CN106091785B - A kind of plate heat exchanger of sheet structure optimization - Google Patents
A kind of plate heat exchanger of sheet structure optimization Download PDFInfo
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- CN106091785B CN106091785B CN201610411050.8A CN201610411050A CN106091785B CN 106091785 B CN106091785 B CN 106091785B CN 201610411050 A CN201610411050 A CN 201610411050A CN 106091785 B CN106091785 B CN 106091785B
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Classifications
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- 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
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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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The present invention provides a kind of plate heat exchanger, the flow that the heat exchanging fluid of heat exchange is participated in the plate heat exchanger is different, the plate heat exchanger includes heat exchange plate, at least one by-passing parts are set in the small heat exchange plate of flow, the flow path for the heat exchanging fluid for flowing through heat exchange plate is divided at least two flow manifolds by the by-passing parts, by-passing parts set opening, so that Cheng Liudao is divided to be cascaded structure in the heat exchange plate, so that the small heat exchanging fluid of flow forms S-shaped runner on heat exchange plate, flow dividing structure is optimized design.The present invention is in the case where 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, more particularly to a kind of plate heat exchanger, belong to the field of heat exchangers of F28D.
Background technology
Under normal circumstances, 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 (referring to volume flow) of two kinds of fluids is not much different, the runner of same fluid can be adopted at this time
Mode in parallel parallel to each other is taken, such as Fig. 1 a, the coefficient of heat transfer of two side liquid of plate heat exchanger is not much different at this time, whole heat exchange
The device coefficient of heat transfer is very high, and so sets it is also possible that the inlet and outlet of two kinds of fluids are all on an end plate 5, such as Fig. 1 b institutes
Show, be conducive to plate heat exchanger disassembles maintenance and plate cleaning.But changed if two kinds of flows differ larger fluid
When hot, if two kinds of fluids all take the fluid passage of parallel connection, occur that the flow velocity of smaller flow is too low, so as to cause lower
The coefficient of heat transfer.Therefore low-flow fluid passage is usually arranged to the form of series connection, as shown in Figure 2 a, thus can not will be cold
Four inlet and outlet 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,
Fluid inlet and outlet connectors are all set on two end plates, when heat exchanger is in connection status with pipeline, plate heat exchanger will be dismantled tired
For hardly possible, it is necessary to which both ends are dismantled, it is inconvenient to cause to overhaul.
The content of the invention
The present invention only changes sealing structure to realize the hot and cold unequal need of side liquid actual internal area with same plate
Ask, and the plate heat exchanger that these plates assemble can save very big installation using the assembling form of unilateral adapter
And maintenance cost.
To achieve these goals, technical scheme is as follows：
A kind of plate heat exchanger, it is different to participate in the flow of the heat exchanging fluid of heat exchange in the plate heat exchanger, described board-like
Heat exchanger includes heat exchange plate, it is characterised in that at least one by-passing parts are set in the small heat exchange plate of flow, it is described
The flow path for the heat exchanging fluid for flowing through heat exchange plate is divided at least two flow manifolds by by-passing parts, and by-passing parts set and open
Mouthful so that divide Cheng Liudao to be cascaded structure in the heat exchange plate, so that the small heat exchanging fluid of flow is in heat exchange plate
Upper formation S-shaped runner.
Preferably, heat exchange plate sets ripple, the height of ripple is different；On same plate, along the flowing road of fluid
Footpath, the wave height in same split channel gradually rise.
Preferably, the Opening length L1 of by-passing parts, the length of by-passing parts is L2, and 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。
Preferably, the direction flowed along fluid, the width W of different flow manifolds constantly subtracts on same plate
It is few.
Compared with prior art, plate heat exchanger of the invention and its heat exchange plate have the following advantages：
1) present invention only changes sealing structure to realize that hot and cold side liquid actual internal area is unequal with same plate
Demand, and the plate heat exchanger that these plates assemble can save very big peace using the assembling form of unilateral adapter
Dress and maintenance cost.
2) present invention devises the flow point that plate heat exchange area is divided into several parts on the basis of traditional sheet structure
Seal groove is cut, to coordinate with the caulking gum gasket of respective shapes, realizes and the flow area of whole plate is divided into several small portions
Point, length of flow of the fluid in a plate passage is become multiple flows after segmentation by a flow before segmentation, from
And improve flow velocity.When facilitating the plate heat exchanger to design, flow differs heat exchange area and circulation in the case of larger two kinds of fluid heat transfers
The matching of area.
