CN105571348B - The heat exchanger that a kind of finned tube angle is gradually changed - Google Patents
The heat exchanger that a kind of finned tube angle is gradually changed Download PDFInfo
- Publication number
- CN105571348B CN105571348B CN201511008877.6A CN201511008877A CN105571348B CN 105571348 B CN105571348 B CN 105571348B CN 201511008877 A CN201511008877 A CN 201511008877A CN 105571348 B CN105571348 B CN 105571348B
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- Prior art keywords
- tube
- heat exchanger
- intercommunicating pore
- flat
- heat exchange
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Classifications
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- 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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel 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
- 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
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- 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
- F28F2215/08—Fins with openings, e.g. louvers
Abstract
The invention provides a kind of heat exchanger, the heat exchanger includes two headers and the heat exchanger tube being arranged between two headers；The heat exchanger tube is flat heat exchange tube, the fin is arranged in flat tube, the fin includes sloping portion, be spaced apart for fluid passage to form multiple passage aisles by the sloping portion, the angle that adjacent sloping portion is formed is A, included angle A in different flat heat exchange tubes it is of different sizes, as the distance apart from inlet tube is more remote, the included angle A that the sloping portion in described flat heat exchange tube is formed is increasing.The present invention is by setting included angle A with the change apart from inlet tube so that fluid, so that fluid is evenly distributed in heat exchanger tube, improves heat exchange efficiency to the small heat exchange Bottomhole pressure remote apart from inlet tube of flow resistance, improves service life.
Description
Technical field
The present invention relates to heat exchanger, more particularly, to a kind of shell-and-tube heat exchanger.
Background technology
Flat tube was widely used in automotive air conditioning units and house or commercial air-conditioner heat exchanger in recent years.It is this kind of flat
Pipe inside sets multiple small passages, and when in use, heat exchanging fluid flows through the multiple passages in flat tube.Because flat tube exchanges heat
Area is big, therefore, it is possible to greatly improve heat transfer effect.
In the prior art, assignment of traffic is uneven to ask because causing apart from inlet tube near-far problem to there is heat exchanger tube
Topic, for example, nearer apart from inlet tube, fluid flow is more in heat exchanger tube, and more remote apart from inlet tube, and heat exchanger tube fluid flow is just
It is fewer.Prior art is all utilized in being provided with assignment of traffic in header and loses or pressure distribution member, by flow or
The mode of pressure distribution causes in heat exchanger tube that assignment of traffic is uniform, but causes the part to increase, and manufacture is difficult, cost increase.
The invention provides a kind of new assignment of traffic measure so that assignment of traffic is uniform in whole Tube Sheet of Heat Exchanger.
Regarding to the issue above, the invention provides a kind of new shell-and-tube heat exchanger, so as to solve the feelings of heat exchanger tube heat exchange
The uneven problem of internal pressure under condition.
The content of the invention
The invention provides a kind of new flat tube heat exchanger, so as to solve the technical problem for above occurring.
To achieve these goals, technical scheme is as follows：
A kind of heat exchanger, the heat exchanger includes upper lower header and the heat exchanger tube being arranged between lower header；It is described
Heat exchanger tube is flat heat exchange tube, including flat tube and fin, and the flat tube includes side wall and tube wall parallel to each other, the side
Wall connects the end of parallel tube wall, and fluid passage is formed between the side wall and the parallel tube wall, and the fin is set
Between tube wall, the fin includes favouring the sloping portion of tube wall, and described sloping portion is connected with tube wall, the inclination
Be spaced apart for fluid passage to form multiple passage aisles by part；Intercommunicating pore is set on sloping portion, so that adjacent is small logical
Road communicates with each other；The heat exchanger includes inlet tube, and the inlet tube is arranged on upper header, what adjacent sloping portion was formed
Angle is A, it is characterised in that：Included angle A in different flat heat exchange tubes it is of different sizes, as the distance apart from inlet tube is got over
Far, the included angle A that the sloping portion in described flat heat exchange tube is formed is increasing.
Preferably, as the distance apart from inlet tube is more remote, what the sloping portion in described flat heat exchange tube was formed
Included angle A becomes big amplitude more and more higher.
