CN106643235B - A kind of recuperative heat exchanger and preparation method thereof - Google Patents
A kind of recuperative heat exchanger and preparation method thereof Download PDFInfo
- Publication number
- CN106643235B CN106643235B CN201611119652.2A CN201611119652A CN106643235B CN 106643235 B CN106643235 B CN 106643235B CN 201611119652 A CN201611119652 A CN 201611119652A CN 106643235 B CN106643235 B CN 106643235B
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- runner
- layer
- heat exchanger
- flow channel
- channel layer
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A kind of recuperative heat exchanger, it is bonded to each other and is constituted by the hot fluid runner and cold fluid runner that section is rectangle, along its axial direction a flow channel layer is constituted by close-packed arrays before and after converting bend with multiple not closed annular heat exchange runner unit forms, multiple such flow channel layers radially fit closely nesting, hot fluid runner and cold fluid runner is set axially and radially mutually to interlock, hot fluid and cold fluid axially and radially Two-Dimensional Heat.The heat exchanger has the advantages that heat exchange area is big, the coefficient of heat transfer is high, compactedness is good, flow turbulence degree is high, less scaling and applied widely.
Description
Technical field
The present invention relates to heat exchanger, especially a kind of recuperative heat exchanger being made of multi-layer helical shape runner and its
Production method.
Background technology
Heat exchanger is the industries such as chemical industry, the energy, metallurgy, power effectively setting for changing fluid working substance temperature condition
It is standby.The heat transfer efficiency of heat exchanger is directly proportional to heat exchange area, is positively correlated with the turbulivity of flowing.Heat is handed on engineer application
Parallel operation requires have big heat exchange area to improve heat transfer efficiency first, at the same time it is wished that its is compact-sized, volume reduces as possible.It is compact
Property heat exchange area size that refer in heat exchanger unit volume included, unit m2/m3。
The increase of heat exchange area needs root often with the increase of flow resistance during heat exchanger designs or type selecting
Choice is made according to actual demands of engineering heat exchanging area and flow resistance.
Heat exchanger can be divided into dividing wall type, hybrid, heat accumulating type three categories according to heat mode is transmitted.So-called dividing wall type is
Referring between hot fluid and cold fluid has a solid wall surface, two kinds of fluids to be not directly contacted with, and heat is transmitted by wall surface.Its
In, recuperative heat exchanger includes the various structures shapes such as shell-and-tube, immersion, bushing type, spiral plate type, board-like, plate-fin again
Formula.
Shell-and-tube exchanger is most widely used at present, the disadvantage is that compactedness is not high, drag losses are larger, Yi Jie
Dirt；Immersion heat exchanger compactedness is poor, and fluid turbulent degree is low；Tube-in-tube heat exchanger is suitable only for the small traffic flow of high temperature and pressure
The heat exchange of body, smaller scope of application；Board-like and plate fin type heat exchanger compactedness is good, and rough heat exchange is spread all in runner
Face, heat exchange area compare larger, but equally exist the larger defect of flow resistance；Spiral heat exchanger items technology refers to
Mark relatively mild, but its heat transfer type is with board-like, plate-fin is the same, is still one dimensional heat transfer, heat transfer area, heat transfer efficiency and space
Utilization rate is still not ideal enough.
Invention content
In view of the above-mentioned defects in the prior art, the object of the present invention is to provide a kind of compact-sized, heat transfer areas greatly, heat transfer
Efficiency and the high recuperative heat exchanger and preparation method thereof of turbulivity.
Recuperative heat exchanger provided by the invention is mutually pasted by hot fluid runner and cold fluid runner that section is rectangle
It closes and constitutes；Its main feature is that the heat exchanger is in an axial direction with multiple not closed annular heat exchange runner unit forms by converting bend
Front and back close-packed arrays constitute a flow channel layer, and multiple such flow channel layers radially fit closely nesting, make hot fluid runner and
Cold fluid runner is axially and radially mutually interlocking, and hot fluid and cold fluid are axially and radially Two-Dimensional Heat.
