CN1159564C - Heat exchanger for air conditioner - Google Patents
Heat exchanger for air conditioner Download PDFInfo
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- CN1159564C CN1159564C CNB971969264A CN97196926A CN1159564C CN 1159564 C CN1159564 C CN 1159564C CN B971969264 A CNB971969264 A CN B971969264A CN 97196926 A CN97196926 A CN 97196926A CN 1159564 C CN1159564 C CN 1159564C
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- 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
- F28D1/047—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 bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- 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
- F28F1/325—Fins with openings
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Other Air-Conditioning Systems (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
A heat exchanger used for an air conditioner, wherein a plurality of fins (10) are provided in parallel, through which a plurality of windward heat exchanger tubes (13) and a plurality of leeward heat exchanger tubes (14) are passed. The heat exchanger tubes (13, 14) are provided so as to extend in substantially the same direction in a generally staggered manner. In the intermediate portions of the fins which are located between the windward heat exchanger tubes (13) and the leeward heat exchanger tubes (14), cuts (15) are provided. The cuts (15) are arranged in the same direction as the heat exchanger tubes (13, 14) and extend in the direction which crosses the direction X in which the cuts are arranged. Owing to this construction, the unnecessary transfer of heat via the fins is prevented, and, moreover, a sufficient level of rigidity of the fins can be secured.
Description
Technical field
The present invention relates to be applicable to the heat exchanger of conditioner etc., particularly intersect and connect what is called on the fin that is arranged on several and row arrangement and intersect plate fin type heat exchanger about heat-transfer pipe.
Background technology
By means of the heat pump type air adjusting device of using refrigerating circuit during to indoor heating, the effect of indoor heat converter performance condenser, the function of outdoor heat converter performance evaporimeter.In this occasion, have condenser function heat exchanger be represented as the intersection plate fin type heat exchanger, Figure 10 shows an example in the past of such heat exchanger.In such heat exchanger, a plurality of fin 40 of being made up of heat-conductive characteristic good metal such as aluminium are arranged side by side in accordance with regulations at interval, several hairpin shape heat-transfer pipes 11 insert in this fin 40, and its end interconnects with U-shaped tube connector 12 simultaneously.Adopt this structure, on wind first sidepiece 40a of above-mentioned several fin 40 and second sidepiece of wind 40b, be equipped with several heat- transfer pipes 13,14 respectively, these heat- transfer pipe 13,14 integral body are staggered.
In above-mentioned heat exchanger, be divided into up and down from the cold-producing medium of compressor from inlet tube 9 that both direction flows into the heat-transfer pipe 14 of wind downside, and after carrying out heat exchange between the air A by fin 40, flow in the heat-transfer pipe 13 of wind upside.And, flow into cold-producing medium in the heat-transfer pipe 13 of wind upside again and by after exchanging between 40 the air A in the heat radiation, flow out from both direction interflow up and down and from outlet 8, return compressor through pressure reducer and evaporimeter again.
, flow through the temperature of cold-producing medium of above-mentioned heat exchanger by descending gradually with the heat exchange of air A and through flowing of heat-transfer pipe 13,14.Figure 11 shows the hairpin shape heat-transfer pipe 11 in the above-mentioned heat exchanger in the past and the temperature of U-shaped tube connector 12 each several parts.The left side of figure shows the syndeton of hairpin shape heat-transfer pipe 11 and U-shaped tube connector 12, and the curve map on Dui Ying right side shows its temperature with it.At first, near the temperature inlet tube 9 is the highest, about 90 ℃.On the other hand, near the temperature outlet 8 is minimum, about 30 ℃.And near the above-mentioned inlet tube 9 near outlet 8, though temperature reduced gradually after cold-producing medium longshore current road and air A carried out heat exchange, as shown in the figure, by B portion, C portion that dotted line surrounded, its variations in temperature gets muddled.This be since near the minimum outlet 8 of near the heat-transfer pipe the highest inlet tube of temperature 9 (near the heat-transfer pipe inlet) 14a and temperature heat-transfer pipe (near the heat-transfer pipe outlet) 13a near position ground dispose and both use the cause of same fin 40.Promptly in B portion, because heat-transfer pipe 14a is along the position that is configured near the heat-transfer pipe 13a of approaching side outlet down up and down near entering the mouth, near the heat transferred fin 40 of the overheated gas that heat-transfer pipe 14a flows the process inlet also imposes on the supercooling liquid that flows through near heat-transfer pipe 13a exporting, and temperature is risen significantly.And in C portion, because heat-transfer pipe 13a is along the position that is configured in up and down near near the heat-transfer pipe 14a last side entrance near the outlet, low temperature through near the mobile supercooling liquid of the heat-transfer pipe 13a outlet also passes to fin 40 and imposes on the overheated gas that flows through near the heat-transfer pipe 14a inlet, and temperature is reduced significantly.So the heat conduction by fin 40 is carried out between inlet tube 9 sides and outlet 8 sides, because of unnecessary hot-fluid has caused remarkable reduction as the thermal efficiency of condenser.
Therefore, in the prior art, proposed as shown in figure 12 between the heat-transfer pipe 14 of the heat-transfer pipe 13 of wind upside and wind downside, dispose several slits 41, make wind first sidepiece 40a of fin 40 and the improved heat exchanger (reference example such as spy open flat 3-194370 communique) that second sidepiece of wind 40b heat separates by this slit 41.
But the situation that slit 41 as shown in figure 12 is set on the fin 40 is compared with the fin 40 that this slit 41 is not set, and has reduced the fin 40 shown in this figure and has been arranged side by side counter-bending rigidity on the direction (directions of heat- transfer pipe 13,14 insertions).The reduction of the operation when like this, having caused pressure processing post processing fin 40 or when inserting hairpin shape heat-transfer pipe 11 in the stacked fin 40 etc.In addition, when carrying out above-mentioned operation, because of fin 40 produces the problem that heat-exchange capacity reduces and flowing resistance the increases generation that distortion has caused heat exchanger.
Summary of the invention
The present invention proposes in order to solve the existing problem of above-mentioned conventional art, and its objective is provides a kind of can preventing to take place also can guarantee that fin has the heat exchanger of enough rigidity by the unwanted heat conduction of fin.
In order to achieve the above object, heat exchanger of the present invention, it is the intersection plate fin type heat exchanger, several fin have been arranged side by side, first specific direction perforation ground, sidepiece upper edge alignment arrangements of wind at this fin has several wind upside heat-transfer pipes, simultaneously in second sidepiece upper edge of its wind with the roughly the same direction of above-mentioned wind upside heat-transfer pipe connect alignment arrangements several wind downside heat-transfer pipes are arranged, in addition, along specific direction spaced reciprocally alignment arrangements several otch are arranged, make first sidepiece of wind and second sidepiece thermal release of wind of above-mentioned fin, it is characterized in that having at least a direction of intersecting to extend ground in the above-mentioned otch and be provided with along orientation with above-mentioned otch.
The orientation of above-mentioned otch and the extension of above-mentioned at least one otch are provided with direction and intersect angulation when being θ, and preferably θ satisfies 5 °≤θ≤175 °.
In above-mentioned heat exchanger, owing to have one at least in above-mentioned several otch, preferably all otch all extend along the direction that intersects with the otch orientation and are provided with, so, can reduce orientation with otch and be the reduction of rigidity of the fin of flexural center, therefore, unwanted heat conduction can be avoided, and the rigidity of fin can be guaranteed through fin.
In one embodiment, above-mentioned wind upside heat-transfer pipe becomes staggered with wind downside heat-transfer pipe overall alignment, above-mentioned several otch are arranged between each adjacent wind upside heat-transfer pipe and the wind downside heat-transfer pipe, extend simultaneously be arranged to the center that is connected both between imaginary line intersect.
In this occasion and since otch be arranged to the center that is connected wind upside heat-transfer pipe and wind downside heat-transfer pipe between the structure that intersects of imaginary line, therefore, can prevent unwanted hot the conduction reliably through fin.
In one embodiment, above-mentioned wind upside heat-transfer pipe and wind downside heat-transfer pipe, its size is made the roughly the same diameter of being represented by W1, and above-mentioned otch extends that to be arranged on above-mentioned imaginary line be in the scope represented with W2 of its width at center, and has equation 0.4≤W2/W1≤1.3 to set up.
According to this structure, can prevent unwanted heat conduction reliably through fin, can avoid the rigidity of fin to reduce under the user mode usually simultaneously.
When the distance between the peripheral part of wind upside heat-transfer pipe on the above-mentioned imaginary line and the face-off of wind downside heat-transfer pipe is L1, and above-mentioned otch has equation 0.2≤L2/L1≤0.8 to set up when being L2 from the distance of the above-mentioned peripheral part of the wind downside heat-transfer pipe of point to imaginary line that intersect with above-mentioned imaginary line.So, can further prevent unwanted heat conduction reliably through fin.
In another embodiment, on first sidepiece of wind of above-mentioned fin and second sidepiece of wind, be respectively arranged with the louver board, this louver board forms in the following manner, it is outstanding towards ventilation road direction that it cuts off the edge, direction is set in the extension at this cut-out edge simultaneously and direction of ventilation intersects, and above-mentioned otch is arranged on formed pars intermedia between the louver board of the louver board of wind upside and wind downside.
In this occasion, can improve heat-exchange capacity by above-mentioned louver board.And, can prevent unnecessary heat conduction through fin, can eliminate the reduction of fin rigidity simultaneously.
When the width of above-mentioned pars intermedia on the direction that wind upside heat-transfer pipe and wind downside heat-transfer pipe are arranged side by side is W3, when the above-mentioned width that is arranged side by side on the direction that extends the scope that above-mentioned otch is set is W4, has equation 0.4≤W4/W3≤0.9 to set up.
In this occasion, can further prevent unnecessary heat conduction reliably through fin, can eliminate the reduction of fin rigidity simultaneously.
Further, distance adjacent along the orientation of above-mentioned wind upside heat-transfer pipe or wind downside heat-transfer pipe and that stand facing each other between the two heat-transfer pipe centers, ground is L3, when the wind upside heat-transfer pipe of above-mentioned orientation and the distance between the above-mentioned otch center are L4, there is equation 0.3≤L4/L3≤0.7 to set up in addition.In this occasion, can prevent unnecessary heat conduction reliably through fin.
In one embodiment, when the high temperature side cold-producing medium flows through above-mentioned wind downside heat-transfer pipe, the low temperature side cold-producing medium also flows by wind upside heat-transfer pipe, on the other hand, in first sidepiece of the wind of above-mentioned fin, form at the wind upside of wind downside heat-transfer pipe and to be clipped in two fin connecting portions between the wind upside louver board.
In this structure, make first sidepiece of wind of a part of heat transferred fin of wind downside heat-transfer pipe by the fin connecting portion, can prevent to be clipped in first sidepiece of wind the unusual reduction of the portion temperature between the wind upside heat-transfer pipe thus.As a result, can guarantee sufficient heat-exchange capacity.
In an embodiment again, when the orientation of above-mentioned wind upside heat-transfer pipe or wind downside heat-transfer pipe and the extension of above-mentioned otch were provided with the direction angulation and are θ, θ satisfied 5 °≤θ≤175 °.At this moment, preferably adjacent otch is intersected on the contrary with the orientation with wind upside heat-transfer pipe 13 or wind downside heat-transfer pipe 14 and extend to be provided with.In this occasion, can further prevent unnecessary heat conduction reliably through fin, can guarantee that fin has enough rigidity simultaneously.
The simple declaration of accompanying drawing
Fig. 1 is to use the refrigerating circuit figure of the heat pump type air adjusting device of heat exchanger of the present invention.
Fig. 2 is the perspective view of interchanger one embodiment of the present invention.
Fig. 3 is the front view of fin section embodiment illustrated in fig. 2.
Fig. 4 is the front view of the fin section of another embodiment of interchanger of the present invention.
Fig. 5 A is that expression forms the perspective view that the otch of Fig. 3 and fin shown in Figure 4 constitutes.
Fig. 5 B, 5C, 5D are the perspective views of the above-mentioned otch variation of expression.
Fig. 6 is the curve map of the relation of expression slit patterns and heat-exchange capacity, and the heat-exchange capacity value when showing W2/W1=0 is 1.0 situation with respect to the W2/W1 heat-exchange capacity of value respectively.
Fig. 7 is the curve map of the relation of expression slit patterns and heat-exchange capacity, and the heat-exchange capacity value when showing L2/L1=0.5 is 1.0 situation with respect to the L2/L1 heat-exchange capacity of value respectively.
Fig. 8 is the curve map of the relation of expression slit patterns and heat-exchange capacity, and the heat-exchange capacity value when showing W4/W3=0 is 1.0 the situation heat-exchange capacity with respect to the W4/W3 value.
Fig. 9 is the curve map of the relation of expression slit patterns and heat-exchange capacity, and the heat-exchange capacity value when showing L4/L3=0.5 is 1.0 situation with respect to the L4/L3 heat-exchange capacity of value respectively.
Figure 10 is the perspective view of heat exchanger of example in the past.
Figure 11 represents the curve map of the heat transfering tube of heat exchanger each several part temperature of example in the past.
Figure 12 is the perspective view that the heat exchanger of example in the past improves example.
The optimised form that carries out an invention
Hereinafter be described in detail the specific embodiment of heat exchanger of the present invention with reference to accompanying drawing.
Fig. 1 is the refrigerating circuit figure that has the heat pump type air adjusting device of refrigerating circuit.In the figure, the 1st, compressor, the 2nd, four-way switching valve, the 3rd, and be provided with the indoor heat converter of indoor fan 7, the 4th, pressure reducers such as capillary, the 5th, and be provided with the outdoor heat converter of outdoor fan 6.In addition, in the figure, the 8th, accumulator.When this conditioner carried out heating operation, four-way switching valve 2 switched to solid line one side, drive compression machine 1.So cold-producing medium is flowed through from compressor 1 behind indoor heat converter 3, pressure reducer 4, the outdoor heat converter 5, turns back to compressor 1, the effect of above-mentioned indoor heat converter 3 performance condensers, the effect of outdoor heat converter 5 performance evaporimeters simultaneously.Though Fig. 2 shows the structure of the indoor heat converter 3 that has condenser function when carrying out heating operation briefly,, the component parts identical with heat exchanger member in the past shown in Figure 10 indicates same symbol.The structure of this indoor heat converter 3 is except the shape of fin 10, and is identical with conventional art shown in Figure 10.That is to say that a plurality of fin 10 of being made up of heat-conductive characteristic good metal such as for example aluminium are arranged side by side in accordance with regulations at interval, several hairpin shape heat-transfer pipes 11 insert in this fin, and its end interconnects with U-shaped tube connector 12 simultaneously.Adopt this structure, on wind first sidepiece 10a of above-mentioned several fin 10 and second sidepiece of wind 10b, be equipped with several heat- transfer pipes 13,14 respectively, these heat- transfer pipes 13,14 are staggered for integral body.Cold-producing medium both direction about inlet tube 9 is divided into from compressor 1 flows into the heat-transfer pipe 14 of wind downside, and through carrying out after the heat exchange between the fin 10 flow air A, flows in the heat-transfer pipe 13 of wind upside.Carry out after the heat exchange once more between cold-producing medium in the heat-transfer pipe 13 of inflow wind upside and the process fin 10 flow air A, collaborate together from both direction up and down, and, turn back to compressor 1 again through pressure reducer 4 and evaporimeter 5 then from outlet 8 outflows.
Hereinafter utilize Fig. 3 to describe the fin 10 of above-mentioned indoor heat converter 3 in detail.Shown in this figure 13 is wind upside heat-transfer pipes, and 14 is wind downside heat-transfer pipes.There is shown its section.The diameter of these heat- transfer pipes 13,14 is identical, and the size of diameter is represented with the W1 among the figure.In the drawings, the 15th, otch.This otch 15 with the center that is connected adjacent above-mentioned wind upside heat-transfer pipe 13 and wind downside heat-transfer pipe 14 between imaginary line 20 mode of intersecting extend setting.Its crossover location is, when the distance between the peripheral part that the wind upside heat-transfer pipe 13 on the above-mentioned imaginary line 20 and wind downside heat-transfer pipe 14 stand facing each other mutually is L1, when distance from the above-mentioned peripheral part of above-mentioned wind downside heat-transfer pipe 14 to above-mentioned crossover location is L2, have following formula to set up:
0.2≤L2/L1≤0.8
The scope of set above-mentioned otch 15 is that when being the center with above-mentioned imaginary line 20, its width W 2 satisfies following formula:
0.4≤W2/W1≤1.3
Further, above-mentioned otch 15 is by following scope setting, promptly when the orientation of wind downside heat-transfer pipe 14 and otch 15 folded angles are θ, 5 °≤θ≤175 °, simultaneously, between the adjacent otch 15 as shown in Figure 3, to be provided with mutually oppositely and with mode that above-mentioned orientation intersects.Its concrete shape can be made of the slotted hole shown in Fig. 5 A in addition.Because wind downside heat-transfer pipe 14 is roughly being arranged in parallel to each other with wind upside heat-transfer pipe 13, so above-mentioned otch 15 also is arranged to also have same angle with respect to the orientation of wind upside heat-transfer pipe 13.
In the heat exchanger of above-mentioned formation, extension is being provided with several otch 15 on fin 10.These otch 15 dispose side by side along the orientation of wind downside heat-transfer pipe 14 or wind upside heat-transfer pipe 13, and simultaneously, its bearing of trend becomes 5 °～175 ° predetermined angular with above-mentioned orientation.Therefore, the bearing of trend of otch 15 and orientation X are inconsistent, and can avoid making orientation x is the reduction of rigidity of the fin 10 of flexural center.Thereby the operation when having improved fin 10 and using can prevent the reduction of the heat exchange performance that the distortion because of fin 10 causes and the increase of flowing resistance simultaneously.
In addition, in above-mentioned heat exchanger,, can prevent the aweather unnecessary heat conduction of first sidepiece 10a of second sidepiece of wind 10b from fin 10 by on the fin 10 between wind upside heat-transfer pipe 13 and the wind downside heat-transfer pipe 14, otch 15 being set.And, when the diameter of above-mentioned heat- transfer pipe 13,14 is W1, when width that the zone of otch 15 is set is W2,0.4≤W2/W1.So, can suppress above-mentioned unnecessary heat conduction reliably, shown in Fig. 6 curve map, like that, can give full play to heat-exchange capacity.In addition, because W2/W1≤1.3 can avoid the rigidity of fin 10 to reduce under the user mode usually.Moreover, because 0.2≤L2/L1≤0.8, make above-mentioned otch 15 be arranged on the central portion of imaginary line 20, thus, shown in the curve map of Fig. 7 like that, can give full play to heat-exchange capacity.
Fig. 4 shows another embodiment of the present invention.Component parts identical with component parts embodiment illustrated in fig. 3 among Fig. 4 indicates same symbol.In this heat exchanger, on first sidepiece of wind 100a of fin 100, be provided with wind upside louver board 16,17, on second sidepiece of wind 100b, be provided with wind downside louver board 18.These louver boards the 16,17, the 18th allow its part protuberance and the so-called joint-cutting type (with reference to Fig. 5 B) that forms from the surface of fin 100, edge 16a, the 17a of its cut-out, 18a are with outstanding towards the ventilation road direction of air A and form with mode that this direction of ventilation A intersects.And on first sidepiece of wind 100a of fin 100, at wind upside (left side of Fig. 4) the formation fin connecting portion 19 of wind downside heat-transfer pipe 14, this fin connecting portion 19 is clipped between two set wind upside louver boards 16,17 of wind lower side.On fin 100, on formed pars intermedia between the wind downside louver board 18 of the wind upside louver board 16,17 of wind lower side and wind top side, dispose several otch 15, these otch 15 are crossing with the imaginary line 20 between the center that is connected adjacent and the wind upside heat-transfer pipe 13 that stands facing each other and wind downside heat-transfer pipe 14 with arranging.And when the width of above-mentioned pars intermedia was W3, above-mentioned otch 15 is arranged on this pars intermedia under the prerequisite that following equation is set up central portion width was in the zone of W4:
0.4≤W4/W3≤0.9
In addition, the orientation almost parallel of the orientation X of above-mentioned otch 15 and wind downside heat-transfer pipe 14, therefore also with the orientation almost parallel of wind upside heat-transfer pipe 13.If along the wind upside heat-transfer pipe 13 of this orientation and the distance between wind downside heat-transfer pipe 14 centers is L3, along the distance between the center of the wind upside heat-transfer pipe 13 of equidirectional and above-mentioned otch 15 is L4, and then above-mentioned otch 15 is arranged on the position that following equation is set up:
0.3≤L4/L3≤0.7
Further, above-mentioned otch 15 also forms in the following manner, and its orientation X and bearing of trend angulation θ are 5 °～175 °, and the bearing of trend of adjacent cut 15 is opposite each other.
In the heat exchanger of above-mentioned formation, owing to be provided with louver board 16,17,18 on the surface of fin 100, its edge 16a, 17a, 18a give prominence to towards the ventilation road direction of air A, therefore, improve the exothermal efficiency of fin 100, and improved heat-exchange capacity.In addition, by otch 15 is set, can prevent unnecessary heat conduction on the indoor heat converter that can improve heat-exchange capacity by fin 100.And identical with the situation of the embodiment that utilizes Fig. 3 to illustrate, otch 15 is arranged the ground configuration along the orientation of wind downside heat-transfer pipe 14 or wind upside heat-transfer pipe 13, and its bearing of trend becomes 5 °～175 ° predetermined angular with above-mentioned orientation.Therefore, direction is set in the extension of otch 15 and orientation X is inconsistent, and can avoid with the orientation is that the rigidity of fin 100 of flexural center reduces.As a result, the operation in the time of can improving fin 100 uses.
In addition, in above-mentioned heat exchanger, by on the fin 100 between wind upside heat-transfer pipe 13 and the wind downside heat-transfer pipe 14, otch 15 being set, can prevent the aweather unnecessary heat conduction of first sidepiece 100a of second sidepiece of wind 100b from fin 100, and, between wind upside louver board 16,17 and the wind downside louver board 18 width of formed pars intermedia be W3, when width that the zone of otch 15 is set is W4,0.4≤W4/W3.Thus, can suppress above-mentioned unwanted heat conduction reliably.Like that, identical shown in Fig. 8 curve with the situation of the foregoing description shown in Figure 3, can give full play to heat-exchange capacity.Moreover, because W4/W3≤0.9, so, can avoid the rigidity of fin 100 to reduce.Further, because 0.3≤L4/L3≤0.7, above-mentioned otch 15 is arranged on the central portion of imaginary line 20, and therefore, this situation is the same with situation embodiment illustrated in fig. 3, like that, can give full play to heat-exchange capacity shown in the curve of Fig. 9.
In addition, owing to the heat-exchange capacity height between the air A of fin 100 that is provided with louver board 16,17,18 and process, particularly the temperature of wind upside heat-transfer pipe 13 pars intermedia each other of first sidepiece of its wind 100a is easy to descend, therefore, the occasion that can not give full play to heat-exchange capacity is arranged.But, in the present embodiment, owing to be provided with fin connecting portion 19, therefore, there is a part of heat of the wind downside heat-transfer pipe 14 that high temperature refrigerant flows through to pass to first sidepiece of wind 100a by above-mentioned fin connecting portion 19 at the wind upside of wind downside heat-transfer pipe 14.As a result, can prevent the abnormal low temperatureization of the above-mentioned part of first sidepiece of wind, improve heat-exchange capacity.
More than, though specific embodiments of the invention are illustrated,, the present invention is not limited to above-mentioned form, can make various changes within the scope of the invention.For example, above-mentioned otch 15 is except adopting the slotted hole structure shown in Fig. 5 A, also can adopt the kerf structure that allows a fin part swell shown in Fig. 5 B, or adopt the blind window structure that allows side depression (or protuberance) shown in Fig. 5 C, can also adopt the plunging type structure that around slotted hole, is provided with flange shown in Fig. 5 D.In either case, all otch 15 should be on fin 10,100, formed, the aweather unwanted heat conduction of first sidepiece 10a, 100a can be prevented from second sidepiece of wind 10b, the 100b of fin 10,100 by this otch 15.In addition, though above the situation that otch 15 is set on when heating indoor heat converter 3 as condenser function is illustrated,, when refrigeration, also this otch 15 can be set on the outdoor heat converter 5 as condenser function.
Industrial application
Heat exchanger of the present invention is applicable to the heat pump type air adjusting device that has refrigerating circuit Deng.
