CN86206722U - Single tube structure of spray heat-exchanger - Google Patents
Single tube structure of spray heat-exchanger Download PDFInfo
- Publication number
- CN86206722U CN86206722U CN 86206722 CN86206722U CN86206722U CN 86206722 U CN86206722 U CN 86206722U CN 86206722 CN86206722 CN 86206722 CN 86206722 U CN86206722 U CN 86206722U CN 86206722 U CN86206722 U CN 86206722U
- Authority
- CN
- China
- Prior art keywords
- tube
- single tube
- tube structure
- fin
- wall
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Images
Abstract
The utility model relates to the single tube structure of a spray heat-exchanger, which comprises the coaxial-arranged inner tube and outer tube. The outer tube is a corrugated tube, the inner tube is a pyramidal tube whose diameter is gradually zoomed out from the air inlet to the air outlet, the outer wall of the inner tube is provided with ribs, and the jet small holes are drilled on the ribs. The utility model can improve the heat exchange efficiency, reduce the pressure loss on the side of air, which is uneasy to deposit dust and easy to clean.
Description
The utility model relates to a kind of single tube structure of efflux heat-exchanger, can be used for the flue gas waste heat recovery of smelting and heating, forge furnace, heat-treatment furnace and other Industrial Stoves.
General tubulose efflux heat-exchanger single tube commonly used both at home and abroad at present is made up of the concentric seamless pipe of two joints, and outer tube is light pipe or weldering ribbed pipe, and interior pipe is processed with some groups of apertures.Cold air vertically sprays to outer tube wall from interior pipe aperture, and the heat of outer tube is taken away, and cold air is heated.For example, BP GB2164-438 discloses a kind of heat exchanger single tube structure, and this structure outer tube is cylindrical light pipe, and interior pipe is cylindrical, and there are many jet flow apertures on the surface.This structure is because outer tube is a light pipe, and the heat exchange area of unit volume is little, and the fume side exothermic coefficient is low, and the heat exchange effect is undesirable; Self can't solve thermal expansion and dust stratification problem.Interior pipe adopts cylindrical tube, annular channel is a uiform section between interior pipe and outer tube, along with the increase of spray orifice ejection flow, the annular channel gas flow also increases gradually, and the air-flow of rising will make the stream thigh of ejection be offset, this phenomenon is even more serious at the heat exchanger exit place, cause a part of cold air after the spray orifice ejection, directly mix, reduced air preheating temperature with preheating gas, also seriously undermined simultaneously jet flow stream burst impulsive force, influenced the heat exchange efficiency of heat exchanger wall.In addition, because jet flow stream thigh is bigger with the impact of circulation ascending fluid, energy loss, the pressure loss are all bigger.Spray orifice is the thin-walled hole, and local resistance loss is big, and it is also big that jet flow stream strand and circulation impact the mixed tensor loss, therefore, causes the air side drag losses of this heat exchanger very big, the heat exchange effect is not ideal enough.
The purpose of this utility model is intended to make improvements according to the said structure defective, and is a kind of rational in infrastructure to obtain, the air preheating temperature height, and the air side drag losses is little, is difficult for dust stratification, and deashing is easy to novel heat exchanger single tube structure.
To achieve these goals, the utility model is achieved in that efflux heat-exchanger single tube structural design is constituted for the inner and outer pipes by coaxial setting that outer tube adopts bellows, and interior pipe is a conial tube, and outer wall of inner tube is provided with fin, and spurt hole is arranged on the fin.Adopt the purpose of this structure to be, outer tube changes bellows into can make the stream thigh of pipe spray orifice ejection in the jet flow that the outer tube wall impulsive force is tending towards evenly having improved the coefficient of convective heat transfer of whole heat-transfer surface.Interior pipe adopts the taper streamline structure, has changed annular channel flow area vertically between inner and outer pipes, and its Changing Pattern meets the Changing Pattern of loop turn gas flow.Alleviated of the influence of annular channel ascending air, reduced the gas friction loss jet flow stream thigh.Outer wall of inner tube is set up equal diameter fin vertically, and the jet flow aperture is drilled on the rib central cross-section, has changed the character of spray orifice, makes original thin-walled hole, becomes ozzle shape spray orifice, the pressure loss that the local contraction of fluid produces when having overcome by the thin-walled hole.Owing to air-flow and annular channel ascending air in the spray orifice that is drilled on the fin separate, respectively walk its road, avoided interacting of two fluids substantially, reduced the energy loss and the pressure loss of jet flow stream thigh.
