CN106643235A - Recuperative heat exchanger and manufacturing method thereof - Google Patents
Recuperative heat exchanger and manufacturing method thereof Download PDFInfo
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- CN106643235A CN106643235A CN201611119652.2A CN201611119652A CN106643235A CN 106643235 A CN106643235 A CN 106643235A CN 201611119652 A CN201611119652 A CN 201611119652A CN 106643235 A CN106643235 A CN 106643235A
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- layer
- heat exchanger
- hot fluid
- flow channel
- channel layer
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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 recuperative heat exchanger is composed of hot fluid flow channels and cold fluid flow channels, wherein the hot fluid flow channels and the cold fluid flow channels are attached to each other and sections of the hot fluid flow channels and the cold fluid flow channels are in rectangular shapes. The hot fluid flow channels and the cold fluid flow channels are tightly arranged front and back to form a flow channel layer in the axial direction through conversion curves in the mode of a plurality of un-closed annular heat exchanging flow channel units. Multiple flow channel layers are radially tightly attached and nested, the hot fluid flow channels and the cold fluid flow channels are mutually staggered in the axial and radial directions, and hot fluid and cold fluid axially and radially conduct two-dimensional heat transferring. The heat exchanger has the advantages that the heat exchanging area is large, the coefficient of heat exchanging is high, compactness is good, the flow turbulence degree is high, scaling is not liable to occur, and application ranges are wide.
Description
Technical field
The present invention relates to heat exchanger, particularly a kind of recuperative heat exchanger being made up of multi-layer helical shape runner and its
Preparation method.
Background technology
Heat exchanger is that the industries such as chemical industry, the energy, metallurgy, power are used to change effectively setting for fluid working substance temperature conditionss
It is standby.The heat transfer efficiency of heat exchanger is directly proportional to heat exchange area, with the turbulivity for flowing into positive correlation.To heat friendship on engineer applied
Parallel operation requires first big heat exchange area to improve heat transfer efficiency, at the same time it is wished that its compact conformation, volume diminution as far as possible.It is compact
Property refers to the heat exchange area size included in heat exchanger unit volume, and unit is 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 major types according to transmission heat mode.So-called dividing wall type is
Refer to and have a solid wall surface between hot fluid and cold flow body, two kinds of fluids are not directly contacted with, and heat is transmitted by wall.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, and it has the disadvantage that compactedness is not high, drag losses is 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 HTHP low discharge stream
The heat exchange of body, the scope of application is less；Board-like and plate fin type heat exchanger compactedness is good, and rough heat exchange is spread all in runner
Face, heat exchange area compares larger, but equally exists the larger defect of flow resistance；Spiral heat exchanger items technology refers to
Mark is relatively mild, but its heat transfer type is the same with board-like, plate-fin, is still one dimensional heat transfer, heat transfer area, heat transfer efficiency and space
Utilization rate is still not ideal enough.
The content of the invention
For the defect of above-mentioned prior art, it is an object of the invention to provide a kind of compact conformation, heat transfer area be big, heat transfer
High recuperative heat exchanger of efficiency and turbulivity and preparation method thereof.
The recuperative heat exchanger that the present invention is provided, is mutually pasted by hot fluid runner and cold fluid flow road of the section for rectangle
Close and constitute；It is characterized in, the heat exchanger is vertically with multiple not closed annular heat exchange runner unit forms by changing bend
In front and back close-packed arrays constitute a flow channel layer, and multiple such flow channel layers are radially brought into close contact nesting, make hot fluid runner and
Cold fluid flow road is axially and radially mutually interlocking, and hot fluid and cold flow body are axially and radially Two-Dimensional Heat.
The preparation method of recuperative heat exchanger of the present invention is：
First a cylinder is rolled into as the inwall of recuperative heat exchanger most inner flow passage layer with rectangle metal sheet, and
Cylinder welding is closed；Then by width for runner endoporus radial thickness banding metal sheet along the track of heat exchange runner unit
The outside of cylinder is welded on, as the shared side wall of the hot fluid runner and cold fluid flow road of most inner flow passage layer, and will be arranged on
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, roll and in coiling process while make itself and the sidewall weld, welded after the completion of rolling
Closure is connect, is changed at layer bend position in correspondence and is cut out a rectangular opening, as end the interface of layer bend is changed, complete most inner flow passage
The making of layer；Then using the outer wall of most inner flow passage layer as the inwall of second channel layer from inside to outside, by same procedure welding the
The shared side wall in the cold fluid flow road and hot fluid runner of two flow channel layers, while two ends are changed into a layer bend welding fabrication, then uses
Rectangle metal sheet completes the making of second channel layer from inside to outside as the outer wall of second channel layer from inside to outside；So follow
Ring, until completing the making of outermost flow channel layer, by thermal fluid inlet and cold fluid inlet one end of outermost flow channel layer is located at.