Preferably, the intercommunicating pore is shaped as the first isosceles triangle；Adjacent sloping portion is connected on tube wall,
Triangle between adjacent sloping portion and tube wall, triangle between adjacent sloping portion and tube wall is
Two isosceles triangles, adjacent sloping portion is the waist of the second isosceles triangle；The drift angle of the first isosceles triangle is B, second
The drift angle of 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 0.58<a<0.59,1.65<b<1.75,1.78<c<1.85;
50°<A<150°；30°<B<80°.
Preferably, a=0.5849, b=1.6953, c=1.8244;
80°<A<120°；50°<B<60°.
Compared with prior art, flat heat exchange tube of the invention has the following advantages：
1）The present invention is by setting included angle A with the change apart from inlet tube so that fluid is to the small distance of flow resistance
The remote heat exchange Bottomhole pressure of inlet tube, so that fluid is evenly distributed in heat exchanger tube.
2）The present invention on the fin of flat tube by setting intercommunicating pore, it is ensured that the connection between adjacent passage aisle, solution
The uneven problem of internal pressure in the case that certainly flat tube exchanges heat, improves heat exchange efficiency, improves service life.
3）The present invention along the change of flowing, that is, ensures rational in heat exchanger tube by the rational size for determining intercommunicating pore
Pressure, ensures to reach fully heat exchange again.
4）The present invention is by substantial amounts of experiment, it is determined that the physical dimension of optimal flat heat exchange tube, so that ensureing
In the case of heat exchange resistance so that heat transfer effect reaches most preferably.
Brief description of the drawings
Fig. 1 is the structural representation of present invention heat exchanger；
Fig. 2 is flat tube cross-sectional structure schematic diagram of the present invention；
Fig. 3 is the structural representation of the flat tube cross section that present invention outside sets fin；
Fig. 4 is the structural representation in the cross section that one flat tube inner fin of the present invention sets connection hole location；
Fig. 5 is the improved structure schematic diagram that present invention outside sets outer fin flat tube cross section；
Fig. 6 is the schematic diagram that the present invention sets intercommunicating pore structure sloping portion plane；
Fig. 7 is another schematic diagram that the present invention sets intercommunicating pore structure sloping portion plane；
Fig. 8 is triangle intercommunicating pore structure schematic diagram of the invention.
Reference is as follows：
1 flat tube, 2 fluid passages, 3 tube walls, 4 sloping portions, 5 summits, 6 intercommunicating pores, 7 fins, 8 upper collecting chambers, 9 next parts
Case, 10 passage aisles, 11 outside fins, 12 side walls, 13 inlet tubes, 14 outlets.
Specific embodiment
Specific embodiment of the 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.
A kind of heat exchanger, as shown in figure 1, the heat exchanger includes upper collecting chamber 8 and lower header 9 and is arranged on lower header
Heat exchanger tube between 8,9.Fin 11 is set between the heat exchanger tube.The heat exchanger can widely use such as automobile heat exchange
Device, air-conditioning heat exchanger etc..
As shown in Fig. 2 the heat exchanger tube is flat heat exchange tube, including 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, and the side wall 12 is parallel with described
Fluid passage 2 is formed between tube wall 3, the fin 7 is arranged between tube wall 3, the fin 7 includes favouring the inclination of tube wall
Part 4, described sloping portion 4 is connected with parallel tube wall 3, and be spaced apart for fluid passage 2 to form many by the sloping portion 4
Individual passage aisle 10, adjacent sloping portion 4 is connected on tube wall, and three are constituted between the adjacent sloping portion 4 and tube wall 3
It is angular；Intercommunicating pore 6 is set on sloping portion 4, so that adjacent passage aisle 10 communicates with each other.
Preferably, the side wall 2 is arc-shaped.
By setting 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 in the small passage aisle of neighbouring pressure flow, solve flat tube exchange heat in the case of internal pressure it is uneven
And the excessive problem of local pressure, 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 heat exchanger tube.
Preferably, same sloping portion 4 sets multiple intercommunicating pores 6, along the flow direction of fluid, described connection
The area in hole 6 is increasing.
It is found through experiments that, by becoming larger for area, compared with area is identical, can further reduces flowing
Resistance, can reduce about 10% or so flow resistance, but heat exchange efficiency is not substantially reduced.