Claims (4)
1, a kind of heat exchanger, it is the intersection plate fin type heat exchanger, several fin (10 have been arranged side by side, 100), at this fin (10,100) first sidepiece of wind (10a, 100a) the upper edge specific direction connects the ground alignment arrangements several wind upside heat-transfer pipes (13), simultaneously at second sidepiece of its wind (10b, 100b) the roughly the same direction of upper edge and above-mentioned wind upside heat-transfer pipe (13) connects the ground alignment arrangements several wind downside heat-transfer pipes (14), in addition, along specific direction spaced reciprocally alignment arrangements several otch (15) are arranged, make above-mentioned fin (10,100) first sidepiece of wind (10a, 100a) with second sidepiece of wind (10b, 100b) thermal release, having at least a direction of intersecting along the orientation (x) with above-mentioned otch (15) to extend ground in the above-mentioned otch (15) is provided with
On first sidepiece of wind (100a) of above-mentioned fin (100) and second sidepiece of wind (100b), be respectively arranged with louver board (16,17; 18), this louver board (16,17; 18) form in the following manner, it cuts off edge (16a, 17a; 18a) outstanding towards ventilation road direction, should cut off edge (16a, 17a simultaneously; Direction is set in extension 18a) and direction of ventilation intersects, and above-mentioned otch (15) is arranged on formed pars intermedia between the louver board (18) of the louver board (16,17) of wind upside and wind downside.
2, heat exchanger according to claim 1, it is characterized in that, when the width of above-mentioned pars intermedia on the direction that wind upside heat-transfer pipe (13) and wind downside heat-transfer pipe (14) are arranged side by side is W3, when the above-mentioned width that is arranged side by side on the direction that extends the scope that above-mentioned otch (15) is set is W4, has equation 0.4≤W4/W3≤0.9 to set up.
3, heat exchanger according to claim 1, it is characterized in that, distance adjacent along the orientation of above-mentioned wind upside heat-transfer pipe (13) or wind downside heat-transfer pipe (14) and that stand facing each other between two heat-transfer pipes (the 13 and 14) center, ground is L3, when the wind upside heat-transfer pipe (13) of above-mentioned orientation and the distance between above-mentioned otch (15) center are L4, there is equation 0.3≤L4/L3≤0.7 to set up in addition.
4, heat exchanger according to claim 1, it is characterized in that, when the high temperature side cold-producing medium flows through above-mentioned wind downside heat-transfer pipe (14), the low temperature side cold-producing medium also flows by wind upside heat-transfer pipe (13), on the other hand, in first sidepiece of wind (100a) of above-mentioned fin (100), form the fin connecting portion (19) that is clipped between two wind upside louver boards (16,17) at the wind upside of wind downside heat-transfer pipe (14).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP307342/1996 | 1996-10-31 | ||
| JP8307342A JPH10132480A (en) | 1996-10-31 | 1996-10-31 | Heat exchanger for air conditioner |
| JP307342/96 | 1996-10-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1228833A CN1228833A (en) | 1999-09-15 |
| CN1159564C true CN1159564C (en) | 2004-07-28 |
Family
ID=17967970
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB971969264A Expired - Fee Related CN1159564C (en) | 1996-10-31 | 1997-10-16 | Heat exchanger for air conditioner |
Country Status (12)
| Country | Link |
|---|---|
| EP (1) | EP0936432B1 (en) |
| JP (1) | JPH10132480A (en) |
| KR (1) | KR20000034784A (en) |
| CN (1) | CN1159564C (en) |
| AU (1) | AU710016B2 (en) |
| DE (1) | DE69718343T2 (en) |
| ES (1) | ES2190544T3 (en) |