Compared with prior art, it is an advantage of the invention that：
1st, the present invention due to cold fluid and hot fluid be Two-Dimensional Heat, its heat exchange area, compactedness, heat transfer efficiency and flow turbulence degree
Increase substantially than the spiral heat exchanger of same volume.
2nd, compared with heat-exchangers of the plate type, the present invention is with little, the less scaling advantage of flow resistance.
3rd, compare with shell-and-tube with immersion heat exchanger, compactedness of the present invention is greatly improved.
4th, 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
Accompanying 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 for intercepting；
Fig. 3 is outermost flow channel layer to secondary outflow channel layer transition diagram；
Fig. 4 is heat exchanger head end front view vertically；
Fig. 5 is along Fig. 4 A-A sectional drawings；
Fig. 6 is heat exchanger most inner flow passage layer cold fluid flow road and hot fluid runner exit section schematic diagram.
Specific embodiment
Below in conjunction with drawings and Examples, the present invention will be further described.
With reference to Fig. 1 and Fig. 2, the present embodiment heat exchanger is by the hot fluid runner 7 and the phase of cold fluid flow road 8 that section is rectangle
Mutually laminating is (as shown in Figure 2) is constituted, along its axial direction with eight shown in Fig. 2 not closed annular heat exchange runner unit form by pair arcs
Close-packed arrays constitute a flow channel layer before and after shape conversion bend 5, before and after eight in each flow channel layer heat exchange runner unit includes
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 sequence number group in different flow channel layers the different hot fluid flow passage units of correspondence and
Cold fluid flow road unit, black represents the shared side wall in hot fluid runner and cold fluid flow road in Fig. 1).By ten this structures
Flow channel layer R1 to R10 be radially mutually brought into close contact nesting, constitute the main body of heat exchanger.With reference to Fig. 3, Fig. 4 and Fig. 5, with
As a example by outermost flow channel layer R1, the conversion regime of adjacent channels interlayer is：Last heat exchange runner unit of flow channel layer R1 is in warm
Exchanger tail end turn over about 270 ° after (heat exchanger of a diameter of 800mm changes the length of layer bend by changing layer bend 6
120mm or so) heat exchanger head end it is return, to make inside and outside flow channel layer in hot fluid runner (grains of sand figure in Fig. 3 and Fig. 5
Shown in case) and cold fluid flow road (in Fig. 3 and Fig. 5 white pattern shown in) radially can be interlaced, to realize cold fluid and hot fluid footpath
To heat transfer, by the converted bend of position Z16 and Z15 and Z13 and Z12 need to be located at when last heat exchange runner unit is return
The docking of heat exchange runner unit, centre vacates the runner dead zone 9 corresponding with Z14 positions as shown in black pattern in Fig. 3 and Fig. 5,
Then it is close to the head end of the interior wallflow to heat exchanger of outermost flow channel layer R1, constitutes time outflow channel layer R2.Flow channel layer R2 is in heat friendship
The head end of the parallel operation return tail end to heat exchanger in the same fashion, constitutes third flow channel layer R3.So come and go, radially certainly outer
R1 to R10 totally ten flow channel layers are inwardly constituted, hot fluid runner and cold fluid flow road is made 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 heat exchanger head end outermost flow channel layer (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 flow body in above-mentioned heat exchanger is as follows：
Hot fluid and cold flow body are respectively by the thermal fluid inlet 1 and cold flow body for being arranged in heat exchanger head end outermost flow channel layer
Entrance 2 is flowed 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
OK, air stream enter runner turning area is entered when running close one week, converted bend proceeds to the 2nd circumference to be continued to do circumferential operation；Run to
Again second conversion bend turning of Jing continues to do circumferential operation runner turning area into the 3rd circumference；So circulation, until operation
Return to after the tail end of heat exchanger, after entering time outflow channel layer R2, in the same fashion heat exchanger head end is continued to run with, such as
This reciprocal 10 times, hot fluid and cold flow body are respectively by hot fluid outlet ports 3 for being arranged in heat exchanger head end most inner flow passage layer and cold
Fluid issuing 4 flows out.What the hot fluid and cold flow body in heat exchanger was presented is circumferential operation, axially operation and radially operation
Superposition, wherein the direction of circumferential operation is constant from start to finish, axially operates in and changes break-in after layer.
