CN103148643A - Air conditioner - Google Patents
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- CN103148643A CN103148643A CN2012103042825A CN201210304282A CN103148643A CN 103148643 A CN103148643 A CN 103148643A CN 2012103042825 A CN2012103042825 A CN 2012103042825A CN 201210304282 A CN201210304282 A CN 201210304282A CN 103148643 A CN103148643 A CN 103148643A
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Abstract
The invention provides an air conditioner which is further improved in terms of performance of heat transfer between the air conditioner and the air. In a heat exchanger (6), a plurality of first heat transfer pipes arranged on a windward side of a fin and a plurality of second heat transfer pipes arranged on a leeward side of the fin are disposed along substantially the same direction. Cutting portions are disposed among the plurality of first heat transfer pipes, and cutting grooves are disposed between the plurality of first heat transfer pipes and the plurality of second heat transfer pipes. A connecting portion is disposed between one cutting groove and the adjacent cutting groove and is shorter than a distance between each two heat transfer pipes among the plurality of first heat transfer pipes, and the cutting portions longer than the connecting portions are disposed adjacent to the connecting portions. The cutting grooves arranged between the plurality of first heat transfer pipes and the plurality of second heat transfer pipes are configured to be eccentric to the plurality of first heat transfer pipes or the plurality of second heat transfer pipes relative to a central line of a first column.
Description
Technical field
The present invention relates to air conditioner.
Background technology
In air conditioner in (air conditioner, air-conditioning equipment), when utilizing heat exchanger as condenser, the refrigerant temperature in condensation territory and to cross the poor change of refrigerant temperature in cold territory large.Therefore, when having formed intersection finned tube (cross-fin tube) type heat exchanger with a plurality of row, produce the heat that the cold-producing medium in condensation territory possesses and conduct (leading across biographies) between the row of fin, the phenomenon that moves to the low-temperature refrigerant in mistake cold territory.Therefore, existence is as the problem of the hydraulic performance decline of condenser.As the technology that solves this problem, the technology that known patent document 1 is put down in writing.
The prior art document
Patent documentation
Patent documentation 1: Japanese patent laid-open 8-54194 communique
For improve and air between heat transfer property, have the scheme of having cut section in the fin setting.On the other hand, for heat conduction between the row that prevent fin, a part of sometimes cutting off fin arranges grooving.And, also exist for improve and air between heat transfer property, and prevent above-mentioned heat conduction, and with grooving with cut the scheme of section.But, only utilize such technology, still inadequate as the technology that prevents heat conduction and raising hot property.
Summary of the invention
The present invention makes in view of above-mentioned problem, its purpose be to provide further improved and air between the air conditioner of heat transfer property.
The result that the present inventors attentively study in order to solve above-mentioned problem, thus found can solve above-mentioned problem by the configuration that makes the section of having cut and grooving become regulation, and completed the present invention.
According to the present invention, can provide and air between the air conditioner that further improves of heat transfer property.
Description of drawings
Fig. 1 means the integrally-built figure of the air conditioner 100 of present embodiment.
Fig. 2 means the figure of structure of the indoor heat exchanger 6 of the air conditioner 100 that is applicable to present embodiment.
Fig. 3 means the figure of structure of the reheater 6b of the 1st embodiment that is applicable to indoor heat exchanger 6.
Fig. 4 means the figure of structure of the reheater 6b of the 1st embodiment that is applicable to indoor heat exchanger 6.
Fig. 5 means near the enlarged drawing of connecting portion of the reheater 6b of the 1st embodiment that is applicable to indoor heat exchanger 6.
Fig. 6 means the chart of total heat dissipation capacity of reheater 6b.
Fig. 7 means the chart of total heat dissipation capacity of reheater 6b.
Fig. 8 means the chart of heat dissipation capacity of the first row of reheater 6b.
Fig. 9 means the figure of structure of the reheater 6bB of the 2nd embodiment that is applicable to indoor heat exchanger 6.
Figure 10 means the figure of structure of the reheater 6bB of the 2nd embodiment that is applicable to indoor heat exchanger 6.
Figure 11 means the figure of structure of the reheater 6bC of the 3rd embodiment that is applicable to indoor heat exchanger 6.
Figure 12 means the figure of structure of the reheater 6bD of the 4th embodiment that is applicable to indoor heat exchanger 6.
Figure 13 means the figure of structure of the reheater 6bE of the 5th embodiment that is applicable to indoor heat exchanger 6.
