CN106091785A - The plate type heat exchanger that a kind of sheet structure optimizes - Google Patents
The plate type heat exchanger that a kind of sheet structure optimizes Download PDFInfo
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- CN106091785A CN106091785A CN201610411050.8A CN201610411050A CN106091785A CN 106091785 A CN106091785 A CN 106091785A CN 201610411050 A CN201610411050 A CN 201610411050A CN 106091785 A CN106091785 A CN 106091785A
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- Prior art keywords
- heat exchange
- flow
- plate
- heat exchanger
- fluid
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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
- F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F11/00—Arrangements for sealing leaky tubes and conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
- F28F21/081—Heat exchange elements made from metals or metal alloys
- F28F21/085—Heat exchange elements made from metals or metal alloys from copper or copper alloys
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/24—Arrangements for promoting turbulent flow of heat-exchange media, e.g. by plates
Abstract
The invention provides a kind of plate type heat exchanger, the flow of the heat exchanging fluid participating in heat exchange in described plate type heat exchanger is different, described plate type heat exchanger includes heat exchange plate, in the heat exchange plate that flow is little, at least one by-passing parts is set, the flow path flowing through the heat exchanging fluid of heat exchange plate is divided at least two flow manifold by described by-passing parts, by-passing parts arranges opening, making point Cheng Liudao in described heat exchange plate is cascaded structure, so that the little heat exchanging fluid of flow forms S-shaped runner on heat exchange plate, flow dividing structure is optimized design.The present invention in the case of realizing maximum heat exchange amount, the dimensionally-optimised relation of the optimal heat exchange plate summed up.
Description
Technical field
The invention belongs to field of heat exchangers, particularly relate to a kind of plate type heat exchanger, belong to the field of heat exchangers of F28D.
Background technology
Generally, the cross-sectional area of plate-type heat exchanger slab both sides cold and hot fluid passage is equal (Fig. 1 a).?
In such cases, if the flow of two kinds of fluids (referring to volume flow) is more or less the same, now the runner of same fluid can be adopted
Taking the mode of parallel connection parallel to each other, such as Fig. 1 a, now the coefficient of heat transfer of plate type heat exchanger two side liquid is more or less the same, whole heat exchange
The device coefficient of heat transfer is the highest, and so arranges it is also possible that the import and export of two kinds of fluids are all on an end plate 5, such as Fig. 1 b institute
Showing, the beneficially maintenance of disassembling of plate type heat exchanger is cleaned with plate.If but two kinds of flows differ bigger fluid and change
During heat, if two kinds of fluids all take fluid passage in parallel, then the flow velocity that there will be relatively low discharge is the lowest, thus causes lower
The coefficient of heat transfer.Therefore the usual form that low-flow fluid passage is arranged to series connection, as shown in Figure 2 a, thus cannot be by cold
Four import and export of hot fluid are provided entirely on an end plate, can only be arranged on two end plates 5,6, as shown in Figure 2 b,
All arranging fluid inlet and outlet connectors on two end plates, when heat exchanger is in connection status with pipeline, dismounting is stranded by plate type heat exchanger
Difficulty, needs two ends to dismantle, and causes maintenance inconvenience.
Summary of the invention
The present invention only changes sealing structure with same plate and realizes the hot and cold unequal need of side liquid actual internal area
Ask, and the plate type heat exchanger that these plates assemble uses the unilateral assembling form taken over, and can save the biggest installation
And maintenance cost.
To achieve these goals, technical scheme is as follows:
A kind of plate type heat exchanger, the flow of the heat exchanging fluid participating in heat exchange in described plate type heat exchanger is different, described board-like
Heat exchanger includes heat exchange plate, it is characterised in that arrange at least one by-passing parts in the heat exchange plate that flow is little, described
The flow path flowing through the heat exchanging fluid of heat exchange plate is divided at least two flow manifold by by-passing parts, and by-passing parts arranges and opens
Mouthful so that point Cheng Liudao in described heat exchange plate is cascaded structure, so that the little heat exchanging fluid of flow is at heat exchange plate
Upper formation S-shaped runner.
