CN105546848B - Solar water heater with collector pipe with inner fins with competitively-changed heights - Google Patents
Solar water heater with collector pipe with inner fins with competitively-changed heights Download PDFInfo
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- CN105546848B CN105546848B CN201511008812.1A CN201511008812A CN105546848B CN 105546848 B CN105546848 B CN 105546848B CN 201511008812 A CN201511008812 A CN 201511008812A CN 105546848 B CN105546848 B CN 105546848B
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 29
- 238000010521 absorption reaction Methods 0.000 claims abstract description 25
- 239000012530 fluid Substances 0.000 claims abstract description 24
- 239000011521 glass Substances 0.000 claims description 12
- 239000011148 porous material Substances 0.000 claims description 12
- 238000009413 insulation Methods 0.000 claims description 10
- 230000009467 reduction Effects 0.000 claims description 5
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000002035 prolonged effect Effects 0.000 abstract 1
- 238000002474 experimental method Methods 0.000 description 7
- 238000012546 transfer Methods 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000009826 distribution Methods 0.000 description 4
- 238000011161 development Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000003014 reinforcing effect Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000012774 insulation material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000005336 safety glass Substances 0.000 description 1
- 238000009738 saturating Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 238000004544 sputter deposition Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S10/00—Solar heat collectors using working fluids
- F24S10/90—Solar heat collectors using working fluids using internal thermosiphonic circulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
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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
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/44—Heat exchange systems
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a solar water heater. The solar water heater comprises a heat collector, and the heat collector comprises a collector pipe, and the collector pipe comprises a flat pipe and ribs; the flat pipe comprises parallel pipe walls and side walls, and the side walls are connected with the ends of the parallel pipe walls; a fluid channel is formed between the side walls and the parallel pipe walls, and the inner fins are arranged on the inner wall of a heat absorption end of the collector pipe; and the heights of the inner fins are continuously decreased at the heat absorption end in the direction from the middle portion of the cross section of the collector pipe to the two sides. According to the solar water heater, the inner fins are changed in the direction from the middle portion of the cross section of the heat absorption end to the two sides, heat absorption can be further strengthened and can be even, and the service life of the collector pipe is prolonged.
Description
Technical field
The invention belongs to field of solar energy, more particularly to a kind of solar water heater.
Background technology
With the high speed development of modern social economy, the mankind are increasing to the demand of the energy.But coal, oil, day
So the traditional energy storage level such as gas constantly reduce, it is increasingly in short supply, rising steadily for price is caused, while conventional fossil fuel is caused
Problem of environmental pollution it is also further serious, these all limit the development of society and the raising of human life quality significantly.The energy
Problem has become most one of distinct issues of contemporary world.Thus seek the new energy, particularly free of contamination cleaning energy
Source has become the focus of present people's research.
Solar energy is a kind of inexhaustible clean energy resource, and stock number is huge, and earth surface is received every year
Solar radiant energy total amount be 1 × 1018KWh, is consume gross energy in world's year more than 10,000 times.Countries in the world are all too
It is positive can by the use of important as new energy development, the Chinese government exists《The government work report》Also clearly propose already to accumulate
New forms of energy are developed in pole, and wherein the utilization of solar energy is especially in occupation of prominent position.Reach tellurian yet with solar radiation
Energy density is little（About one kilowatt per square metre）, and and be discontinuous, this brings certain tired to large-scale exploitation
It is difficult.Therefore, in order to extensively utilize solar energy, technical problem is not only solved, and is economically must be able to routine energy
Source mutually competes.
Generally, solar water heater is absorbed heat using thermal-collecting tube, but thermal-collecting tube is because heat transfer problem, may
The loss of heat conduction heat, and because thermal-collecting tube inside arranges fin, cause fluid resistance to rise, so as to cause the coefficient of heat transfer low
Problem.