Figure 14 means the figure of structure of the cooler 6aA of the 6th embodiment that is applicable to indoor heat exchanger 6.
in figure: 6-indoor heat exchanger (heat exchanger), 6a-cooler, 6b-reheater, 10-grooving, 10a-grooving (the 1st grooving), 10b-grooving (the 2nd grooving), 11-connecting portion, 11a-connecting portion (the 1st connecting portion), 11b-connecting portion (the 2nd connecting portion), 12-cut section, 12a-cut section's (the 1st has cut section), 12b-cut section, 12c-cut section's (the 2nd has cut section), 12d-cut section, 13-heat-transfer pipe, 13a-heat-transfer pipe (consisting of the heat-transfer pipe of more than the 1st heat-transfer pipe), 13b-heat-transfer pipe (consisting of the heat-transfer pipe of more than the 2nd heat-transfer pipe), 13c-heat-transfer pipe (consisting of the heat-transfer pipe of more than the 3rd heat-transfer pipe), 20a-center line (line between the center of more than the 1st heat-transfer pipe of link), 20b-center line (line between the center of more than the 2nd heat-transfer pipe of link), 20c-center line (line between the center of more than the 3rd heat-transfer pipe of link), center line between the 21a-row (center line between the 1st row), center line between the 21b-row (center line between the 2nd row).
The specific embodiment
Below, with reference to accompanying drawing, illustrate to be used for implementing mode of the present invention (present embodiment).At first, with reference to Fig. 1 and Fig. 2, the overall structure of the air conditioner of present embodiment is described.Afterwards, with reference to Fig. 3 ~ Fig. 8, the structure of the heat exchanger of the air conditioner that consists of present embodiment is described.In addition, Fig. 9 ~ Figure 14 is the variation with reference to the 1st embodiment of Fig. 1 ~ Fig. 8 explanation.
1. the 1st embodiment
The air conditioner of the 1st embodiment is hot Pump air conditioner.Particularly, the air conditioner 100 of the 1st embodiment shown in Fig. 1 (refrigerating circulation system figure) is made of compressor 1, cross valve 2, outdoor heat exchanger 3, outdoor draft fan 4, expansion valve 5, indoor heat exchanger 6 and indoor blower 7.In addition, in Fig. 1, represent the flow direction of cold-producing medium with the arrow in figure.
During the cooling operation of air conditioner 100 (Fig. 1 (a)), be supplied to outdoor heat exchanger 3 by the cold-producing medium of compressor (Compressor) 1 compression by cross valve 2.At this moment, the direction of cross valve 2 is redefined for the mode as shown in Fig. 1 (a).And the cold-producing medium that is supplied to outdoor heat exchanger 3 carries out heat exchange with the outdoor air that is imported by outdoor draft fan 4, thereby condensation liquefaction is carried out in heat radiation.Afterwards, the liquid refrigerant in outdoor heat exchanger 3 condensations passes through expansion valve 5 decompressions, temperature decline, arrival indoor heat exchanger 6.Like this, the cold-producing medium that is supplied to indoor heat exchanger 6 carries out heat exchange at indoor heat exchanger 6 and the room air that is imported by indoor blower 7.And cold-producing medium evaporates from the room air heat absorption, again is supplied to compressor 1.At this moment, be discharged into indoor air and become cold wind.
On the other hand, air conditioner 100 heat when running, the direction setting of cross valve 2 is the mode shown in Fig. 1 (b).Therefore, by the cold-producing medium that compressor 1 compresses, at first be supplied to indoor heat exchanger 6 and carry out heat exchange and condensation.Particularly, compressed by compressor 1 and cold-producing medium that temperature rises at indoor heat exchanger 6 to indoor radiating (namely discharging warm braw), cold-producing medium self condensation.Afterwards, after expansion valve 5 decompressions, utilize outside heat to evaporate at outdoor heat exchanger 3 by outdoor draft fan 4.Afterwards, cold-producing medium is supplied to compressor 1 again.
Fig. 2 is the figure of the structure of the in detail expression indoor heat exchanger 6 that is applicable to air conditioner 100.More specifically, Fig. 2 is the side view of indoor heat exchanger 6, and cold-producing medium flows in the interior edge of heat-transfer pipe 13 direction vertical with paper.Indoor wind all can be narrated below with the cooler 6a and the reheater 6b(that consist of indoor heat exchanger 6 as shown in the figure) whole Surface Contact.And, the contact and heated air is released into indoor.In addition, in Fig. 2, the flow direction of the cold-producing medium when having represented to heat running.Therefore, the flow direction and the illustrated opposite direction of the cold-producing medium during cooling operation.
Cooler 6a becomes the heat exchanger that is divided into 3 row by grooving 10.By these groovings 10, can suppress the heat conduction between heat-transfer pipe 13.Cold-producing medium is divided into two-way and is supplied to cooler 6a, the independently heat-transfer pipe 13 of flowing through respectively.After cold-producing medium was discharged from cooler 6a independently, cold-producing medium collaborated again to a system.Reheater 6b is also separated by grooving 10, becomes the heat exchanger of 3 row.Just, 2 row of downwind side (row 6b2, row 6b3) are made of two systems (two heat-transfer pipe 13), and 1 row of weather side (row 6b1) are these two systems interflow and a system obtaining.
Pressure-reducing valve 8 is used carrying out so-called when running heat dehumidifying again, at cooling operation, control in the little mode of decompression amplitude variation when heating running.
Air conditioner 100(indoor heat exchanger 6) heat when running, from compressor 1(with reference to Fig. 1) the cold-producing medium fork of the HTHP of discharging flows into from two of the downwind side of cooler 6a.Then, in heat-transfer pipe 13, the weather side that flows to shown in dotted line is during this period to the air heat radiation that contacts.Thus, air is heated, and heated air (warm braw) is supplied to indoor.
Cold-producing medium interflow from cooler 6a discharges also branches to two heat-transfer pipes 13 again via pressure-reducing valve 8, is supplied to reheater 6b.The cold-producing medium that is supplied to reheater 6b becomes the two-phase state of liquids and gases.Then, in reheater 6b, cold-producing medium is further to the air heat radiation, thus cold-producing medium liquefaction.On the other hand, heated air is discharged into indoor.
In reheater 6b, more past leeward sidles, and air themperature rises gradually.Therefore, constitute: flow with respect to the condensation territory cold-producing medium that is the mistake cold territory of low temperature the side (row 6b1) of being in the wind.And, for the thermal conductivity in the heat-transfer pipe 13 of the cold-producing medium that improved cold territory, system's number is reduced to a system from two systems, improve flow velocity.Therefore, roughly, the cold-producing medium of condensation process (gas) is from the weather side of reheater 6b flow through the 2nd row (row 6b2) and the 3rd row (being listed as 6b3) these two systems.On the other hand, the cold-producing medium of the liquefaction system of weather side the 1st row (row 6b1) that flows through.
The fin of reheater 6b (fin) 9 is for becoming one structure with 3 row (row 6b1, row 6b2, row 6b3).Therefore, be in the 2nd row (condensation territory of condensation process; Row 6b2) heat that cold-producing medium discharges might flow into the 1st row that become low temperature that liquefy by fin 9 and (cross cold territory; Row 6b1) cold-producing medium.And if produce such phenomenon, the heat of cold-producing medium returns to cold-producing medium self rather than air, so radiating efficiency reduces.That is, the heat between such cold-producing medium that utilizes fin 9 moves, and the heat dissipation capacity from the cold-producing medium to the air is reduced, thus heating capacity decline, thereby not preferred.Therefore, be indoor heat exchanger 6 at cooler 6a and reheater 6b() in, between each row, grooving 10 etc. is set, suppress the heat conduction between row.Thus, prevent that heat-transfer pipe 13 heat each other from moving.
Next, describe the structure of the reheater 6b of the indoor heat exchanger 6 that consists of air conditioner 100 in detail with reference to Fig. 3 ~ Fig. 8.Should illustrate, in Fig. 3 ~ Fig. 5, hollow arrow represents the flow direction of air.And identical symbol is given in the parts identical with Fig. 1 and Fig. 2 and zone, omits detailed explanation.
Fig. 3 is the side view of the direction vertical with the flow direction of the cold-producing medium of reheater 6b shown in Figure 2.As the reheater 6b of heat exchanger, as shown in Figure 3, be to have fin 9, connect fin 9 and be set to staggered a plurality of heat-transfer pipes 13, be arranged on the grooving 10 on surface of fin 9 and the intersection fin-and-tube type heat exchanger of having cut section 12.