Preferably, along the flow direction of fluid, the amplitude that the area change of intercommunicating pore 6 is big is increasing.By experiment
It was found that, the amplitude that the change of the area of intercommunicating pore 6 is big is increasing, it is ensured that in the case of heat exchange efficiency, further reduce stream
Dynamic resistance, can about reduce by 5% or so flow resistance.
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 intercommunicating pore 6 on different sloping portions 4 constantly diminishes.Wherein, it is located at
The centre position of tube wall 3 in the centre position of flat tube 1, i.e. Fig. 2 cross-sectional views, the area of intercommunicating pore 6 is maximum.It is main former
Because being to be found through experiments that, because fluid distribution is uneven, intermediate pressure is maximum, is gradually reduced to pressure at both sides from centre.Cause
The distribution of this connection hole area so that the fluid at middle part flows to both sides as far as possible, the flow resistance in the middle part of reduction, while in order to
Avoid the excessive reduction for causing heat exchange area of perforated area so that perforated area is changed according to pressure, reduce resistance
While, further improve heat exchange efficiency.
Preferably, along the centre of flat tube cross section to the direction of side wall 12, the described company on different sloping portions 4
The amplitude that the area of through hole 6 constantly diminishes is increasing.It is also the Changing Pattern for meeting flowing pressure by being arranged such, enters
While one step reduction flow resistance, heat exchange efficiency is improved.
Preferably, the intercommunicating pore 6 is shaped as isosceles triangle, the midpoint to top on the base of the isosceles triangle
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, two adjacent fixed points of sloping portion 45 are connected,
The summit 5 is connected with tube wall 3.Because it is plane to set 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 installation is 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
Face forms vertex of a triangle, and the vertex of a triangle is located on tube wall.
The flow direction of fluid is from left to right in Fig. 6.But left and right herein is the stream for illustrating fluid along intercommunicating pore
Dynamic direction, is not offered as actual certain left and right flowing.
Preferably, isosceles triangle base midpoint to drift angle length be L.
As shown in figure 8, the drift angle of the isosceles triangle is B, as shown in fig. 6, along the flow direction of fluid, it is same
Sloping portion 4 sets multiple triangle intercommunicating pores 6.Preferably, along the flow direction of fluid, same sloping portion 4 sets
Multiple intercommunicating pores 6 are put, along the flow direction of fluid, in the case where base length keeps constant, described intercommunicating pore drift angle B
It is less and less.It is found through experiments that, by tapering into for intercommunicating pore drift angle B, compared with drift angle B is identical, it is ensured that
In the case of heat exchange efficiency, flow resistance is further reduced, can about reduce by 7% or so flow resistance.
Preferably, along the flow direction of fluid, the amplitude that drift angle B diminishes is increasing.It is found through experiments that, drift angle
The amplitude that B diminishes is increasing, it is ensured that in the case of heat exchange efficiency, further reduces flow resistance, can about reduce
4% or so flow resistance.
Preferably, along the flow direction of fluid, same sloping portion sets multiple rows of intercommunicating pore 6, as shown in Figures 6 and 7,
Often row's the distance between intercommunicating pore is S2, and it with the base of the intercommunicating pore of adjacent row is to calculate distance that the S2 is.
Preferably, as shown in fig. 7, multiple rows of intercommunicating pore 6 is shifted structure.
Find in an experiment, the area of intercommunicating pore can not be excessive, it is excessive if the loss of heat exchange area, reduction can be caused to change
The thermal efficiency, it is too small if, cause local pressure distribute it is still uneven, similarly, the distance of adjacent tube wall 3 can not be excessive, excessive
The reduction of heat exchange efficiency can be caused, it is too small that flow resistance can be caused excessive.Found according to experiment, the drift angle of the first isosceles triangle
It is the change of certain rule with the drift angle of the second isosceles triangle, such as the second isosceles triangle drift angle becomes big, so as to cause to change
The passage aisle area of the passage of heat increases, and corresponding flow resistance diminishes, therefore now the circulation area of the second isosceles triangle is just
Diminish, can so reduce the area of intercommunicating pore 6, while in the case of ensureing flow resistance, improving heat exchange efficiency.Therefore the
There is following relation between one isosceles triangle 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 0.58<a<0.59,1.65<b<1.75,1.78<c<1.85;
50°<A<150°；30°<B<80°.
Preferably, a=0.5849, b=1.6953, c=1.8244;
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 relation herein, reach optimal heat exchange efficiency.