Corrugated outer tube of the present utility model is to be pressed into the corrugated sheet that the cross section is the near sinusoidal curve with metal sheet, it is bent into to have the cylindrical tube of encircling ripple and be welded again.The regularity of distribution by pipe spray orifice jet velocity in analyzing as can be known, jet flow stream thigh is very inhomogeneous to the VELOCITY DISTRIBUTION of stream strand border each point from its axle center, near place, axle center speed maximum, be positioned at boundary speed minimum away from the axle center, therefore, stream strand air-flow particle is also different to the impulsive force of wall, after being ejected into flat board, place, axle center speed maximum, the air-flow particle is just maximum to the impulsive force of wall, stream turbulence is just the highest, and coefficient of convective heat transfer is also maximum; And stream burst boundary jet speed is less, and the air-flow particle is also less to the impulsive force of wall, and stream turbulence weakens, and coefficient of convective heat transfer is also less.Therefore, jet flow stream thigh is uneven with the coefficient of heat transfer of wall at the whole coverage rate of stream thigh, address this problem and to make whole stream strand each air-flow particle that the impulsive force of wall is tending towards identical, the impulsive force that makes full use of stream strand each particle is broken the boundary layer, make fluid and wall obtain best coefficient of convective heat transfer, in addition, because the speed of jet flow particle is directly proportional with the jet flow distance, therefore, the outer tube shaped design is become the shape approximate with spray orifice velocity flow profile rule, the stream burst impulsive force to whole outer wall is tending towards evenly, and for the ease of processing and manufacturing, the outer tube ripple is approximate to be replaced with the Sine distribution rule.Also improved simultaneously the heat exchange area of unit volume.
The Guan Weicong air inlet arrives the diminishing heavy wall conial tube that waits of gas outlet diameter in of the present utility model, and the annular channel flow area of forming along axial inner and outer pipes is strengthened gradually, to reduce the influence of the circulation rate of climb to jet flow stream thigh.Because inner tube outer surface is streamlined, the friction loss of air-flow also decreases simultaneously.So basically, solved the elongated problem that efflux heat-exchanger is not easy to do, efflux heat-exchanger single tube length under the equal pressure loss and volume can be increased, diameter can reduce, and has dwindled the floor space and the volume of efflux heat-exchanger.
Fin of the present utility model is to be provided with to the total length equal diameter along interior tubular axis, is the radial outer wall of inner tube that is uniformly distributed in by a plurality of identical fins, and interior pipe and fin are cylinder iron to make one.Compared with prior art, the fin of the utility model setting makes that air-flow and annular channel ascending air separate in the spray orifice, take their own roads, therefore, gas between both sides of the chest can directly not influence the stream thigh in the spray orifice, thereby has guaranteed that jet flow stream thigh can vertically spray to the outer tube wall basically, has reduced the impact of jet flow stream thigh with the annular channel air-flow, reduced the energy loss and the pressure loss of jet flow stream thigh, improved the coefficient of convective heat transfer of gas outside wall surface.