The production method of recuperative heat exchanger of the present invention is：
Rectangle metal sheet is first used as the inner wall of recuperative heat exchanger most inner flow passage layer, rolls into a cylinder, and
Cylinder welding is closed；Then by width be runner endoporus radial thickness band-like metal sheet along the track of heat exchange runner unit
It is welded on the outside of cylinder, the side wall shared as the hot fluid runner and cold fluid runner of most inner flow passage layer, and setting is existed
Layer bend welding fabrication simultaneously is changed in the hot fluid outlet ports and cold fluid outlet of the flow channel layer and end；Then rectangle metal sheet is used
As the outer wall of the flow channel layer, rolls and in coiling process while making itself and the sidewall weld, welded after the completion of rolling
Closure is connect, a rectangular opening is cut into corresponding change at layer bend position, the interface of layer bend is changed as end, completes most inner flow passage
The making of layer；Then using the outer wall of most inner flow passage layer as the inner wall of second channel layer from inside to outside, by same procedure welding the
The shared side wall of the cold fluid runner and hot fluid runner of two flow channel layers, while a layer bend welding fabrication is changed at both ends, then use
Outer wall of the rectangle metal sheet as second channel layer from inside to outside completes the making of second channel layer from inside to outside；So follow
Thermal fluid inlet and cold fluid inlet are located at one end of outermost flow channel layer by ring until completing the making of outermost flow channel layer.
Compared with prior art, it is an advantage of the invention that：
1, of the invention since cold fluid and hot fluid is Two-Dimensional Heat, heat exchange area, compactedness, heat transfer efficiency and flow turbulence degree
Increased substantially than the spiral heat exchanger of same volume.
2, compared with heat-exchangers of the plate type, the present invention is with small, the less scaling advantage of flow resistance.
3, compared with shell-and-tube and immersion heat exchanger, compactedness of the present invention greatly improves.
4, compared with tube-in-tube heat exchanger, compactedness of the present invention is high, and metered flow is big, and the scope of application is wider.
Description of the drawings
Attached drawing is the schematic diagram of the embodiment of the present invention, wherein：
Fig. 1 is the axonometric drawing of heat exchanger body；
Fig. 2 is the schematic diagram of the single heat exchange runner unit of interception；
Fig. 3 is outermost flow channel layer to secondary outflow channel layer transition diagram；
Fig. 4 is heat exchanger head end front view in an axial direction；
Fig. 5 is along Fig. 4 A-A cross-section diagrams；
Fig. 6 is heat exchanger most inner flow passage layer cold fluid runner and hot fluid runner exit section schematic diagram.
Specific implementation mode
Below in conjunction with drawings and examples, the present invention will be further described.
The present embodiment heat exchanger is 8 phase of hot fluid runner 7 and cold fluid runner of rectangle by section combined with Figure 1 and Figure 2,
Mutually fitting it is (as shown in Figure 2) composition, along its axial direction with eight shown in Fig. 2 not closed annular heat exchange runner unit form pass through double arcs
Close-packed arrays constitute a flow channel layer before and after shape converts bend 5, and eight heat exchange runner units in each flow channel layer include front and back
It is followed successively by Z1, Z3, Z5, Z7, Z9, Z11, Z13, Z15 and Z2, Z4, Z6, Z8, Z10, Z12, Z14, Z16 totally ten six hot and cold stream
Body flow passage unit (wherein odd indexed group and even number serial number group corresponded in different flow channel layers different hot fluid flow passage units and
Cold fluid flow passage unit, black indicates hot fluid runner and the shared side wall of cold fluid runner in Fig. 1).By ten this structures
Flow channel layer R1 to R10 radially mutually fit closely nesting, constitute the main body of heat exchanger.In conjunction with Fig. 3, Fig. 4 and Fig. 5, with
For outermost flow channel layer R1, the conversion regime of adjacent channels interlayer is：The last one heat exchange runner unit of flow channel layer R1 is in warm
By changing layer bend 6, (length that the heat exchanger of a diameter of 800mm changes layer bend is after exchanger tail end turns over about 270 °
120mm or so) heat exchanger head end it is return, to make the hot fluid runner (grains of sand figure in Fig. 3 and Fig. 5 in inside and outside flow channel layer
Shown in case) and cold fluid runner (in Fig. 3 and Fig. 5 shown in white pattern) it is radial can be interlaced, to realize cold fluid and hot fluid diameter
To heat transfer, by the converted bend of position Z16 and Z15 and Z13 and Z12 need to be located at when the last one heat exchange runner unit is return
The docking of heat exchange runner unit, centre vacates runner corresponding with the positions the Z14 dead zone 9 as shown in black pattern in Fig. 3 and Fig. 5,
Then it is close to the interior wallflow of outermost flow channel layer R1 to the head end of heat exchanger, constitutes time outflow channel layer R2.Flow channel layer R2 is handed in heat
The head end of the parallel operation return tail end to heat exchanger in the same fashion constitutes third flow channel layer R3.It is so round-trip, radial from outer
R1 to R10 totally ten flow channel layers are inwardly constituted, make hot fluid runner and cold fluid runner axially and radially in mutual shown in Fig. 5
Interleaved state realizes cold fluid and hot fluid in axially and radially Two-Dimensional Heat.The thermal fluid inlet 1 and cold fluid inlet 2 of heat exchanger
It is arranged in the outermost flow channel layer of heat exchanger head end (as shown in Figure 1 and Figure 4)；Hot fluid outlet ports 3 and cold fluid outlet 4 are arranged in heat
Exchanger head end most inner flow passage layer (as shown in figures 1 to 6).