Preferably, H=7-15mm.It is further used as preferably, 9<H<12mm.
Preferably, the length on the first isosceles triangle base is h, equation below is met：
0.25<d*（h/H）<0.38；Wherein d is parameter, 0.5<d<1.8；
H is with the distance between relative face of adjacent tube wall.
Preferably, 0.8<d<1.2.
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 is 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 heat exchanger tube, while reducing flow resistance.
The present invention is, by the thousands of numerical simulations and test data of multiple various sizes of heat exchanger tubes, to meet work
In the case of industry requirement 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.
For intercommunicating pore size along fluid flow direction or along from the centre of heat exchanger tube cross section tube wall to side wall 2
In the case of changing, also still it is applied to above-mentioned formula, by regulation coefficient or other intercommunicating pore sizes can be selected
To meet.
Preferably, the base of the adjacent isosceles triangle intercommunicating pore of described same row is all on one wire, it is same
The adjacent intercommunicating pore distance of row is S1, the 2.9 × h<S1<3.3 × h, wherein S1 are connected with two neighboring isosceles triangle
The distance at the midpoint on the base in hole.Preferably 3.2 × h=S1.
Preferably, the base of the isosceles triangle of the intercommunicating pore of adjacent row is parallel to each other, the summit of isosceles triangle is arrived
The distance at base 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, two weighted average on base are taken 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 intercommunicating pore different for front and rear row size is also still applicable.
Preferably, the wall thickness of fin is 0.6-1.1mm；Preferably, 0.8-1.0mm.
For the specific dimensional parameters do not mentioned, it is designed according to normal heat exchanger.
Preferably, as shown in Fig. 2 the outside of tube wall 3 in flat tube 1 sets fin 11.
Preferably, the fin is straight panel shape, the bearing of trend of fin along fluid flow direction, i.e., such as Fig. 2 institutes
Show, along perpendicular to the direction of paper.
Preferably, along the flow direction of fluid, the height of outside fin 11 constantly increases, and highly increased amplitude is got over
Come bigger.By increasing fin height, so as to increase the heat exchange area of fin.Experiment finds, high with fin by being arranged such
The identical heat exchange efficiency compared, about 5% can be improved of degree.
Preferably, as shown in figure 5, along the centre of the cross section of flat tube 1 to both sides, the height of the fin 11 is continuous
Reduce.Wherein, positioned at the centre position of flat tube 1, the height highest of fin.
Because being found by experiment that, flat tube is most in middle part radiating, and from middle part to both sides, radiating is tapered into, therefore
By the outside fin height change for setting flat tube, so that the area of dissipation of flat tube is maximum at middle part, in both sides most
It is small so that middle part heat-sinking capability is maximum, so meets the heat dissipation law of flat tubular heat so that flat tube radiating is equal on the whole
It is even, it is to avoid flat tube local temperature is overheated, and causes radiating effect excessively poor, causes the shortening of flat tube lifetime.
It is preferred that, the heat exchanging fluid is water.
Preferably, the heat exchanger includes inlet tube 13 and outlet 14, the inlet tube 13 is arranged on upper header 8
On, outlet 14 is arranged in lower collector pipe 9.Preferably, the inlet tube 13 and outlet 14 are arranged on the same of heat exchanger
Side, for example, being all disposed within heat exchanger left side as shown in Figure 1.
Preferably, inlet tube 13 is arranged on the upper position of the side of upper header 8, outlet 14 is arranged on lower collector pipe 9
The lower position of side.
Preferably, the area of the intercommunicating pore 6 in different flat tubes is different, as the distance apart from inlet tube 13 is got over
Far, the area of the intercommunicating pore 6 in described flat tube is bigger.By being arranged such so that nearer apart from inlet tube 13, then because
The area of intercommunicating pore 6 is smaller, then cause the resistance of flow of fluid to become big, so that fluid is in the small heat exchanger tube of flow resistance
Flowing so that fluid gets over the heat exchange Bottomhole pressure of distant positions towards the distance apart from inlet tube 13, so that fluid distribution is equal
It is even.