The preparation method of the present embodiment is as follows：
First roll into a cylinder as the inwall of flow channel layer R10 with rectangle metal sheet, after welded closed by width for stream
The banding 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 flow road of layer, and by the hot fluid outlet ports 3 of the flow channel layer, the and of cold fluid outlet 4
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
The welding with the side wall is carried out simultaneously, by outer wall welded closed after the completion of rolling, and is cut at the position of layer bend 6 in corresponding changing
A rectangular opening is cut out, as end the interface of layer bend is changed, complete the making of most inner flow passage layer R10；Then with flow channel layer R10's
Outer wall welds the shared side wall of the cold fluid and hot fluid runner of flow channel layer R9 as the inwall of flow channel layer R9, and two ends are changed into laminar flow
The simultaneously welding fabrication of road 6, then the outer wall of flow channel layer R9 is made as with rectangle coiled metal, with flow channel layer R10 same ways
Complete the making of flow channel layer R9；So circulation, until the making of outermost flow channel layer R1 is completed, by thermal fluid inlet 1 and cold flow body
Entrance 2 is located at one end of outermost flow channel layer R10.
With a diameter of 800mm, axial length as 1600mm, the section of cold fluid and hot fluid runner be respectively 25mm × 15mm, footpath
To having 20 flow channel layers, per layer of axial direction to have as a example by the heat exchanger of 32 heat exchange runner units, its heat transfer effect is changed by calculating
Hot area about 72.65m2, Compact index is 91m2/m3, the nominal pressure of work is in below 2.5MPa.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, per layer have 8
The heat exchange runner unit number of individual heat exchange runner unit, its runner layer number and each flow channel layer can be increased or decreased；It is cold and hot
The inlet and outlet of fluid is also not necessarily limited to be arranged in same one 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 flow road can be exchanged；Cold fluid and hot fluid can both take following current to exchange heat, also can countercurrent flow.These
Change within protection scope of the present invention.
Claims (2)
1. a kind of recuperative heat exchanger, by section is for the hot fluid runner of rectangle and cold fluid flow road is bonded to each other constitutes；Its
It is characterised by:The heat exchanger is vertically with multiple not closed annular heat exchange runner unit forms by tight before and after conversion bend
A flow channel layer is arranged to make up, multiple such flow channel layers are radially brought into close contact nesting, make hot fluid runner and cold fluid flow
Road is axially and radially mutually interlocking, and hot fluid and cold flow body are axially and radially Two-Dimensional Heat.
2. the preparation method of recuperative heat exchanger described in claim 1, it is characterised in that：First with rectangle metal sheet as
The inwall 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 banding metal sheet of endoporus radial thickness along heat exchange runner unit Antiinterference in the outside of cylinder, as most inner flow passage layer
The shared side wall of hot fluid runner and cold fluid flow road, and the hot fluid outlet ports and cold fluid outlet of the flow channel layer will be arranged on
And layer bend welding fabrication simultaneously is changed in end；Then rolled and rolled as the outer wall of the flow channel layer with rectangle metal sheet
During make itself and the sidewall weld simultaneously, by its welded closed after the completion of rolling, changing at layer bend position in correspondence and cutting
Go out a rectangular opening, as end the interface of layer bend is changed, complete the making of most inner flow passage layer；Then with the outer wall of most inner flow passage layer
As the inwall of second channel layer from inside to outside, by same procedure the cold fluid flow road and hot fluid runner of second channel layer are welded
Shared side wall, while by layer bend welding fabrication that change at two ends, then with 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 circulation, until the making of outermost flow channel layer is completed, by heat
Fluid intake 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 true CN106643235A (en) | 2017-05-10 |
| CN106643235B 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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| Country | Link |
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| CN (1) | CN106643235B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114353556A (en) * | 2021-12-31 | 2022-04-15 | 无锡市张华医药设备有限公司 | Large-scale strip-wound spiral micro-channel heat exchanger and brazing process thereof |
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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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114353556A (en) * | 2021-12-31 | 2022-04-15 | 无锡市张华医药设备有限公司 | Large-scale strip-wound spiral micro-channel heat exchanger and brazing process thereof |
| 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 |
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| Publication number | Publication date |
|---|---|
| CN106643235B (en) | 2018-07-27 |
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