CN103105081B - A kind of large-scale plate-fin heat exchanger - Google Patents
A kind of large-scale plate-fin heat exchanger Download PDFInfo
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- CN103105081B CN103105081B CN201310064331.7A CN201310064331A CN103105081B CN 103105081 B CN103105081 B CN 103105081B CN 201310064331 A CN201310064331 A CN 201310064331A CN 103105081 B CN103105081 B CN 103105081B
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Abstract
A kind of large-scale plate-fin heat exchanger, include the some layer fluid passages be arranged in juxtaposition, every layer fluid passage is by fin, flow deflector, dividing plate and strip of paper used for sealing composition, described fluid passage is provided with the import and export of fluid at side opening, undertaken being connected and being communicated with by the turning channel of 90 degree between the passage of described import and export and the passage at fin place, the turning channel of described 90 degree is by dividing plate, strip of paper used for sealing and three to five sections of flow deflectors are spliced to form successively, wherein, one end of first paragraph flow deflector is positioned at import and export, the other end of first paragraph flow deflector is connected with one end of second segment flow deflector, the other end of second segment flow deflector is connected with one end of the 3rd section of flow deflector, by that analogy, the other end of final stage flow deflector is connected with fin, stop to the channel direction at fin place from the channel direction of import and export, in the turning channel of described 90 degree, after each section of flow deflector splicing, corner sum is 90 degree.The invention solves the problem that prior art medium-and-large-sized plate-fin heat exchanger volume is larger.
Description
Technical field
The present invention relates to a kind of plate-fin heat exchanger, be specifically related to a kind of large-scale plate-fin heat exchanger being applied to oil, chemical industry and energy manufacture field and using.
Background technology
Along with industry competition aggravation, the product that performance is good and light and handy more can be won the market, and equally, for large-scale plate-fin heat exchanger, only has and large-scale plate-fin heat exchanger is done little carrying out, could improve the market competitiveness.
In prior art, professional standard NB/T47006-2009(JB/T4757 see National Energy Board of China is recommended) " aluminum plate-fin type heat exchanger " Section 3.3, term and definition, heat exchanger (i.e. heat exchanger) is made up of annexes such as plate bundle, end socket, adapter and bearings, wherein plate bundle is stacked successively on demand by the passage of each fluid, and soldering is integral.Each passage is by dividing plate (or side plate), fin 1(or flow deflector), the part such as strip of paper used for sealing 2 forms (shown in accompanying drawing 1 ~ 3), every layer of passage is all provided with the import and export 6 of fluid in a particular direction.Plate-fin heat exchanger has requirement when designing to the Pressure Drop between fluid inlet and outlet, and the Pressure Drop between import and outlet is the smaller the better.Research shows, produces the factor of considerable influence and comprises following two aspects: 1, plate-fin heat exchanger comprises diversion section and straight-through part to Pressure Drop, fluid at diversion section, particularly 90 degree diversion sections of turning, comparatively greatly, Pressure Drop is larger for the pressure loss; 2, Pressure Drop is directly related with the resistance of fluid, and the resistance of fluid is relevant with the width of passage, and wide then resistance is little, narrow then resistance is large, and namely the wide then Pressure Drop of heat exchanger channels is large, and narrow then Pressure Drop is little, that is, plate-fin heat exchanger smaller volume, then Pressure Drop becomes large.Therefore, after the Pressure Drop between fluid inlet and outlet is determined, want large-scale plate-fin heat exchanger to do little, we can consider that the Pressure Drop reducing diversion section compensates the Pressure Drop increased because reducing volume.
Summary of the invention
The invention provides a kind of large-scale plate-fin heat exchanger, its objective is the problem that after will solve the Pressure Drop of the medium-and-large-sized plate-fin heat exchanger of prior art between fluid inlet and outlet determines, volume is larger.