Particularly, in reheater 6b, cold-producing medium is in the internal flow of the heat-transfer pipe 13 of staggered configuration.Reheater 6b constitutes 3 row as mentioned above.And, by grooving 10(10a, the 10b that arranges between each row), suppress as described above the heat conduction between each row.And each grooving 10 way therein is provided with connecting portion 11(11a, 11b), so compare with the situation that there is no connecting portion 11, guaranteed the intensity of fin 9.And, each heat-transfer pipe 13(13a, 13b, 13c) roughly equidirectionally side by side, dispose the 12(12a of the section of having cut, 12b, 12c, the 12d that extend along column direction between them).Thus, can with the heat of cold-producing medium without being delivered to lavishly air, improve the heat conductivility of air and fin 9.
At this, at the grooving 10a that is arranged between the 1st row and the 2nd row, connecting portion 11a is arranged near the substantial middle (substantial middle) of (intersegmental distance) between two heat-transfer pipe 13a adjacent with the 1st row.And, at the weather side of connecting portion 11a, be adjacent to dispose the longer 12a of the section of having cut of length of the Length Ratio connecting portion 11a of column direction.And, with respect to center line 21a between row, grooving 10a is eccentric in the 12a of the section of the having cut side of weather side and configures, and between these row, center line 21a is apart from being identical distance from the center line 20a at the center of the heat-transfer pipe 13a of the link weather side that is represented by dotted lines and the center line 20b at center that links the heat-transfer pipe 13b of the 2nd row.
In addition, in present embodiment, grooving 10a is eccentric in cut section's 12a side to mean, make with and grooving 10a be the mode of same linearity and the connecting portion 11a that arranges close to the 12a of the section of having cut that is arranged between adjacent heat-transfer pipe 13.Therefore, cut the 12a of section side in the situation that grooving 10a is eccentric in, if grooving 10a is long apart from the eccentric amplitude of center line 21a between row, grooving 10a shortens with the distance of having cut the 12a of section.That is, if determined eccentric amplitude, connecting portion 11a and the distance of having cut between the 12a of section are also determined.Also identical about grooving 10b.
Further describe this point with reference to Fig. 4.Be arranged on grooving 10a between the 1st row and the 2nd row on the direction vertical with flow of refrigerant, be arranged on and the 12a of the section of having cut and cut section 12b between adjacent with downwind side that weather side is adjacent.Concrete position is, grooving 11a is disposed at and is listed as a center line 21a and compares the more close 12a(of the section weather side of having cut).That is, on the direction vertical with flow of refrigerant, the distance of having cut between the 12a of section and connecting portion 11a is shorter than the distance of having cut between the 12b of section and connecting portion 11a.
That is, the following setting is eccentric in weather side with grooving 10a and the interval 30a that cut between the 12a of section than grooving 10b and the narrower mode of interval 30b of having cut between the 12c of section.By such configuration grooving 10a, make grooving 10a and the fin width of having cut between the 12a of section narrows down, can dwindle the sectional area in cold-producing medium flowed the fin zone in cold territory.
With reference to Fig. 5, further describe this point.Fig. 5 is the enlarged drawing of the A section of Fig. 4.Dispose length (width) at grooving 10a and be the connecting portion 11a of W1.And length (width) is adjacent setting of weather side of the 12a of the section of having cut and the connecting portion 11a of W2.And the distance (distance between centers of heat- transfer pipe 13a, 13a) that is disposed between heat-transfer pipe 13a, the 13a of the both sides of having cut the 12a of section is W3.
As mentioned above, if the temperature of cold-producing medium of the temperature of the cold-producing medium of the heat-transfer pipe 13a that relatively flows through and the heat-transfer pipe 13b that flows through, the temperature of the cold-producing medium of the heat-transfer pipe 13a that was in cold territory of flowing through is low.And, if this temperature difference is larger, higher to the radiating efficiency (situation when heating running) of air.Therefore, prevent that the heat conduction from heat-transfer pipe 13b to heat-transfer pipe 13a is very important.
When carrying out heat conduction from heat-transfer pipe 13b to heat-transfer pipe 13a, the shortest heat conduction distance is the straight line (double dot dash line in figure) at the center of each heat-transfer pipe of link 13a, 13b.But, be provided with grooving 10a in reheater 6b, so the beeline during heat conduction becomes the straight line (heavy line) by the end of connecting portion 11a.And, in reheater 6b, arrange because grooving 10a and connecting portion 11a are moved further to weather side, so that beeline becomes is longer.Therefore, the heat conduction distance is elongated, so have advantages of in heat-transfer pipe 13 difficult generation heat conduction each other.