Additionally, thermal-collecting tube heat absorbing end is in endothermic process, each position heat exchange amount of heat absorbing end is different, so as to cause local
Heat exchange is uneven.
For the problems referred to above, the invention provides a kind of new solar water heater, so as to solve the feelings of thermal-collecting tube heat absorption
The problem that the coefficient of heat transfer is low and its heat exchange is uneven under condition.
The content of the invention
The invention provides a kind of new solar energy system, so as to the technical problem for solving above to occur.
To achieve these goals, technical scheme is as follows：
A kind of solar water heater, including water tank, transparency glass plate, thermal insulation layer, absorption film and heat collector, the heat collector
Including thermal-collecting tube, the thermal-collecting tube includes heat absorbing end and release end of heat, and the release end of heat is arranged in water tank；The absorption film is arranged
In the one side towards the sun of thermal-collecting tube heat absorbing end, transparency glass plate is covered in the heat absorbing end top of thermal-collecting tube, heat absorbing end with it is saturating
Thermal insulation layer is set between bright glass plate；
The thermal-collecting tube includes flat tube and fin, and the flat tube includes tube wall parallel to each other and side wall, the side
Wall connects the end of parallel tube wall, fluid passage is formed between the side wall and the parallel tube wall, in the suction of thermal-collecting tube
Inner rib plate is set on the inwall of hot junction, and the inner rib plate is straight panel shape, and the bearing of trend of inner rib plate is along heat absorbing end to release end of heat
Direction.
Preferably, along heat absorbing end to the direction of release end of heat, inner rib plate height constantly increases.
Preferably, along heat absorbing end to the direction of release end of heat, the amplitude that inner rib plate highly increases is increasing.
Preferably, in heat absorbing end, along the centre of thermal-collecting tube cross section to both sides, the height of the inner rib plate constantly subtracts
It is few.
Preferably, in heat absorbing end, along the centre of thermal-collecting tube cross section to both sides, the height reduction of the inner rib plate
Amplitude constantly increases.
Preferably, the thermal-collecting tube release end of heat includes fin, the fin is arranged between tube wall, and the fin includes
Favour the sloping portion of tube wall, described sloping portion and parallel tube wall connection, the sloping portion by fluid passage that
This separates to form multiple passage aisles, and adjacent sloping portion connects on tube wall, the adjacent sloping portion and tube wall it
Between it is triangle；Intercommunicating pore is set on sloping portion, so that adjacent passage aisle communicates with each other, intercommunicating pore is isosceles three
Angular, the triangle constituted between the adjacent sloping portion and tube wall is isosceles triangle；
The drift angle of the isosceles triangle of intercommunicating pore is B, the isoceles triangle constituted between adjacent sloping portion and tube wall
The drift angle of shape is A, then meet equation below：
Sin(B)=a+b*sin(A/2) -c* sin(A/2)2；
Wherein a, b, c are parameters, wherein 0.565<a<0.559,1.645<b<1.753,1.778<c<1.883;
60°<A<160°；35°<B<90°.
9. solar water heater as claimed in claim 8, a=0.5931, b=1.6948, c=1.8432;
80°<A<120°；50°<B<60°.
Compared with prior art, solar water appliance of the invention has following advantage：
1）The present invention arranges inner rib plate inside thermal-collecting tube heat absorbing end, and inner rib plate is set to into straight panel shape and along suction
Hot junction to heat release extreme direction extends so that the fluid space formed between inner rib plate is consistent with the flow direction of fluid, from
And flow resistance is reduced, while also increasing reinforcing heat absorption.
2）By the height of inner rib plate the change along bearing of trend and the section along heat absorbing end middle part to two
The change of side, can cause further reinforcing heat absorption, and cause heat absorption uniform, extend the life-span of thermal-collecting tube.
3）The present invention on the fin of thermal-collecting tube release end of heat by arranging intercommunicating pore, it is ensured that the company between adjacent passage aisle
It is logical, solve the problems, such as that the internal pressure in the case of thermal-collecting tube heat exchange is uneven, heat exchange efficiency is improve, improve and use the longevity
Life.