For achieving the above object, the technical solution used in the present invention is: a kind of large-scale plate-fin heat exchanger, include the some layer fluid passages be arranged in juxtaposition, every layer fluid passage is by fin, flow deflector, dividing plate and strip of paper used for sealing composition, described fluid passage is provided with the import and export of fluid at side opening, undertaken being connected and being communicated with by the turning channel of 90 degree between the passage of described import and export and the passage at fin place, its innovation is: the turning channel of described 90 degree is by dividing plate, strip of paper used for sealing and three to five sections of flow deflectors are spliced to form successively, wherein, one end of first paragraph flow deflector is positioned at import and export, the other end of first paragraph flow deflector is connected with one end of second segment flow deflector, the other end of second segment flow deflector is connected with one end of the 3rd section of flow deflector, by that analogy, the other end of final stage flow deflector is connected with fin, from the channel direction of import and export to the channel direction at fin place only, in the turning channel of described 90 degree, after each section of flow deflector splicing, corner sum is 90 degree, wherein, the flow deflector that every section of flow deflector is adjacent is compared crank degree and is more than or equal to 10 degree and is less than or equal to 50 degree, is formed repeatedly, the turning channel of 90 degree that low-angle is turned with this.
Related content in technique scheme is explained as follows:
1, in such scheme, every layer fluid passage comprises diversion section and straight-through part, when fluid passage side opening is provided with the import and export of fluid, and the turning channel that diversion section is corresponding 90 degree, the straight-through corresponding described fin of part.
2, in such scheme, described import and export are import or exports of every layer fluid passage.
Design principle of the present invention and beneficial effect are: the universal calculation equation of local resistance loss when fluid flowing is turned:
h
r=k
r×v
2×ρ/2
Wherein: k
rfor coefficient of partial resistance; V is flowing velocity; ρ is fluid density.
Fluid can produce following loss when change flows to: fluid frontal impact tube wall and produce power loss; The turbulence loss of recirculating zone; Flow divert and the internal losses etc. when shrinking.Typical Representative is the anxious local losses turning 90 degrees elbow.Learnt by experiment, resistance coefficient k
rvalue and steering angle α, d/ ρ (d is caliber or equivalent diameter, and ρ is the radius of curvature of turning) and whether flow path channel wall smooth, coarse etc. that factor is relevant.Table 1 is k
rthe relation of value and steering angle α and stream roughness, table 2 is k
rthe relation of value and d/ ρ.
Table 1
| α | 5 | 10 | 15 | 30 | 45 | 60 | 90 |
| Light pipe k r | 0.02 | 0.03 | 0.04 | 0.13 | 0.24 | 0.47 | 1.13 |
| Extra heavy pipe k r | 0.03 | 0.04 | 0.06 | 0.17 | 0.31 | 0.58 | 1.20 |
Table 2
| d/ρ | 0.25 | 0.4 | 0.6 | 0.8 | 1.0 | 1.2 | 1.4 |
| k r | 0.131 | 0.14 | 0.16 | 0.206 | 0.294 | 0.44 | 0.66 |
As can be seen from Table 1: no matter light pipe or extra heavy pipe (extra heavy pipe refers to the pipe that flow path channel wall is coarse), after the turning of wide-angle is made into low-angle turning several times, significantly can reduce coefficient of partial resistance k
r.Such as, the light pipe elbow of 90 degree: its coefficient of partial resistance k when once having turned
r=1.13, be divided into secondary and turn each turn 45 degree, then its coefficient of partial resistance k
r=2 × 0.24=0.48, is divided into and turns each turn 30 degree for three times, then its coefficient of partial resistance k
r=3 × 0.13=0.39.Be divided into 0.425 times that each coefficient of partial resistance turning 45 degree of secondary turning is 90 degree of coefficient of partial resistances of turning, i.e. 0.48/1.13=0.425, be divided into 0.345 times that each coefficient of partial resistance turning 30 degree of turning for three times is 90 degree of coefficient of partial resistances of turning, i.e. 0.39/1.13=0.345.If be divided into secondary to have turned, and each angle turned is not etc., and as first time turns 30 degree, second time turns 60 degree, or turns 60 degree as first time, turns 30 degree for the second time, then its coefficient of partial resistance k
r=0.13+0.47=0.60, the resistance coefficient of this situation is 1.25 times of the coefficient of partial resistance of equal angular 45 degree of secondary turning situations.The angle of therefore turning is less, and its comprehensive coefficient of partial resistance is less.Equally, another problem as can be seen from Table 2: namely the ratio d/ ρ of caliber and radius of curvature when turning is less, then coefficient of partial resistance is less.Therefore, when waiting caliber, the radius of curvature of turning should be the bigger the better.
