CN2745017Y - Shell and tube type coaxial dual cyclone heat-exchange apparatus - Google Patents
Shell and tube type coaxial dual cyclone heat-exchange apparatus Download PDFInfo
- Publication number
- CN2745017Y CN2745017Y CN 200420083360 CN200420083360U CN2745017Y CN 2745017 Y CN2745017 Y CN 2745017Y CN 200420083360 CN200420083360 CN 200420083360 CN 200420083360 U CN200420083360 U CN 200420083360U CN 2745017 Y CN2745017 Y CN 2745017Y
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- China
- Prior art keywords
- shell
- tube
- heat
- heat exchange
- coaxial dual
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Abstract
The utility model relates to a shell and tube type coaxial dual vortex heat exchange apparatus. Two ends of the shell and tube type coaxial dual vortex heat exchange apparatus are provided with fixing tube plates, and a plurality of heat exchange tube bundles are installed inside a shell body. A support center tube is also installed on the center inside the shell body. An external spiral baffle plate is installed on the outer side of the support center tube. An internal spiral baffle plate is installed inside the support center tube. A tube opening on the side of the shell body is communicated with an external vortex device. The space inside the support center tube is effectively used by the utility model. The volume of a heat exchanger is not increased, meanwhile, a heat exchange area can be effectively augmented, and the heat exchange efficiency of the heat exchanger is enhanced.
Description
(1) technical field
The utility model relates to the heat transmission equipment technical field, specifically is meant the coaxial dual eddy flow heat-exchanger rig of a kind of shell-tube type.
(2) background technology
The energy is the important substance basis of economic growth and social progress, with three big pillars of material, information formation modernized society.The energy is not only the power of the national economic development, and is the index of weighing overall national strength and living standards of the people and national civilized development degree.Industries such as oil, chemical industry, power, metallurgy, refrigeration are the pillar industries of China, also are the conventional industries of high energy consumption, and its energy consumption accounts for 40% of total energy consumption.In these high energy consumption industry, the height of heat exchanger heat-transfer performance directly affects the energy consumption level of industrial system.As the general heat transmission equipment of a class, shell and tube exchanger is used widely in industries such as oil, chemical industry, power, refrigeration, air-conditioning and electric power.In various dissimilar heat exchangers, shell and tube exchanger is simple because of making, cost is low, applicability is strong and advantage such as convenient operating maintenance is used the most general.From the structure of shell and tube exchanger, its augmentation of heat transfer comprises supporting construction between novel heat-transfer pipe and pipe.Overall structure helical baffle heat exchanger is a kind of new and effective heat transmission equipment, but because one-piece auger dividing plate shell and tube exchanger need be provided with eddy flow deflection plate centre of support pipe, make the interior useful space heat exchange area of heat-exchanger rig reduce, influenced the further performance of heat exchanger performance.
(3) summary of the invention
The utility model is exactly the defective that exists in the above-mentioned prior art in order to solve, provide a kind of shell-tube type coaxial dual eddy flow heat-exchanger rig, effectively utilized the space in the pipe of centre of support, when not increasing heat exchanger volume, can effectively increase heat exchange area, improve the heat exchange efficiency of heat exchanger.
Fig. 1 is the coaxial dual eddy flow heat-exchanger rig structural representation of shell-tube type of the present utility model, its two ends are provided with in the housing 2 of fixed tube sheet 1 some heat-exchanging tube bundles 6 are installed, centre of support pipe 3 is also installed at center in the housing 2, the centre of support is managed 3 outsides external spiral deflection plate 4 is installed, in the centre of support pipe 3 inside spin deflection plate 5 is installed, the shell-side mouth of pipe 7 is communicated with outer eddy flow device.
The utility model is particularly useful for the integral cyclone heat-exchanger rig.