Preferably, as the distance apart from inlet tube 13 is more remote, such as pipe a, b, c, d, e, the f distance in Fig. 1 is entered
Mouth pipe 13 is more and more remote, and the area of the intercommunicating pore 6 in described flat tube becomes big amplitude more and more higher.It is found through experiments that,
Become the increase of big amplitude by area, enable to fluid distribution more uniform.That is the area of pipe a intercommunicating pores 6<Pipe b is connected
The area in hole 6<The area of pipe c intercommunicating pores 6<The area ... of pipe d intercommunicating pores 6, the rest may be inferred.
The area of the intercommunicating pore 6 in the heat exchanger tube of the farthest of inlet tube 13 is the heat exchange apart from inlet tube 13 most nearby
1.4-1.6 times of the area of the intercommunicating pore 6 in pipe, preferably 1.5 times.
Preferably, the quantity of the intercommunicating pore 6 in every heat exchanger tube is identical.
Preferably, the quantity of the intercommunicating pore 6 on each sloping portion is identical.A piece area for the intercommunicating pore of flat tube 6
Calculated using all intercommunicating pore gross areas are changed on flat tube.
Preferably, the distributed quantity of the intercommunicating pore 6 in different flat tubes is different, with the distance apart from inlet tube 13
More remote, the distributed quantity of the intercommunicating pore 6 in described flat tube is more and more.By being arranged such so that apart from inlet tube 13
Nearer, then because the distributed quantity of intercommunicating pore 6 is few, the circulation area between passage aisle is smaller, then cause the resistance of flow of fluid
Become big, so that fluid is to the small heat exchange Bottomhole pressure of flow resistance so that fluid is got over towards the distance apart from inlet tube 13
The heat exchange Bottomhole pressure of distant positions, so that fluid distribution is uniform.
Preferably, as the distance apart from inlet tube 13 is more remote, the distributed quantity of the intercommunicating pore 6 in described flat tube
Become many amplitude more and more highers.It is found through experiments that, the increase of big amplitude is become by area, enables to fluid distribution more
Uniformly.
The area of the intercommunicating pore 6 in the heat exchanger tube of the farthest of inlet tube 13 is the heat exchange apart from inlet tube 13 most nearby
1.4-1.6 times of the distributed quantity of the intercommunicating pore 6 in pipe, preferably 1.5 times.
It is preferred that, the area of each intercommunicating pore 6 is identical.
Preferably, included angle A in different flat tubes is of different sizes.As the distance apart from inlet tube 13 is more remote,
The included angle A that sloping portion 4 in described flat tube is formed is increasing.By being arranged such so that got over apart from inlet tube 13
Closely, then because diminishing for included angle A, causes the circulation area of passage aisle smaller, then the resistance of flow of fluid is caused to become big, so that
Fluid is obtained to the small heat exchange Bottomhole pressure of flow resistance so that fluid gets over the heat exchange of distant positions towards the distance apart from inlet tube 13
Bottomhole pressure, so that fluid distribution is uniform.
Preferably, as the distance apart from inlet tube 13 is more remote, the folder that the sloping portion 4 in described flat tube is formed
Angle A becomes big amplitude more and more higher.It is found through experiments that, the increase of big amplitude is become by A, enables to fluid distribution more
Uniformly.
It is preferred that, the same included angle A of the intercommunicating pore of flat tube 6 is calculated using average angle, i.e., by multiple angles
Weighted average is calculated.
It is preferred that, the included angle A of same all intercommunicating pores 6 of flat tube is equal.
Preferably, the base length h of the isosceles triangle intercommunicating pore 6 of all heat exchanger tubes is equal, in different flat tubes
Drift angle B it is of different sizes.As the distance apart from inlet tube 13 is more remote, isosceles triangle intercommunicating pore in described flat tube
Drift angle B is less and less.By being arranged such so that nearer apart from inlet tube 13, then because the change of drift angle B is big, intercommunicating pore 6 is caused
Circulation area it is smaller, then cause the resistance of flow of fluid to become big, so that fluid flows in the small heat exchanger tube of flow resistance
It is dynamic so that fluid gets over the heat exchange Bottomhole pressure of distant positions towards the distance apart from inlet tube 13, so that fluid distribution is uniform.
Preferably, as the distance apart from inlet tube 13 is more remote, isosceles triangle intercommunicating pore in described flat tube
Drift angle B less and less amplitude more and more higher.It is found through experiments that, the increase of the amplitude diminished by drift angle B, enables to stream
Body distribution is more uniform.