In plate-fin heat exchanger, fluid needs 90 degree of turnings to be common phenomenons.Lateral opening fluid channel structure as modal plate-fin heat exchanger is exactly typical example (shown in accompanying drawing 1 ~ 3).Accompanying drawing 1 is the typical turning structure once completing 90 degree, although flow deflector employs two pieces in this structure, not giving full play to due effect, is the version that in all version, turning resistance is maximum.To be typical fluids to have been turned 90 degree of structures of turning by secondary accompanying drawing 2, and this structure is the version of the best that secondary is turned, namely angularly turn for 45 degree, in this structure, flow deflector is made up of A type flow deflector and C type flow deflector, near the one piece of flow deflector imported and exported in A type flow deflector corresponding diagram, this flow deflector one base is the thickness of strip of paper used for sealing, and C type flow deflector is the flow deflector be connected with fin, for trapezoidal portions, namely.Accompanying drawing 3 is after fluid enters plate-fin heat exchanger, and through the allocating task just completing fluid of once turning, the effect of turning structure is between accompanying drawing 1 and accompanying drawing 2.Accompanying drawing 2 is a kind of form best in three kinds of turning structures, in order to analyze the relation between each physical dimension of this version more fully, the structure of accompanying drawing 2 is carried out refinement, shown in accompanying drawing 4: a is flow deflector inlet opens width, b is strip of paper used for sealing 2 width, Wi is plate-fin heat exchanger effective width, and ∠ p is 45 degree, and L is A type flow deflector length.As can be seen from accompanying drawing 4, every fluid secondary 45 degree of corners complete 90 degree of plate-fin heat exchangers of turning, its A type flow deflector and the size of C type flow deflector can be fixed: because a, Wi, b are known dimensions, so A type flow deflector length dimension L:L=Wi+b-a.And the size of C type flow deflector is also all known, namely three right-angle sides are respectively: Wi, a, a, then another limit is also determined.The present invention makes flow deflector comprise three to five sections of flow deflectors on prior art basis, right-angled bend is divided into three low-angles to turn, thus reduce fluid at the resistance of right angle turn, thus can the Pressure Drop between fluid inlet and outlet determine after large-scale plate-fin heat exchanger volume can be done little.
Accompanying drawing explanation
Accompanying drawing 1 is the schematic diagram of the structure one of the flow deflector of the lateral opening fluid passage of existing large-scale plate-fin heat exchanger;
Accompanying drawing 2 is the schematic diagram of the structure two of the flow deflector of the lateral opening fluid passage of existing large-scale plate-fin heat exchanger;
Accompanying drawing 3 is the schematic diagram of the structure three of the flow deflector of the lateral opening fluid passage of existing large-scale plate-fin heat exchanger;
Accompanying drawing 4 is the physical dimension figure of the flow deflector in accompanying drawing 2;
Accompanying drawing 5 is the structural representation of the flow deflector of the lateral opening fluid passage of embodiment of the present invention large-scale plate-fin heat exchanger;
Accompanying drawing 6 is the physical dimension figure of the flow deflector in accompanying drawing 5.
In above accompanying drawing: 1, fin; 2, strip of paper used for sealing; 3, first paragraph flow deflector; 4, second segment flow deflector; 5, the 3rd section of flow deflector; 6, import and export.