As preferably, heat exchange plate arranges ripple, and the height of ripple is different；On same plate, along the flowing road of fluid
Footpath, the wave height in same split channel gradually rises.
As preferably, the Opening length L1 of by-passing parts, a length of L2 of by-passing parts, flow manifold width W, then meet
Following relational expression:
L1/L=a-b*Ln (L1/W)-c* (L1/W)；
Wherein L=L1+L2；
400<L<800mm,80<L1<140mm,130<W<150mm；Ln is logarithmic function
0.17<L1/L<0.22,0.5<L1/W<1.1
0.18<a<0.21,0.014<b<0.016,0.0035<c<0.004。
As preferably, along the direction of fluid flowing, the width W of flow manifolds different on same plate constantly subtracts
Few.
Compared with prior art, plate type heat exchanger and the heat exchange plate thereof of the present invention has the advantage that
1) present invention only changes with same plate and seals structure to realize hot and cold side liquid actual internal area unequal
Demand, and the plate type heat exchanger that these plates assemble uses the unilateral assembling form taken over, and can save the biggest peace
Dress and maintenance cost.
2) present invention devises on the basis of conventional panels chip architecture and is divided into the flow process of a few part to divide plate heat exchange area
Cut seal groove, coordinate with the caulking gum pad with respective shapes, it is achieved the flow area of whole plate is divided into several little portion
Point, fluid length of flow in a plate passage become segmentation by a flow process before segmentation after multiple flow processs, from
And improve flow velocity.When facilitating plate type heat exchanger to design, flow differs heat exchange area and circulation in the case of bigger two kinds of fluid heat transfers
The coupling of area.
3) present invention passes through test of many times, obtains an optimum heat exchange plate optimum results, and is carried out by test
Checking, thus demonstrate the accuracy of result.
4) material of new heat exchange plate is developed.
5) material of new gasket seal is developed.
6) arranged by the change of channel width, improve the coefficient of heat transfer.
Accompanying drawing explanation
Fig. 1 is the prior art plate type heat exchanger schematic diagram that a runner is in parallel；
Fig. 2 is the schematic diagram of the prior art plate type heat exchanger of runner series connection；
Fig. 3 is the schematic diagram of the present invention point journey sheet structure；
Fig. 4 is the structural representation of the present invention point journey pad；
Fig. 5 is the sheet structure schematic diagram of the fluid that the flow of the present invention is big；
Fig. 6 is the structural representation of the present invention point journey plate；
Fig. 7 is the scale diagrams of point journey plate of Fig. 3.
Reference is as follows:
1 first fluid import, 2 first fluid outlets, 3 second fluid imports, 4 second fluid outlets, 5 end plates, 6 end plates, 7
Flow manifold, 8 flow seal grooves, 9 flow seal pads, 10 heat exchange plates, 11 flow manifolds, 12 flow manifolds.
Detailed description of the invention
Below in conjunction with the accompanying drawings the detailed description of the invention of the present invention is described in detail.
Herein, without specified otherwise, relating to formula, "/" represents that division, "×", " * " represent multiplication.
The heat exchange plate 10 used in a kind of plate type heat exchanger, arranges at least one distributary division in described heat exchange plate 10
Part, the flow path flowing through the heat exchanging fluid of heat exchange plate is divided at least two and divides Cheng Liudao 7 by described by-passing parts, described
A point Cheng Liudao 7 in heat exchange plate 10 is cascaded structure.Cascaded structure by above-mentioned point Cheng Liudao 7 so that fluid is therefore
Through all of point of Cheng Liudao 7, as shown in Figure 6, so that heat exchanging fluid forms S-shaped runner on heat exchange plate 10.