3) present invention obtains an optimal heat exchange plate optimum results, and carry out by testing by test of many times
Verification, so as to demonstrate the accuracy of result.
4) material of new heat exchange plate is developed.
5) material of new gasket seal is developed.
6) set by the change of channel width, improve the coefficient of heat transfer.
Brief description of the drawings
Fig. 1 is the prior art plate heat exchanger schematic diagram of a runner parallel connection；
Fig. 2 is the schematic diagram of the prior art plate heat exchanger of runner series connection；
Fig. 3 is the schematic diagram of point journey sheet structure of the invention；
Fig. 4 is the structure diagram of point journey gasket of the invention；
Fig. 5 is the sheet structure schematic diagram of the big fluid of the flow of the present invention；
Fig. 6 is the structure diagram of point journey plate of the invention；
Fig. 7 is the scale diagrams of point journey plate of Fig. 3.
Reference numeral is as follows：
1 first fluid import, the outlet of 2 first fluids, 3 second fluid imports, the outlet of 4 second fluids, 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.
Embodiment
The embodiment of the present invention is described in detail below in conjunction with the accompanying drawings.
Herein, if without specified otherwise, it is related to formula, "/" represents division, and "×", " * " represent multiplication.
The heat exchange plate 10 used in a kind of plate heat exchanger, sets at least one distributary division in the heat exchange plate 10
Part, the flow path for the heat exchanging fluid for flowing through heat exchange plate is divided at least two points of Cheng Liudao 7 by the by-passing parts, described
Cheng Liudao 7 is divided to be cascaded structure in heat exchange plate 10.Pass through the above-mentioned cascaded structure for dividing Cheng Liudao 7 so that fluid is therefore
Divide Cheng Liudao 7 by all, as shown in fig. 6, so that heat exchanging fluid forms S-shaped runner on heat exchange plate 10.
By setting by-passing parts so that the small fluid of flow can be full of whole heat exchange plate, so as to avoid appearance
The heat exchange area of some fluid shorts, so as to add the coefficient of heat transfer, improves the coefficient of heat transfer of whole heat exchanger；It is in addition, logical
Cross setting by-passing parts so that the fluid of small flow can also realize the parallel connection of the fluid passage in multiple plates, such as Fig. 1 a
It is shown, avoid the need to improve the coefficient of heat transfer and small fluid passage is arranged to the structure of the series connection shown in Fig. 2 a, so as to
So that four inlet and outlet 1-4 of fluid are all disposed within same end plate, so that easy to maintain.
Preferably, the volume flow of large flow fluid is more than 2 times of the volume flow of small flow material.
Preferably, by-passing parts are realized by seal groove 8 and gasket 9, the seal groove 8 is arranged on heat exchanger plates
On piece, by the way that gasket 9 is inserted into seal groove 8, so as to form by-passing parts.
Preferably, by-passing parts are realized by directly setting sealing strip on heat exchange plate.Preferably, sealing
Bar and heat exchange plate are integrated.
On the fluid inlet of heat exchange plate and the upper and lower ends of outlet, i.e. the upper and lower ends of Fig. 3, by-passing parts are at one end
It is closing, is that opening is set in the other end, wherein along left and right directions, aperture position is to be disposed alternately at upper and lower ends,
So ensure that fluid passage forms S-shaped.
It is upper bottom left that before note that and direction up and down mentioned later, which is not limited in use state,
Right direction, herein just for the sake of the structure of the plate in statement Fig. 3.
Fig. 3, the plate described in 6 are because be provided with two by-passing parts, therefore the inlet and outlet of fluid are arranged on upper end with
End.1 or odd number by-passing parts can certainly be set, the inlet and outlet position of fluid at this time is located on the same end,
It is located at upper end or lower end at the same time.
Foregoing S-shaped runner can be half of S-shaped, for example, only set a by-passing parts situation or
Whole S-shaped, such as the combination of Fig. 3,6 form or multiple S-shapeds and/or half of S-shaped, such as set and be more than 2
The situation of by-passing parts, such as 3 by-passing parts are exactly the combination of 1 one S-shapeds and half of S-shaped, and 4 by-passing parts are exactly 2 S
Shape, etc. and so on.
For the form using gasket, preferably, setting between gasket and heat exchange plate for plate heat exchanger piece
Gasket integrated design, therefore present invention provides the gasket used in plate heat exchanger in one between heat exchange plate.Institute
State and at least one flow seal pad 9 is set in gasket, the flow seal pad 9 will flow through the flowing of the heat exchanging fluid of heat exchange plate
Path is divided at least two points of Cheng Liudao 7, divides Cheng Liudao 7 to be cascaded structure in the heat exchange plate 10, so that heat exchange
Fluid forms S-shaped runner on heat exchange plate 10.
In numerical simulation and it was found that, by setting by-passing parts, the increase of the heat exchanger coefficient of heat transfer is enabled to, but
It is while also brings the increase of flow resistance.Found by numerical simulation and experiment, for the width of flow manifold, if mistake
It is small, flow resistance can be caused excessive, the pressure-bearing of heat exchanger is too big, and is flowed there may be runner both sides boundary layer along fluid
Direction overlaps, and causes the coefficient of heat transfer to decline, and width of flow path is excessive to also result in the coefficient of heat transfer for reducing plate heat exchanger, therefore
There is a suitable numerical value for split channel 7；Also there is certain requirement for the length of by-passing parts opening, if opening
It is too small, the quantity that fluid is flowed through by opening can be caused too small, reduce the coefficient of heat transfer while pressure is increased, similarly, such as
Fruit is excessive, then fluid can produce short-circuited region, does not have corresponding heat transfer effect, therefore also has for opening one suitable long
Degree.Therefore the ruler of an optimization is met between the Opening length of by-passing parts, the length of by-passing parts, flow manifold width
Very little relation.
Therefore, the present invention be by the thousands of secondary numerical simulations and test data of the heat exchanger of multiple and different sizes,
Meet (below 2.5MPa) in the case of industrial requirements pressure-bearing, in the case where realizing maximum heat exchange amount, what is summed up optimal changes
The dimensionally-optimised relation of hot plate piece.
As shown in fig. 7, the Opening length L1 of by-passing parts, the length of by-passing parts is L2, flow manifold width W, then expires
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 the farthest position for reaching fluid passage from the position that opening occurs edge along by-passing parts
Put, such as the A points in Fig. 7.
Preferably, a=0.19, b=0.015, c=0.0037；
Preferably, being continuously increased with L1/W, the numerical value of a is constantly reduced；
Preferably, being continuously increased with L1/W, the numerical value of b, c are continuously increased.
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
Take the heat transfer effect that above-mentioned formula obtains best.
It is preferred that the plate spacing 4-6mm of heat exchanging plate of heat exchanger, preferably 5mm.
For, using gasket and the integrated form of gasket, in the case of also meeting above-mentioned formula, heat exchange is imitated in Fig. 4
Fruit is optimal.
Preferably, multiple by-passing parts are parallel to each other.
Preferably, the direction (more remote i.e. apart from the fluid inlet of heat exchange plate) flowed along fluid, same heat exchanger plates
The width W of the different flow manifold of on piece is constantly reduced.For example, 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.By flow manifold width W constantly reduce can fluid it is continuous
Acceleration, avoid because fluid operation is slow caused by being short of power.
Preferably, the direction flowed along fluid, the width W of same flow manifold are constantly reduced.For example, shunting stream
In road 7, along fluid flow direction (i.e. Fig. 3 is from top to bottom), width W is constantly reduced.At this time, for the W in preceding formula
Using mean breadth W.
Preferably, on various heat exchange plate, more remote apart from heat exchanger fluid entrance, flow manifold width is smaller.Mainly
It is more remote apart from entrance, then distribution fluid is fewer, and the change fluid for passing through width of flow path ensures certain flow velocity.
Preferably, heat exchange plate sets ripple, the height of ripple is different.On same plate, along the flowing road of fluid
Footpath, the wave height in same split channel gradually rise, such as in flow manifold 7, along fluid flow direction (i.e. Fig. 3
From top to bottom), wave height gradually rises.
Preferably, flow manifold is more remote apart from heat exchange plate fluid inlet distance, the ripple in different flow manifolds
Height is higher, for example, the wave height in the flow manifold 7 in Fig. 3 is less than flow manifold 11, the wave height of flow manifold 11
Less than flow manifold 12.
Preferably, on various heat exchange plate, more remote apart from heat exchanger fluid entrance, wave height is higher.Mainly away from
More remote from entrance, then distribution fluid is fewer, and the change fluid for passing through wave height ensures certain flow velocity.
Preferably, heat exchange plate sets ripple, the density of ripple is different.On same plate, along the flowing road of fluid
Footpath, the corrugation density in same split channel become larger, such as in flow manifold 7, along fluid flow direction (i.e. Fig. 3
From top to bottom), corrugation density becomes larger.
Preferably, flow manifold is more remote apart from heat exchange plate fluid inlet distance, the ripple in different flow manifolds
Density becomes larger.For example, 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
Preferably, on various heat exchange plate, more remote apart from heat exchanger fluid entrance, corrugation density is bigger.Mainly away from
More remote from entrance, then distribution fluid is fewer, and the change fluid for passing through wave height ensures certain flow velocity.
Preferably, wave height noted earlier and/or the increased amplitude of density are less and less.
Preferably, the heat exchange plate uses Cu alloy material, the copper alloy by copper, iron, manganese, cerium, magnesium, tin,
Silver, chromium and other auxiliary materials are process, and percentage by weight shared by each component is respectively in the copper alloy：Copper 71.2%~
82.5%th, iron 3.3%~4.5%, manganese 1.1%~2.5%, cerium 0.35%~0.45%, magnesium 0.77%~1.3%, tin
0.028%~0.14%, silver 0.06%~0.09%, chromium 0.3%~0.9%, remaining as auxiliary material.
Preferably, the auxiliary material is mixed and processed by zinc chloride and charcoal.
Preferably, percentage by weight shared by each component is respectively in the copper alloy：Copper 76.3%, iron 4.4%, manganese
1.8%th, cerium 0.5%, magnesium 1.07%, tin 0.007%, silver 0.75%, chromium 0.6%, remaining as auxiliary material.
The processing method of above-mentioned copper alloy is as follows：
1st, cathode copper is melted with intermediate frequency furnace and is warming up to 1300~1400 DEG C, addition crome metal, 33 points of silver insulation
Clock；
2nd, after pulling clinker out, add remaining component and stir evenly.Then tapping casting, and furnace temperature is controlled at 1340 DEG C；
3rd, cast using semi continuous, when casting is protected with nitrogen；
4th, casting is forged as needed or pressure processing is into parts, it is small that parts are then heated to 900 DEG C of insulations 3
When hardening, then at a temperature of 479 DEG C insulation 2~3 it is small when carry out ageing treatment；
There is the high characteristic of high temperature resistant, thermal conductivity factor through copper alloy made of above-mentioned specification, and substantially improve resistance
Shape ability and wearability.
Preferably, the gasket seal between gasket 9 and/or heat exchange plate uses elastomeric material.The elastomeric material
It is prepared from the following raw materials in parts by weight：7-9 parts of ethylene propylene diene rubber, 3-6 parts of butadiene-styrene rubber, 6-8 parts of zinc oxide, white carbon 13-
15 parts, 4-5 parts of accelerating agent, 2-8 parts of foaming agent, 5-6 parts of naphthenic oil, 20 parts of titanium dioxide, 50-55 parts of natural rubber, Rhein dissipates 10-
13 parts, 15-17 parts of silicon rubber, 2 parts of carborundum, 2 parts of Melamine, 0.6 part to 1.5 parts of antioxidant, 4 parts to 6 parts of softening agent, sulphur
2.2 parts to 4 parts of agent.
Preferably, 8 parts of ethylene propylene diene rubber, 5 parts of butadiene-styrene rubber, 7 parts of zinc oxide, 14 parts of white carbon, 4 parts of accelerating agent, hair
4 parts of infusion, 6 parts of naphthenic oil, 20 parts of titanium dioxide, 52 parts of natural rubber, Rhein dissipate 12 parts, 16 parts of silicon rubber, 2 parts of carborundum, and three
2 parts of polynitriles amine, 0.9 part of antioxidant, 5 parts of softening agent, 3 parts of vulcanizing agent.
Manufacture method includes the following steps：
A. the ethylene propylene diene rubber, butadiene-styrene rubber, zinc oxide, white carbon, accelerating agent, foaming are sequentially added in mixer
Agent, naphthenic oil, titanium dioxide, natural rubber, Rhein dissipate, silicon rubber, carborundum, Melamine and accelerating agent and antioxidant, so
Start mixer afterwards and carry out first time mixing, 70 seconds to 75 seconds time, temperature is 60 DEG C to 70 DEG C；
B. softening agent is added in the mixer of step A and carries out second of mixing, 75 seconds time, temperature is less than 105 DEG C, so
Postcooling dumping；
C. vulcanize：The glue of step B is discharged on tablet press machine and adds vulcanizing agent and turns refining, time 125-140 second, under
Piece to obtain the final product.
Preferably, accelerating agent is diphenylguanidine.
Preferably, the accelerating agent is dithiocar-bamate；The antioxidant is Tissuemat E；The softening agent
For paraffin；The vulcanizing agent is curing resin.
The rubber has the following advantages that：1) by adding the material compounding of zinc oxide, titanium dioxide, resulting materials elasticity
It is good, and there is certain hardness, wear-resisting durable, long lifespan is not easy to wear.2) due to using Tissuemat E as anti-aging
Agent, can improve the persistence, hardness and abrasion resistance of rubber；3) vulcanization time is short, rubber is handed over by the macromolecular of linear structure
Be unified into the macromolecular for space network, the rubber of output its anti-tensile, stretch surely, wear-resisting performance it is good.
The two side walls of the heat exchange plate 3 set erosion resistant coating.Low-temperature receiver and/or the erosion resistant coating of heat source side wall are by coating
Anticorrosive paint generates, and the mass percent of anticorrosive paint component is as follows：Zinc flake 6.6-8.3%, aluminium oxide 8-9%, boron
Acid is 7.2-9.2%, and acrylic acid 0.7-0.9%, wetting dispersing agent 0.4-0.5%, thickener 0.15-0.23%, disappears
Infusion is 0.14-0.23%, the water of surplus.This kind of coating is by spraying, brushing, dip-coating is applied over heat exchange plate surface, 80 ±
10 DEG C dry 10~60 minutes, and 280 ± 40 DEG C cure sintering 30~60 minutes, form good anti-corrosion coating.
The method for preparing above-mentioned water-based anticorrosive paint, this method are implemented according to following steps,
A, by coating gross mass percentage, a certain amount of water is weighed respectively, 0.4% wetting dispersing agent and 0.23% disappears
Infusion, it is then admixed together, it is sufficiently stirred and is allowed to dissolving and is made coating mixed liquor A 1, then is added into mixed liquor A 1 and account for coating
8.3% flake metal powder of gross mass, stirs evenly and coating mixed liquor A 2 is made；
B, by coating gross mass percentage, 7.3% boric acid is weighed, mixed liquor is formed, is added in 20%~40% water
Fully inorganic acid mixed liquid B 1 is made in dissolving, then 8% oxidate powder is added into mixed liquid B 1, and nothing is made in stirring to no precipitation
Machine acid mixed liquid B 2；
C, by coating gross mass percentage, 0.7% acrylic acid is weighed, is added in 5%~15% water, is sufficiently stirred
Reducing agent mixed liquor C uniformly is made；
D, by coating gross mass percentage, 0.15% thickener hydroxyethyl cellulose is weighed, is added to 2.5%~15%
Water in, stir to dissolving be translucent shape and without gel occur i.e. stopping stirring thickener mixed liquor D is made；
E, the inorganic acid mixed liquid B 2 of preparation is added in coating mixed liquor A 2, then adds reducing agent mixed liquor C and match somebody with somebody
The 1/5~1/2 of amount processed, adds thickener mixed liquor D, adds the water of surplus, continue stirring 30~90 minutes, directly while stirring
Untill coating mixed liquor uniformity soilless sticking particle, remaining reducing agent mixed liquor C is finally added, is stirred for 10~40
Minute, to obtain the final product.
This kind of coating is by spraying, brushing, dip-coating is applied over fin pipe surface, and 80 ± 10 DEG C dry 10~60 minutes, and 280
± 40 DEG C cure sintering 30~60 minutes, form good anti-corrosion coating.
The wetting dispersing agent is the SA-20 in peregal series, and the thickener selects hydroxyethyl cellulose；It is described
Defoamer select tributyl phosphate.
Preferable one embodiment, from low-temperature receiver to heat source side, the heat of low-temperature receiver erosion resistant coating, heat exchange plate and heat source erosion resistant coating
The coefficient of expansion is sequentially reduced.It is that the erosion resistant coating of heat source side is first heated because during heat exchange to be why arranged such, first swollen
It is swollen, then it is outwards heat exchange plate, low-temperature receiver side erosion resistant coating expanded by heating, therefore low-temperature receiver erosion resistant coating, heat exchange plate and heat successively
The thermal coefficient of expansion of source erosion resistant coating, which is sequentially reduced, can ensure that expansion rate is consistent substantially, ensure the connection of each layer compactness and
Stability.In this way, low-temperature receiver and the erosion resistant coating of heat source side take anticorrosive paint noted earlier, by varying anticorrosive paint into
Divide the change so as to fulfill thermal coefficient of expansion.Other different anticorrosive paints can certainly be used to realize the change of thermal coefficient of expansion
Change.Such as above-mentioned anticorrosive paint is only used in side, opposite side uses other anti-corrosion materials.
Fig. 5 illustrates the flow channel of the big fluid of flow, in fact, for the present invention, two kinds of heat exchanging fluids are all
The small fluid of flow can be used.Such as in the case where heat exchange plate is certain, flow all very littles of two kinds of fluids, two kinds at this time
The flow channel of fluid can take the plate of Fig. 3, Fig. 6 form.
Although the present invention is disclosed as above with preferred embodiment, the present invention is not limited to this.Any art technology
Personnel, without departing from the spirit and scope of the present invention, can make various changes or modifications, therefore protection scope of the present invention should
When being subject to claim limited range.
Claims (6)
1. a kind of plate heat exchanger, it is different to participate in the flow of the heat exchanging fluid of heat exchange in the plate heat exchanger, described board-like to change
Hot device includes heat exchange plate, and at least one by-passing parts are set in the small heat exchange plate of flow, and the by-passing parts will flow
The flow path of heat exchanging fluid through heat exchange plate is divided at least two points of Cheng Liudao, and by-passing parts set opening so that described
Heat exchange plate in divide Cheng Liudao to be cascaded structure so that the small 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, the length of by-passing parts is L2, divides journey width of flow path W, then meets 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 heat exchanger as claimed in claim 1, it is characterised in that a=0.19, b=0.015, c=0.0037.
3. plate heat exchanger as claimed in claim 1, it is characterised in that with being continuously increased for L1/W, the numerical value of a constantly subtracts
It is few.
4. plate heat exchanger as claimed in claim 1, it is characterised in that with being continuously increased for L1/W, the numerical value of b, c are continuous
Increase.
5. plate 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。
6. plate heat exchanger as claimed in claim 5, it is characterised in that the flow velocity of the fluid of split channel is 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)
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| 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 |
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| CN201510200921.7A Division CN104792199B (en) | 2015-04-23 | 2015-04-23 | The plate type heat exchanger that a kind of heat exchanging fluid flow is different |
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| CN106091785A CN106091785A (en) | 2016-11-09 |
| CN106091785B true CN106091785B (en) | 2018-05-15 |
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| CN201510200921.7A Expired - Fee Related CN104792199B (en) | 2015-04-23 | 2015-04-23 | The plate type heat exchanger that a kind of heat exchanging fluid flow is different |
| CN201610404042.0A Active CN105973041B (en) | 2015-04-23 | 2015-04-23 | A kind of plate type heat exchanger of width of flow path change |
| CN201610411050.8A Active CN106091785B (en) | 2015-04-23 | 2015-04-23 | A kind of plate heat exchanger of sheet structure optimization |
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| 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 |
| CN110537070B (en) * | 2017-04-27 | 2021-01-12 | 三菱电机株式会社 | 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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- 2015-04-23 CN CN201510200921.7A patent/CN104792199B/en not_active Expired - Fee Related
- 2015-04-23 CN CN201610404042.0A patent/CN105973041B/en active Active
- 2015-04-23 CN CN201610411050.8A patent/CN106091785B/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 |
|---|---|
| CN106091785A (en) | 2016-11-09 |
| CN105973041A (en) | 2016-09-28 |
| CN104792199B (en) | 2016-06-29 |
| CN104792199A (en) | 2015-07-22 |
| CN105973041B (en) | 2018-03-13 |
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Effective date of registration: 20230707 Address after: Room 428, Production Building, Dia Venture Base, 2766 Yingxiu Road, Lixia District, Jinan, Shandong 250101 Patentee after: Shandong Joule Clean Energy Technology Co.,Ltd. Address before: No.17923, Jingshi Road, Lixia District, Jinan City, Shandong Province Patentee before: SHANDONG University |