In order to guarantee realization fully of the present utility model, the ejection end of the jet flow aperture on the interior pipe fin is expansion circular cone ozzle.The interior pipe spray orifice of prior art is column thin-walled hole, the local resistance of this hole, flow, flow velocity lose all bigger, and the pressure loss is relevant with the planform in aperture, the utility model changes the shape in hole into expansion conical ozzle, resistance coefficient is descended, and make speed, spray orifice distributes under certain situation, jet flow stream burst area coverage can be increased, heat-transfer surface can be effectively utilized wall.
The axis of the jet flow aperture on each fin is perpendicular to interior tubular axis line, and passes through the summit of the outside projection curve of corrugated outer tube.Because the jet flow particle velocity is big, corresponding jet flow distance also increases, and when one timing of fluid particle quality, changes the jet flow distance and just can change jet speed, just can change the impulsive force size of air-flow particle to the outer tube wall face.Adopt sinusoidal bellows, the stream burst impulsive force to outer tube wall is tending towards evenly, thereby obtains best exothermic coefficient.
Compared with prior art, the utility model is because the employing bellows is the jet flow outer tube, with ribbing conial tube is interior pipe, and the air preheating temperature of heat exchanger is improved, and the pressure loss reduces (seeing Table 1), and because the bellows shaft section is a sine curve, retractility is very strong, has solved the thermal expansion problem of heat exchanger, and owing to expand with heat and contract with cold along with variation of temperature makes pipe fitting, and make the dust stratification layer tissue of outer surface very loose, be easy to remove.Table 1 is two groups of efflux heat-exchanger single tube model machines that structural parameters are identical, is the result of performance comparison test in box type heater.
Test shows: compared with prior art, the utility model makes air preheating temperature improve 50～100 ℃, and heat exchange efficiency improves more than 10%, and the air side pressure loss reduces by 100～150 millimeters of water.
Jet pipe of the present utility model in manufacture process in pipe for cast iron, outer tube can use stainless steel, alumetized steel or straight carbon steel according to the flue gas difference.
Below in conjunction with accompanying drawing an embodiment is described:
Fig. 1 is the installation diagram of jet pipe.Be assembled by outer tube (1) and interior pipe (2), the right-hand member of pipe is an air inlet, and left end is the gas outlet.
Fig. 2 is the axial section of jet flow outer tube.Outer tube (1) is to be pressed into the corrugated sheet that the cross section is the near sinusoidal curve with metal sheet, is bent into that the garden column jecket of band ripple is welded again.
Fig. 3 is the axial section of pipe in the jet flow.Interior pipe (2) is the diminishing heavy wall conial tube that waits from air inlet to the gas outlet diameter, and its outer wall has the fin (3) of total length equal diameter setting vertically, is drilled with jet flow aperture (4) on the fin.
Fig. 4 is the A-A cross sectional view of pipe in the jet flow.Interior pipe and fin among the figure are made one, are radial by a plurality of identical fins and evenly are arranged on the outer wall of inner tube.
Claims (6)
1, a kind of efflux heat-exchanger single tube structure is made of the inner and outer pipes of coaxial setting, and interior pipe is provided with some groups of spurt holes, it is characterized in that: it is conial tube that the outer tube total length adopts bellows, interior pipe, and outer wall of inner tube is provided with axial fin, and spurt hole is arranged on the fin.
2, single tube structure according to claim 1 is characterized in that: the Guan Weicong air inlet is to the diminishing heavy wall conial tube that waits of gas outlet diameter in said.
3, single tube structure according to claim 1 is characterized in that: pipe and fin are cylinder iron to make one in said, are radial by a plurality of identical fins and evenly are arranged on the outer wall of inner tube.
4, single tube structure according to claim 1 is characterized in that: said fin is isodiametric along interior tubular axis to total length.
5, single tube structure according to claim 1 is characterized in that: the ejection end of said spurt hole is the coniform ozzle of expansion, tubular axis line in the axis normal of spurt hole.