By arranging by-passing parts so that the fluid that flow is little can be full of whole heat exchange plate, thus avoids appearance
The heat exchange area of some fluid short, thus add the coefficient of heat transfer, improve the coefficient of heat transfer of whole heat exchanger；Additionally, it is logical
Cross and by-passing parts is set so that the fluid of low discharge also is able to realize the parallel connection of the fluid passage in multiple plates, such as Fig. 1 a
Shown in, it is to avoid in order to improve the coefficient of heat transfer, little fluid passage is set to the structure of the series connection shown in Fig. 2 a, such that it is able to
Four the import and export 1-4 making fluid are all disposed within same end plate, so that easy to maintenance.
As preferably, the volume flow of large flow fluid is more than 2 times of the volume flow of low discharge fluid.
As preferably, by-passing parts is realized by seal groove 8 and sealing gasket 9, and described seal groove 8 is arranged on heat exchanger plates
On sheet, by being inserted in seal groove 8 by sealing gasket 9, thus form by-passing parts.
As preferably, by-passing parts is to realize by directly arranging sealing strip on heat exchange plate.As preferably, seal
Bar and heat exchange plate integration manufacture.
On the fluid inlet of heat exchange plate and the two ends up and down of outlet, i.e. the two ends up and down of Fig. 3, by-passing parts is at one end
Being to close, arrange opening at the other end, wherein along left and right directions, aperture position is to be disposed alternately at upper and lower two ends,
So ensure that fluid passage forms S-shaped.
What before note that and direction up and down mentioned later was not limited in use state is upper bottom left
Right direction, is only used to state the structure of the plate in Fig. 3 herein.
Fig. 3, plate described in 6 because being provided with two by-passing parts, therefore the import and export of fluid be arranged on upper end and under
End.Can certainly arrange 1 or odd number by-passing parts, the import and export position of fluid now is located on same one end,
It is positioned at upper end or lower end the most simultaneously.
Foregoing S-shaped runner can be half S-shaped, the most only arranges the situation of a by-passing parts, it is also possible to be
Whole S-shaped, such as Fig. 3, the form of 6, it is also possible to be the combination of multiple S-shaped and/or half S-shaped, such as arrange more than 2
The situation of by-passing parts, such as 3 by-passing parts are exactly the combination of 1 one S-shaped and half S-shaped, and 4 by-passing parts are exactly 2 S
Shape, etc. by that analogy.
For using the form of sealing gasket, as preferably, the setting between sealing gasket and heat exchange plate for plate heat exchanger sheet
Pad integrated design, therefore present invention provides the pad used between heat exchange plate in plate type heat exchanger in.Institute
Stating and arrange at least one flow seal pad 9 in pad, described flow seal pad 9 will flow through the flowing of the heat exchanging fluid of heat exchange plate
Path is divided at least two and divides Cheng Liudao 7, and point Cheng Liudao 7 in described heat exchange plate 10 is cascaded structure, so that heat exchange
Fluid forms S-shaped runner on heat exchange plate 10.
In numerical simulation with it was found that, by arranging by-passing parts, it is possible to make the heat exchanger coefficient of heat transfer increase, but
It it is the increase simultaneously also bringing flow resistance.Found by numerical simulation and experiment, for the width of flow manifold, if mistake
Little, flow resistance can be caused excessive, the pressure-bearing of heat exchanger is too big, and may produce runner dual-side interlayer and flow along fluid
Direction overlaps, and causes the coefficient of heat transfer to decline, the excessive coefficient of heat transfer reducing plate type heat exchanger that also results in of width of flow path, therefore
For split channel 7, there is a suitable numerical value；Length for by-passing parts opening also has certain requirement, if opening
Too small, the quantity that fluid can be caused to be flow through by opening is too small, reduces the coefficient of heat transfer while increasing pressure, in like manner, as
The most excessive, then fluid can produce short-circuited region, does not has corresponding heat transfer effect, therefore opening is also had to a suitable length
Degree.Therefore between the Opening length of by-passing parts, the length of by-passing parts, flow manifold width, meet an optimized chi
Very little relation.