When carrying out design of heat exchanger, given (designing requirement) thermic load is selected cast and pipe parameter etc. then, and is determined required heat transfer area thus earlier.Actual heat transfer area is by the number of tubes of determining the pipe parameter and two factor decisions of effective tube length, and these two factors are all closely related with spillage of material and cost.Naturally there is an optimized design problem in the middle of this, as long as but fix one of them factor, another factor has also just been decided.The number of pipe is in case determine that the required pipe number of turns of arranging is also just determined, so can determine the shell side internal diameter by given tube pitch thereupon.
The utility model compared with prior art has following advantage and beneficial effect:
1. the utility model adopts coaxial dual flow passage structure, can make shell and tube exchanger symmetrical configuration, no flow blind angle, form closely nested between tube side and the shell side, can thoroughly eliminate shell and tube exchanger because of pipe vibrations and bursting accident that unreasonable structure caused, guarantee that shell and tube evaporator is long-term, efficient, even running.
2. the utility model adopts dual eddy flow heat exchange mode, can effectively keep the structure of heat exchanger shell pass and the equilibrium that fluid distributes thereof, thoroughly eliminate because of the unbalance internal stress that causes, and then reduce the loss in head of managing outer medium significantly, provide wide space and great potential for further increasing flow velocity with the outer heat-transfer film coefficient of enhanced tube.
(4) description of drawings
Fig. 1 is the coaxial dual eddy flow heat-exchanger rig structural representation of the utility model shell-tube type.
(5) specific embodiment
Embodiment 1
Now be calculated as example, illustrate the practical application of the coaxial dual eddy flow heat-exchanger rig of shell-tube type with 60 tons of/hour solvent naphtha design of heat exchanger and heating power.
Device shown in Figure 1: adopt φ 16 * 1 low rib copper tube (spacing of fin 1.0mm, the high 1.5mm of rib) enhanced tubes, shell side is selected the helical baffle augmentation of heat transfer for use and is reduced flow resistance.The stringing mode: triangle or rhombus distribute, and walk cooling water in the pipe, and shell side leads to solvent naphtha.
1. design parameter
Heat exchange amount: Q
0=500000kcal/h=580kW
Cooling medium: running water or recirculated water
Solvent naphtha: its specific heat C
p=0.36kcal/kg * ℃, proportion ρ=.76
Import Compressed Gas temperature: 90 ℃
Outlet Compressed Gas temperature: 42 ℃
Cooling water inlet temperature: t
S1=34 ℃
Cooling water outlet temperature: t
S2=47 ℃
Cooling water flow: 44m
3/ h
2. designing and calculating
Helical baffle adopts 40 ° of helical angle structures, and block board thickness is got 5mm.Estimate unit are heat flow (in outer surface) q
0=28000W/m
2
Required outer surface heat transfer area: F
0=Q
0/ q
0=580 * 10
3/ 28000=20.7m
2
If the straight length total length of every heat exchanger tube is set at L=3000mm, behind the deduction tube plate thickness, actual heat exchange length is L=2965mm.
Required pipe sum: N=F
0/ π d
0L ≈ 116
The centre-to-centre spacing that pipe is arranged: s=1.25d
0=24mm
Package can be selected D for use with reference to the catalogue of steel pipes with straight
0δ=300 * 6 (reality can be arranged 116 and be managed).
Barrel diameter: D
0=300mm; D
i=288mm
Embodiment 2
Design and heating power with reference to embodiment 1 calculate, and we have designed 60 tons of/hour solvent naphtha heat exchangers: adopt φ 19 * 1 low rib (spacing of fin 1.0mm, the high 1.5mm of wing) intensify heat transfer pipes.Pipe range 3000mm, barrel diameter D
0=300mm.
Adopting triangle mode stringing, is recirculated cooling water in the pipe, and cooling water inlet temperature is 34 ℃, and outlet temperature is 476 ℃, cooling water flow 50m
3/ h, shell side leads to solvent naphtha.Its structure adopts coaxial dual eddy flow helical baffles structure as shown in Figure 1, pipe number: 116.