Detailed description of the invention
Below in conjunction with drawings and Examples, the invention will be further described:
Embodiment: a kind of large-scale plate-fin heat exchanger
Shown in accompanying drawing 5, include the some layer fluid passages be arranged in juxtaposition, every layer fluid passage is by fin 1, flow deflector, dividing plate and strip of paper used for sealing 2 form, described fluid passage is provided with the import and export 6 of fluid at side opening, undertaken being connected and being communicated with by the turning channel of 90 degree between the passage at described import and export 6 place and the passage at fin 1 place, the turning channel of described 90 degree is by dividing plate, strip of paper used for sealing 2 and three sections of flow deflectors are spliced to form successively, wherein, one end of first paragraph flow deflector 3 is positioned at import and export 6 place, the other end of first paragraph flow deflector 3 is connected with one end of second segment flow deflector 4, the other end of second segment flow deflector 4 is connected with one end of the 3rd section of flow deflector 5, the other end of the 3rd section of flow deflector 5 is connected with fin 1, channel direction from import and export 6 place to the channel direction at fin 1 place only, in the turning channel of described 90 degree, after each section of flow deflector splicing, corner sum is 90 degree, wherein, the flow deflector that every section of flow deflector is adjacent is compared crank degree and is equaled 30 degree, namely the corner of the relative first paragraph flow deflector 3 of second segment flow deflector 4 is 30 degree, the corner of the 3rd section of relative second segment flow deflector 4 of flow deflector 5 is 30 degree, and relative 3rd section of flow deflector 5 corner of fin 1 is 30 degree, with this formed three times, low-angle turn the turning channel of 90 degree.
Shown in accompanying drawing 6, the present embodiment is turned 30 degree by three times and is completed 90 degree of situations of turning: turning for three times is on the basis that accompanying drawing is turned for 4 two times, C type flow deflector fdej is divided into two again, namely the A type flow deflector that in the present embodiment first paragraph flow deflector 3 respective figure 4, secondary is turned, second segment flow deflector 4 and the 3rd section of flow deflector 5 corresponding C type flow deflector fdej two pieces of dividing, below can analyze the size of first paragraph flow deflector 3, second segment flow deflector 4 and the 3rd section of flow deflector 5:
After Wi, b, a tri-sizes are known, first light from j, make the straight line jc becoming 30 degree of angles with line segment je, then do to become the straight line intersection section jc at 30 degree of angles in m point with line segment dc from d point, and make dm=jm.Know thus: d point will try gather and obtain, object is first corner 30 degree of angles after making fluid go out A type flow deflector, the distance jm that the distance dm flowed through flows through after equaling second time corner 30 degree, and completes the flowing of fluid in flow deflector.Connect fm intersection section je in g point, the corresponding four limit type fdeg flow deflectors of described second segment flow deflector 4, described 3rd section of flow deflector 5 corresponding triangle jfg flow deflector.Below the position proving d point: connect jd, due to ∠ edh=30 °, ∠ cje=30 °, ∠ dej=90 °, is easy to obtain ∠ jmd=150 °, in triangle jdm, leg-of-mutton two limit jm=md, so ∠ mjd=∠ mdj=15 °, therefore ∠ jdc=∠ djg=45 °, then je=de=a(a is flow deflector A/F).Meanwhile, L=Wi+b-a, the length L namely in accompanying drawing 6 is identical with the length L in accompanying drawing 4.It can thus be appreciated that: the first paragraph flow deflector 3 that 30 degree of turnings are three times and the A type flow deflector of 45 degree of turning secondaries are identical, turn