Therefore, the present invention is thousands of the numerical simulations by multiple various sizes of heat exchangers and test data,
Meet in the case of industrial requirements pressure-bearing (below 2.5MPa), in the case of realizing maximum heat exchange amount, optimal the changing summed up
The dimensionally-optimised relation of hot plate sheet.
As it is shown in fig. 7, the Opening length L1 of by-passing parts, a length of L2 of by-passing parts, flow manifold width W, then full
The following relational expression of foot:
L1/L=a-b*Ln (L1/W)-c* (L1/W)；
Wherein L=L1+L2；
400<L<800mm,80<L1<140mm,130<W<150mm；Ln is logarithmic function
0.17<L1/L<0.22,0.5<L1/W<1.1
0.18<a<0.21,0.014<b<0.016,0.0035<c<0.004。
Wherein Opening length is along by-passing parts, from the position that opening occurs along the farthest position reaching fluid passage
Put, such as the A point in Fig. 7.
As preferably, a=0.19, b=0.015, c=0.0037；
As preferably, along with being continuously increased of L1/W, the numerical value of a constantly reduces；
As preferably, along with being continuously increased of L1/W, the numerical value of b, c is continuously increased.
As preferably, the flow velocity of the fluid of split channel is 0.4-0.8m/s, it is preferable that 0.5-0.6m/s, under this flow velocity
The heat transfer effect taking above-mentioned formula to obtain is best.
Preferably, plate spacing 4-6mm of heat exchanging plate of heat exchanger, preferably 5mm.
For the form integrated with pad using sealing gasket in Fig. 4, in the case of also meeting above-mentioned formula, heat exchange is imitated
Fruit is optimum.
As preferably, multiple by-passing parts are parallel to each other.
As preferably, along the direction (i.e. the fluid intake of distance heat exchange plate is the most remote) of fluid flowing, same heat exchanger plates
The width W of flow manifolds different on sheet constantly reduces.Such as, the width of the flow manifold 7 in Fig. 3 is more than flow manifold
11, the width of flow manifold 11 is more than flow manifold 12.Constantly reduced so that fluid is continuous by flow manifold width W
Acceleration, it is to avoid because the fluid that causes of being short of power runs slowly.
As preferably, along the direction of fluid flowing, the width W of same flow manifold constantly reduces.Such as, shunting stream
In road 7, along fluid flow direction (i.e. Fig. 3 is from top to bottom), width W constantly reduces.Now, for the W in preceding formula
Use mean breadth W.
As preferably, on various heat exchange plate, distance heat exchanger fluid entrance is the most remote, and flow manifold width is the least.Mainly
Be that distance entrance is the most remote, then distribution fluid is the fewest, makes fluid ensure certain flow velocity by the change of width of flow path.
As preferably, heat exchange plate arranges ripple, and the height of ripple is different.On same plate, along the flowing road of fluid
Footpath, the wave height in same split channel gradually rises, such as in flow manifold 7, along fluid flow direction (i.e. Fig. 3
From top to bottom), wave height gradually rises.
As preferably, flow manifold distance heat exchange plate fluid intake distance is the most remote, the ripple in different flow manifolds
The highest, such as, the wave height in flow manifold 7 in Fig. 3 is less than flow manifold 11, the wave height of flow manifold 11
Less than flow manifold 12.
As preferably, on various heat exchange plate, distance heat exchanger fluid entrance is the most remote, and wave height is the highest.Mainly away from
From entrance more away from, then distribution fluid is the fewest, makes fluid ensure certain flow velocity by the change of wave height.
As preferably, heat exchange plate arranges ripple, and the density of ripple is different.On same plate, along the flowing road of fluid
Footpath, the corrugation density in same split channel becomes larger, such as in flow manifold 7, along fluid flow direction (i.e. Fig. 3
From top to bottom), corrugation density becomes larger.