| HK (1) | HK1019354A1 (en) |
| MY (1) | MY118256A (en) |
| PT (1) | PT936432E (en) |
| TW (1) | TW415582U (en) |
| WO (1) | WO1998019126A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103537529A (en) * | 2012-07-12 | 2014-01-29 | 珠海格力电器股份有限公司 | Punching method of air-cooled heat exchanger and air-cooled heat exchanger |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100347894B1 (en) * | 2000-07-06 | 2002-08-09 | 엘지전자주식회사 | Heat exchanger |
| KR20040004967A (en) * | 2002-07-08 | 2004-01-16 | 한라공조주식회사 | A fin of heatexchanger |
| JP4495090B2 (en) * | 2006-02-03 | 2010-06-30 | ダイキン工業株式会社 | Air conditioner |
| KR20090022840A (en) * | 2007-08-31 | 2009-03-04 | 엘지전자 주식회사 | Heat exchanger |
| DE102008024562B4 (en) * | 2008-05-21 | 2021-06-10 | Stiebel Eltron Gmbh & Co. Kg | Heat pump device with a finned tube heat exchanger as an evaporator |
| MX2012013792A (en) | 2010-05-31 | 2012-12-17 | Sanden Corp | Heat exchanger and heat pump that uses same. |
| KR20140116625A (en) * | 2013-03-25 | 2014-10-06 | 엘지전자 주식회사 | A heat exchanger |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58108394A (en) * | 1981-12-21 | 1983-06-28 | Hitachi Ltd | Heat exchanger |
| JPS58138994A (en) * | 1982-02-15 | 1983-08-18 | Fuji Heavy Ind Ltd | Heat exchanger |
| JPH02254269A (en) * | 1989-03-27 | 1990-10-15 | Hitachi Ltd | Finned tube type heat exchanger |
| DE3938842A1 (en) * | 1989-06-06 | 1991-05-29 | Thermal Waerme Kaelte Klima | CONDENSER FOR A VEHICLE AIR CONDITIONING REFRIGERANT |
| JP2753354B2 (en) | 1989-12-22 | 1998-05-20 | 株式会社日立製作所 | Heat exchanger for air conditioner |
| DE4220823C2 (en) * | 1992-06-25 | 1996-08-29 | Thermal Waerme Kaelte Klima | Heating heat exchanger for passenger cars with at least two partial heat exchangers |
| KR0128678B1 (en) * | 1994-07-21 | 1998-04-04 | 김광호 | Air-condition machinery of heat exchanger |
| JP3256634B2 (en) * | 1994-08-10 | 2002-02-12 | 三菱電機株式会社 | Heat exchanger |
-
1996
- 1996-10-31 JP JP8307342A patent/JPH10132480A/en active Pending
-
1997
- 1997-10-16 CN CNB971969264A patent/CN1159564C/en not_active Expired - Fee Related
- 1997-10-16 PT PT97944133T patent/PT936432E/en unknown
- 1997-10-16 DE DE69718343T patent/DE69718343T2/en not_active Expired - Lifetime
- 1997-10-16 KR KR1019980710166A patent/KR20000034784A/en not_active Application Discontinuation
- 1997-10-16 ES ES97944133T patent/ES2190544T3/en not_active Expired - Lifetime
- 1997-10-16 WO PCT/JP1997/003729 patent/WO1998019126A1/en active IP Right Grant
- 1997-10-16 EP EP97944133A patent/EP0936432B1/en not_active Expired - Lifetime
- 1997-10-16 AU AU45731/97A patent/AU710016B2/en not_active Ceased
- 1997-10-23 TW TW088203348U patent/TW415582U/en not_active IP Right Cessation
- 1997-10-28 MY MYPI97005095A patent/MY118256A/en unknown
-
1999
- 1999-10-07 HK HK99104402A patent/HK1019354A1/en not_active IP Right Cessation
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103537529A (en) * | 2012-07-12 | 2014-01-29 | 珠海格力电器股份有限公司 | Punching method of air-cooled heat exchanger and air-cooled heat exchanger |
| CN103537529B (en) * | 2012-07-12 | 2015-08-26 | 珠海格力电器股份有限公司 | Punching method of air-cooled heat exchanger and air-cooled heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20000034784A (en) | 2000-06-26 |
| DE69718343D1 (en) | 2003-02-13 |
| WO1998019126A1 (en) | 1998-05-07 |
| TW415582U (en) | 2000-12-11 |
| PT936432E (en) | 2003-03-31 |
| EP0936432A1 (en) | 1999-08-18 |
| AU710016B2 (en) | 1999-09-09 |
| AU4573197A (en) | 1998-05-22 |
| CN1228833A (en) | 1999-09-15 |
| EP0936432A4 (en) | 2000-01-19 |
| DE69718343T2 (en) | 2003-09-18 |
| EP0936432B1 (en) | 2003-01-08 |
| MY118256A (en) | 2004-09-30 |
| JPH10132480A (en) | 1998-05-22 |
| HK1019354A1 (en) | 2000-02-03 |
| ES2190544T3 (en) | 2003-08-01 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20040728 Termination date: 20111016 |