6, single tube structure according to claim 1, it is characterized in that: the axis of spurt hole is positioned at the summit of the outside projection curve of corrugated outer tube.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86206722 CN86206722U (en) | 1986-09-06 | 1986-09-06 | Single tube structure of spray heat-exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86206722 CN86206722U (en) | 1986-09-06 | 1986-09-06 | Single tube structure of spray heat-exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN86206722U true CN86206722U (en) | 1987-09-30 |
Family
ID=4809303
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86206722 Withdrawn CN86206722U (en) | 1986-09-06 | 1986-09-06 | Single tube structure of spray heat-exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN86206722U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103206878A (en) * | 2013-05-03 | 2013-07-17 | 南京高和环境工程有限公司 | Non-phase change fluid heat exchange element for low-temperature waste heat recovery and heat exchanger |
| CN103968612A (en) * | 2014-05-14 | 2014-08-06 | 天津商业大学商业科技实业总公司 | Liquid jetting type heat exchanger of refrigerating system |
| CN110567310A (en) * | 2019-10-08 | 2019-12-13 | 广东石油化工学院 | Enhanced heat transfer method for shell-and-tube heat exchanger |
| CN115947401A (en) * | 2022-10-24 | 2023-04-11 | 福建龙净环保股份有限公司 | Evaporation treatment system for desulfurization wastewater |
-
1986
- 1986-09-06 CN CN 86206722 patent/CN86206722U/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103206878A (en) * | 2013-05-03 | 2013-07-17 | 南京高和环境工程有限公司 | Non-phase change fluid heat exchange element for low-temperature waste heat recovery and heat exchanger |
| CN103968612A (en) * | 2014-05-14 | 2014-08-06 | 天津商业大学商业科技实业总公司 | Liquid jetting type heat exchanger of refrigerating system |
| CN110567310A (en) * | 2019-10-08 | 2019-12-13 | 广东石油化工学院 | Enhanced heat transfer method for shell-and-tube heat exchanger |
| CN115947401A (en) * | 2022-10-24 | 2023-04-11 | 福建龙净环保股份有限公司 | Evaporation treatment system for desulfurization wastewater |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| GB2045913A (en) | Fluid flow arrangements | |
| WO2017111636A1 (en) | Fired heat exchanger | |
| CN201032418Y (en) | Plate type evaporative condenser | |
| CN103574632A (en) | Baffle board radiant tube burner heat exchanger and heat exchange method | |
| CN106979714A (en) | A kind of lozenge fin tube beam | |
| CN104930540B (en) | The flow-guiding structure of air preheater smoke inlet | |
| CN86206722U (en) | Single tube structure of spray heat-exchanger | |
| CN102818268A (en) | Triple-stroke air-preheating radiant tube burner heat exchanger | |
| CN213041072U (en) | Tube type heat exchanger | |
| CN214655036U (en) | High-efficient buggy preheating device | |
| CN209623472U (en) | A kind of heat exchange element | |
| CN112813211A (en) | High-efficient buggy preheating device | |
| CN208920177U (en) | A kind of new and effective heating plant | |
| CN113624038A (en) | Shell and tube heat exchanger | |
| CN202884969U (en) | Triple-travel air preheating radiant tube nozzle heat exchanger | |
| CN101832728A (en) | Heat exchange pipe | |
| CN203240927U (en) | Conical heat exchanger | |
| CN201983678U (en) | Heat exchange pipe and burner with spiral flat pipe self preheating device | |
| CN207180462U (en) | Shell-and-plate heat exchanger liquid distribution mixing arrangement | |
| CN206037815U (en) | Spiral baffling board for heat exchanger | |
| CN204730237U (en) | The flow-guiding structure of air preheater smoke inlet | |
| CN203533608U (en) | Baffle plate type radiant tube burner heat exchanger | |
| CN205299936U (en) | Gas combustion hot blast furnace | |
| CN2290016Y (en) | No-baffle varying-area channel axial flow heat exchanger | |
| CN212843113U (en) | Heat transfer pipe and boiler |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| 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 |