As preferably, flow manifold distance heat exchange plate fluid intake distance is the most remote, the ripple in different flow manifolds
Density becomes big.Such as, the corrugation density in flow manifold 7 in Fig. 3 is less than flow manifold 11, the corrugation density of flow manifold 11
Less than flow manifold 12
As preferably, on various heat exchange plate, distance heat exchanger fluid entrance is the most remote, and corrugation density is the biggest.Mainly away from
From entrance more away from, then distribution fluid is the fewest, makes fluid ensure certain flow velocity by the change of wave height.
As preferably, the amplitude that wave height noted earlier and/or density increase is more and more less.
As preferably, described heat exchange plate uses Cu alloy material, described copper alloy by copper, ferrum, manganese, cerium, magnesium, stannum,
Silver, chromium and other auxiliary materials process, in described copper alloy percentage by weight shared by each composition be respectively as follows: copper 71.2%～
82.5%, ferrum 3.3%～4.5%, manganese 1.1%～2.5%, cerium 0.35%～0.45%, magnesium 0.77%～1.3%, stannum
0.028%～0.14%, silver 0.06%～0.09%, chromium 0.3%～0.9%, remaining as auxiliary material.
As preferably, described auxiliary material is mixed and processed by zinc chloride and Linesless charcoal.
As preferably, in described copper alloy, percentage by weight shared by each composition is respectively as follows: copper 76.3%, ferrum 4.4%, manganese
1.8%, cerium 0.5%, magnesium 1.07%, stannum 0.007%, silver 0.75%, chromium 0.6%, remaining as auxiliary material.
The processing method of above-mentioned copper alloy is as follows:
1, with intermediate frequency furnace cathode copper melted and be warming up to 1300～1400 DEG C, adding crome metal, silver insulation 33 points
Clock；
2, after pulling slag out, add remaining composition and stir.Then tapping casting, and control furnace temperature at 1340 DEG C；
3, use semi continuous casting, protect with nitrogen during casting；
4, as required foundry goods is forged or pressure processing becomes parts, then parts are heated to 900 DEG C of insulations 3 little
Time hardening, then at a temperature of 479 DEG C insulation within 2～3 hours, carry out Ageing Treatment；
The copper alloy made through above-mentioned specification has characteristic high temperature resistant, that heat conductivity is high, and substantially improves resistance
Shape ability and wearability.
As preferably, the gasket seal between sealing gasket 9 and/or heat exchange plate uses elastomeric material.Described elastomeric material
It is made up of the raw material of following parts by weight: ethylene propylene diene rubber 7-9 part, butadiene-styrene rubber 3-6 part, zinc oxide 6-8 part, white carbon 13-
15 parts, accelerator 4-5 part, foaming agent 2-8 part, naphthenic oil 5-6 part, titanium dioxide 20 parts, natural rubber 50-55 part, Rhein dissipates 10-
13 parts, silicone rubber 15-17 part, carborundum 2 parts, Melamine 2 parts, 0.6 part to 1.5 parts of age resistor, softening agent 4 parts to 6 parts, sulfur
Agent 2.2 parts to 4 parts.
As preferably, ethylene propylene diene rubber 8 parts, butadiene-styrene rubber 5 parts, zinc oxide 7 parts, white carbon 14 parts, accelerator 4 parts, send out
Infusion 4 parts, naphthenic oil 6 parts, titanium dioxide 20 parts, natural rubber 52 parts, Rhein dissipates 12 parts, 16 parts of silicone rubber, carborundum 2 parts, and three
Polynitriles amine 2 parts, 0.9 part of age resistor, softening agent 5 parts, vulcanizing agent 3 parts.
Manufacture method comprises the steps:
A. in banbury, it is sequentially added into described ethylene propylene diene rubber, butadiene-styrene rubber, zinc oxide, white carbon, accelerator, foaming
Agent, naphthenic oil, titanium dioxide, natural rubber, Rhein dissipate, silicone rubber, carborundum, Melamine and accelerator and age resistor, so
Rear startup banbury carries out the most mixing, and 70 seconds to 75 seconds time, temperature is 60 DEG C to 70 DEG C；
B. adding softening agent in the banbury of step A and carry out the most mixing, 75 seconds time, temperature is less than 105 DEG C, so
Rear cooling binder removal；
C. sulfuration: the glue of step B is discharged on tablet machine add vulcanizing agent and turns refining, second time 125-140, under
Sheet and get final product.