4）By intercommunicating pore along the area change in flat tube cross-sectional direction, while resistance is reduced, further
Improve heat exchange efficiency.
5）The present invention is by substantial amounts of experiment, it is determined that the physical dimension of optimal flat thermal-collecting tube, so that ensureing
In the case of heat exchange resistance so that heat transfer effect reaches most preferably.
Description of the drawings
Fig. 1 is solar water heater cross section structure schematic diagram of the present invention；
Fig. 2 is thermal-collecting tube cross-sectional structure schematic diagram of the present invention；
Fig. 3 is the cross section structural representation at one thermal-collecting tube inner rib plate setting lead to the hole site of the present invention；
Fig. 4 is the schematic diagram that the present invention arranges through-hole structure sloping portion plane；
Fig. 5 is another schematic diagram that the present invention arranges through-hole structure sloping portion plane；
Fig. 6 is the triangle through hole structural representation of the present invention；
Fig. 7 is the cross-sectional view of thermal-collecting tube heat absorbing part of the present invention；
Fig. 8 is the cross-sectional view of currently preferred thermal-collecting tube heat absorbing part.
Reference is as follows：
1 thermal-collecting tube, 2 fluid passages, 3 tube walls, 4 sloping portions, 5 summits, 6 intercommunicating pores, 7 fins, 8 water tanks, 9 heat absorbing ends,
10 release end of heat, 11 base plates, 12 absorption films, 13 glass plates, 14 thermal insulation layers, 15 inner rib plates.
Specific embodiment
The specific embodiment of the present invention is described in detail below in conjunction with the accompanying drawings.
Herein, if without specified otherwise, being related to formula, "/" represents division, and "×", " * " represent multiplication.
The present invention relates to a kind of solar water heater, the structure of the solar water heater is as shown in figure 1, the solar energy
Water heater includes water tank 8 and heat collector, and the heat collector includes thermal-collecting tube 1, and the thermal-collecting tube 1 is flat hot pipe.The thermal-arrest
Pipe 1 includes heat absorbing end 9 and release end of heat 10, and the release end of heat 10 is arranged in water tank 8.Heat absorbing end 9 absorbs solar energy, by heat release
End 10 transfers heat to the water in water tank.
The solar thermal collector also includes transparency glass plate 13, thermal insulation layer 14, absorption film 12.Absorption film 12 is arranged on collection
Above the heat absorbing end 9 of heat pipe 1（I.e. towards the one side of the sun）, transparency glass plate 13 is covered in the front of the heat absorbing end 9 of thermal-collecting tube,
Thermal insulation layer 17 is left between heat absorbing end 9 and transparency glass plate 16, preferably, thermal insulation layer is vacuum layer.As preferably clear glass
Glass plate 16 adopts safety glass, thermal insulation layer for vacuum layer；Preferably, absorption film 12 is arranged on heat pipe 1 by way of sputtering
The front of heat absorbing end 9.
Base plate 11 is arranged on the bottom of thermal-collecting tube 1, and the base plate is insulation material.
Preferably, the thickness of thermal insulation layer 17 is 18mm～25mm；As preferably 20 mm.
As shown in Fig. 2 in release end of heat 10, the thermal-collecting tube includes flat tube 1 and fin 7, the flat tube 1 includes mutual
Parallel tube wall 3 and side wall 12, the side wall 12 connects the end of parallel tube wall 2, the side wall 12 and the parallel pipe
Fluid passage 2 is formed between wall 3, the fin 7 is arranged between tube wall 3, the fin 7 includes favouring the rake of tube wall
Divide 4, described sloping portion 4 connects with parallel tube wall 3, and the sloping portion 4 is spaced apart fluid passage 2 to form multiple
Passage aisle 10, adjacent sloping portion 4 connects on tube wall, and between the adjacent sloping portion 4 and tube wall 3 triangle is constituted
Shape；Intercommunicating pore 6 is set on sloping portion 4, so that adjacent passage aisle 10 communicates with each other.