Result of the test shows, coaxial dual eddy flow helical baffles structure makes heat exchanger more steady, not only thoroughly eliminated the vibration of pipe, and the shell fluid pressure loss is minimum: reaching under the prerequisite of equal heat transfer property, the shell-side flow resistance only is 1/3 of a common shell and tube exchanger.Obviously,, then can increase substantially the flow velocity of fluid, thereby further improve the film coefficient of heat transfer of shell-side, strengthen the overall efficiency of heat exchanger at shell-side as if being design considerations with equal shell-side flow resistance.
Claims (1)
1, the coaxial dual eddy flow heat-exchanger rig of a kind of shell-tube type, it is characterized in that two ends are provided with is equipped with some heat-exchanging tube bundles (6) in the housing of fixed tube sheet (1) (2), centre of support pipe (3) is also installed at center in the housing (2), external spiral deflection plate (4) is installed in centre of support pipe (3) outside, inside spin deflection plate (5) is installed in the centre of support pipe (3), and the shell-side mouth of pipe (7) is communicated with outer eddy flow device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420083360 CN2745017Y (en) | 2004-08-27 | 2004-08-27 | Shell and tube type coaxial dual cyclone heat-exchange apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420083360 CN2745017Y (en) | 2004-08-27 | 2004-08-27 | Shell and tube type coaxial dual cyclone heat-exchange apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2745017Y true CN2745017Y (en) | 2005-12-07 |
Family
ID=35579796
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200420083360 Expired - Fee Related CN2745017Y (en) | 2004-08-27 | 2004-08-27 | Shell and tube type coaxial dual cyclone heat-exchange apparatus |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2745017Y (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100434858C (en) * | 2007-03-09 | 2008-11-19 | 西安交通大学 | Combined multi-shell spiral baffle plate shell-and-tube heat exchanger |
| CN100498180C (en) * | 2007-07-11 | 2009-06-10 | 华南理工大学 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
| CN100533037C (en) * | 2008-01-04 | 2009-08-26 | 华南理工大学 | Continuous spiral traverse baffle double shell side combined special-shaped tube bundle heat exchanger |
| US8540011B2 (en) | 2007-02-09 | 2013-09-24 | Xi'an Jiaotong University | Shell-and-tube heat exchanger with helical baffles |
| CN105258424A (en) * | 2015-11-13 | 2016-01-20 | 福建德兴节能科技有限公司 | Circulating cooling water system energy conservation method based on strengthened heat transmission |
| CN110567298A (en) * | 2019-09-23 | 2019-12-13 | 重庆邮电大学 | Nested formula spiral baffling board and heat exchanger |
-
2004
- 2004-08-27 CN CN 200420083360 patent/CN2745017Y/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8540011B2 (en) | 2007-02-09 | 2013-09-24 | Xi'an Jiaotong University | Shell-and-tube heat exchanger with helical baffles |
| CN100434858C (en) * | 2007-03-09 | 2008-11-19 | 西安交通大学 | Combined multi-shell spiral baffle plate shell-and-tube heat exchanger |
| CN100498180C (en) * | 2007-07-11 | 2009-06-10 | 华南理工大学 | Rectangular tube bundle heat exchanger adopting swirl plate support and its intensified heat-conduction method |
| CN100533037C (en) * | 2008-01-04 | 2009-08-26 | 华南理工大学 | Continuous spiral traverse baffle double shell side combined special-shaped tube bundle heat exchanger |
| CN105258424A (en) * | 2015-11-13 | 2016-01-20 | 福建德兴节能科技有限公司 | Circulating cooling water system energy conservation method based on strengthened heat transmission |
| CN110567298A (en) * | 2019-09-23 | 2019-12-13 | 重庆邮电大学 | Nested formula spiral baffling board and heat exchanger |
| CN110567298B (en) * | 2019-09-23 | 2021-03-16 | 重庆邮电大学 | Nested formula spiral baffling board and heat exchanger |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |