CN103930747B - Plate fin and tube type heat exchanger and there is the refrigerated air-conditioning system of this plate fin and tube type heat exchanger - Google Patents
Plate fin and tube type heat exchanger and there is the refrigerated air-conditioning system of this plate fin and tube type heat exchanger Download PDFInfo
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- CN103930747B CN103930747B CN201280052472.0A CN201280052472A CN103930747B CN 103930747 B CN103930747 B CN 103930747B CN 201280052472 A CN201280052472 A CN 201280052472A CN 103930747 B CN103930747 B CN 103930747B
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- 238000004378 air conditioning Methods 0.000 title claims description 23
- 238000003466 welding Methods 0.000 claims description 55
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- 238000007254 oxidation reaction Methods 0.000 description 7
- 230000006866 deterioration Effects 0.000 description 6
- 230000009467 reduction Effects 0.000 description 6
- 239000003507 refrigerant Substances 0.000 description 6
- 230000032683 aging Effects 0.000 description 5
- 239000007788 liquid Substances 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000004927 fusion Effects 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 238000012546 transfer Methods 0.000 description 4
- PNEYBMLMFCGWSK-UHFFFAOYSA-N Alumina Chemical compound [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 description 3
- 230000009471 action Effects 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 3
- 229910000679 solder Inorganic materials 0.000 description 3
- 239000004411 aluminium Substances 0.000 description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
-
- 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
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
-
- 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
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
-
- 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
- F28F2215/12—Fins with U-shaped slots for laterally inserting 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
- F28F2275/00—Fastening; Joining
- F28F2275/06—Fastening; Joining by welding
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
The present invention relates to a kind of plate fin and tube type heat exchanger, on the surface of flat tube (51) and fin (52), be formed and the valley of the mountain portion of minimum altitude and lowest depth linked and the length that obtains is more than 10 μm concavo-convex.
Description
Technical field
The present invention relates to and heat-transfer pipe is inserted the multi-disc plate-shaped fins arranged at predetermined intervals and the plate fin and tube type heat exchanger formed and the refrigerated air-conditioning system with this plate fin and tube type heat exchanger.
Background technology
In the past, there is following plate fin and tube type heat exchanger, being such as the heat-transfer pipe (hereinafter referred to as flat tube) of flat by section shape, by being formed with flat tube equal number and the otch of same intervals along plate face length direction of principal axis, inserting the plate-shaped fins arranged at predetermined intervals.And plate-shaped fins adopts corrugated and makes the heat exchanger of the ripple fin and tube type of flat tube and fin contacts generally be used to (for example, referring to patent documents 1) such as such as mobile applications in wavy mountain valley.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2001-296088 publication (Fig. 1, Fig. 2 etc.)
Summary of the invention
The problem that invention will solve
The heat exchanger of ripple fin and tube type is applicable to the condenser of freeze cycle, but has inappropriate part as evaporimeter use.This is because, when the heat exchanger of ripple fin and tube type is utilized as evaporimeter, when carrying out heat exchange with air, when the temperature of the cold-producing medium of flat Bottomhole pressure is reduced to the dew point of air, moisture in air condenses on heat exchanger surface, produces dew (drain water).If the dew produced on heat exchanger surface from fin end face or flat tube surface by promptly draining, special problem would not be caused.
But, when the heat exchanger of ripple fin and tube type, there are 2 following drainage deterioration reasons, (1) dew is easily trapped in the valley of corrugated fin, and (2) dew is easily trapped in the upper surface (surface on the long side direction of flat tube) of flat tube.Drainage is poor, and when dew is detained, the flowing resistance on heat exchanger surface increases, and reduced terrifically by the air quantity of heat exchanger, the ability as heat exchanger reduces significantly.Its result, evaporating temperature also reduces further, and dew changes to frost and grows, and is absorbed in the vicious circle that flowing resistance increases further, air quantity reduces, ability reduces.
The present invention researches and develops for solving above-mentioned problem, its objective is the plate fin and tube type heat exchanger providing the drainage improved in fin and flat tube and the refrigerated air-conditioning system with this plate fin and tube type heat exchanger.
Solve the technical scheme of problem
Plate fin and tube type heat exchanger of the present invention, it inserts with the flat tube making section be flat pattern the mode being formed at the otch of fin and is formed, this flat pattern is make long side be straight line and short brink is the curve of semicircle shape, it is characterized in that, on the surface of at least one in described flat tube and described fin, formed and the valley of the mountain portion of minimum altitude and lowest depth is linked and the length that obtains is more than 10 μm multiple concavo-convex.
Refrigerated air-conditioning system of the present invention is used as evaporimeter by above-mentioned plate fin and tube type heat exchanger.
The effect of invention
According to plate fin and tube type heat exchanger of the present invention, the surface due at least one in fin and flat tube is formed multiple concavo-convex, so the surface of fin and flat tube can be made to have hydrophily effect, and increase substantially drainage.
According to refrigerated air-conditioning system of the present invention, owing to having above-mentioned plate fin and tube type heat exchanger, so use the flowing resistance increase that also significantly can reduce and be caused by dew as evaporimeter, and can maintaining heat exchange capacity.
Accompanying drawing explanation
Fig. 1 is the figure of the fusion bonding process of the heat exchanger summarily representing embodiments of the present invention 1.
Fig. 2 is the key diagram of the welding material used for illustration of the flat tube of the heat exchanger of embodiments of the present invention 1 or the welding of fin.
Fig. 3 is the summary stereogram represented partially amplifying existing ripple finned tube exchanger in the past.
Fig. 4 is the figure of contact with moisture angle before and after the welding on the flat tube of the heat exchanger representing embodiments of the present invention 1 and the surface of fin and hydrophilic relation.
Fig. 5 is the schematic diagram for illustration of contact with moisture angle and hydrophilic relation.
Fig. 6 is the observation figure on the surface of flat tube before and after the welding of the heat exchanger schematically representing embodiments of the present invention 1 and fin.
Fig. 7 is the schematic cross sectional view of a part for the irregular fin of formation of the heat exchanger summarily representing embodiments of the present invention 1 and the section shape of flat tube.
Fig. 8 is the key diagram of the effect had of heat exchanger for illustration of embodiments of the present invention 1.
Fig. 9 is the key diagram of the welding material used for illustration of the flat tube of the heat exchanger of embodiments of the present invention 2 and the welding of fin.
Figure 10 is the key diagram of the heat exchanger for illustration of embodiments of the present invention 3.
Figure 11 is the key diagram for illustration of the fin of the heat exchanger of embodiments of the present invention 3 and the wall thickness of flat tube.
Figure 12 is the loop diagram of the basic structure of the refrigerated air-conditioning system schematically representing embodiments of the present invention 4.
Detailed description of the invention
Below, based on accompanying drawing, embodiments of the present invention are described.
Embodiment 1
Fig. 1 is the figure of the fusion bonding process of the heat exchanger 50 summarily representing embodiments of the present invention 1.The heat exchanger 50 of embodiments of the present invention 1 is described based on Fig. 1.In addition, comprise Fig. 1, in figures in the following, there is the situation that the magnitude relationship of each component parts is different from reality.
As shown in Figure 1, heat exchanger 50 has section and is that long leg is divided into straight line and short side part is multiple flat tubes 51 formed by aluminium etc. of the flat of the curve of such as semicircle shape etc.Multiple flat tube 51 was arranged in parallel along the direction orthogonal with the path direction of the cold-producing medium at Bottomhole pressure with arbitrary interval.In addition, heat exchanger 50 has the fin 52 formed by aluminium etc. of multiple tabular (rectangular-shaped).Fin 52 was arranged in parallel along the path direction (with the direction that also column direction is orthogonal of flat tube 51) of cold-producing medium with the arbitrary interval specified.In addition, fin 52 be flat tube 51 and rectangular-shaped longer than the length of the width (paper left and right directions) of flat tube 51 of the length of column direction, thus in the following description, using the width of flat tube 51 as short side direction, using the also column direction of flat tube 51 as long side direction.
In flat tube 51, be provided with multiple hole 53 in the direction of the width side by side.Have such as the cold-producing medium with the air heat exchange passed through in heat exchanger 50 in the internal flow in this hole 53.In addition, fin 52 is formed with the otch 54 of multiple U-shaped along long side direction.Each otch 54 is corresponding with each flat tube 51, thus such as to be formed with arbitrary interval (except two ends) with flat tube 51 equal number.In addition, each otch 54 is formed as at the width of the long side direction of fin 52 width dimensions roughly the same with flat tube 51.This otch 54 is formed by the mode opened with one end of fin 52.That is, otch 54 is formed along the long side direction of fin 52 with comb teeth-shaped with being set up in parallel.
The manufacturing process of heat exchanger 50 is described.
First, the end face of the fin 52 of the primary side (on the left of paper) of air stream and the end (end on the left of paper) of flat tube 51 have the gap 52A of regulation, from the secondary side (on the right side of paper) of air stream, flat tube 51 are inserted the otch 54 of fin 52.Then, fin 52 and flat tube 51 are fused by the welding material of solder etc.Thus, the core (main portion) of heat exchanger 50 is made.In addition, although Fig. 1 is not shown, fin 52 also can form erecting of gate (bridge-type) that a part for the fin 52 between each otch 54 is erected.Like this, by erecting the heat exchange promoting air and cold-producing medium.