And, on the shortest path of the heat conduction that represents with heavy line in Fig. 5, exist and cut the 12a of section.That is the mode of, intersecting with the straight line of the end (being the end of connecting portion 11a) of the center that links heat-transfer pipe 13a and grooving 10a and the 12a of the section of having cut that is arranged between heat-transfer pipe 13a sets has cut the 12a of section.Therefore, can make by grooving 10a and connecting portion 11a heat conduction apart from elongated basis, also by make the up and down by grooving 10a and cut the 12a of section clamping the rectangular area between the upper and lower every narrowing down, thereby the sectional area in the time of can reducing the heat conduction of this rectangular area, inhibition heat conduction.That is, can suppress the heat-transfer pipe 13a of the 1st row and the heat conduction between the 2nd heat-transfer pipe 13b that is listed as.
And, make grooving 10a be eccentric in weather side, thereby the heat transfer area of the 2nd row can be set significantly.Thus, can increase fin 9 from the 2nd row to the heat dissipation capacity of air.
And, intersegmental neighbouring from heat-transfer pipe 13 farthest apart from central authorities.Therefore, transmit from the heat of heat-transfer pipe 13 is difficult, so might reduce (being that fin efficiency descends) near the heat dissipation capacity central authorities.But in reheater 6b, grooving 10a and the interval of having cut between the 12b of section broaden.Therefore, near intersegmental central authorities at the 2nd row, heat transfer area is large, so from the easy heat conduction of heat-transfer pipe 13b, fin efficiency be difficult for to descend.That is, be difficult for generation to the decline of the radiating efficiency of air heat radiation.Like this, can effectively utilize by making the heat transfer surface area of eccentric the 2nd row that enlarge of grooving 10a.
And connecting portion 11a is configured near heat-transfer pipe 13a intersegmental central authorities of weather side, so by making grooving 10a windward side shifting, can make as mentioned above the heat conduction distance between heat-transfer pipe 13a and heat-transfer pipe 13b elongated.Thus, can further improve the effect that suppresses heat conduction.
As mentioned above, make grooving 10a eccentric with respect to center line 21a between row, thus can be in the 1st row, reduce grooving 10a and cut distance between the 12a of section, inhibition heat conduction.And, in the 2nd row, increased can heat conduction fin area, and promote to intersegmental near central authorities heat conduction and improve the efficient of fin, thereby can improve heat transfer property.
And if the heat conduction of inhibition from heat-transfer pipe 13b to heat-transfer pipe 13a, the surface temperature of the fin 9 of the 1st row descends.Thus, easily 9 transmission from heat-transfer pipe 13a to fin of heat easily produce the heat radiation to air.That is, from the heat dissipation capacity increase of the cold-producing medium in the 1st row, heating capacity increases.And heat transfer property improvement and heat transfer area increase along with the condensation territory all can bring to the increase of the heat dissipation capacity of air heat radiation, so heating capacity increases.Therefore, can make with the heat output of air to increase in the both sides of the 1st row and the 2nd row, can provide energy saving high aircondition.
In addition, in the present embodiment, do not consider issuable heat conduction between heat-transfer pipe 13b and heat-transfer pipe 13c.About this point, carry out aftermentioned with reference to Fig. 6.
Fig. 6 mean in the situation of the W1 that changes in Fig. 5 and W2, from the chart of the variation of total heat dissipation capacity of the 1st row and the 2nd row.Transverse axis is the value Rw(=(W2-W1 that the difference with W1 and W2 obtains divided by W3)/W3).And the longitudinal axis is the total heat dissipation capacity from the 1st row and the 2nd row.In addition, in the project of total heat dissipation capacity, do not consider from the 3rd row (not shown in Fig. 5.Row 6b3 in Fig. 3) heat dissipation capacity.
As shown in Figure 6, Rw is 0.15 o'clock, total heat dissipation capacity minimum (minimum).Produce this phenomenon based on following reason.If namely reduce Rw, in other words increase W1, or reduce W2, or increase W3, the heat conduction between heat- transfer pipe 13a, 13b increases.Therefore, the heat dissipation capacity from the 2nd row increases.But in this situation, the heat dissipation capacity of the 1st row reduces.
On the other hand, if increase Rw, in other words reduce W1, or increase W2, or reduce W3, the heat conduction between heat- transfer pipe 13a, 13b is suppressed.Therefore, the heat dissipation capacity from the 2nd row reduces.But in this situation, the heat dissipation capacity of the 1st row increases.Thus, expression exists by both balances the minimum condition that becomes.
