CN104019491A - Heat exchanger preventing layer shedding - Google Patents
Heat exchanger preventing layer shedding Download PDFInfo
- Publication number
- CN104019491A CN104019491A CN201410208275.4A CN201410208275A CN104019491A CN 104019491 A CN104019491 A CN 104019491A CN 201410208275 A CN201410208275 A CN 201410208275A CN 104019491 A CN104019491 A CN 104019491A
- Authority
- CN
- China
- Prior art keywords
- fin
- base tube
- tube
- heat exchanger
- finned
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
The invention provides a finned tube exchanger and relates to a heat exchanger preventing layer shedding. The heat exchanger comprises an upper collecting tube, a lower collecting tube and finned tubes connected between the upper collecting tube and the lower collection tube. Anti-corrosion layers are arranged inside basic tubes, and the basic tubes are coated with abrasion-resistant layers. The thermal expansion coefficients of the anti-corrosion layers, the basic tubes and the abrasion-resistant layers are gradually increased. The expansion coefficients of all the layers of the heat exchanger are optimized to prevent all the layers from shedding and make heat exchange efficiency be maximized so that energy can be saved, and the purposes of environmental friendliness and energy saving can be achieved.
Description
The present invention is that application number is 201310483171.X, and what denomination of invention was the patent of invention of " a kind of inner-finned-tube heat exchanger " divides an application.
Technical field
The invention belongs to field of heat exchangers, relate in particular to a kind of heating heat exchanger.
Background technology
The terminal device of Home Heating, thermal source is generally city central heating, self-built boiler room, community, Domestic wall stove etc., by heat conduction, radiation, convection current, heat is dispelled the heat out, allows the temperature in room get a promotion.
In heat exchanger; be suitable for widely at present finned tube exchanger; by fin, can expand area of dissipation; strengthen heat transfer effect; but the setting of the heat exchanger types of finned tube and finned tube parameter is the quality of influencer's radiating effect all; and at present in the situation that of energy crisis; urgent need will be saved the energy; meet social sustainable development; therefore need to develop a kind of new finned tube, need the structure of finned tube to be optimized simultaneously, make it reach heat exchange efficiency and maximize; to save the energy, reach the object of environmental protection and energy saving.
Summary of the invention
Technical problem to be solved by this invention is to provide a kind of new linear pattern closed finned tube heat exchanger.
To achieve these goals, technical scheme of the present invention is as follows: a kind of finned tube exchanger of enclosed construction, the finned tube that comprises upper header, lower collector pipe and connection upper header and lower collector pipe, described finned tube comprises circular base tube and the first fin, the second fin, the extended line that the first fin and the second fin are arranged on outside and the first fin and second fin of base tube intersects at the central axis of base tube at the place, the center of circle of base tube, and the first fin and the second fin are symmetrical along the first level crossing picture by base tube central axis; Described finned tube comprises the 3rd fin and the 4th fin, and described the 3rd fin, the 4th fin are symmetrical with the first fin and the second fin mirror image respectively along the second plane, and described the second plane is vertical with the first plane and pass through the central axis of base tube; Between described the first fin and the second fin, the first brace is set, between described the 3rd fin and the 4th fin, the second brace is set, the first brace and the second brace are circular arc type metallic plate; The 3rd fin of the first fin, the second fin and adjacent fins pipe and the 4th fin form space; The central axis at place, the center of circle of described circular arc-shaped metal plate and the central axes of base tube; Described base tube is straight tube, and the central axis of described adjacent base tube is parallel to each other; The first fin of adjacent base tube is parallel to each other.
Angle between described the first fin and the second fin is A, and the length of the first fin and the second fin is L, and the outer radius of base tube is R, the fin height H along base tube on axially, and above-mentioned four relation meets following formula:
Sin(A/2)=a×(L/R)
2+b×(L/R)+c，
H/(R×10)=e×Sin(A/2)
2-f×Sin(A/2)+h，
Wherein, A unit is angle, 60 ° of <A<110 °,
L is of a size of mm, 12mm<L<80mm,
The unit of R is mm, 10mm<R<80mm,
The unit of H is mm, 800mm<R<1200mm,
A, b, c, e, f, h are coefficient, and the scope of a is 0.04-0.042, and the scope of b is 0.266-0.28, and the scope of c is 0.36-0.37, and the scope of e is 21-23, and the scope of f is 44-45, and h is 23-25.
The optimum of parameter is: a is that 0.0412, b is that 0.02715, c is that 0.03628, e is that 22, f is that 44.37, h is 23.86.
Preferably the distance between adjacent base tube central axis is S=d * (L+R) * sin (A/2) as one, and wherein d is 1.1-1.2.
The optimum results of d is 1.118.
The material of described base tube and fin is aluminium alloy, and the mass percent of the component of described aluminium alloy is as follows: 3.0%Cu, and 1.9%Mg, 1.6%Ag, 0.6%Mn, 0.25%Zr, 0.3%Ce, 0.23%Ti, 0.38%Si, all the other are Al.
The pipe inside of described base tube arranges anticorrosive coat, and the outside of base tube is coated with coating rubbing-layer, and the thermal coefficient of expansion of anticorrosive coat, base tube and wearing layer increases successively.
Described heat exchanger also comprises control system, and described control system is controlled the flow velocity that enters water in heat exchanger according to indoor temperature.
Described control system comprises: temperature sensor, flow controller and central controller, and flow controller is controlled the flow velocity that enters heat exchanger, described temperature sensor is used for measuring indoor temperature, when indoor temperature reaches the first temperature, central controller controls flow controller reaches the first flow velocity, when indoor temperature reaches the second temperature higher than the first temperature, central controller controls flow controller reaches the second flow velocity lower than the first flow velocity, when indoor temperature reaches the 3rd temperature higher than the second temperature, central controller controls flow controller reaches the 3rd flow velocity lower than the second flow velocity, when indoor temperature reaches the 4th temperature higher than the 3rd temperature, central controller controls flow controller reaches the 4th flow velocity lower than the 3rd flow velocity, when indoor temperature reaches the 5th temperature higher than the 4th temperature, central controller cuts out flow controller, stops water to enter heat exchanger.
Described anticorrosive coat is grouped into by following one-tenth:
Zinc flake 8.3%, aluminium oxide is 8%, and boric acid is 7.3%, and acrylic acid is 0.7%, and wetting dispersing agent is 0.4%, and thickener is 0.15%, and defoamer is 0.23%, the water of surplus.
Described wetting dispersing agent is the SA-20 in peregal series, and described thickener is selected hydroxyethylcellulose, and described defoamer is selected tributyl phosphate.
Base tube axially near the part of upper header and lower collector pipe, there is no fin.
Base tube is greater than the length that there is no fin part near upper fin near the length of the part that there is no fin of the part of lower collector pipe.
The circulation area of upper header inner fluid reduces gradually along fluid flow direction.
The inside of upper header arranges deflector, and described deflector extends to the lower tilt of upper header from the position of heat exchanger entrance pipe.
The top wall of upper header extends to the lower tilt of upper header from the position of heat exchanger entrance pipe.
The shape of flow deflector is the shape of straight plate shape or arc.
Compared with prior art, the present invention has advantages of as follows:
1) the invention provides a kind of new finned tube, and because the extension line of fin and the center of circle of base tube of finned tube overlap, thereby make heat transfer effect reach best;
2) the present invention is by test of many times, designed the fin of different tube diameters, differing heights, angle and tested, thereby obtained an optimum fin optimum results, and verified by test, thereby proved the accuracy of result;
3), by the reasonable distribution to the mass percent of the component of aluminium alloy, improve high-fire resistance and the high-termal conductivity of finned tube;
4) thermal coefficient of expansion of anticorrosive coat, base tube and wearing layer increases successively, guarantees that the expansion rate of each layer is identical, guarantees combining closely of each layer, prevents from coming off in logical hot water;
5) by control system, automatically control the flow velocity of the water that enters heat exchanger, keep room temperature to reach a stable numerical value;
6) by base tube axially near the part of upper header and lower collector pipe, there is no fin, the air that has guaranteed base tube bottom can carry out in the space of finned tube smoothly, reached good suction effect, also can guarantee simultaneously air technology to top convection current, increase the effect of heat convection;
7) by base tube, near the length of the part that there is no fin of the part of lower collector pipe, be greater than the length that there is no fin part of close upper fin, can increase convection effects;
8) dwindling gradually of the circulation area by upper header inner fluid, makes fluid flow flow velocity keep maximum, augmentation of heat transfer;
9), by the Based Intelligent Control of electric heater, realize energy-conservation.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of heat exchanger of the present invention.
Fig. 2 is the cross sectional representation of finned tube.
Fig. 3 is the schematic diagram of Heat Exchanger Control System.
Fig. 4 is the schematic diagram that Fig. 3 sees from left side.
Fig. 5 is the heat exchanger schematic diagram with deflector.
Fig. 6 is the heat exchanger schematic diagram that upper header sectional area shrinks gradually.
Fig. 7 is the sectional drawing of second embodiment of the invention.
Fig. 8 is the schematic diagram of base tube inner fin.
Reference numeral is as follows:
1 upper header, does not have the part of fin, 3 lower collector pipe in 2 base tubes, 4 finned tubes, 5 base tubes, 6 water the first fins, 7 gaps, 8 first braces, 9 second fins, 10 the 4th fins, 11 the 3rd fins, 12 second braces, 13 central controllers, 14 flow controllers, 15 temperature sensors, 16 temperature sensors, 17 heat exchangers, 18 inlet tubes, 19 outlets, 20 deflectors, 21 upper header upper surfaces, 22 vacuum-pumping tubes, 23 temperature controllers, 24 fins, 25 heating rods, 26 inner fins, 27 otch, 28 projections.
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
A kind of finned tube exchanger 17 of enclosed construction, comprise upper header 1, lower collector pipe 3 and be connected upper header 1 and the finned tube 4 of lower collector pipe 3, described finned tube 4 comprises circular base tube 5 and the first fin 6, the second fin 9, the extended line that the first fin 6 and the second fin 9 are arranged on outside and the first fin 6 and second fin 9 of base tube 5 intersects at the central axis of base tube at the place, the center of circle of base tube 5, and the first fin 6 and the second fin 9 are symmetrical along the first plane B mirror image by base tube central axis; Described finned tube comprises the 3rd fin 11 and the 4th fin 10, described the 3rd fin 11, the 4th fin 10 are symmetrical with the first fin 6 and the second fin 9 mirror images respectively along the second plane C, and described the second plane C is vertical with the first plane B and pass through the central axis of base tube 5; Between described the first fin 6 and the second fin 9, the first brace 8 is set, it is circular arc type metallic plate that the second brace 12, the first braces 8 and the second brace 12 are set between described the 3rd fin 11 and the 4th fin 10; The central axes of the central axis of described circular arc-shaped metal plate and base tube 5; Described base tube is straight tube, and the central axis of described adjacent base tube is parallel to each other.
Preferably, the first fin of adjacent base tube is parallel to each other, represents that the second fin of adjacent base tube is also parallel to each other, and in like manner, the 3rd fin, the 4th fin are also parallel to each other.This feature shows that finned tube arranges according to equidirectional.
It should be explained that, as shown in Figure 2, the central axis of base tube is exactly the line that the set of the centre point on the cross section of base tube 5 forms, and the central axis of circular arc-shaped metal plate is exactly the line that the set of the centre point of circular arc-shaped metal plate on cross section forms.The central axes of the central axis of described circular arc-shaped metal plate and base tube 5 just refers to that, on cross section, circular arc-shaped metal plate and base tube are concentric circles.
Preferably, the size of all finned tubes is all identical.
By above-mentioned setting, make to form a gap 7 between fin and brace, in heat convection, gap 7 has just formed a kind of chimney effect, can strengthen heat exchange.
The 3rd fin of the first fin, the second fin and adjacent fins pipe and the 4th fin form space, and this space forms certain space, can form chimney effect, adds strong convection, augmentation of heat transfer.
Angle between described the first fin 6 and the second fin 9 is A, and the length of the first fin 6 and the second fin 9 is L, and the outer radius of base tube is R, and certainly, because mirror image is symmetrical, the length of the 3rd fin 11 and the 4th fin 10 is also L naturally.But find in practice, in heat transfer process. if fin angle is too small, can hinder heat exchange, because the words that fin angle is too small, cause the first fin, the distance of the second fin is too near, temperature boundary layer starts in the direction along with base tube height to overlap in closed area, gas temperature approaches tube wall temperature and moves closer to hot saturated, flow resistance increases, finally worsen on the contrary heat exchange, the advantage performance of outer fin is not out, same reason, constantly increase along with angle, make brace originally nearer apart from the distance of base tube, make equally temperature boundary layer in closed area, in the direction along with base tube height, start to overlap, gas temperature approaches tube wall temperature and moves closer to hot saturated, flow resistance increases, finally worsen on the contrary heat exchange, therefore angle has an optimum value.
For finned length, if oversize, even because the heat of base tube could arrive in time the end of fin or be effective also not obvious, if too short, expand heat exchange area too little, cannot reach a good heat transfer effect, so the height of fin also there is an optimum value.
For the distance between two finned tubes, if first distance is too near or completely close, between the brace of two finned tubes, the space of distance (referring to Fig. 1) is too little, air cannot enter by the gap between fin the space forming between finned tube, heat exchange now can only rely on from heat exchanger bottom and enter air, cannot reach good heat convection effect, same reason, if the distance is too far, the the one the second the 3 4th fins of finned tube cannot form the space of effective chimney effect, thereby cause heat transfer effect variation, therefore for the distance between two finned tubes, also need a suitable numerical value.
As shown in Figure 4, the base tube 5 of height H on axial along to(for) fin, also need to have a suitable numerical value, if fin height is too high, on the top of fin, because boundary layer starts in the direction along with base tube height to overlap in closed area, cause the deterioration of heat exchange, in like manner, highly too low, heat exchange is not given full play to, thereby affects heat transfer effect.
Therefore, the present invention is the size relationship of the finned tube of the best heat exchanger that sums up of the test data of the heat exchanger by a plurality of different sizes.Because finned tube also has included angle A, these three variablees of finned length L, fin height H, therefore, introduce two characteristic sin (A/2), L/R, H/R, R is the radius of base tube here, heat dissipation capacity maximum from heat transfer effect, has calculated nearly 200 kinds of forms.Described size relationship is as follows:
Angle between described the first fin and the second fin is A, and the length of the first fin and the second fin is L, and the outer radius of base tube is R, the fin height H along base tube on axially, and above-mentioned four relation meets following formula:
Sin(A/2)=a×(L/R)
2+b×(L/R)+c，
H/(R×10)=?e×Sin(A/2)
?2-f×Sin(A/2)+h，
Wherein, A unit is angle, 60 ° of <A<110 °,
L is of a size of mm, 12mm<L<80mm,
The unit of R is mm, 10mm<R<80mm,
The unit of H is mm, 800mm<R<1200mm,
A, b, c, e, f, h are coefficient, and the scope of a is 0.04-0.042, and the scope of b is 0.266-0.28, and the scope of c is 0.36-0.37, and the scope of e is 21-23, and the scope of f is 44-45, and h is 23-25.
By testing after result of calculation, by the numerical value of computation bound and median, the result of gained matches with formula substantially again, and error is substantially in 4%, and maximum relative error is no more than 6%, and mean error is 2%.
The optimum of coefficient optimization is: a is that 0.0412, b is that 0.02715, c is that 0.03628, e is that 22, f is that 44.37, h is 23.86.
Preferably, the distance between adjacent base tube central axis is S=d * (L+R) * sin (A/2), and wherein d is 1.1-1.2.
As shown in Figure 2, the distance between adjacent base tube central axis is exactly the distance between two base tube centers of circle on cross section.
The optimum results of d is 1.118.
The material of base tube and fin is aluminium alloy, and the mass percent of the component of described aluminium alloy is as follows: 3.0%Cu, and 1.9%Mg, 1.6%Ag, 0.6%Mn, 0.25%Zr, 0.3%Ce, 0.23%Ti, 0.38%Si, all the other are Al.
The manufacture method of aluminium alloy is: adopt vacuum metallurgy melting, argon for protecting pouring becomes circle base, through 600 ℃ of homogenising, processes, and at 400 ℃, adopts and is hot extruded into bar, and then after 580 ℃ of solution hardening, at 200 ℃, carry out artificial aging processing.Thermal conductivity factor is for being greater than 250W/ (m*k).
Base tube and fin can be integrally manufactured, also can split manufacture, and base tube and fin can be also different materials, and for example base tube is above-mentioned aluminium alloy, and fin can adopt other alloys, and wherein other alloy compositions are as follows:
Mass percent is as follows: Ni 30%; Cr 20%; Al 6%; C 0.03%; B 0.016%; Co 2%; Ti 3%; Nb 0.1%; La 0.2%; Ce 0.2%; Fe surplus.
The manufacture method of alloy is: by the composition smelting and pouring according to electrothermal alloy in vaccum sensitive stove, become ingot, then at 1200-900 ℃, alloy pig forge hot is become to bar, at 1200-900 ℃, be rolled into dish material, then in room temperature cold-drawn, become the silk material of different size.
After tested, above-mentioned alloy has very high thermal conductivity factor.
The pipe inside of described base tube 5 arranges anticorrosive coat, and the outside of base tube is coated with coating rubbing-layer, and the thermal coefficient of expansion of anticorrosive coat, base tube and wearing layer increases successively.Why so arranging is because in the process of heat supply, the anticorrosive coat of the inside of finned tube is first heated, first expand, then be outwards the second layer, the 3rd layer of expanded by heating successively, therefore from inside to outside three layers of expansion number of times increase successively and can guarantee that expansion rate is consistent substantially, guarantee compactness and the stability of each layer of connection.
As shown in Figure 3, described heat exchanger also comprises control system, and described control system is controlled the flow velocity that enters water in heat exchanger according to indoor temperature.
Described control system comprises: temperature sensor (not illustrating in Fig. 3), flow controller 14 and central controller 13, and flow controller 14 is controlled the flow velocity of the water that enters heat exchanger, described temperature sensor is used for measuring indoor temperature, when indoor temperature is during lower than the first temperature, flow controller is all opened, when indoor temperature reaches the first temperature, central controller controls flow controller reaches the first flow velocity, the first flow velocity will be lower than the flow velocity of all opening, when indoor temperature reaches the second temperature higher than the first temperature, central controller controls flow velocity reaches the second flow velocity lower than the first flow speed controller, when indoor temperature reaches the 3rd temperature higher than the second temperature, central controller controls flow controller reaches the 3rd flow velocity lower than the second flow velocity, when indoor temperature reaches the 4th temperature higher than the 3rd temperature, central controller controls flow controller reaches the 4th flow velocity lower than the 3rd flow velocity, when indoor temperature reaches the 5th temperature higher than the 4th temperature, central controller cuts out flow controller, stops water to enter heat exchanger.
The 5th temperature is exactly for very high temperature, and for example more than 25 ℃, the first temperature is exactly lower temperature, for example, below 15 ℃.By above-mentioned setting, can according to temperature, control the more heat of heat exchanger, reach the effect of saving the energy, especially next step will develop according to heat charging, therefore will inevitably receive an acclaim.
In addition, can set temperature sensor 15,16 be used for measuring the temperature of water that enters and go out heat exchanger.
Described control system can be a single-chip microcomputer, and control panel can be set, and control panel is arranged on top or the bottom of heat exchanger, also can be arranged on the pipeline that enters heat exchanger.
Described anticorrosive coat is to generate by applying anticorrosive paint, and anticorrosive paint is grouped into by following one-tenth: zinc flake 8.3%, and aluminium oxide is 8%, and boric acid is 7.3%, and acrylic acid is 0.7%, and wetting dispersing agent is 0.4%, and thickener is 0.15%, and defoamer is 0.23%, the water of surplus.
A method of preparing above-mentioned water-based anticorrosive paint, the method is implemented according to following steps,
A, press coating gross mass percentage, take respectively a certain amount of water, 0.4% wetting dispersing agent and 0.23% defoamer, then admixed together, fully stir to make it to dissolve and make coating mixed liquor A 1, to adding 8.3% the flake metal powder that accounts for coating gross mass in mixed liquor A 1, stir and make coating mixed liquor A 2 again;
B, press coating gross mass percentage, take 7.3% boric acid, form mixed liquor, join in the water of 20-40% and fully dissolve and make inorganic acid mixed liquid B 1, then to the oxidate powder that adds 8% in mixed liquid B 1, be stirred to without precipitation and make inorganic acid mixed liquid B 2;
C, press coating gross mass percentage, take 0.7% acrylic acid, join in the water of 5-15%, stir and make reducing agent mixed liquor C;
D, press coating gross mass percentage, take 0.15% thickener hydroxyethylcellulose, join in the water of 2.5-15%, be stirred to and dissolve be translucent shape and gel-free and occur stopping stirring making thickener mixed liquor D;
E, the inorganic acid mixed liquid B 2 of preparation is joined in coating mixed liquor A 2, then the 1/5-1/2 that adds reducing agent mixed liquor C amount of preparation, add while stirring thickener mixed liquor D, the water that adds again surplus, continue to stir 30～90 minutes, until coating mixed liquor uniformity without agglomerated particle, finally adds remaining reducing agent mixed liquor C again, stir again 10-40 minute, obtain.
This kind of coating is applied over finned tube surface by spraying, brushing, dip-coating, dries 10-60 minute for 80 ± 10 ℃, and 280 ± 40 ℃ of curing sintering 30-60 minute, form good anti-corrosion coating.
Described wetting dispersing agent is the SA-20 in peregal series, and described thickener is selected hydroxyethylcellulose; Described defoamer is selected tributyl phosphate.
As shown in Figure 1, base tube 5 axially near the part of upper header and lower collector pipe, there is no fin.The air that can guarantee like this bottom can enter in the space forming between fin, out from air top, strengthens convection effects simultaneously.
As shown in Figure 4, base tube 5 is greater than the length that there is no fin part near upper fin near the length of the part that there is no fin of the part of lower collector pipe.Main because be that bottom air surface density is large, can guarantee entering of more air, upper air density is little, and air more easily rises, so can keep air to enter and go out finned tube amount being substantially consistent.
Preferably, bottom do not have the length of the part of fin account for base tube 5 length 5%, top do not have the length of the part of fin account for base tube 5 length 3%.
As shown in Figure 8, the inwall of base tube 5 can arrange fin 26, for example, straight fins or helical fin can be set, and the height of described fin can be along with increasing gradually in the mobile direction of fluid, the highest fin height be minimum 1.05-1.1 doubly.Main cause is along with the mobile direction of fluid, the temperature of fluid declines gradually, and its heat transfer effect is reduced gradually, by increasing the height of inner fins, difference is set, heat exchange on can enhance fluid flow direction, thus heat transfer effect is consistent on the whole along fluid flow direction.
As shown in Figure 8, the direction of extending along inner fin, the top of inner fin 26 is arranged at intervals with otch 27.
Preferably, the degree of depth of otch 27 be inner fin 26 height 0.2-0.4 doubly.The width of otch is the 30-60% of inner fin total length.
Preferably, along with the mobile direction of fluid, the increase gradually of the degree of depth of otch 27.Preferably, bosom is the most shallow 1.05-1.15 of place times.
Preferably, along with the mobile direction of fluid, the increase gradually of the density of otch 27.Preferably, thickness is the thinnest 1.03-1.12 of place times.
Preferably, inner fin is spiral inner fin, with the helical angle of the central axis of base tube 5 be 30-60 °.
Because upper header is interior on the flow direction of fluid, the flowing pressure of fluid is more and more less, thereby the maldistribution of the fluid in the finned tube making, rate of flow of fluid in the finned tube of rear portion is declined, therefore in order to guarantee that the pressure of the fluid in upper header remains unchanged, the present invention has designed the circulation area of upper header 1 inner fluid is reduced gradually along fluid flow direction, like this can be so that enter large that the flow velocity of the fluid in finned tube keeps as far as possible, especially be positioned at the finned tube of fluid flow downstream, thus augmentation of heat transfer.
As a preferred embodiment, as shown in Figure 5, the inside of upper header 1 arranges deflector 20, described deflector 20 is inclined, from the top of upper header 1, extend to the bottom of upper header 1 always, make the fluid circulation area of upper header start to reduce gradually from heat exchanger entrance pipe 18, can guarantee that like this upper collecting chamber keeps consistency along the pressure on fluid flow direction, it is large that thereby the flow velocity that makes to enter the fluid in finned tube keeps as far as possible, thereby augmentation of heat transfer.
Flow deflector 20 is connected with two of the left and right wall of upper header, wherein at left wall, and the position that heat exchanger entrance pipe 18 is connected with upper header 1, deflector 20 is positioned at the top of inlet tube and heat collector junction.
As an embodiment that can replace, can cancel flow deflector, directly the top wall 21 of upper header 1 is set to skewed, as shown in Figure 6, from the position of inlet tube, towards the lower tilt of upper header 1, extend, thereby make in upper header 1, along the flow direction of fluid, fluid circulation area starts to reduce gradually from heat exchanger entrance pipe 18.
The top of upper header can be straight tabular, can be also arcuate structure.
As another one embodiment, as shown in Figure 7, described heat exchanger 17 can be electric heating heat exchanger.
The base tube at Fig. 7 heat exchanger both ends only arranges the fin of inner side, for outside, fin is not set, main cause is to make full use of heat-dissipating space because inner side fin is set can be so that form suction channel between the fin of adjacent finned tube, for the fin in outside, cannot form suction channel, therefore outside fin is deleted and can be saved space, space is fully left for to inner side fin simultaneously, can augmentation of heat transfer.This feature is equally also applicable to embodiment above.
The upper header 1 of heat exchanger, lower collector pipe 3 and finned tube 4 have formed the passage of fluid circulation.On upper header, be provided with vacuum-pumping tube 22, vavuum pump, by vacuum orifice pipe 22, is evacuated the inner chamber of upper header 1, lower collector pipe 3 and finned tube 4, then by vacuum-pumping tube 22, pours into appropriate superconducting fluid, and superconducting fluid finally flow in lower collector pipe 3.Injection rate until superconducting fluid reaches after normal capacity, then vacuum-pumping tube 22 is sealed.
