CN100498180C - Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method - Google Patents
Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method Download PDFInfo
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- CN100498180C CN100498180C CNB2007100291187A CN200710029118A CN100498180C CN 100498180 C CN100498180 C CN 100498180C CN B2007100291187 A CNB2007100291187 A CN B2007100291187A CN 200710029118 A CN200710029118 A CN 200710029118A CN 100498180 C CN100498180 C CN 100498180C
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- tube bundle
- heat exchanger
- rectangular tube
- heat
- spinning disk
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Abstract
The invention discloses a rectangle tube bundle heat-exchanger supported by the vortex sheet and a strengthening heat-transfer method. The heat-exchanger comprises the following parts: a barrel body, a plurality of rectangle tube bundles, a tube plate, an up and down sub, a shell pass of the heat-exchanger, an in-out interface of the shell pass, wherein the tube inside of the rectangle tube bundle is equipped with the vortex sheets at uniform interval along the axial and transverse, the direction of the vortex sheet central line and the direction of the rectangle tube bundle central line is same, the rotating direction of the adjacent vortex sheet is different, the intertube in the rectangle tube bundle is equipped with the vortex sheets at uniform interval along the axial and transverse. The strengthening heat-transfer method improves the flowing speed of the heat-transfer boundary layer in dependence on the helical flow and the self vortex, which strengthens the convective heat transfer of the fluid. The vortex sheet provides the effective support and fixation function at the plate spacing for the rectangle tube bundle, which strengthens the heat-transfer of the rectangle tube bundle. The heat-changer can be used widely in the industry air heat-transfer.
Description
Technical field
The present invention relates to heat exchanger, particularly a kind of rectangular tube bundle heat exchanger that adopts spinning disk to support.The invention still further relates to described heat exchanger and realize the method for augmentation of heat transfer.
Background technology
Have now at industry-wide all kinds of shell-and-tube heat exchangers, support the shell-and-tube heat exchanger of normal optical slip pipe bundle as traditional segmental baffle, adopt the augmentation of heat transfer shell-and-tube heat exchanger (Chinese patent: ZL200420015378.0 and ZL200420088741.1) of cavity ring web plate and eddy flow web plate support convergent-divergent tube bank etc., multiple plate type heat exchanger is also arranged, as dull and stereotyped plate type heat exchanger and corrugated plating plate type heat exchanger etc.
The advantage of shell-and-tube heat exchanger is that mechanical seal is good, the bearing capacity height, sealing between cold and hot two side runners of tube side and shell side has only welding or the expanded joint sealing between the tube-to-tube sheet connection of tube bank two ends, therefore can be applied to the heat exchange occasion of many high temperature and high pressure, and the heat-transfer pipe flow area of tube side and shell side is bigger, be difficult for being stopped up by dirt, be convenient to cleaning, the flow resistance of fluid is lower, the operation energy consumption of heat exchanger is less, but shortcoming is the pipe thickness big (1～4mm) of heat-transfer pipe, the consumption of the metal material of heat exchanger is more under the condition of certain heat exchange area, the advantage of plate type heat exchanger is that heat exchange area is bigger in the unit heat exchanger volume, the heat exchanger compactness, (0.2～0.8mm) as heat exchange element can to adopt the thin-wall metal plate, the consumption of metal material is far below shell-and-tube heat exchanger under the condition of identical heat exchange area, but shortcoming is that the mechanical seal difficulty of heat exchanger is big, seal length between cold and hot two side runners comprises the surrounding of every heat exchanger plates face in cold and hot both sides, amount to the sealing on 8 borders, need the border of sealing oversize, admittedly being easy to generate fluid leaks, the heat exchange occasion that should not be used for high temperature and high pressure, and need to rely on the fin of plate to support between the plate of plate type heat exchanger, distance between plates is less, fluid flow resistance is bigger, causes dirt to stop up easily, and the operation energy consumption of heat exchanger is bigger, the heat exchanger runner is not easy cleaning, therefore common plate type heat exchanger can not be applicable to high temperature, low-density, the flue gas of enormousness flow and the heat exchange between the flue gas.