for three times is only that the C type flow deflector of secondary turning is divided into two pieces, and point-score is also easy to: in the C type flow deflector fdej that secondary is turned, cross the straight line jc that j point does to become with je limit 30 °, do to become the straight line of 30 degree to hand over jc line in m point with de limit after d point, connecting fm hands over je line in g point, then namely the fdeg flow deflector of triangle jfg and quadrangle is that the C type flow deflector that secondary is turned is divided into two pieces of new flow deflector sizes.Since the C type flow deflector size of 45 degree of turning secondaries is fixing, then 30 ° of turning second segment flow deflectors 4 of three times and the size of the 3rd section of flow deflector 5 also should be fixing.Obtain the size of second segment flow deflector 4 and the 3rd section of flow deflector 5 below by computational analysis: cross the vertical line mk that m point makes jf line, cross m point and make the vertical line mn friendship dj of jd line in n point.In triangle jde, jd=1.4142a, then jn=0.7071a, ∠ mjn=15 °, so jm=jn/cos15 °=0.7071a/0.9659=0.7321a, due to ∠ mjk=45 °+15 °=60 °, can obtain thus: jk=jm × cos60 °=0.5jm=0.366a, mk=0.866jm=0.866 × 0.7321a=0.634a, fk=Wi-0.366a, ∠ mfk=tg
-1° (mk/fk)=tg
-1[0.634a/ (Wi-0.366a)] °, jg=Wi × tg (∠ mfk)=Wi × (mk/fk)=Wi [0.366a/ (Wi-0.336a)], eg=a-jg=a-Wi [0.366a/ (Wi-0.336a)], to sum up, the size of second segment flow deflector 4 can be obtained: two straight flange: de=a of quadrangle fdeg; Eg=a-Wi [0.366a/ (Wi-0.336a)], the size of the 3rd section of flow deflector 5: two straight flange jf=Wi of triangle fgj; Jg=Wi [0.366a/ (Wi-0.336a)], other each limit can be drawn by trigonometric function.
Contrast accompanying drawing 4 and accompanying drawing 6 can be found out: three times of the present embodiment 30 ° of areas of flowing through C type flow deflector in accompanying drawing 4 than secondary 45 ° of turning fluids of turning just in time expand the area of triangle jdm.And the position of m point is after the opening size a of A type flow deflector determines, the position of m point is fixing, and the width dimensions of plate-fin heat exchanger has nothing to do.The short side dimension jg of the 3rd section of flow deflector 5 reduces with the increase of plate-fin heat exchanger width dimensions Wi.
From accompanying drawing 6: ∠ mfk=tg
-1° (mk/fk)=tg
-1[0.634a/ (Wi-0.366a)] °, because physical dimension a is different with Wi, larger than a more than two times of general Wi, as Wi=470mm, a=100mm.Then ∠ mfk=tg
-1(63.4/433.4)=8.3 °, therefore can find out: ∠ mfk is very little, and now ∠ dfg calculated value is 7.866 °, and these two angles are all very little.Therefore three 30 ° of second segment flow deflectors 4 of turning and the wedge angle of the 3rd section of flow deflector 5 all very sharp, to note during preservation.
Flow deflector of the present invention can also comprise the 4th section of flow deflector or/and the 5th section of flow deflector, namely four turnings or five turnings can not divided to realize 90 degree of turnings, these modes all can realize in theory, but f point place in fact in figure 6 can be difficult to accomplish, because the wedge angle of four turnings or five turnings is sharper, be all easy to damage in manufacture, preservation process.
2 in the present invention is represent the length between 2, and such as dm refers to the line segment length of dm, and dm=jm, refer to that line segment dm equals line segment jm.
Above-described embodiment, only for technical conceive of the present invention and feature are described, its object is to person skilled in the art can be understood content of the present invention and implement according to this, can not limit the scope of the invention with this.All equivalences done according to Spirit Essence of the present invention change or modify, and all should be encompassed within protection scope of the present invention.