If Rw is less than 0.15, total heat dissipation capacity is tended to increase.But as mentioned above, the heat dissipation capacity from the 1st row that the impact of heat conduction is large reduces.Therefore, from cold this viewpoint of the mistake that realizes cold-producing medium, not preferred.Therefore, from cold this viewpoint of the mistake that realizes cold-producing medium, preferably suppress the impact of heat conduction, and total heat dissipation capacity is increased.Particularly, preferred Rw is more than 0.15, more preferably more than 0.2.So the mode that preferably satisfies these scopes with Rw sets connecting portion 11a, has cut section 12 and heat-transfer pipe 13a.
Particularly, for example design reheater 6b, make W1=2mm, W2=13mm, W3=20mm.In such situation, Rw is 0.55, can suppress the impact of heat conduction and increase whole heat dissipation capacity.In addition, in the 1st embodiment, design reheater 6b in the mode that becomes these values.
And Fig. 7 has represented that width W 1 is with respect to the ratio (connecting ratio R c) of width W 3 and the relation between total heat dissipation capacity.Transverse axis is to connect ratio R c(=W1/W3), the longitudinal axis is total heat dissipation capacity.Total heat dissipation capacity with the connection ratio 0(of the situation (that is, the situation of connecting portion 11a not being set) that is equivalent to cut apart fully namely W1=0) be starting point, and ratio increases and temporary transient increasing along with connecting, reduction after Rc is to become greatly (maximum) at 0.2 o'clock.Afterwards, if Rc is larger than 0.6, be that 0 situation is also little than Rc.
In addition, chart shown in Figure 7 is the chart that obtains when the 12a of the section of having cut shown in Figure 5 is not set.Therefore, in the situation that be provided with the reheater 6b shown in Figure 5 that has cut the 12a of section, the Rc that becomes when being the large total heat dissipation capacity of total heat dissipation capacity of 0 o'clock than Rc is larger than 0.6.This is because even set significantly Rc, because the 12a of section has been cut in existence, and heat conduction is obstructed.
Therefore, in order to increase total heat dissipation capacity in the mode that does not rely on the shape of cutting the 12a of section, preferably become with Rc width W 1 and the spacing W3 that mode below 0.6 is set connecting portion 11a.That is, preferably become the mode below 0.6 with W1 divided by the value (being Rc) of W3, set connecting portion 11a and heat-transfer pipe 13a.
Wherein, the mode that preferably becomes below 0.2 with Rc sets connecting portion 11a and heat-transfer pipe 13a.Just, if Rc is reduced to below 0.2, total heat dissipation capacity becomes lower than peak value.But, as shown in Figure 8, sharply increase than 0.2 little zone at Rc from the 1st heat dissipation capacity that is listed as.
In the situation that consider and be applicable to air conditioner, preferably get rid of the impact of heat conduction as far as possible, increase the heat dissipation capacity from the 1st row, increase degree of supercooling.Thus, the condensation enthalpy difference in heat exchanger is enlarged.Therefore, can suppress be used to making the constant circulating mass of refrigerant of heat dissipation capacity, can reduce the workload (being operating cost) of compressor.
Given this, increase in order to make the heat dissipation capacity from the 1st row, preferred Rc is below 0.2.Especially, in the 1st embodiment, as mentioned above, make W1=2mm, W2=13mm, W3=20mm.Therefore, Rc=W1/W3=0.1 can make the heat dissipation capacity from the 1st row increase.So, greatly improved the performance of the air conditioner of having used reheater 6b.
Yet as shown in Fig. 3 waited, reheater 6b consisted of with 3 row (row 6b1,6b2,6b3).And reheater 6b(more specifically is listed as the heat-transfer pipe 13c of 6b3) the middle cold-producing medium that flows into 2 above-mentioned phase states.Therefore, the heat-transfer pipe 13b of the 2nd row of flowing through and the cold-producing medium of heat-transfer pipe 13c of the 3rd row all are in the condensation territory, so the temperature constant of the cold-producing medium of flowing through.Therefore, produce hardly heat conduction between these row.
In the situation that can not consider these heat conduction, if unrestrictedly make grooving 10b eccentric, the heat transfer area of the 2nd row is diminished.And, might grooving 10b and the 12c of the section of having cut of the 2nd row between distance narrow down, the suppressed and fin efficiency decline of heat conduction.
Therefore, in reheater 6b, adopted as shown in Figure 3 the grooving 10b between the 2nd row and the 3rd row to be arranged on center line 21b(between row at the line of the centre of the line between the center of the line between the center that links heat-transfer pipe 13b and link heat-transfer pipe 13c) on formation.Thus, can keep the heat transfer property of the 2nd row and the 3rd row higher.