The operation of hot fluid and cold fluid in above-mentioned heat exchanger is as follows：
Hot fluid and cold fluid are respectively by being arranged in the thermal fluid inlet 1 and cold fluid of the outermost flow channel layer of heat exchanger head end
Entrance 2 flows into, and in outermost flow channel layer R1, cold fluid and hot fluid is the circumferential fortune for doing circumferential fashion in the non-conversion racetrack portion of runner
Row, operation continue to do circumferential operation close to, into air stream enter runner turning area, converted bend is transferred to the 2nd circumference at one week；It runs to
Runner turning area continues to do circumferential operation through second conversion bend turning into the 3rd circumference again；So cycle, until operation
Return after to the tail end of heat exchanger, into after secondary outflow channel layer R2, heat exchanger head end continues to run in the same fashion, such as
This reciprocal 10 times, hot fluid and cold fluid are respectively by being arranged in the hot fluid outlet ports 3 of heat exchanger head end most inner flow passage layer and cold
Fluid outlet 4 flows out.The circumferential operation of hot fluid and cold fluid presentation in heat exchanger axially runs and radially runs
Superposition, wherein the direction circumferentially run is constant from beginning to end, axially operates in deflecting after changing layer.
The production method of the present embodiment is as follows：
The inner wall for first using rectangle metal sheet as flow channel layer R10 rolls into a cylinder, by width is stream after welded closed
The band-like metal sheet of road endoporus radial thickness along heat exchange runner unit Antiinterference in the outside of cylinder, as most inner flow passage
The shared side wall of the hot fluid runner and cold fluid runner of layer, and by the hot fluid outlet ports of the flow channel layer 3,4 and of cold fluid outlet
The welding fabrication simultaneously of layer bend 6 is changed in end, the outer wall of the flow channel layer is then made as with rectangle coiled metal, in coiling process
It is carried out at the same time the welding with the side wall, by outer wall welded closed after the completion of rolling, and is cut at the corresponding position for changing layer bend 6
A rectangular opening is cut out, the interface of layer bend is changed as end, completes the making of most inner flow passage layer R10；Then with flow channel layer R10's
Inner wall of the outer wall as flow channel layer R9 welds the shared side wall of the cold fluid and hot fluid runner of flow channel layer R9, and laminar flow is changed at both ends
The welding fabrication simultaneously of road 6, then be made as with rectangle coiled metal the outer wall of flow channel layer R9, with flow channel layer R10 same ways
Complete the making of flow channel layer R9；So cycle, until the making of outermost flow channel layer R1 is completed, by thermal fluid inlet 1 and cold fluid
Entrance 2 is located at one end of outermost flow channel layer R10.
Section with a diameter of 800mm, axial length 1600mm, cold fluid and hot fluid runner is respectively 25mm × 15mm, diameter
To for having 20 flow channel layers, every layer of axial direction to have the heat exchanger of 32 heat exchange runner units, heat transfer effect is changed by calculating
Hot area about 72.65m2, Compact index 91m2/m3, the nominal pressure of work is in 2.5MPa or less.Wherein compactedness is far high
In shell-and-tube exchanger；Heat exchange area, compactedness and flow turbulence degree are superior to the spiral shell of identical flow resistance and same volume
Plate turning type heat exchanger.Its scope of application is close with spiral heat exchanger, compactedness between spiral heat exchanger and
Between heat-exchangers of the plate type.
It should be noted that present heat exchanger be not limited to radially to have described in embodiment 10 flow channel layers, every layer have 8
The heat exchange runner unit number of a heat exchange runner unit, runner layer number and each flow channel layer can increase or decrease；It is cold and hot
The inlet and outlet of fluid is also not necessarily limited to be arranged in the same end of heat exchanger, can also be arranged in the head and the tail two of heat exchanger
End；Hot fluid runner and cold fluid runner can be interchanged；Cold fluid and hot fluid can both take downstream heat transfer, also can countercurrent flow.These
Change within protection scope of the present invention.