It is preferred that, the drift angle B of the same intercommunicating pore of flat tube 6 is calculated using average drift angle, i.e., by multiple drift angles
Weighted average is calculated.
It is preferred that, the drift angle B of all intercommunicating pores 6 in same flat tube is equal.
Preferably, the L of the isosceles triangle intercommunicating pore 6 of all heat exchanger tubes is equal, the bottom side length in different flat tubes
Degree h's is of different sizes, as the distance apart from inlet tube 13 is more remote, the base of isosceles triangle intercommunicating pore in described flat tube
Length h is increasing.By being arranged such so that nearer apart from inlet tube 13, then because base length h's diminishes, the company of causing
The circulation area of through hole 6 is smaller, then cause the resistance of flow of fluid to become big, so that fluid is to the small heat exchanger tube of flow resistance
Interior flowing so that fluid gets over the heat exchange Bottomhole pressure of distant positions towards the distance apart from inlet tube 13, so that fluid distribution
Uniformly.
Preferably, as the distance apart from inlet tube 13 is more remote, isosceles triangle intercommunicating pore in described flat tube
Base length h increasing amplitude more and more higher.It is found through experiments that, the increase of big amplitude, energy is become by base length h
Enough so that fluid distribution is more uniform.
It is preferred that, the base length h of the same intercommunicating pore of flat tube 6 is calculated using average drift angle, i.e., by multiple bottoms
The weighted average of edge lengths h is calculated.
It is preferred that, the base length h of same all intercommunicating pores 6 of flat tube is equal.
Preferably, same sloping portion sets multiple rows of intercommunicating pore 6, as shown in Figures 3 and 4, often arrange between intercommunicating pore away from
From being S2, the S2's in different flat tubes is of different sizes, and as the distance apart from inlet tube 13 is more remote, described S2 is increasingly
It is small.By being arranged such so that nearer apart from inlet tube 13, then because S2 is bigger, cause the circulation area of intercommunicating pore 6 smaller,
Then cause the resistance of flow of fluid to become big, so that fluid is to the small heat exchange Bottomhole pressure of flow resistance so that fluid towards
The heat exchange Bottomhole pressure of distant positions is got over apart from the distance of inlet tube 13, so that fluid distribution is uniform.
Preferably, as the distance apart from inlet tube 13 is more remote, S2 less and less amplitude more and more higher.By experiment
It was found that, the increase of the amplitude diminished by S2 enables to fluid distribution more uniform.
It is preferred that, the same S2 of the intercommunicating pore of flat tube 6 is calculated using average drift angle, i.e., put down by the weighting of multiple S2
Calculate.
It is preferred that, the S2 of same all intercommunicating pores 6 of flat tube is equal.
Preferably, the base of the adjacent isosceles triangle intercommunicating pore of described same row is all on one wire, it is same
The adjacent intercommunicating pore distance of row is S1, and the S1's in different flat tubes is of different sizes, as the distance apart from inlet tube 13 is got over
Far, described S1 is less and less.By being arranged such so that nearer apart from inlet tube 13, then because S1 is bigger, intercommunicating pore is caused
6 circulation area is smaller, then cause the resistance of flow of fluid to become big, so that fluid flows in the small heat exchanger tube of flow resistance
It is dynamic so that fluid gets over the heat exchange Bottomhole pressure of distant positions towards the distance apart from inlet tube 13, so that fluid distribution is uniform.
Preferably, as the distance apart from inlet tube 13 is more remote, S1 less and less amplitude more and more higher.By experiment
It was found that, the increase of the amplitude diminished by S1 enables to fluid distribution more uniform.
It is preferred that, the same S1 of the intercommunicating pore of flat tube 6 is calculated using average drift angle, i.e., put down by the weighting of multiple S1
Calculate.
It is preferred that, the S1 of same all intercommunicating pores 6 of flat tube is equal.
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
It is defined when by claim limited range.