As preferably, accelerator is diphenylguanidine.
As preferably, described accelerator is dithiocar-bamate；Described age resistor is Tissuemat E；Described softening agent
For paraffin；Described vulcanizing agent is curing resin.
Described rubber has the advantage that 1) compounded by the material of interpolation zinc oxide, titanium dioxide, resulting materials is elastic
Good, and there is certain hardness, wear-resisting durable, the life-span is long, the most easy to wear.2) owing to using Tissuemat E as anti-aging
Agent, can improve the persistence of rubber, hardness and abrasion resistance；3) cure time is short, makes rubber be handed over by the macromole of linear structure
Be unified into the macromole for space network, its anti-tensile of the rubber of output, surely stretch, wear-resisting performance good.
The two side walls of described heat exchange plate 3 arranges anticorrosive coat.The anticorrosive coat of low-temperature receiver and/or heat source side wall is by coating
Anticorrosive paint generates, and the mass percent of anticorrosive paint component is as follows: zinc flake 6.6-8.3%, and aluminium oxide is 8-9%, boron
Acid is 7.2-9.2%, and acrylic acid is 0.7-0.9%, and wetting dispersing agent is 0.4-0.5%, and thickening agent is 0.15-0.23%, disappears
Infusion is 0.14-0.23%, the water of surplus.This kind of coating by spraying, brush, dip-coating is applied over heat exchange plate surface, 80 ±
Drying 10～60 minutes for 10 DEG C, 280 ± 40 DEG C of solidifications sinter 30～60 minutes, form good anti-corrosion coating.
The method preparing above-mentioned water-based anticorrosive paint, the method according to following steps implement,
A, by coating gross mass percentage ratio, weigh disappearing of a certain amount of water, the wetting dispersing agent of 0.4% and 0.23% respectively
Infusion, the most admixed together, it is sufficiently stirred for being allowed to dissolving and makes coating mixed liquor A 1, then addition accounts for coating in mixed liquor A 1
The flake metal powder of the 8.3% of gross mass, stirs and makes coating mixed liquor A 2；
B, by coating gross mass percentage ratio, weigh 7.3% boric acid, form mixed liquor, join in the water of 20%～40%
Fully dissolving and make mineral acid mixed liquid B 1, then add the oxidate powder of 8% in mixed liquid B 1, stirring makes nothing to without precipitation
Machine acid mixed liquid B 2；
C, by coating gross mass percentage ratio, weigh the acrylic acid of 0.7%, join in the water of 5%～15%, be sufficiently stirred for
Uniformly make reducing agent mixed liquor C；
D, by coating gross mass percentage ratio, weigh the thickening agent hydroxyethyl cellulose of 0.15%, join 2.5%～15%
Water in, stirring to dissolve be translucent shape and without gel occur i.e. stop stirring making thickening agent mixed liquor D；
E, the mineral acid mixed liquid B 2 of preparation is joined in coating mixed liquor A 2, be subsequently adding reducing agent mixed liquor C and join
The 1/5～1/2 of amount processed, adds thickening agent mixed liquor D while stirring, adds the water of surplus, continues stirring 30～90 minutes, directly
To coating mixed liquor uniformity soilless sticking granule, finally add remaining reducing agent mixed liquor C, be stirred for 10～40
Minute, to obtain final product.
This kind of coating by spraying, brush, dip-coating is applied over finned tube surface, dries 10～60 minutes for 80 ± 10 DEG C, 280
± 40 DEG C of solidifications sinter 30～60 minutes, form good anti-corrosion coating.
Described wetting dispersing agent is the SA-20 in peregal series, and described thickening agent selects hydroxyethyl cellulose；Described
Defoamer select tributyl phosphate.