Claims (1)
1. a large-scale plate-fin heat exchanger, include the some layer fluid passages be arranged in juxtaposition, every layer fluid passage is by fin (1), flow deflector, dividing plate and strip of paper used for sealing (2) composition, described fluid passage is provided with the import and export (6) of fluid at side opening, undertaken being connected and being communicated with by the turning channel of 90 degree between the passage at described import and export (6) place and the passage at fin (1) place, it is characterized in that: the turning channel of described 90 degree is by dividing plate, strip of paper used for sealing (2) and three to five sections of flow deflectors are spliced to form successively, wherein, one end of first paragraph flow deflector (3) is positioned at import and export (6) place, the other end of first paragraph flow deflector (3) is connected with one end of second segment flow deflector (4), the other end of second segment flow deflector (4) is connected with one end of the 3rd section of flow deflector (5), by that analogy, the other end of final stage flow deflector is connected with fin (1), channel direction to fin (1) place from importing and exporting the channel direction at (6) place is stopped, in the turning channel of described 90 degree, after each section of flow deflector splicing, corner sum is 90 degree, wherein, the flow deflector that every section of flow deflector is adjacent is compared crank degree and is more than or equal to 10 degree and is less than or equal to 50 degree, is formed repeatedly, the turning channel of 90 degree that low-angle is turned with this.
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| CN201310064331.7A CN103105081B (en) | 2013-02-28 | 2013-02-28 | A kind of large-scale plate-fin heat exchanger |
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|---|---|---|---|
| CN201310064331.7A CN103105081B (en) | 2013-02-28 | 2013-02-28 | A kind of large-scale plate-fin heat exchanger |
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| CN103105081A CN103105081A (en) | 2013-05-15 |
| CN103105081B true CN103105081B (en) | 2015-09-02 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP6599121B2 (en) * | 2015-04-13 | 2019-10-30 | 日野自動車株式会社 | Heat exchanger and waste heat recovery device |
| CN106288927A (en) * | 2016-09-21 | 2017-01-04 | 天津商业大学 | A kind of uniform distribution plate-fin heat exchanger flow deflector |
| CN108955292A (en) * | 2017-05-18 | 2018-12-07 | 江苏视野天地环保研究院有限公司 | A kind of heat exchanger core body |
| CN107289373A (en) * | 2017-07-17 | 2017-10-24 | 海南金渔创新科技有限公司 | A kind of lightweight super high power waterproof fish-luring light |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1056922C (en) * | 1996-07-24 | 2000-09-27 | 西安交通大学 | Annular flow like biphase heat exchanger |
| DE102011105968A1 (en) * | 2011-06-29 | 2013-01-03 | Airbus Operations Gmbh | Ram air channel arrangement for air conditioning apparatus of commercial airplane to cool airplane cabin, has control device placed downstream to air outlet such that control device exhibits cross section extending in direction of outlet |
| CN203163560U (en) * | 2013-02-28 | 2013-08-28 | 苏州三川换热器有限公司 | Large-scale plate-fin heat exchanger |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL1022794C2 (en) * | 2002-10-31 | 2004-09-06 | Oxycell Holding Bv | Method for manufacturing a heat exchanger, as well as heat exchanger obtained with the method. |
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2013
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1056922C (en) * | 1996-07-24 | 2000-09-27 | 西安交通大学 | Annular flow like biphase heat exchanger |
| DE102011105968A1 (en) * | 2011-06-29 | 2013-01-03 | Airbus Operations Gmbh | Ram air channel arrangement for air conditioning apparatus of commercial airplane to cool airplane cabin, has control device placed downstream to air outlet such that control device exhibits cross section extending in direction of outlet |
| CN203163560U (en) * | 2013-02-28 | 2013-08-28 | 苏州三川换热器有限公司 | Large-scale plate-fin heat exchanger |
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Address after: 215101 31 Tong Chun Road, Mu Du Town, Wuzhong District, Suzhou, Jiangsu Patentee after: Suzhou Sanchuan heat exchanger Limited by Share Ltd Address before: 215104 No. 26 Guandu Road, Yuexi Town, Wuzhong District, Suzhou, Jiangsu Patentee before: Suzhou Sanchuan Heat Exchanger Co., Ltd. |
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Granted publication date: 20150902 Termination date: 20200228 |