Fig. 2 is the key diagram of the welding material used for illustration of the welding of flat tube 51 and fin 52.Based on the welding of Fig. 2 simple declaration fin 52 and flat tube 51.Fin 52 and flat tube 51 are fused by the welding material of solder etc., but when welding also can using with mother metal 55 phase independently material use as welding material.Or, also on the surface of mother metal 55 forming fin 52 and flat tube 51, (coated) welding material can be added as clad 56 in advance as illustrated in fig. 2.Mother metal 55 becomes the constituent material of flat tube 51 and fin 52.
Fig. 3 is the summary stereogram represented partially amplifying existing ripple finned tube exchanger (hereinafter referred to as heat exchanger 50 ') in the past.Based on Fig. 3 simple declaration heat exchanger 50 '.In addition, in figure 3, dew 59 is shown in the lump.
As shown in Figure 3, heat exchanger 50 ' has flat tube (hereinafter referred to as flat tube 51 ') in the same manner as heat exchanger 50.In the same manner as flat tube 51, this flat tube 51 ' is for flat outer contour shape and have multiple hole 53 ', is cavernous heat-transfer pipe.In addition, heat exchanger 50 ' has wavy fin (hereinafter referred to as fin 52 ').And heat exchanger 50 ' is the mountain valley of the ripple at fin 52 ', and form by contacting with flat tube 51 '.This heat exchanger 50 is generally used to mobile applications etc.
But there are following two drainage deterioration reasons in heat exchanger 50 ', is easily detained dew in the valley of fin 52 ' as described above; The upper surface (surface on the long side direction of flat tube 51 ') of flat tube 51 ' is easily detained dew.
And the fin 52 of heat exchanger 50 is tabulars, therefore as heat exchanger 50 ', dew can not be detained in the valley of fin 52 '.And the end face of the fin 52 of the primary side of the air stream in heat exchanger 50 and flat tube 51 have the gap (the gap 52A shown in Fig. 1) of regulation, thus, dew promptly along the end face of fin 52 by draining.That is, the end face of the fin 52 of the primary side of air stream can not incision 54 cut off, and can not cut off the flowing of dew, can realize draining smoothly.Thus, first drainage deterioration reason is solved.
Below, the mechanism improved about the hydrophily on the surface of heat exchanger 50 is described.
Fig. 4 is the figure of contact with moisture angle before and after the welding on the surface representing flat tube 51 and fin 52 and hydrophilic relation.In addition, in the diagram, the respective hydrophily relative to contact with moisture angle (°) after the reliability test before showing the welding on the surface of flat tube 51 and fin 52, after welding, after welding.
Contact with moisture angle is the index of " wetability " on the surface representing flat tube 51 and fin 52.Here, moisture is fallen the surface of flat tube 51 and fin 52, the water droplet of attachment with the tangent line on the contact portion end on the surface of flat tube 51 and fin 52, with the surperficial angulation θ of flat tube 51 and fin 52 as contact with moisture angle.This contact with moisture angle is determined by the relation of the respective interface energy of gas, liquid, solid.In general, if contact with moisture angle is little, then hydrophily is large, if contact with moisture angle is large, then hydrophily is little.
As shown in Figure 4, before the welding of flat tube 51 and fin 52, nearly 90 ° of contact with moisture corner connection, and after fusing, contact with moisture angle is reduced to 40 ~ 50 °.It can thus be appreciated that after fusing, hydrophily improves.This is because, utilize the heat of welding, make the surface oxidation of fin 52 and flat tube 51, defined by this oxide small concavo-convex from the teeth outwards.If formed small concavo-convex on the surface of fin 52 and flat tube 51, then the contact with moisture angle on surface reduces, and the mobility of the water (such as, dew or drain water) on surface improves, and drainage improves.Thus, second drainage deterioration reason is solved.In addition, as long as contact with moisture angle is below 60 °, the mobility of the water on the surface of fin 52 and flat tube 51 just improves.
Fig. 5 is the schematic diagram for illustration of contact with moisture angle and hydrophilic relation.In addition, in Figure 5, drop shape when (a) represents that contact with moisture angle is large, drop shape when (b) represents that contact with moisture angle is little.
As shown in Fig. 5 (a), when contact with moisture angle is large, the shape subglobular of the water droplet observed from the side, therefore the surface tension of water droplet becomes large.That is, contact with moisture angle is larger, and hydrophily is less.On the other hand, as shown in Fig. 5 (b), when contact with moisture angle is little, the shape of the water droplet observed from the side is close to flat, and therefore the surface tension of water droplet diminishes.And hydrophily step-down refers to that drainage is deteriorated.That is, when contact with moisture angle is large, as shown in Fig. 5 (a), water droplet easily remains on fin, and when contact with moisture angle is little, as shown in Fig. 5 (b), water droplet is difficult to remain on fin.