By arranging intercommunicating pore 6, it is ensured that the connection between adjacent passage aisle 10, so that in the big passage aisle of pressure
Fluid can flow into the little passage aisle of neighbouring pressure, solve flat tube exchange heat in the case of internal pressure it is uneven
And the problem that local pressure is excessive, so as to promote abundant flowing of the fluid in heat exchanger channels, heat exchange efficiency is improve, together
When also improve the service life of thermal-collecting tube.
Preferably, the centre of the tube wall 3 along flat tube cross section（The centre of tube wall 3 i.e. in Fig. 2 cross-sectional views
Position）To both sides Ce Bi12 directions, the described area of through hole 6 on different sloping portions 4 constantly diminishes.Wherein, positioned at flat
The centre position of tube wall 3 in the centre position of flat pipe 1, i.e. Fig. 2 cross-sectional views, the area of through hole 6 is maximum.Main cause is
It is found through experiments, because fluid distribution is uneven, intermediate pressure is maximum, is gradually reduced to pressure at both sides from centre.Therefore it is logical
The distribution of hole area so that the fluid at middle part flows as far as possible to both sides, the flow resistance in the middle part of reduction, while in order to avoid opening
Hole area is excessive to cause the reduction of heat exchange area so that perforated area is changed according to pressure, while resistance is reduced,
Further improve heat exchange efficiency.
It is described logical on different sloping portions 4 preferably, along the centre of flat tube cross section to the direction of side wall 12
The amplitude that the area of hole 6 constantly diminishes is increasing.It is also the Changing Pattern for meeting flowing pressure by being arranged such, enters one
While step reduces flow resistance, heat exchange efficiency is improved.
Preferably, the intercommunicating pore 6 is shaped as isosceles triangle, the midpoint on the base of the isosceles triangle is to top
The direction at angle is identical with the flow direction of fluid.That is, the drift angle direction of isosceles triangle is fluid flow direction.Pass through
Experiment discovery, drift angle direction is set to be consistent with flow direction, can improve heat exchange efficiency, while reducing flowing resistance
Power.By being arranged such, 10% or so heat exchange efficiency can be improved, while reducing by 9% or so resistance.
Preferably, triangle between described adjacent sloping portion and tube wall is isosceles triangle, after
Referred to as the second isosceles triangle.By being set to isosceles triangle, it is ensured that flow of fluid is uniform, heat transfer effect is improved.
Preferably, the sloping portion summit 5 is plane, the summit 5 of two adjacent sloping portions 4 is connected,
The summit 5 is connected with tube wall 3.Because it is plane to arrange fixed point 5, hence in so that sloping portion 4 is big with tube wall contact area, from
And cause the more fully preferably contact of tube wall and sloping portion.So that install being more prone to, it is to avoid slide.
Preferably, in triangle between adjacent sloping portion 4 and tube wall, the relative interior table of sloping portion 4
The tie point in face forms vertex of a triangle, and the vertex of a triangle is located on tube wall.
As shown in fig. 6, the drift angle of the isosceles triangle is B, such as Fig. 4, it is same along the flow direction of fluid shown in 5
Individual sloping portion 4 arranges multiple rows of triangle through hole 6.As shown in figure 5, many exhausting holes 6 are shifted structure.
Find in an experiment, the area of through hole can not be excessive, it is excessive if can cause the loss of heat exchange area, reduce heat exchange
Efficiency, it is too small if, cause local pressure distribution it is still uneven, in the same manner, the distance of adjacent tube wall 3 can not be excessive, cross conference
Cause the reduction of heat exchange efficiency, it is too small that flow resistance can be caused excessive.According to experiment find, the drift angle of the first isosceles triangle and
The drift angle of the second isosceles triangle is the change of certain rule, and such as the second isosceles triangle drift angle becomes big, so as to cause heat exchange
The passage aisle area of passage increases, and corresponding flow resistance diminishes, therefore now the circulation area of the second isosceles triangle will
Diminish, can so reduce the area of through hole 6, while in the case of ensureing flow resistance, improving heat exchange efficiency.Therefore first etc.
There is following relation between lumbar triangle shape and the second isosceles triangle drift angle：
The drift angle of the first isosceles triangle is B, and the drift angle of the second isosceles triangle is A, then meet equation below：
Sin(B)=a+b*sin(A/2) -c* sin(A/2)2；
Wherein a, b, c are parameters, wherein 0.565<a<0.559,1.645<b<1.753,1.778<c<1.883;
60°<A<160°；35°<B<90°.
Preferably, a=0.5931, b=1.6948, c=1.8432;
80°<A<120°；50°<B<60°；
By above-mentioned formula, it may be determined that the optimal pass between the first isosceles triangle and the second isosceles triangle drift angle
System, ensure that in the case where flow resistance is met under here relation, reach optimal heat exchange efficiency.
Preferably, H=7-18mm.It is further used as preferably, 10<H<11mm.
Preferably, the length on the first isosceles triangle base is h, equation below is met：
0.28<d*（h/H）<0.36；Wherein d is parameter, 0.7<d<2.0；
H is with the distance between relative face of adjacent tube wall.
Preferably, 1.0<d<1.4.
Preferably, as drift angle is the increase of A, described d diminishes.
Preferably, with the increase of H, described d diminishes.
The width of tube wall be W, preferably 7.4>W/H>4.6, further preferably, 6.8>W/H>5.6.
One, by above-mentioned optimization design, can further improve the heat exchange property of thermal-collecting tube, while reducing flow resistance.
For sloping portion formed drift angle A it is different in the case of, for example along tube wall sidewall direction from middle part to both sides,
The less and less situation of included angle A that described adjacent sloping portion is formed, the A in formula above takes sloping portion adjacent
Two drift angles mean value calculating.
The present invention is the thousands of numerical simulations and test data by multiple various sizes of thermal-collecting tubes, is meeting work
Industry is required in the case of pressure-bearing（Below 10MPa）, in the case where maximum heat exchange amount is realized, the optimal flat tube wall for summing up
Dimensionally-optimised relation.
Preferably, the base of the adjacent isosceles triangle through hole of described same row is all on one wire, same row
Adjacent through hole distance is S1, the 2.9 × h<S1<3.3 × h, wherein S1 are with the bottom of two neighboring isosceles triangle through hole
The distance at the midpoint on side.Preferably 3.2 × h=S1.
Preferably, the base of the isosceles triangle of the through hole of adjacent row is parallel to each other, the summit of isosceles triangle is on earth
The distance at side midpoint be L, adjacent row apart from S2 be 3.8*L<S2<4.8*L.Preferably S2=4.4*L
When the base of the isosceles triangle of adjacent row is different, take the weighted average on two bases to calculate.
Preferably, the angle of the isosceles triangle of same row is identical with base.I.e. shape is identical, is equal
Shape.
For formula above, the through hole different for front and rear row size, also still it is suitable for.
Preferably, the wall thickness of fin is 0.5-0.9mm；Preferably, 0.6-0.7mm.
For the concrete dimensional parameters do not mentioned, it is designed according to normal heat exchanger.
The fin 7 is positioned only at release end of heat 10.
Preferably, such as Fig. 7, shown in 8, the setting inner rib plate 15 on the inwall of heat absorbing end 9 of thermal-collecting tube 1.
Preferably, the inner rib plate 15 is straight panel shape, the flowing of the bearing of trend of inner rib plate 15 along fluid evaporator
Direction, i.e., along heat absorbing end 9 to heat release extreme direction, in other words along the axial movement of thermal-collecting tube heat absorbing end 9.By so setting
Put so that the fluid space formed between inner rib plate is consistent with the flow direction of fluid, so as to reduce flow resistance, while
Also increase reinforcing heat absorption.
Preferably, along heat absorbing end 9 to heat release extreme direction, the height of inner rib plate 15 constantly increases, the width that height increases
Degree is increasing.By increasing the height of inner rib plate 15, so as to increase the heat exchange area of inner rib plate 15.Experiment finds, by such
Arrange, compared with fin height is identical, about 7% heat exchange efficiency can be improved.
Preferably, as shown in fig. 7, along the cross section of 1 heat absorbing end of thermal-collecting tube 10 centre to both sides, the inner rib plate 15
Height constantly reduce.Wherein, positioned at the centre position of the heat absorbing end 10 of thermal-collecting tube 1, the height highest of inner rib plate 15.
Because being found by experiment that, thermal-collecting tube heat absorbing end is most in middle part heat absorption, and from middle part to both sides, heat absorption gradually becomes
It is little, therefore by arranging the height change of inner rib plate 15 of thermal-collecting tube, so that the endotherm area of thermal-collecting tube heat absorbing end is at middle part
Maximum, it is minimum in both sides so that middle part heat absorption capacity is maximum, so meets the heat absorption rule of thermal-collecting tube heat absorbing end heat so that
On the whole the heat absorption of thermal-collecting tube heat absorbing end is uniform, it is to avoid thermal-collecting tube heat absorbing end local temperature is overheated, causes radiating effect excessively poor, causes
The shortening in thermal-collecting tube heat absorbing end life-span.
By above-mentioned setting, enable to middle part flow resistance and become big, more fluids to heat absorbing end both sides are distributed so that
Fluid distribution is more uniform.
Preferably, from centre to both sides, the amplitude that the height of the inner rib plate 15 is reduced constantly increases.
It is also the heat absorption rule for meeting thermal-collecting tube heat absorbing end by above-mentioned setting, further improves thermal-collecting tube heat absorbing end
Heat absorption efficiency, it is ensured that the overall heat absorption of thermal-collecting tube heat absorbing end is uniform, and temperature is uniform, increases the life-span of thermal-collecting tube.
Preferably, the thermal-collecting tube is gravity assisted heat pipe.
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 defined by claim limited range.
Claims (5)
1. a kind of solar water heater, including water tank, transparency glass plate, thermal insulation layer, absorption film and heat collector, the heat collector bag
Thermal-collecting tube is included, the thermal-collecting tube includes heat absorbing end and release end of heat, and the release end of heat is arranged in water tank；The absorption film is arranged on
The one side towards the sun of thermal-collecting tube heat absorbing end, transparency glass plate is covered in the heat absorbing end top of thermal-collecting tube, heat absorbing end with it is transparent
Thermal insulation layer is set between glass plate；
Characterized in that, the thermal-collecting tube includes flat tube and fin, the flat tube includes tube wall parallel to each other and side wall,
The side wall connects the end of parallel tube wall, fluid passage is formed between the side wall and the parallel tube wall, in thermal-arrest
Inner rib plate is set, and the inner rib plate is straight panel shape, the bearing of trend of inner rib plate is along heat absorbing end to putting on the heat absorbing end inwall of pipe
The direction in hot junction；
The thermal-collecting tube release end of heat includes fin, and the fin is arranged between tube wall, and the fin includes favouring tube wall
Sloping portion, described sloping portion connects with parallel tube wall, and the sloping portion is spaced apart fluid passage to form many
Individual passage aisle, adjacent sloping portion connects on tube wall, triangle between the adjacent sloping portion and tube wall；
Intercommunicating pore is set on sloping portion, so that adjacent passage aisle communicates with each other, intercommunicating pore is isosceles triangle, described adjacent
Sloping portion and tube wall between constitute triangle be isosceles triangle；
Along flat tube cross section tube wall centre to both sides sidewall direction, the connection hole area on different sloping portions is continuous
Diminish；
Along the centre of flat tube cross section to sidewall direction, the described via area on different sloping portions constantly diminishes
Amplitude it is increasing.
