6) is a partition board with a circular arc end surface cross section, and the figure (7) is a partition board with any arc end surface cross section.
FIG. 8 is a schematic view of the heat exchange tube of FIG. 1 after the position of the partition plate has been translated; the diaphragm fixation position is shown translated by a distance q.
FIG. 9 is a graph of the average resistance coefficient of heat exchange tubes at different Reynolds numbers. The existence of the rear clapboard obviously reduces the resistance borne by the heat exchange tube under different Reynolds numbers, and the resistance coefficient can be reduced by 35 percent to the maximum. The reason is that the static pressure of the negative pressure area on the wall surface of the heat exchange tube is obviously increased along with the increase of the length of the rear clapboard, so that the pressure difference resistance borne by the heat exchange tube is reduced, and the total resistance coefficient is reduced.
FIG. 10 is a graph of frequency amplitude analysis of lift coefficient of a heat exchange tube. Where, fig. 10A corresponds to Re 4 × 103Fig. 10B corresponds to Re 2 × 104Fig. 10C corresponds to Re 3.6 × 104(ii) a Due to the existence of the rear partition plate, the lift fluctuation borne by the heat exchange tube is obviously reduced under different Reynolds numbers, and the maximum reduction of the amplitude of the lift coefficient can reach 50%. The reason is that the existence of the rear short partition plate causes the high negative pressure area generated by the boundary layer separation at the upper part of the heat exchange tube along with the increase of the length of the partition plateThe negative pressure is obviously reduced, which is an important reason for reducing the fluctuation amplitude of the lift coefficient of the heat exchange tube. The frequency corresponding to the maximum value of the lift coefficient amplitude is the vortex shedding frequency of the tail edge of the heat exchange tube, and the vortex shedding frequency of the tail edge of the heat exchange tube is reduced due to the existence of the rear partition plate, so that the vibration of the heat exchange tube is reduced.
The heat exchange tube can adjust the thickness parameter of the clapboard according to the practical application condition under the condition that the length parameter h of the clapboard is not changed; for example, the thickness of the partition plate can be selected according to the actual arrangement condition of the heat exchange tubes in the heat exchanger, and a rear partition plate which is more matched with the heat exchange tubes is designed. The round tube and the partition plate (comprising the front partition plate and the rear partition plate) of the heat exchange tube can be manufactured and processed respectively according to related processes, and can be assembled and used after being inspected to be qualified, and can also be integrally formed.
It will be understood by those skilled in the art that the foregoing is only a preferred embodiment of the present invention, and is not intended to limit the invention, and that any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (2)
1. A heat exchange tube applied to a shell-and-tube heat exchanger is characterized by comprising a round tube (2), wherein a baffle plate (4) is arranged on the periphery of the round tube (2),
reynolds number Re of fluid outside the heat exchange tube meets 3.6 multiplied by 104≤Re≤105(ii) a The round tube (2) is provided with a front clapboard (1) and/or a rear clapboard (3), wherein the round tube (2) is divided into two areas by taking the central axis which is perpendicular to the incoming flow direction of the heat exchange tube and passes through the round tube (2) as a reference interface, one area which is firstly contacted with the incoming flow in the two areas is a front area, the other area is a rear area, the front clapboard (1) is positioned on the front area of the round tube (2), and the plane of the front clapboard (1) is parallel to the incoming flow direction; the rear clapboard (3) is positioned on the rear area of the round pipe (2), and the plane of the rear clapboard (3) is parallel to the incoming flow direction; and is
The front baffle (1) is a flat plate with a wave-shaped, saw-toothed or trapezoidal front edge; the rear clapboard (3) is a flat plate with the tail edge in a wavy, zigzag or trapezoidal shape; the front baffle (1) is a flat plate with the end surface of which the cross section is triangular, trapezoidal or circular arc; the rear partition plate (3) is a flat plate with the end surface of which the cross section is triangular, trapezoidal or circular arc;
the outer diameter of the circular tube (2) is recorded as D, and the projection lengths of the front partition plate (1) and the rear partition plate (3) on a plane perpendicular to the central axis of the circular tube (2) are recorded as h, so that the h satisfies the following conditions: h is more than or equal to 0 and less than or equal to 0.6 multiplied by D.
2. A heat exchange tube for use in a shell-and-tube heat exchanger according to claim 1, wherein the distance q1 between the contact line between the front partition (1) and the round tube (2) and the plane passing through the central axis of the round tube (2) and parallel to the incoming flow direction satisfies 0 ≦ q1 ≦ 0.2 xd; the distance q2 between the contact line between the rear clapboard (3) and the round tube (2) and the plane which passes through the central axis of the round tube (2) and is parallel to the incoming flow direction meets the condition that q2 is not less than 0 and not more than 0.2 xD.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611031481.8A CN106482565B (en) | 2016-11-18 | 2016-11-18 | Heat exchange tube and shell-and-tube heat exchanger adopting same |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201611031481.8A CN106482565B (en) | 2016-11-18 | 2016-11-18 | Heat exchange tube and shell-and-tube heat exchanger adopting same |
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| CN106482565A CN106482565A (en) | 2017-03-08 |
| CN106482565B true CN106482565B (en) | 2020-05-22 |
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| CN102052875B (en) * | 2010-12-16 | 2012-03-21 | 昆明理工大学 | Novel heat transfer tube for strengthening mixing of fluid at tail of tube |
| TWI550161B (en) * | 2014-07-14 | 2016-09-21 | rong-fang Huang | Eddy current elimination structure |
| CN204174521U (en) * | 2014-09-22 | 2015-02-25 | 长安大学 | Suppress the pneumatic structure of bridge column type suspension rod Vortex-excited vibration |
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| CN2336313Y (en) * | 1998-08-10 | 1999-09-01 | 深圳世能实业有限公司 | Axial finned coal saver tube |
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| CN201540055U (en) * | 2009-12-22 | 2010-08-04 | 天津市亚通制冷空调设备有限公司 | Special refrigeration evaporation pipe with Y-shaped fin |
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| CN106482565A (en) | 2017-03-08 |
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Inventor after: Yang Kun Inventor after: Wang Jiabing Inventor after: Sun Minghan Inventor after: Jiao Shuobo Inventor before: Wang Jiabing Inventor before: Sun Minghan Inventor before: Yang Kun Inventor before: Jiao Shuobo |
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