A preferred embodiment, from low-temperature receiver to heat source side, low-temperature receiver anticorrosive coat, heat exchange plate and the heat of thermal source anticorrosive coat
The coefficient of expansion is sequentially reduced.Why being arranged such and be because during heat exchange, the anticorrosive coat of heat source side is first heated, the most swollen
Swollen, it is the most outwards heat exchange plate, low-temperature receiver side anticorrosive coat expanded by heating, therefore low-temperature receiver anticorrosive coat, heat exchange plate and heat
The thermal coefficient of expansion of source anticorrosive coat is sequentially reduced and can ensure that expansion rate keeps consistent substantially, it is ensured that each layer connect compactness and
Stability.So, the anticorrosive coat of low-temperature receiver and thermal source side takes anticorrosive paint noted earlier, becomes by changing anticorrosive paint
Divide thus realize the change of thermal coefficient of expansion.Other different anticorrosive paints can certainly be used to realize the change of thermal coefficient of expansion
Change.Such as only use above-mentioned anticorrosive paint in side, opposite side uses other anti-corrosion material.
Fig. 5 illustrates the flow channel of the big fluid of flow, it practice, for the present invention, two kinds of heat exchanging fluids are all
The fluid that flow is little can be used.Such as in the case of heat exchange plate is certain, the flow of two kinds of fluids is the least, now two kinds
The flow channel of fluid can take the plate of Fig. 3, Fig. 6 form.
Although the present invention discloses as above with preferred embodiment, but the present invention is not limited to this.Any art technology
Personnel, without departing from the spirit and scope of the present invention, all can make various changes or modifications, and therefore protection scope of the present invention should
When being as the criterion with claim limited range.
Claims (5)
1. a plate type heat exchanger, the flow of the heat exchanging fluid participating in heat exchange in described plate type heat exchanger is different, described board-like changes
Hot device includes heat exchange plate, arranges at least one by-passing parts in the heat exchange plate that flow is little, and described by-passing parts will stream
Being divided at least two flow manifold through the flow path of the heat exchanging fluid of heat exchange plate, by-passing parts arranges opening so that described
Heat exchange plate in a point Cheng Liudao be cascaded structure so that the little heat exchanging fluid of flow forms S-shaped stream on heat exchange plate
Road；It is characterized in that, the Opening length L1 of by-passing parts, a length of L2 of by-passing parts, flow manifold width W, then meet such as
Lower relational expression:
L1/L=a-b*Ln (L1/W)-c* (L1/W)；
Wherein L=L1+L2；
400<L<800mm,80<L1<140mm,130<W<150mm；Ln is logarithmic function
0.17<L1/L<0.22,0.5<L1/W<1.1
0.18<a<0.21,0.014<b<0.016,0.0035<c<0.004。
2. plate type heat exchanger as claimed in claim 1, it is characterised in that a=0.19, b=0.015, c=0.0037.
3. plate type heat exchanger as claimed in claim 1, it is characterised in that along with being continuously increased of L1/W, the numerical value of a constantly subtracts
Few.
4. plate type heat exchanger as claimed in claim 1, it is characterised in that along with being continuously increased of L1/W, the numerical value of b, c is continuous
Increase.