Summary of the invention
It is bigger for the consumption of shell-and-tube heat exchanger metal material to the objective of the invention is to overcome existing heat exchanger technology, and plate type heat exchanger leaks easily, and the shortcoming that operation energy consumption is higher, a kind of high temperature that is applicable to is provided, low-density, the rectangular tube bundle heat exchanger that the employing spinning disk of heat exchange between enormousness flow flue gas and the flue gas supports.
The present invention also aims to provide described heat exchanger to realize the method for augmentation of heat transfer.
As Fig. 1, shown in Figure 2, the rectangular tube bundle heat exchanger that employing spinning disk of the present invention supports, comprise cylindrical shell 5, place in the cylindrical shell 5 and along drum shaft to several width rectangular tube bundle 4 of differing and being parallel to each other, place the tube sheet 2 at rectangular tube bundle 4 two ends, the last low head 1 that links to each other with two ends tube sheet 2,9 and the inlet and outlet connectors 10 of heat exchanger tube side and shell side, 12,3,11, the inlet and outlet connectors 10 of tube side, 12 with last low head 1,9 connect, the inlet and outlet connectors 3 of shell side, 11 are connected with cylindrical shell 5, in the pipe of rectangular tube bundle 4 vertically with laterally roughly evenly at interval split spinning disk 8, the center line of spinning disk 8 is consistent with the centerline direction of rectangular tube bundle 4, the rotation direction of adjacent spinning disk 8 is opposite, between the tube and tube of rectangular tube bundle 4 also vertically with laterally roughly evenly at interval split spinning disk 8.
Preferred version: described spinning disk 8 is at the short twisted strip of sheet, preferred 180～360 degree of torsional angle, and the rate of turning round (is turned round rate: be 1.5～10 the ratio of slip length and slip width when the spinning disk Rotate 180 is spent).
Spinning disk 8 in the pipe contacts with two inwalls of rectangular tube bundle 4, and the spinning disk 8 between the tube and tube contacts with the outer wall of adjacent rectangular tube bundle 4.
Described spinning disk 8 connects and composes one group of group horizontal cyclone sheet group with thin band steel 7 between laterally, fix with some positioning tie bars 6 in same horizontal cyclone sheet group on axial.
Described rectangular tube bundle 4 constitutes certain distance between plates of being separated by between two plates by the parallel-plate face of two both sides sealings; The parallel-plate face is the plate face of smooth plate face or the concavo-convex rough rib face of band periodicity, broken line finned surface that described concavo-convex rough rib face is a convergent-divergent shape or corrugated curve finned surface, and the roughness height of finned surface is 1%～20% of a rectangular tube distance between plates, as Fig. 5, shown in Figure 6.
Preferred 10mm～the 100mm of the spacing of described rectangular tube bundle 4, described spinning disk 8 is the spacing of 1.2～12 times of rectangular tube bundles 4 in horizontal spacing, is the spacing of 3～60 times of rectangular tube bundles 4 in axial spacing.
The direction of the inlet and outlet connectors 10,12 of described heat exchanger tube side can be connected with last low head 1,9 in 0～360 degree horizontal direction, and the inlet and outlet connectors 3,11 of shell side is connected with cylindrical shell in the horizontal direction.
Use rectangular tube bundle heat exchanger that employing spinning disk of the present invention supports and realize the method for augmentation of heat transfer: fluid is every during through one group of horizontal cyclone sheet group in the pipe of rectangular tube bundle 4 and between pipe, form some parallel and separate spiral flows, afterwards, spiral flow relies on the motional inertia of fluid self to keep spin current and decay gradually in the spacing of two groups of horizontal cyclone sheets, when fluid is organized horizontal cyclone sheet through next, form spiral flow again again, the fluid streamwise repeats the process of described spiral flow and spin current, fluid spiral flow and spin current make fluid improve in the flowing velocity of heat transfer boundary layer, convection heat transfer' heat-transfer by convection that can the efficient hardening fluid, because fluid is very little in the flow resistance in spin current zone, so only need pay the cost of less resistance, just can obtain the raising of big heat transfer property.