Claims (2)
1. a kind of recuperative heat exchanger is bonded to each other and is constituted by the hot fluid runner and cold fluid runner that section is rectangle；Its
It is characterized in that:The heat exchanger is passed through with multiple not closed annular heat exchange runner unit forms close before and after conversion bend in an axial direction
It is arranged to make up a flow channel layer, multiple such flow channel layers radially fit closely nesting, make hot fluid runner and cold fluid flow
Road is axially and radially mutually interlocking, and hot fluid and cold fluid are axially and radially Two-Dimensional Heat.
2. the production method of recuperative heat exchanger described in claim 1, it is characterised in that：First use rectangle metal sheet between
The inner wall of wall type heat exchanger most inner flow passage layer, rolls into a cylinder, and cylinder welding is closed；Then it is runner by width
The band-like metal sheet of endoporus radial thickness along heat exchange runner unit Antiinterference in the outside of cylinder, as most inner flow passage layer
Hot fluid runner and the shared side wall of cold fluid runner, and hot fluid outlet ports and cold fluid outlet in the flow channel layer will be set
And layer bend welding fabrication simultaneously is changed in end；Then rectangle metal sheet is used as the outer wall of the flow channel layer, rolls and is being rolled
Make itself and the sidewall weld simultaneously in the process, by its welded closed after the completion of rolling, is cut in corresponding change at layer bend position
Go out a rectangular opening, the interface of layer bend is changed as end, completes the making of most inner flow passage layer；Then with the outer wall of most inner flow passage layer
As the inner wall of second channel layer from inside to outside, the cold fluid runner and hot fluid runner of second channel layer are welded by same procedure
Shared side wall, while a layer bend welding fabrication is changed at both ends, then use rectangle metal sheet as second flow channel from inside to outside
The outer wall of layer completes the making of second channel layer from inside to outside；So cycle, until the making of outermost flow channel layer is completed, it will be hot
Fluid inlet and cold fluid inlet are located at one end of outermost flow channel layer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611119652.2A CN106643235B (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger and preparation method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611119652.2A CN106643235B (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger and preparation method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106643235A CN106643235A (en) | 2017-05-10 |
| CN106643235B true CN106643235B (en) | 2018-07-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611119652.2A Expired - Fee Related CN106643235B (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger and preparation method thereof |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114353556B (en) * | 2021-12-31 | 2024-03-01 | 无锡市张华医药设备有限公司 | Large-scale belt-wound spiral micro-channel heat exchanger and brazing process thereof |
Citations (7)
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|---|---|---|---|---|
| US4391616A (en) * | 1980-07-24 | 1983-07-05 | Toyo Boseki Kabushiki Kaisha | Method of dehumidification |
| CN85102624A (en) * | 1985-04-01 | 1986-09-03 | 张力中 | Reverse spiral energy-saving heat exchanger heat treatment method and practical |
| JP2001174096A (en) * | 1999-12-16 | 2001-06-29 | Smc Corp | Heat exchanger for temperature regulator |
| CN101122632A (en) * | 2006-08-07 | 2008-02-13 | 西门子公司 | Gradient coil system and magnetic resonance chromatography X-ray camera |
| CN102322752A (en) * | 2011-08-01 | 2012-01-18 | 西安交通大学 | Heat exchanger |
| CN102840777A (en) * | 2012-08-01 | 2012-12-26 | 北京丰凯换热器有限责任公司 | Aluminum plate-fin type annular heat radiator with radially flowing fluid |
| CN206235215U (en) * | 2016-12-08 | 2017-06-09 | 沈阳航空航天大学 | A kind of recuperative heat exchanger |
-
2016
- 2016-12-08 CN CN201611119652.2A patent/CN106643235B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4391616A (en) * | 1980-07-24 | 1983-07-05 | Toyo Boseki Kabushiki Kaisha | Method of dehumidification |
| CN85102624A (en) * | 1985-04-01 | 1986-09-03 | 张力中 | Reverse spiral energy-saving heat exchanger heat treatment method and practical |
| JP2001174096A (en) * | 1999-12-16 | 2001-06-29 | Smc Corp | Heat exchanger for temperature regulator |
| CN101122632A (en) * | 2006-08-07 | 2008-02-13 | 西门子公司 | Gradient coil system and magnetic resonance chromatography X-ray camera |
| CN102322752A (en) * | 2011-08-01 | 2012-01-18 | 西安交通大学 | Heat exchanger |
| CN102840777A (en) * | 2012-08-01 | 2012-12-26 | 北京丰凯换热器有限责任公司 | Aluminum plate-fin type annular heat radiator with radially flowing fluid |
| CN206235215U (en) * | 2016-12-08 | 2017-06-09 | 沈阳航空航天大学 | A kind of recuperative heat exchanger |
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| CN106643235A (en) | 2017-05-10 |
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Granted publication date: 20180727 Termination date: 20181208 |