As the atomization 50-60 ℃ time of the superconducting fluid of heat transfer medium, its heat conduction is fast, energy-conservation, safety, and superconducting fluid itself is nontoxic, tasteless, atomization in the pipeline of sealing, and self circulation does not need to use pipeline circulation.Superconducting fluid is little to the sidewall operating pressure of finned tube, and non-corrosiveness, "dead", has reached long service life, the object of safe handling.
Heating rod 25 is set in lower collector pipe 3, and at an end set temperature controller 23 of lower collector pipe 3, for controlling the temperature of heat exchanger.During use, plug in, the button on twisting temperature controller 23 is to suitable temperature, and heating rod 25 energisings are heated, and after being heated, superconducting fluid atomization rapidly under vacuum state, riddles each finned tube, upper lower collector pipe, reaches the object that continues fast heating.When reaching the temperature of temperature controller 23 settings, temperature controller is controlled heating rod and is stopped heating, and when the temperature arranging lower than temperature controller 23, temperature controller 23 is controlled heating rods and heated.
The outer setting of heating rod 25 is fin 24 again, for increasing heat exchange area, and augmentation of heat transfer.
Certainly, as an alternative, the heat exchanging fluid in heat exchanger can be set to water, by vacuumizing, makes water atomization 50-60 ℃ time, prevents from, because the temperature of water is too high, causing heat exchanger outer wall too hot.
In order to reach better heating effect, control system can be set, according to indoor temperature, automatically control the heating power of heating rod 25.Described control system comprises: temperature sensor and central controller, and described temperature sensor is used for measuring indoor temperature, and central controller is adjusted heating power automatically according to the numerical value of indoor temperature.The specific embodiment is as follows:
When indoor temperature is during lower than the first temperature, heating rod 25 heats with the first power, when indoor temperature reaches the first temperature, central controller heating rod 25 heats to be less than the second power of the first power, when indoor temperature reaches the second temperature higher than the first temperature, central controller controls heating rod 25 heats to be less than the 3rd power of the second power, when indoor temperature reaches the 3rd temperature higher than the second temperature, central controller controls heating rod 25 heats to be less than the 4th power of the 3rd power, when indoor temperature reaches the 4th temperature higher than the 3rd temperature, central controller controls heating rod 25 heats to be less than the 5th power of the 4th power, when indoor temperature reaches the 5th temperature higher than the 4th temperature, central controller stops heating by control heating rod 25.
For specific embodiment content described above, for example material of finned tube, coating, be equally also applicable to the embodiment of Fig. 7.
Although the present invention discloses as above with preferred embodiment, the present invention is not defined in this.Any those skilled in the art, without departing from the spirit and scope of the present invention, all can make various changes or modifications, so protection scope of the present invention should be as the criterion with claim limited range.
Claims (2)
1. the finned tube exchanger of an enclosed construction, the finned tube that comprises upper header, lower collector pipe and connection upper header and lower collector pipe, described finned tube comprises circular base tube and the first fin, the second fin, the extended line that the first fin and the second fin are arranged on outside and the first fin and second fin of base tube intersects at the central axis of base tube at the place, the center of circle of base tube, and the first fin and the second fin are symmetrical along the first level crossing picture by base tube central axis; Described finned tube comprises the 3rd fin and the 4th fin, and described the 3rd fin, the 4th fin are symmetrical with the first fin and the second fin mirror image respectively along the second plane, and described the second plane is vertical with the first plane and pass through the central axis of base tube; Between described the first fin and the second fin, the first brace is set, between described the 3rd fin and the 4th fin, the second brace is set, the first brace and the second brace are circular arc type metallic plate; The 3rd fin of the first fin, the second fin and adjacent fins pipe and the 4th fin form space; The central axis at place, the center of circle of described circular arc-shaped metal plate and the central axes of base tube; Described base tube is straight tube, and the central axis of described adjacent base tube is parallel to each other, and the inwall of base tube arranges inner fin, the direction of extending along inner fin, and the top of inner fin is arranged at intervals with otch; It is characterized in that, the pipe inside of described base tube arranges anticorrosive coat, and the outside of base tube is coated with coating rubbing-layer, and the thermal coefficient of expansion of anticorrosive coat, base tube and wearing layer increases successively.