The present invention compared with prior art has following advantage and effect: metallic plate (thickness 0.2～0.8mm) the making rectangular tube bundle 4 that can adopt thin-walled, can overcome shell-and-tube heat exchanger heat-transfer pipe thickness of pipe wall like this, the many shortcomings of metal material consumption, because rectangular tube bundle 4 has only an axial weld seam, the two ends of rectangular tube bundle 4 are connected with tube sheet 2, therefore being equivalent to every heat transfer plate face has only 3 peripheries to need sealing in cold and hot both sides, being less than every heat transfer plate face of plate type heat exchanger far away has 8 peripheries to need sealing in cold and hot both sides, thereby can significantly reduce the length of seal perimeter, improve the reliability of sealing.In addition, the distance between plates of rectangular tube bundle 4 can be at a distance of bigger, adopt spinning disk 8 as supporting between plate, spinning disk 8 can be played a supporting role in the pipe of rectangular tube bundle 4 and between pipe on the one hand, avoid rectangular tube bundle 4 compressive deformation when inside and outside both sides fluid pressure does not wait, can make fluid produce spiral flow and spin current on the other hand, strengthen in the rectangular tube beam tube and the heat transfer of the fluid convection between pipe, and because fluid is very little in the flow resistance in spin current zone, so only need pay the cost of less resistance, just can obtain the raising of big heat transfer property, it is big to overcome the plate type heat exchanger fluid resistance, the shortcoming that operation energy consumption is high, the distance between plates of rectangular tube bundle 4 is bigger simultaneously, and channel design is simple, is not easy to be stopped up by dirt, be convenient to cleaning, this all is better than plate type heat exchanger.Because possess above advantage, the rectangular tube bundle heat exchanger that adopts spinning disk to support is more suitable in high temperature the flue gas heat exchange occasion of low-density and enormousness flow than existing shell-and-tube heat exchanger and plate type heat exchanger.
Description of drawings
Fig. 1 is the schematic top plan view of heat exchanger of the present invention;
Fig. 2 is the cross-sectional schematic of Fig. 1 along the AA line;
Fig. 3 is the front view of one group of horizontal cyclone sheet group;
Fig. 4 is the vertical view of one group of horizontal cyclone sheet group;
Fig. 5 is the schematic side view that convergent-divergent shape Rough Flat Plate constitutes rectangular tube bundle;
Fig. 6 is the schematic side view that the waveform Rough Flat Plate constitutes rectangular tube bundle;
Fig. 7 is the tube sheet schematic diagram.
Shown in the figure: 1: low head; 2: tube sheet; 3: the shell side ingress interface; 4: rectangular tube bundle; 5: cylindrical shell; 6: positioning tie bar; 7: thin band steel; 8: spinning disk; 9: upper cover; 10: the tube side ingress interface; 11: the shell side discharge coupling; 12: the tube side discharge coupling.
The specific embodiment
Fig. 1,2 show a kind of version of rectangular tube bundle heat exchanger that the present invention adopts spinning disk to support.As Fig. 1, shown in 2, the rectangular tube bundle heat exchanger that adopts spinning disk to support, comprise cylindrical shell 5, place in the cylindrical shell 5 and along drum shaft to several width rectangular tube bundle 4 of differing and being parallel to each other, place the tube sheet 2 at rectangular tube bundle 4 two ends, the last low head 1 that links to each other with two ends tube sheet 2,9 and the inlet and outlet connectors 10 of heat exchanger tube side and shell side, 12,3,11, the inlet and outlet connectors 10 of tube side, 12 with last low head 1,9 connect, the inlet and outlet connectors 3 of shell side, 11 are connected with cylindrical shell 5, in the pipe of rectangular tube bundle 4 vertically with laterally roughly evenly at interval split spinning disk 8, the center line of spinning disk 8 is consistent with the centerline direction of rectangular tube bundle 4, the rotation direction of adjacent spinning disk 8 is opposite, between the tube and tube of rectangular tube bundle 4 also vertically with laterally roughly evenly at interval split spinning disk 8.Described spinning disk 8 is at the short twisted strip of sheet, and torsional angle is 180 degree.Spinning disk 8 in the pipe contacts with two inwalls of rectangular tube bundle 4, and the spinning disk 8 between the tube and tube contacts with the outer wall of adjacent rectangular tube bundle 4.Described spinning disk 8 connects and composes one group of group horizontal cyclone sheet group with thin band steel 7 between laterally, fix with some positioning tie bars 6 in same horizontal cyclone sheet group on axial.