2. solar water heater as claimed in claim 1, in heat absorbing end, along the centre of thermal-collecting tube cross section to both sides, institute
The height for stating inner rib plate is constantly reduced.
3. solar water heater as claimed in claim 2, in heat absorbing end, along the centre of thermal-collecting tube cross section to both sides, institute
Stating the amplitude of the height reduction of inner rib plate constantly increases.
4. solar water heater as claimed in claim 1, the drift angle of the isosceles triangle of intercommunicating pore is B, adjacent rake
Point and tube wall between constitute isosceles triangle drift angle be A, then meet equation below：
Sin(B)=a+b*sin(A/2) -c* sin(A/2)2；
Wherein a, b, c are parameters, wherein 0.565<a<0.559,1.645<b<1.753,1.778<c<1.883;
60°<A<160°；35°<B<90°.
5. solar water heater as claimed in claim 4, a=0.5931, b=1.6948, c=1.8432;
80°<A<120°；50°<B<60°.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511008812.1A CN105546848B (en) | 2015-12-30 | 2015-12-30 | Solar water heater with collector pipe with inner fins with competitively-changed heights |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511008812.1A CN105546848B (en) | 2015-12-30 | 2015-12-30 | Solar water heater with collector pipe with inner fins with competitively-changed heights |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105546848A CN105546848A (en) | 2016-05-04 |
| CN105546848B true CN105546848B (en) | 2017-05-10 |
Family
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| CN111306815A (en) * | 2018-07-07 | 2020-06-19 | 青岛鑫众合贸易有限公司 | Solar water heater with variable interval of evaporation end stabilizing devices |
| CN111189238A (en) * | 2018-07-07 | 2020-05-22 | 青岛鑫众合贸易有限公司 | Solar water heater with density change of condensation end flow equalizing pipe |
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| CN102269538A (en) * | 2010-06-02 | 2011-12-07 | 日立电线株式会社 | Heat transfer tube for refrigerant and heat exchanger |
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| CN202188792U (en) * | 2011-07-26 | 2012-04-11 | 金龙精密铜管集团股份有限公司 | Heat exchanger and internal thread copper pipe thereof |
| EP2781873A1 (en) * | 2011-11-14 | 2014-09-24 | Choi, Sung-hwan | Heat exchange pipe and manufacturing method thereof |
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Address after: 210000 elegant building, No.91 Jiangdong North Road, Gulou District, Nanjing, Jiangsu Province Patentee after: Zhao Wei Address before: 266075 Shandong city of Qingdao province Fuzhou City Road No. 75 building A room 0201 Patentee before: Zhao Wei |
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Effective date of registration: 20191224 Address after: 213000 Zhixi industrial concentration zone, Jintan District, Changzhou City, Jiangsu Province (Longquan solar energy equipment factory) Patentee after: Jiangsu Longquan Solar Energy Technology Co.,Ltd. Address before: 210000 elegant building, No.91 Jiangdong North Road, Gulou District, Nanjing, Jiangsu Province Patentee before: Zhao Wei |
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Effective date of registration: 20210727 Address after: 213200 No. 8, jianerkang Road, Zhixi Town Industrial Park, Jintan District, Changzhou City, Jiangsu Province Patentee after: Changzhou Aohua new energy Co.,Ltd. Address before: 213000 Zhixi industrial concentration area, Jintan District, Changzhou City, Jiangsu Province (Longquan solar energy equipment factory) Patentee before: JIANGSU LONGQUAN SOLAR ENERGY TECHNOLOGY Co.,Ltd. |