2. finned tube exchanger according to claim 1, angle between described the first fin and the second fin is A, and the length of the first fin and the second fin is L, and the outer radius of base tube is R, fin height H on axial along base tube, above-mentioned four relation meets following formula:
Sin(A/2)=a×(L/R)
2+b×(L/R)+c
H/(R×10)=?e×Sin(A/2)
?2-f×Sin(A/2)+h；
Wherein, A unit is angle, 60 ° of <A<110 °,
L is of a size of mm, 12mm<L<80mm,
The unit of R is mm, 10mm<R<80mm,
The unit of H is mm, 800mm<H<1200mm,
A, b, c, e, f, h are coefficient, and the scope of a is 0.04-0.042, and the scope of b is 0.266-0.28, and the scope of c is 0.36-0.37, and the scope of e is 21-23, and the scope of f is 44-45, and h is 23-25.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410208275.4A CN104019491B (en) | 2013-10-16 | 2013-10-16 | Heat exchanger preventing layer shedding |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410208275.4A CN104019491B (en) | 2013-10-16 | 2013-10-16 | Heat exchanger preventing layer shedding |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310483171.XA Division CN103591828B (en) | 2013-10-16 | 2013-10-16 | Heat exchanger with internal finned tubes |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104019491A true CN104019491A (en) | 2014-09-03 |
| CN104019491B CN104019491B (en) | 2015-06-03 |
Family
ID=51436386
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410208275.4A Expired - Fee Related CN104019491B (en) | 2013-10-16 | 2013-10-16 | Heat exchanger preventing layer shedding |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104019491B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2478063Y (en) * | 2001-01-06 | 2002-02-20 | 营口港信铝材有限公司 | Fin hollowed aluminium alloy energy saving radiator |
| CN1403779A (en) * | 2002-10-11 | 2003-03-19 | 西安交通大学 | Internal thread heat-transferring pipe |
| CN1308642C (en) * | 2002-12-10 | 2007-04-04 | 松下电器产业株式会社 | Double-layer tube type heat exchanger |
-
2013
- 2013-10-16 CN CN201410208275.4A patent/CN104019491B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2478063Y (en) * | 2001-01-06 | 2002-02-20 | 营口港信铝材有限公司 | Fin hollowed aluminium alloy energy saving radiator |
| CN1403779A (en) * | 2002-10-11 | 2003-03-19 | 西安交通大学 | Internal thread heat-transferring pipe |
| CN1308642C (en) * | 2002-12-10 | 2007-04-04 | 松下电器产业株式会社 | Double-layer tube type heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104019491B (en) | 2015-06-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103591633B (en) | Electric-heating heat exchanger | |
| CN103471427B (en) | Finned tube radiator with flow guide structure | |
| CN103900401B (en) | Finned tube heat dissipation device with density of protrusions changing | |
| CN103528394B (en) | Arc-shaped sealing type finned tube radiator | |
| CN104019688B (en) | Aluminum alloy heat exchanger | |
| CN103486648B (en) | Automatic temperature-control heat dissipating device | |
| CN103542736A (en) | Inner-fin arc-shaped closed-type finned pipe radiator | |
| CN104697033B (en) | A kind of radiator of electrical heating power Intelligent adjustment | |
| CN103512391B (en) | Arc-shaped enclosed finned tube | |
| CN104019492B (en) | Heat exchanger with height of inner fins changing in flowing direction | |
| CN103471430B (en) | Fin tube with bulges inside | |
| CN103591828B (en) | Heat exchanger with internal finned tubes | |
| CN103884211B (en) | Fin tube radiator with changing bump height | |
| CN104713154B (en) | It is coated with the anticorrosive radiator of special anti-corrosion layer | |
| CN103542734B (en) | Enclosed arc finned tube radiator of different alloys | |
| CN104101247B (en) | Heat exchanger free from fins outside base tubes | |
| CN104019491B (en) | Heat exchanger preventing layer shedding | |
| CN104101242B (en) | Heat exchanger with header with gradually-changed flow area | |
| CN104019689B (en) | Heat exchanger allowing flow velocity to be controlled automatically | |
| CN103471428B (en) | Fin tube radiator | |
| CN103673673B (en) | Linear type closed finned tube | |
| CN103673061A (en) | Metal linear type closed type finned tube radiator | |
| CN103542735A (en) | Enclosed arc finned tube radiator with partial smooth tubes | |
| CN103697720A (en) | Inner fin linear type closed finned tube radiator | |
| CN103697721A (en) | Linear closed finned tubular radiator with anticorrosion coatings |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150603 Termination date: 20161016 |