Described rectangular tube bundle 4 constitutes certain distance between plates of being separated by between two plates by the parallel-plate face of two both sides sealings; The parallel-plate face is the smooth plate face.
The direction of the inlet and outlet connectors 10,12 of described heat exchanger tube side can be connected with last low head 1,9 in 0～360 degree horizontal direction, and the inlet and outlet connectors 3,11 of shell side is connected with cylindrical shell in the horizontal direction.
The inlet and outlet connectors 10,12 of tube side and the pipe inner flow passage of last low head 1,9 and rectangular tube bundle 4 constitute the tube side passage of heat exchanger jointly, runner and the tube sheet 2 common shell side passages that constitute heat exchanger between the inlet and outlet connectors 3,11 of shell side and the pipe of cylindrical shell 5 and rectangular tube bundle 4.
In this example, cylindrical shell 5, low head 1 is 1700mm with the diameter of upper cover 9, wall thickness is 8mm, cylindrical shell 5 long 4000mm, low head 1 is 1100mm with the height of upper cover 9, the diameter of tube sheet 2 is 1000mm, thickness is 30mm, and the slab-thickness of rectangular tube bundle 4 is 0.5mm, and dull and stereotyped spacing is 50mm, the tube pitch of rectangular tube bundle 4 is 50mm, the rectangular tube bundle 4 that in cylindrical shell 5, differs along horizontal uniform 17 width, the length of rectangular tube bundle 4 is 4070mm, the laterally equidistant uniform spinning disk 8 of 150mm in edge in rectangular tube bundle 4 pipes and between pipe, the slip thickness of spinning disk 8 is 2mm, width is 49.5mm, and the rate of turning round is 3, and slip length is 150mm, employing thickness is 2mm, highly for the thin band steel 7 of 15mm laterally uniform spinning disk 8 be connected to one group of horizontal cyclone sheet group, settle 7 groups of horizontal cyclone sheet groups along the axially equidistant 600mm of heat exchanger, the interface diameter of heat exchanger tube side and shell side is 800mm.The consumption of the metal material of this routine heat exchanger can less 40%～50% than shell-and-tube heat exchanger, the reliability of sealing can improve 50% than plate type heat exchanger, the comparable plate type heat exchanger of fluid resistance or operation energy consumption reduces by 30%～40%, be suitable for low-density, the heat exchange occasion of the high-temperature gas of large volume flow and gas is used.
Claims (9)
1, the rectangular tube bundle heat exchanger that adopts spinning disk to support, comprise cylindrical shell (5), place in the cylindrical shell (5) and along drum shaft to several width rectangular tube bundle (4) of differing and being parallel to each other, place the tube sheet (2) at rectangular tube bundle (4) two ends, the last low head (1 that links to each other with two ends tube sheet (2), 9) and the inlet and outlet connectors (10 of heat exchanger tube side and shell side, 12,3,11), the inlet and outlet connectors (10 of tube side, 12) with last low head (1,9) connect, the inlet and outlet connectors (3 of shell side, 11) be connected with cylindrical shell (5), it is characterized in that: in the pipe of rectangular tube bundle (4) vertically with laterally roughly evenly at interval split spinning disk (8), the center line of spinning disk (8) is consistent with the centerline direction of rectangular tube bundle (4), the rotation direction of adjacent spinning disk (8) is opposite, between the tube and tube of rectangular tube bundle (4) also vertically with laterally roughly evenly at interval split spinning disk (8).
2, heat exchanger according to claim 1 is characterized in that: described spinning disk (8) is the short twisted strip of sheet.
3, heat exchanger according to claim 2 is characterized in that: the torsional angle of described spinning disk (8) is 180～360 degree, and the rate of turning round of spinning disk (8) is 1.5～10.
4, according to each described heat exchanger of claim 1 to 3, it is characterized in that: the spinning disk (8) in the pipe contacts with two inwalls of rectangular tube bundle (4), and the spinning disk between the tube and tube (8) contacts with the outer wall of adjacent rectangular tube bundle (4).
5, heat exchanger according to claim 1 is characterized in that: described spinning disk (8) connects and composes one group of group horizontal cyclone sheet group with thin band steel (7) between laterally, fixes with some positioning tie bars (6) in same horizontal cyclone sheet group on axial.