In addition, for guaranteeing hydrophily, when the coating material of coating after being coated with etc., coating material is aging, and its hydrophily effect fails gradually in any case.This is because due to rear coating degradations, engender the aluminum matrix that hydrophily is low, hydrophily worsens thus.And when heat exchanger 50 of embodiment 1, after this aging accelerated test is observed in existence (after the reliability test shown in Fig. 4), its contact angle demonstrates the tendency of reduction, maintains and improves hydrophily effect further.This is because by accelerated test, oxidation is carried out bit by bit, forms the concavo-convex of surface more, attenuates and become close.In hydrophilic continuation, advantage is large.
Fig. 6 is the observation figure on the surface schematically representing flat tube 51 before and after welding and fin 52.In addition, in figure 6, a () represents the surface of the flat tube 51 before welding and fin 52, (b) represents the surface of the flat tube 51 after welding and fin 52, and (c) represents the surface of the flat tube 51 after the reliability test after welding and fin 52.
As can be seen from Figure 6, in any situation before welding, after welding, after accelerated test, the roughness on surface all changes.That is, as can be seen from Figure 6, before welding, surface roughness is little, and after fusing, surface roughness is large, and after accelerated test, surface roughness is larger.This is because, along with before welding, after welding, after accelerated test, formation carefully concavo-convex and thickly changing.In addition, as mentioned above, by adding (coated) welding material in advance on the surface of mother metal, the surface of fin 52 and flat tube 51 being easily formed uniformly concavo-convex, promoting the homogenising of hydrophily effect further.
Fig. 7 is the schematic cross sectional view of the part summarily representing the section shape forming irregular fin 52 and flat tube 51.For obtaining above-mentioned hydrophily effect, the length that the valley in the mountain portion and lowest depth that are formed in the concavo-convex minimum altitude on fin 52 and flat tube 51 links and obtains is preferably more than 10 μm.If formed as minimum of a value concavo-convex using this numerical value, then can reduce contact with moisture angle, increase hydrophily.In addition, to be concavo-convexly preferably formed uniformly, if but the distance valley of the mountain portion of minimum altitude and lowest depth being linked and obtain is more than 10 μm, concavo-convex not necessarily must be evenly.
Fig. 8 is the key diagram of the effect had for illustration of heat exchanger 50.In addition, in fig. 8, (a) represents the stereogram of heat exchanger 50, and (b) represents the side view of the state that the side, ground, direction of insertion side from the flat tube 51 of heat exchanger 50 to fin 52 is observed.In addition, in fig. 8, the flowing of air is represented with blank arrowhead.And, in fig. 8, represent the flowing of water droplet with arrow (1), arrow (2).In addition, in Fig. 8 (a), (b), its section shape is all shown about flat tube 51.
As mentioned above, the fin 52 of heat exchanger 50 is tabulars, and therefore as heat exchanger 50 ', dew can not be trapped in the valley of fin 52 '.And, the end face of the fin 52 of the primary side of the air stream in heat exchanger 50 and flat tube 51 have the gap (the gap 52A shown in Fig. 1) of regulation, thus, dew promptly along the end face of fin 52 by draining (arrow (1)).Thus, first drainage deterioration reason is solved.
In addition, heat exchanger 50 utilizes the heat of the welding of flat tube 51 and fin 52, oxidation fin 52 and the surface of flat tube 51, is formed small concavo-convex by this oxide from the teeth outwards.And concavo-convex by being formed, the hydrophily on the surface of fin 52 and flat tube 51 improves, and the mobility of the water (such as, dew or drain water) on surface improves, and drainage improves (arrow (2)).Thus, second drainage deterioration reason is solved.
Above, according to heat exchanger 50, the surface roughness of fin 52 and flat tube 51 increases, and has hydrophily effect, can improve drainage thus.In addition, according to heat exchanger 50, the hydrophily on the surface of fin 52 and flat tube 51 can be guaranteed by means of only welding, therefore do not need the hydrophily process undertaken by rear coating etc., can also expect that productivity ratio improves and cost reduces.And, according to heat exchanger 50, owing to not needing the hydrophily process undertaken by rear coating etc., so there is not the aging etc. of the coating material of rear coating, the hydrophily on the surface of fin 52 and flat tube 51 can be maintained with the state that reliability is high.
Embodiment 2
Fig. 9 is the key diagram of the welding material used for illustration of the flat tube of the heat exchanger of embodiments of the present invention 2 and the welding of fin.Based on Fig. 9, the welding material that the flat tube of the heat exchanger of embodiments of the present invention 2 and the welding of fin use is described.In addition, in embodiment 2, by with the difference of embodiment 1 centered by be described, the part identical with embodiment 1 marks identical Reference numeral and omits the description.
In embodiment 1, utilize and by the heat of the welding oxide be formed on the surface of fin 52 and flat tube 51, surface roughness is changed, play hydrophily effect.And in embodiment 2, in welding material, add foreign matter in advance, promoted the surface roughness of fin and flat tube thus by welding material, while the oxidation of fin and flat tube self can be suppressed, guarantee hydrophily effect.
In embodiment 2, illustrated by Fig. 2 of embodiment 1, fin and flat tube are fused by the welding material of solder etc.In embodiment 2, also in the same manner as embodiment 1, use and mother metal 55 independently welding material, or use the welding material added in advance on the surface of mother metal 55 to carry out welding.But here, to as illustrated in fig. 9 under the state of welding material that interpolation (coated) is added with foreign matter 57 in advance, the situation of welding fin and flat tube is described.
As shown in Figure 9, the surface of mother metal 55 is pre-formed with the clad 56A becoming welding material.The foreign matter 57 that fusing point is higher than the fusing point of the welding material forming clad 56A is added in this clad 56A with particulate state.As foreign matter 57, the material that preferably selected fusing point is higher than the fusing point of the welding material forming clad 56A, such as aluminium oxide etc.In addition, foreign matter 57 is preferably selected in the mode that can form the particle diameter of concavo-convex degree after fusing on the surface of fin, flat tube.And, foreign matter 57 material that preferably selected electric potential is lower than the material of fin, flat tube wittingly.Like this, when there is moisture in time in heat exchanger, also the surface oxidation of fin, flat tube can be corroded by galvanic corrosion, and then promote the concavo-convex formation on surface of fin, flat tube.
Above, according to the heat exchanger of embodiment 2, while the oxidation that inhibit fin and flat tube self, and the surface roughness of fin and flat tube can be increased, hydrophily effect can be guaranteed.Therefore, in the heat exchanger of embodiment 2, the wall thickness of fin and flat tube self correspondingly can be made thinning, can reduce costs.In addition, if with the addition of the current potential foreign matter 57 lower than the material of fin and flat tube, for aging, the state high relative to hydrophilic reliability can just be maintained.
In addition, according to the heat exchanger of embodiment 2, originally required welding material can be utilized to form oxide layer, without the need to the hydrophily process undertaken by rear coating etc., can expect that productivity ratio improves and cost reduces.And, according to the heat exchanger of embodiment 2, without the need to the hydrophily process undertaken by rear coating etc., therefore there is not the aging etc. of the coating material of rear coating, the hydrophily on the surface of fin and flat tube can be maintained with the state that reliability is high.
Embodiment 3
Figure 10 is the key diagram of the heat exchanger 50B for illustration of embodiments of the present invention 3.The heat exchanger 50B of embodiments of the present invention 3 is described based on Figure 10.
In Fig. 10, (a) represents the side view of the state that the side, ground, direction of insertion side from the flat tube 51 of heat exchanger 50B to fin 52 is observed, and (b) represents the top view of heat exchanger 50B.In addition, in embodiment 3, by with the difference of embodiment 1 and embodiment 2 centered by be described, the part identical with embodiment 1 and embodiment 2 marks identical Reference numeral and omits the description.In addition, in Figure 10 (a), about flat tube 51, show its section shape.
In embodiment 2, add foreign matter 57 to the welding material forming clad 56A in advance, under the state of oxidation that inhibit fin and flat tube self, make the surface roughness of fin and flat tube increase.And in embodiment 3, the flux 58 used to the surface of mother metal 55 in advance adds foreign matter 57, under the state of oxidation that inhibit fin 52 and flat tube 51 self, the surface roughness of fin 52 and flat tube 51 is made to increase.Flux 58 is for the protection of the surface of mother metal 55.It is identical that foreign matter 57 and embodiment 2 illustrate.
If arrange the flux 58 that with the addition of foreign matter 57 on the surface of mother metal 55 becoming fin 52, then, as Suo Shi Figure 10 (a), flux 58 is to the whole regional diffusion (arrow shown in Figure 10 (a)) on the surface of fin 52.In addition, if arrange the flux 58 that with the addition of foreign matter 57 on the surface of mother metal 55 becoming flat tube 51, then as Suo Shi Figure 10 (b), flux 58 is to the whole regional diffusion (arrow shown in Figure 10 (b)) on the surface of flat tube 51.
Figure 11 is the key diagram of the wall thickness for illustration of fin 52 and flat tube 51.The wall thickness of fin 52 and flat tube 51 is described based on Figure 11.In fig. 11, transverse axis represents the wall thickness of the mother metal 55 becoming fin 52 and flat tube 51, and the longitudinal axis represents the Residual Wall Thickness of mother metal 55 except oxide layer from becoming fin 52 and flat tube 51.
The mother metal 55 becoming fin 52 and flat tube 51 defines and forms the promising concavo-convex oxide layer guaranteed needed for hydrophily, and the minimum wall thickness for guaranteeing heat transfer property, compressive resistance guaranteed by needs.Therefore, as shown in figure 11, for mother metal 55, preferably according to can control fusion temp, the time, oxygen concentration the wall thickness of degree decide minimum wall thickness.About this point, be also general in embodiment 1,2.In addition, according to the difference becoming the material of mother metal, the material of welding material, the material of flux, the material of foreign matter, the figure line shown in Figure 11 changes, and the numerical value of fusion temp, time and oxygen concentration need not be determined within the limits prescribed.