5. plate type heat exchanger as claimed in claim 1, it is characterised in that the flow velocity of the fluid of split channel is 0.4-0.8m/
S, it is preferable that 0.5-0.6m/s.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610411050.8A CN106091785B (en) | 2015-04-23 | 2015-04-23 | A kind of plate heat exchanger of sheet structure optimization |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610411050.8A CN106091785B (en) | 2015-04-23 | 2015-04-23 | A kind of plate heat exchanger of sheet structure optimization |
| CN201510200921.7A CN104792199B (en) | 2015-04-23 | 2015-04-23 | The plate type heat exchanger that a kind of heat exchanging fluid flow is different |
Related Parent Applications (1)
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| CN201610411050.8A Active CN106091785B (en) | 2015-04-23 | 2015-04-23 | A kind of plate heat exchanger of sheet structure optimization |
| CN201610404042.0A Active CN105973041B (en) | 2015-04-23 | 2015-04-23 | A kind of plate type heat exchanger of width of flow path change |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106813522A (en) * | 2017-03-24 | 2017-06-09 | 睿能太宇（沈阳）能源技术有限公司 | A kind of heat-exchangers of the plate type and its plate |
| EP3598053B1 (en) * | 2017-04-27 | 2022-05-11 | Mitsubishi Electric Corporation | Plate heat exchanger |
| CN113606967B (en) * | 2021-06-27 | 2023-04-25 | 江阴市富仁高科股份有限公司 | High-pressure micro-channel heat exchanger and manufacturing method thereof |
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| US4042018A (en) * | 1975-09-29 | 1977-08-16 | Des Champs Laboratories Incorporated | Packaging for heat exchangers |
| EP1435502B1 (en) * | 2002-12-30 | 2008-02-27 | Halla Climate Control Corporation | Laminated heat exchanger |
| CN103424024A (en) * | 2012-05-15 | 2013-12-04 | 杭州三花研究院有限公司 | Plate heat exchanger and plate thereof |
| CN103547877A (en) * | 2011-05-24 | 2014-01-29 | 皮尔伯格有限责任公司 | Heat transfer device |
| CN203479107U (en) * | 2013-07-26 | 2014-03-12 | 新乡平原航空器材有限公司 | Heat exchanger core body and heat exchanger |
| CN103868394A (en) * | 2012-12-13 | 2014-06-18 | 杭州三花研究院有限公司 | Circulation board of heat exchanger, heat exchanging unit of heat exchanger and heat exchanger |
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| JP2813732B2 (en) * | 1989-08-11 | 1998-10-22 | アイシン精機株式会社 | Stacked heat exchanger |
| JPH04155191A (en) * | 1990-10-17 | 1992-05-28 | Hitachi Ltd | Lamination type heat exchanger |
| KR0143540B1 (en) * | 1992-08-27 | 1998-08-01 | 코오노 미찌아끼 | Stacked heat exchanger and method of manufacturing the same |
| JP5416451B2 (en) * | 2008-08-01 | 2014-02-12 | 福伸電機株式会社 | Plate heat exchanger |
| JP2013145066A (en) * | 2012-01-13 | 2013-07-25 | Panasonic Corp | Heat exchanger |
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2015
- 2015-04-23 CN CN201510200921.7A patent/CN104792199B/en not_active Expired - Fee Related
- 2015-04-23 CN CN201610411050.8A patent/CN106091785B/en active Active
- 2015-04-23 CN CN201610404042.0A patent/CN105973041B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4042018A (en) * | 1975-09-29 | 1977-08-16 | Des Champs Laboratories Incorporated | Packaging for heat exchangers |
| EP1435502B1 (en) * | 2002-12-30 | 2008-02-27 | Halla Climate Control Corporation | Laminated heat exchanger |
| CN103547877A (en) * | 2011-05-24 | 2014-01-29 | 皮尔伯格有限责任公司 | Heat transfer device |
| CN103424024A (en) * | 2012-05-15 | 2013-12-04 | 杭州三花研究院有限公司 | Plate heat exchanger and plate thereof |
| CN103868394A (en) * | 2012-12-13 | 2014-06-18 | 杭州三花研究院有限公司 | Circulation board of heat exchanger, heat exchanging unit of heat exchanger and heat exchanger |
| CN203479107U (en) * | 2013-07-26 | 2014-03-12 | 新乡平原航空器材有限公司 | Heat exchanger core body and heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105973041A (en) | 2016-09-28 |
| CN104792199B (en) | 2016-06-29 |
| CN105973041B (en) | 2018-03-13 |
| CN104792199A (en) | 2015-07-22 |
| CN106091785B (en) | 2018-05-15 |
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