6, heat exchanger according to claim 1 is characterized in that: described rectangular tube bundle (4) constitutes certain distance between plates of being separated by between two plates by the parallel-plate face of two both sides sealings; The parallel-plate face is the plate face of smooth plate face or the concavo-convex rough rib face of band periodicity, broken line finned surface that described concavo-convex rough rib face is a convergent-divergent shape or corrugated curve finned surface, and the roughness height of finned surface is 1%～20% of a described distance between plates.
7, heat exchanger according to claim 1 is characterized in that: the spacing of described rectangular tube bundle (4) is 10mm～100mm.
8, heat exchanger according to claim 7 is characterized in that, described spinning disk (8) is the spacing of 1.2～12 times of rectangular tube bundles (4) in horizontal spacing, is the spacing of 3～60 times of rectangular tube bundles (4) in axial spacing.
9, the described heat exchanger of one of claim 1-8 is realized the method for augmentation of heat transfer, it is characterized in that, fluid is every during through one group of horizontal cyclone sheet group in the pipe of rectangular tube bundle (4) or between pipe, form some parallel and separate spiral flows, afterwards, spiral flow relies on the motional inertia of fluid self to keep spin current and decay gradually in the spacing of two groups of horizontal cyclone sheet groups, when fluid is organized horizontal cyclone sheet group through next, form spiral flow again again, the fluid streamwise repeats the process of described spiral flow and spin current, fluid spiral flow and spin current make fluid improve in the flowing velocity of heat transfer boundary layer, have strengthened the convection heat transfer' heat-transfer by convection of fluid effectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007100291187A CN100498180C (en) | 2007-07-11 | 2007-07-11 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007100291187A CN100498180C (en) | 2007-07-11 | 2007-07-11 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
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| Publication Number | Publication Date |
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| CN101086427A CN101086427A (en) | 2007-12-12 |
| CN100498180C true CN100498180C (en) | 2009-06-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2007100291187A Expired - Fee Related CN100498180C (en) | 2007-07-11 | 2007-07-11 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103075903A (en) * | 2013-01-30 | 2013-05-01 | 华南理工大学 | Rectangular converging-diverging tube bundle heat exchanger supported by wavy plates and enhanced heat transfer method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1102704A (en) * | 1993-11-10 | 1995-05-17 | 周森泉 | Rotational flow heat exchanger |
| CN1260469A (en) * | 1998-09-16 | 2000-07-19 | 中国石油化工集团公司 | Heat exchange pipe and its manufacture method and application |
| CN2739555Y (en) * | 2004-09-29 | 2005-11-09 | 华南理工大学 | Shell-and-tube heat exchange for vortex net board supporting tube bundle |
| CN2745017Y (en) * | 2004-08-27 | 2005-12-07 | 华南理工大学 | Shell and tube type coaxial dual cyclone heat-exchange apparatus |
| CN1865830A (en) * | 2006-06-07 | 2006-11-22 | 华南理工大学 | Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission |
| CN201059887Y (en) * | 2007-07-11 | 2008-05-14 | 华南理工大学 | Rectangular figure bundled tubes heat exchanger supported by rotational flow piece |
-
2007
- 2007-07-11 CN CNB2007100291187A patent/CN100498180C/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1102704A (en) * | 1993-11-10 | 1995-05-17 | 周森泉 | Rotational flow heat exchanger |
| CN1260469A (en) * | 1998-09-16 | 2000-07-19 | 中国石油化工集团公司 | Heat exchange pipe and its manufacture method and application |
| CN2745017Y (en) * | 2004-08-27 | 2005-12-07 | 华南理工大学 | Shell and tube type coaxial dual cyclone heat-exchange apparatus |
| CN2739555Y (en) * | 2004-09-29 | 2005-11-09 | 华南理工大学 | Shell-and-tube heat exchange for vortex net board supporting tube bundle |
| CN1865830A (en) * | 2006-06-07 | 2006-11-22 | 华南理工大学 | Composite reinforced heat-transmission pipe with partition spilt whirl plate and method for enhancement of thermal transmission |
| CN201059887Y (en) * | 2007-07-11 | 2008-05-14 | 华南理工大学 | Rectangular figure bundled tubes heat exchanger supported by rotational flow piece |
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| CN101086427A (en) | 2007-12-12 |
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