Above, by manufacturing heat exchanger, in embodiment 3, while the oxidation that inhibit fin and flat tube self, the surface roughness of fin and flat tube can be increased, and hydrophily effect can be guaranteed.Therefore, in the heat exchanger of embodiment 3, the wall thickness of fin and flat tube self correspondingly can be made thinning, and can reduce costs.In addition, if with the addition of the current potential foreign matter 57 lower than the material of fin and flat tube, for aging, the state high relative to hydrophilic reliability can also be maintained.
In addition, according to the heat exchanger of embodiment 3, oxide layer can be formed by originally required flux, without the need to the hydrophily process undertaken by rear coating etc., can expect that productivity ratio improves and cost reduces.And, according to the heat exchanger of embodiment 3, without the need to the hydrophily process undertaken by rear coating etc., therefore there is not the aging etc. of the coating material of rear coating, the hydrophily on the surface of fin and flat tube can be maintained with the state that reliability is high.
In addition, as mentioned above, about the present invention, embodiment is divided into 3 and is illustrated, but the feature item of each embodiment can certainly be combined.In addition, in arbitrary embodiment, the concavo-convex of surface about both fin 52 and flat tube 51 is illustrated, and is let alone formed on the surface at any one and concavo-convexly also can play effect.
Embodiment 4
Figure 12 is the loop diagram of the basic structure of the refrigerated air-conditioning system 100 schematically representing embodiments of the present invention 4.Structure and the action of refrigerated air-conditioning system 100 are described based on Figure 12.This refrigerated air-conditioning system 100 circulates in the key element equipment forming freeze cycle by making cold-producing medium, can perform cooling operation or heat running.In addition, in embodiment 4, refrigerated air-conditioning system 100 has any one in the heat exchanger of embodiment 1 ~ 3.In addition, in fig. 12, the flowing of cold-producing medium when solid line represents refrigeration, dotted line represents the flowing of cold-producing medium when heating.
As mentioned above, ripple finned tube exchanger is suitable for using as condenser, but is not suitable as evaporimeter use.And the drainage of the heat exchanger of embodiment 1 ~ 3 is very excellent, thus the flowing resistance increase caused by dew can be reduced significantly, can maintaining heat exchange capacity.Therefore, the heat exchanger of embodiment 1 ~ 3 is also suitable for using as evaporimeter.Therefore, refrigerated air-conditioning system 100 using any one in the heat exchanger of embodiment 1 ~ 3 as requiring the heat source side heat exchanger of function of both condenser and evaporimeter, load-side heat exchanger uses.
Connected as the compressor 1 of key element equipment, heat source side heat exchanger 3, throttling arrangement 102 and load-side heat exchanger 101 by pipe arrangement and be mounted in refrigerated air-conditioning system 100.Wherein, compressor 1 and heat source side heat exchanger 3 are mounted on off-premises station, and throttling arrangement 102 and load-side heat exchanger 101 are mounted on indoor set.In addition, throttling arrangement 102 also can not be mounted in indoor set, and is mounted in off-premises station.In addition, in the discharge side of compressor 1, the running be provided with as requested switches the cross valve 2 of the flowing of cold-producing medium.
Compressor 1 sucks cold-producing medium, and compresses the state that this cold-producing medium becomes high temperature, high pressure, such as, be made up of the frequency-changeable compressor etc. that can carry out volume controlled.Heat source side heat exchanger 3 is for being forced to carry out heat exchange between the air of supply and cold-producing medium from omitting illustrated fan.Any one in the heat exchanger of embodiment 1 ~ 3 is adopted as this heat source side heat exchanger 3.Throttling arrangement 102 makes cold-producing medium reduce pressure and expands, and is made up of the such as electronic expansion valve etc. that can control aperture changeably.Load-side heat exchanger 101 for carrying out heat exchange between the air being forced to supply from the pressure fan omitting illustrated fan etc. and cold-producing medium.Any one in the heat exchanger of embodiment 1 ~ 3 is adopted as this load-side heat exchanger 101.
The action when cooling operation of refrigerated air-conditioning system 100 is described simply and action when heating running.
[cooling operation]
If compressor 1 is driven, then by compressor 1, cold-producing medium is boosted, become high temperature, high pressure state and be discharged.From compressor 1 discharge high temperature, high pressure gas refrigerant flow into heat source side heat exchanger 3 via cross valve 2, carry out heat exchange with air and be cooled, become low temperature, high pressure liquid status and flow out from heat source side heat exchanger 3.This liquid cold-producing medium is inflated decompression in throttling arrangement 102, becomes the two-phase system cryogen of low temperature, low pressure.This two-phase system cryogen flows into load-side heat exchanger 101, evaporating, becoming the gas refrigerant of low temperature, low pressure by carrying out heat exchange with air.Now, machine is supplied to cooling air indoor, carries out the refrigeration of air-conditioning object space.And the low-pressure refrigerant gas flowed out from load-side heat exchanger 101 returns compressor 1 again.
