CN206235215U - A kind of recuperative heat exchanger - Google Patents
A kind of recuperative heat exchanger Download PDFInfo
- Publication number
- CN206235215U CN206235215U CN201621338792.4U CN201621338792U CN206235215U CN 206235215 U CN206235215 U CN 206235215U CN 201621338792 U CN201621338792 U CN 201621338792U CN 206235215 U CN206235215 U CN 206235215U
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- Prior art keywords
- runner
- heat exchanger
- flow channel
- cold fluid
- heat
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Abstract
A kind of recuperative heat exchanger, by section is for the hot fluid runner of rectangle and cold fluid runner is bonded to each other constitutes, along its axial direction a flow channel layer is constituted with multiple close-packed arrays before and after closed annular heat exchange runner unit form is not by changing bend, multiple such flow channel layers are radially brought into close contact nesting, make hot fluid runner and cold fluid runner axially and radially mutually interlocking, 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 good, flow turbulence degree is high, less scaling and applied widely.
Description
Technical field
The utility model is related to heat exchanger, particularly a kind of dividing wall type heat exchange being made up of multi-layer helical shape runner
Device.
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.Heat is handed on engineer applied
Parallel operation requires big heat exchange area to improve heat transfer efficiency first, at the same time it is wished that its compact conformation, volume is tried one's best diminution.It is compact
Property refer to the heat exchange area size included in heat exchanger unit volume, 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 between hot fluid and cold fluid there is a solid wall surface, two kinds of fluids are not directly contacted with, and heat is transmitted by wall.Its
In, the recuperative heat exchanger various structures shape such as including 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 smaller；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.
Utility model content
For the defect of above-mentioned prior art, the purpose of this utility model be to provide a kind of compact conformation, heat transfer area it is big,
Heat transfer efficiency and turbulivity recuperative heat exchanger high.
The recuperative heat exchanger that the utility model is provided, is the hot fluid runner and cold fluid runner phase of rectangle by section
Mutually laminating is constituted；It is characterized in, the heat exchanger is vertically with multiple not closed annular heat exchange runner unit forms by conversion
Close-packed arrays constitute a flow channel layer before and after bend, and multiple such flow channel layers are radially brought into close contact nesting, make hot fluid stream
Axially and radially mutually interlocking, hot fluid and cold fluid are axially and radially Two-Dimensional Heat for road and cold fluid runner.
The preparation method of the utility model recuperative heat exchanger is：
A cylinder first 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 heat exchange runner unit track
The outside of cylinder is welded on, as the hot fluid runner and the shared side wall of cold fluid runner 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, the interface of layer bend is changed as end, 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 of the cold fluid runner 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, thermal fluid inlet and cold fluid inlet is located at one end of outermost flow channel layer.
Compared with prior art, the utility model has the advantages that：
1st, the utility model due to cold fluid and hot fluid be Two-Dimensional Heat, its heat exchange area, compactedness, heat transfer efficiency and flowing are rapid
Mobility is increased substantially than the spiral heat exchanger of same volume.
2nd, compared with heat-exchangers of the plate type, the utility model has flow resistance small, less scaling advantage.
3rd, compared with shell-and-tube and immersion heat exchanger, the utility model compactedness is greatly improved.
4th, compared with tube-in-tube heat exchanger, the utility model compactedness is high, and metered flow is big, and the scope of application is wider.
Brief description of the drawings
Accompanying drawing is the schematic diagram of the utility model embodiment, 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 vertically；
Fig. 5 is along Fig. 4 A-A sectional drawings；
Fig. 6 is heat exchanger most inner flow passage layer cold fluid runner and hot fluid runner exit section schematic diagram.
Specific embodiment
The utility model is described further below in conjunction with drawings and Examples.
With reference to Fig. 1 and Fig. 2, the present embodiment heat exchanger is the hot fluid runner 7 and the phase of cold fluid runner 8 of rectangle by section
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 heat exchange runner units in each flow channel layer include
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 passage unit, black represents 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 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 by changing layer bend 6, (length that the heat exchanger of a diameter of 800mm changes layer bend is
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 white pattern shown in) radially can be interlaced, to realize cold fluid and hot fluid footpath
To heat transfer, by the converted bends 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 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.So come and go, radially certainly outer
R1 to R10 totally ten flow channel layers are inwardly constituted, makes 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 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 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 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 to one week, converted bend is transferred to the 2nd circumference to be continued to do circumferential operation；Run to
Runner turning area is turned through second conversion bend continue to do circumferential operation into the 3rd circumference again；So circulation, until operation
Return after to the tail end of heat exchanger, into after secondary outflow channel layer R2, heat exchanger head end is continued to run with the same fashion, such as
This reciprocal 10 times, hot fluid and cold fluid are respectively by being arranged in hot fluid outlet ports 3 of heat exchanger head end most inner flow passage layer and cold
Fluid issuing 4 flows out.What hot fluid and cold fluid in heat exchanger were 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 deflecting 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 the Antiinterference of heat exchange runner unit 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 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, the interface of layer bend is changed as end, 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, and two ends are changed into laminar flow as the inwall of flow channel layer R9
The welding fabrication simultaneously 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 fluid
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
As a example by having 20 flow channel layers, every layer of axial direction to have 32 heat exchangers of heat exchange runner unit, 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 the utility model heat exchanger is not limited to radially to have described in embodiment 10 flow channel layers, every
Layer has 8 heat exchange runner units, and the heat exchange runner unit number of its runner layer number and each flow channel layer can be increased or decreased；
The inlet and outlet of cold fluid and hot fluid is also not necessarily limited to be arranged in same one end of heat exchanger, can also be arranged in the head of heat exchanger
Tail two ends；Hot fluid runner and cold fluid runner can be exchanged；Cold fluid and hot fluid can both take following current to exchange heat, also can countercurrent flow.
These change within protection domain of the present utility model.
Claims (1)
1. a kind of recuperative heat exchanger, by section is for the hot fluid runner of rectangle and cold fluid runner 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 changing before and after bend closely
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
Axially and radially mutually interlocking, hot fluid and cold fluid are axially and radially Two-Dimensional Heat in road.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621338792.4U CN206235215U (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621338792.4U CN206235215U (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206235215U true CN206235215U (en) | 2017-06-09 |
Family
ID=58979324
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621338792.4U Withdrawn - After Issue CN206235215U (en) | 2016-12-08 | 2016-12-08 | A kind of recuperative heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206235215U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106643235A (en) * | 2016-12-08 | 2017-05-10 | 沈阳航空航天大学 | Recuperative heat exchanger and manufacturing method thereof |
| CN107421357A (en) * | 2017-08-01 | 2017-12-01 | 江西清华泰豪三波电机有限公司 | Radiator and heat dissipation equipment |
-
2016
- 2016-12-08 CN CN201621338792.4U patent/CN206235215U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106643235A (en) * | 2016-12-08 | 2017-05-10 | 沈阳航空航天大学 | Recuperative heat exchanger and manufacturing method thereof |
| CN106643235B (en) * | 2016-12-08 | 2018-07-27 | 沈阳航空航天大学 | A kind of recuperative heat exchanger and preparation method thereof |
| CN107421357A (en) * | 2017-08-01 | 2017-12-01 | 江西清华泰豪三波电机有限公司 | Radiator and heat dissipation equipment |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20170609 Effective date of abandoning: 20180727 |