Claims (2)
1. a kind of heat exchanger, the heat exchanger includes upper lower header and the heat exchanger tube being arranged between lower header；It is described to change
Heat pipe is flat heat exchange tube, including flat tube and fin, and the flat tube includes side wall and tube wall parallel to each other, the side wall
The end of the parallel tube wall of connection, forms fluid passage between the side wall and the parallel tube wall, the fin is arranged on
Between tube wall, the fin includes favouring the sloping portion of tube wall, and described sloping portion is connected with tube wall, the rake
Divide and be spaced apart fluid passage to form multiple passage aisles；Intercommunicating pore is set on sloping portion, so that adjacent passage aisle
Communicate with each other；The heat exchanger includes inlet tube, and the inlet tube is arranged on upper header, it is characterised in that：Same rake
Set up separately and put multiple rows of intercommunicating pore, it is S2 often to arrange the distance between intercommunicating pore, and the S2's in the different flat pipes of flat heat exchange is of different sizes, with
S2 more remote apart from the distance of inlet tube, described less and less；The distance between intercommunicating pore on same heat exchanger tube S2 is equal；
The side wall is arc-shaped.
2. heat exchanger as claimed in claim 1, it is characterised in that as the distance apart from inlet tube is more remote, S2 is less and less
Amplitude more and more higher.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511008877.6A CN105571348B (en) | 2015-12-30 | 2015-12-30 | The heat exchanger that a kind of finned tube angle is gradually changed |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511008877.6A CN105571348B (en) | 2015-12-30 | 2015-12-30 | The heat exchanger that a kind of finned tube angle is gradually changed |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105571348A CN105571348A (en) | 2016-05-11 |
| CN105571348B true CN105571348B (en) | 2017-05-31 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201511008877.6A Expired - Fee Related CN105571348B (en) | 2015-12-30 | 2015-12-30 | The heat exchanger that a kind of finned tube angle is gradually changed |
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| CN (1) | CN105571348B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112283794B (en) * | 2020-10-28 | 2023-12-12 | 青岛海信日立空调系统有限公司 | Indoor air conditioner and fin production method |
| CN113804021B (en) * | 2020-12-18 | 2023-12-26 | 国网山东综合能源服务有限公司 | Shell-and-tube heat exchanger with linear drainage plate with total radian changing along length |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10041919C1 (en) * | 2000-08-25 | 2001-10-31 | Wieland Werke Ag | Internally finned heat exchange tube has fins in individual zones arranged so that adjacent zones have fins offset at zone transition |
| CN101738011B (en) * | 2009-12-15 | 2012-11-21 | 清华大学 | Microfine multi-channel heat pump type air-conditioner heat exchanger with automatic liquid distribution structure |
| JP2014119244A (en) * | 2012-12-19 | 2014-06-30 | Mazda Motor Corp | Heat exchanger |
| CN204142069U (en) * | 2014-10-08 | 2015-02-04 | 贵州晟泰铝业有限公司 | A kind of aluminum heat radiating flat tube |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070012430A1 (en) * | 2005-07-18 | 2007-01-18 | Duke Brian E | Heat exchangers with corrugated heat exchange elements of improved strength |
-
2015
- 2015-12-30 CN CN201511008877.6A patent/CN105571348B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10041919C1 (en) * | 2000-08-25 | 2001-10-31 | Wieland Werke Ag | Internally finned heat exchange tube has fins in individual zones arranged so that adjacent zones have fins offset at zone transition |
| CN101738011B (en) * | 2009-12-15 | 2012-11-21 | 清华大学 | Microfine multi-channel heat pump type air-conditioner heat exchanger with automatic liquid distribution structure |
| JP2014119244A (en) * | 2012-12-19 | 2014-06-30 | Mazda Motor Corp | Heat exchanger |
| CN204142069U (en) * | 2014-10-08 | 2015-02-04 | 贵州晟泰铝业有限公司 | A kind of aluminum heat radiating flat tube |
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| Publication number | Publication date |
|---|---|
| CN105571348A (en) | 2016-05-11 |
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Inventor after: Zhao Wei Inventor before: Zhao Wei Inventor before: Chen Yan Inventor before: Wang Qi |
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Effective date of registration: 20170410 Address after: 266199 Licang, Qingdao Province, No. nine East Road, No. 599, No. Applicant after: QINGAO VOCATIONAL AND TECHNICAL COLLEGE OF HOTEL MANAGEMENT Address before: 266075 Shandong city of Qingdao province Fuzhou City Road No. 75 building A room 0201 Applicant before: Zhao Wei |
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Granted publication date: 20170531 Termination date: 20191230 |