In load-side heat exchanger 101, if the temperature of the cold-producing medium of flowing is reduced to the dew point of air in flat tube (flat tube 51), then the moisture in air condenses on heat exchanger surface, produces dew (drain water).As long as the dew produced on heat exchanger surface is promptly just no problem by draining from fin end face or flat tube surface, but can be built bridge between fin by surface tension, or is trapped in the upper surface of flat tube.If dew is detained gradually, then the flowing resistance on heat exchanger surface increases, and reduced terrifically by the air quantity of heat exchanger, the ability as heat exchanger obviously reduces.Its result, evaporating temperature also reduces further, and dew changes to frost and grows up, and then may be absorbed in the vicious circle of flowing resistance increase, air quantity reduction, inferior capabilities.
For such problem, in refrigerated air-conditioning system 100, owing to being used as load-side heat exchanger 101 by arbitrary heat exchanger of embodiment 1 ~ 3, even if so moisture condensation is on heat exchanger surface, also can drainage dew be suppressed well to be detained efficiently.Therefore, the increase of the flowing resistance on the heat exchanger surface that refrigerated air-conditioning system 100 does not produce because dew is detained and pass through the such problem of the reduction of air quantity of heat exchanger, can suppress the reduction of the ability as heat exchanger.
[heating running]
If compressor 1 is driven, then by compressor 1, cold-producing medium is boosted, become high temperature, high pressure state and be discharged.From compressor 1 discharge high temperature, high pressure gas refrigerant flow into load-side heat exchanger 101 via cross valve 2, carry out heat exchange with air and be cooled, become low temperature, high pressure liquid condition and flow out from load-side heat exchanger 101.Now, machine is supplied to the air heated indoor, carries out heating of air-conditioning object space.This liquid cold-producing medium is inflated decompression by throttling arrangement 102, becomes the two-phase system cryogen of low temperature, low pressure.This two-phase system cryogen flows into heat source side heat exchanger 3, carries out heat exchange and evaporates, become the gas refrigerant of low temperature, low pressure with air.And the low-pressure refrigerant gas flowed out from heat source side heat exchanger 3 returns compressor 1 again.
In heat source side heat exchanger 3, if the temperature of the cold-producing medium of flowing is reduced to the dew point of air in flat tube (flat tube 51), then the moisture in air condenses on heat exchanger surface, produces dew (drain water).As long as the dew produced on heat exchanger surface is promptly just no problem by draining from fin end face or flat tube surface, but can be built bridge between fin by surface tension, or is trapped in the upper surface of flat tube.If dew is detained gradually, then the flowing resistance on heat exchanger surface increases, and reduced terrifically by the air quantity of heat exchanger, the ability as heat exchanger obviously reduces.Its result, evaporating temperature also reduces further, and thus, dew changes to frost and grows up, and then may be absorbed in the vicious circle that flowing resistance increases, air quantity reduces, ability reduces.
For such problem, in refrigerated air-conditioning system 100, owing to being used as heat source side heat exchanger 3 by arbitrary heat exchanger of embodiment 1 ~ 3, even if so moisture condensation is on heat exchanger surface, also can drainage dew be suppressed well to be detained efficiently.Therefore, refrigerated air-conditioning system 100 can not occur by dew be detained the flowing resistance on the heat exchanger surface that produces increase and by the such problem of the reduction of the air quantity of heat exchanger, the reduction of the ability as heat exchanger can be suppressed.
Above, because refrigerated air-conditioning system 100 has any one in the heat exchanger of embodiment 1 ~ 3, so when this heat exchanger is used as evaporimeter, also significantly can reduce the flowing resistance caused by dew and increase, and can maintaining heat exchange capacity.
The explanation of Reference numeral
1 compressor, 2 cross valves, 3 heat source side heat exchangers, 50 heat exchangers, 50 ' heat exchanger, 50B heat exchanger, 51 flat tubes, 51 ' flat tube, 52 fins, the gap of 52A fin and flat tube, 52 ' fin, 53 holes, 53 ' hole, 54 otch, 55 mother metals, 56 clads, 56A clad, 57 foreign matters, 58 flux, 59 dews, 100 refrigerated air-conditioning systems, 101 load-side heat exchangers, 102 throttling arrangements.
Claims (5)
1. a plate fin and tube type heat exchanger, it inserts with the flat tube making section be flat pattern the mode being formed at the otch of fin and is formed, and this flat pattern is make long side be straight line and short brink is the curve of semicircle shape, it is characterized in that,
On the surface of at least one in described flat tube and described fin, formed and make the difference of height of the mountain portion of minimum altitude and the valley of lowest depth be more than 10 μm multiple concavo-convex,
In the welding material for flat tube described in welding and described fin, add surface roughness for increasing described fin and described flat tube in advance and the fusing point foreign matter higher than this welding material.