And, in reheater 6b, as shown in Figure 3, make the Length Ratio of connecting portion 11b that is arranged between the 2nd row and the 3rd row be arranged at the length of the connecting portion 11a between the 1st row and the 2nd row long.There is as mentioned above the temperature difference of cold-producing medium between the 1st row and the 2nd row, so easily produce heat conduction.Therefore, preferably suppress such heat conduction.So preferred connecting portion 11a is narrower.
On the other hand, between the 2nd row and the 3rd row, almost there is no as mentioned above the temperature difference of cold-producing medium, so be difficult for producing heat conduction.At this moment, in the 2nd row, connecting portion 11b is set, thereby near the fin 9 connecting portion 11b is by the heat-transfer pipe 13c heating of the 3rd row.Therefore, fin efficiency becomes better, and heat dissipation capacity increases.So, between the 2nd row and the 3rd row, connecting portion 11b is set widely, thereby can guarantees to rely on the heat transfer property of heat conduction.And, by increasing the width of connecting portion 11b, can also improve fin strength.
As mentioned above, in reheater 6b, can suppress the heat conduction between the 1st row and the 2nd row.And, can suppress the reduction of the caused heat dissipation capacity to the ingress of air heat radiation of such heat conduction, improve the 2nd row and the 3rd fin efficiency that is listed as.Thus, can increase to the heat dissipation capacity of air heat radiation, can improve the heat dispersion of heat exchanger 6 integral body.That is, energy saving improves.Therefore, consist of air conditioner 100 by reheater 6b is used as the reheater of indoor set, can improve the condensation performance, turn round efficiently when heating running.
2. the 2nd embodiment
Next, with reference to Fig. 9 and Figure 10, the structure of the reheater 6bB of the 2nd embodiment is described.Should illustrate, in the following description, the difference between main explanation and above-mentioned reheater 6b, the explanation of omitting same content in order to simplify.And the parts identical with reheater 6b shown in Figure 3 are given identical symbol, omit its detailed explanation.And the structure of the air conditioner beyond reheater 6b is identical with above-mentioned content.
In Fig. 9 and reheater 6bB shown in Figure 10, the position of connecting portion 11a, 11b is different from the position in above-mentioned reheater 6b.Particularly, the connector 11a in reheater 6bB is arranged on the intersegmental distance central authorities (substantial middle) of the heat-transfer pipe 13b of the 2nd row.That is, adjacent with the downside of heat-transfer pipe 13a of the 1st row and arrange.
And connecting portion 11b is arranged near the intersegmental central portion of the 3rd heat-transfer pipe 13c that is listed as.That is, adjacent with the upside of the 12d of the section of having cut of the 3rd row and arrange.
And grooving 10a is with respect to center line 21a between row, and alee side (center line 20b side) is eccentric and arrange.And, from the distance of center line 21a 12b of section to cut between row than short from the distance of the 12a of section to cut of center line 21a row.
With reference to Figure 10, further describe structure shown in Figure 9.Grooving 10a changes and is located at downwind side as mentioned above, but grooving 10a and the interval 31a that is configured between the 12b of the section of having cut of weather side of the 2nd row are narrower than grooving 10b and the interval 31b that is configured between the 12d of the section of having cut of tertial weather side.That is, interval 31a shown in Figure 10 is narrower than interval 31b.
In reheater 6bB, grooving 10a and the distance of having cut between the 12b of section narrow down.The heat transfer area of the fin 9 of the 2nd row reduces, so suppressed to the heat conduction of the 1st row.And 6b is identical with reheater, and the heat conduction distance between heat-transfer pipe 13a and heat-transfer pipe 13b is elongated, and heat conduction is suppressed.
Just, 6b is different from reheater, and on the one hand, the heat transfer area of the 2nd row diminishes, and on the other hand, it is large that the heat transfer area of the 1st row becomes.Therefore, the radiating efficiency from the 1st row rises.Thus, improved fin efficiency.Therefore, increased the heat dissipation capacity of the 1st row, the degree of supercooling of the heat-transfer pipe 13a cold-producing medium of can easily guaranteeing to flow through.
And in reheater 6bB, the width of connecting portion 11b also is set as larger than the width of connecting portion 11a.Thus, fin strength can be improved, and the heat transfer property of heat exchanger integral body can be improved.That is, energy saving improves.So, by being used as the reheater of indoor set, reheater 6bB consists of air conditioner 100, can improve the condensation performance, can turn round efficiently when heating running.