2. a plate fin and tube type heat exchanger, it inserts with the flat tube making section be flat pattern the mode being formed at the otch of fin and is formed, and this flat pattern is make long side be straight line and short brink is the curve of semicircle shape, it is characterized in that,
On the surface of at least one in described flat tube and described fin, formed and make the difference of height of the mountain portion of minimum altitude and the valley of lowest depth be more than 10 μm multiple concavo-convex,
In the flux that the surface of described flat tube and described fin uses, add surface roughness for increasing described fin and described flat tube in advance and the fusing point foreign matter higher than this flux.
3. plate fin and tube type heat exchanger as claimed in claim 1 or 2, it is characterized in that, describedly concavo-convexly to be formed as follows, what be attached to the water droplet on the surface of at least one in described flat tube and described fin is less than 60 ° with the tangent line on the contact portion end on the surface of at least one in flat tube and described fin, with the surperficial angulation of at least one in described flat tube and described fin.
4. plate fin and tube type heat exchanger as claimed in claim 1 or 2, is characterized in that, the oxide-film that the heat produced during described concavo-convex welding by by described flat tube and described fin is formed is formed.
5. a refrigerated air-conditioning system, is characterized in that, is used by the plate fin and tube type heat exchanger described in claim 1 or 2 as evaporimeter.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2012/000130 WO2013105133A1 (en) | 2012-01-11 | 2012-01-11 | Plate fin-and-tube heat exchanger, and refrigeration and air-conditioning system with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103930747A CN103930747A (en) | 2014-07-16 |
| CN103930747B true CN103930747B (en) | 2016-01-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280052472.0A Expired - Fee Related CN103930747B (en) | 2012-01-11 | 2012-01-11 | Plate fin and tube type heat exchanger and there is the refrigerated air-conditioning system of this plate fin and tube type heat exchanger |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20140338876A1 (en) |
| EP (1) | EP2803930B1 (en) |
| JP (1) | JP5661202B2 (en) |
| CN (1) | CN103930747B (en) |
| WO (1) | WO2013105133A1 (en) |
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| WO2015040746A1 (en) * | 2013-09-20 | 2015-03-26 | 三菱電機株式会社 | Heat exchanger, air conditioner device using said heat exchanger, and method for producing said heat exchanger |
| CN104657024A (en) | 2015-03-13 | 2015-05-27 | 京东方科技集团股份有限公司 | Built-in touch screen and display device |
| JP6633317B2 (en) * | 2015-08-05 | 2020-01-22 | 三菱アルミニウム株式会社 | Hydrophilic fin and heat exchanger |
| WO2017072945A1 (en) * | 2015-10-30 | 2017-05-04 | 三菱電機株式会社 | Heat exchanger and air conditioner |
| JP6332377B2 (en) | 2016-09-23 | 2018-05-30 | ダイキン工業株式会社 | Heat exchanger |
| JP6785868B2 (en) * | 2016-10-07 | 2020-11-18 | 三菱電機株式会社 | Air conditioner with heat exchanger and heat exchanger |
| WO2018230430A1 (en) | 2017-06-12 | 2018-12-20 | 株式会社デンソー | Heat exchanger and corrugated fin |
| US11384996B2 (en) * | 2017-10-16 | 2022-07-12 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
| JP6956866B2 (en) * | 2018-05-17 | 2021-11-02 | 三菱電機株式会社 | Refrigeration cycle equipment |
| JP6932262B2 (en) * | 2018-07-27 | 2021-09-08 | 三菱電機株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle equipment |
| JP7118238B2 (en) * | 2019-03-05 | 2022-08-15 | 三菱電機株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
| JP6785937B2 (en) * | 2019-12-11 | 2020-11-18 | 三菱アルミニウム株式会社 | Hydrophilic fins and heat exchanger |
| JP2022148602A (en) * | 2021-03-24 | 2022-10-06 | 東芝キヤリア株式会社 | Heat exchanger |
| US20230121635A1 (en) * | 2021-10-14 | 2023-04-20 | Amulaire Thermal Technology, Inc. | Immersion heat dissipation structure having macroscopic fin structure and immersion heat dissipation structure having fin structure |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2803930B1 (en) | 2018-06-06 |
| CN103930747A (en) | 2014-07-16 |
| US20140338876A1 (en) | 2014-11-20 |
| JPWO2013105133A1 (en) | 2015-05-11 |
| EP2803930A1 (en) | 2014-11-19 |
| WO2013105133A1 (en) | 2013-07-18 |
| EP2803930A4 (en) | 2016-01-13 |
| JP5661202B2 (en) | 2015-01-28 |
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