3. the 3rd embodiment
Next, with reference to Figure 11, the structure of the reheater 6bC of the 3rd embodiment is described.Should illustrate, in the following description, the difference between the described reheater 6b such as main explanation and Fig. 3, the explanation of omitting identical content in order to simplify.And the parts identical with reheater 6b shown in Figure 3 are given identical symbol, omit its detailed explanation.And the structure of the air conditioner beyond reheater 6bC is identical with above-mentioned content.In addition, in Figure 11, omitted the record of center line 21a, 21b between center line 20a, 20b, 20c and row.
In reheater 6bC, the rugosity of heat-transfer pipe 13a is thicker than the rugosity of the heat-transfer pipe 13a in reheater 6b shown in Figure 3.That is, the internal diameter of the heat-transfer pipe 13a in reheater 6bC is thicker than the internal diameter of the heat-transfer pipe 13a in reheater 6b.That is, in the reheater 6bC that consists of heat exchanger 6, in a plurality of heat-transfer pipes that consist of reheater 6bC, the internal diameter of heat-transfer pipe 13a different from the internal diameter of other heat-transfer pipes 13 (slightly).That is, comprise the different heat-transfer pipe of internal diameter 13 in reheater 6bC.
And connecting portion 11b is arranged near the intersegmental central portion of the 3rd heat-transfer pipe 13c that is listed as.
In reheater 6bC, the width of connecting portion 11b also is set as larger than the width of connecting portion 11a.Thus, fin strength can be improved, and the heat transfer property of heat exchanger integral body can be improved.
And, in reheater 6bC, be also that grooving 10a (is equivalent to center line 21a between the row in Fig. 3 with respect to center line between the row between heat-transfer pipe 13a and heat-transfer pipe 13b.Not shown in Figure 11), to having cut the 12a of the section lateral deviation heart.And grooving 10b is arranged on that between row between heat-transfer pipe 13b and heat-transfer pipe 13c, center line (is equivalent to center line 21b between the row in Fig. 3.Not shown in Figure 11) on.These points are identical with reheater 6b shown in Figure 3.
And, in reheater 6bC, grooving 10a and cut being set as than grooving 10b and having cut short apart from 32b between the 12c of section apart from 32a between the 12a of section.Like this, in the situation that the internal diameter of heat-transfer pipe 13a of the 1st row is thick, also can be by making the grooving 10a windward lateral deviation heart (that is, making the heat transfer area minimizing of the 1st row close to having cut the 12a of section), thus identical with reheater 6b, can suppress heat conduction.
And it is large that the heat transfer area of the 2nd row becomes, so can improve the fin efficiency of the 2nd row, can improve the heat transfer property as heat exchanger.That is, energy saving improves.So, by being used as the reheater of indoor set, reheater 6bC consists of air conditioner 100, can improve the condensation performance, can turn round efficiently when heating running.
4. the 4th embodiment
Next, with reference to Figure 12, the structure of the reheater 6bD that the 4th embodiment is related is described.Should illustrate, in the following description, the difference between the reheater 6b shown in main explanation and Fig. 3 etc., the explanation of omitting identical content in order to simplify.And the parts identical with reheater 6b shown in Figure 3 are given identical symbol, omit its detailed explanation.And the structure of the air conditioner beyond reheater 6bD is identical with above-mentioned content.
In reheater 6bD, 3 grooving 10(10a1,10a2,10a3) different respectively with respect to the eccentric amplitude of center line 21a between row.That is, the shortest to the distance of grooving 10a1 from center line 21a between row, the longest to the distance of grooving 10a3 from center line 21a between row.
And though not shown, heat-transfer pipe 13a(13a1,13a2,13a3,13a4 flow through) the temperature of cold-producing medium respectively different.Particularly, cold-producing medium is according to the sequential flowing of heat-transfer pipe 13a1, heat-transfer pipe 13a2, heat-transfer pipe 13a3 and heat-transfer pipe 13a4, and the temperature of cold-producing medium reduces gradually.That is, the temperature of the cold-producing medium of the heat-transfer pipe 13a1 that flows through is the highest, and the temperature of the cold-producing medium of the heat-transfer pipe 13a4 that flows through is minimum.Therefore, in reheater 6bD, be 3 according to the temperature of the cold-producing medium of flow through heat-transfer pipe 13a1,13a2,13a3,13a4 with the heat-transfer pipe 13b(that flows through in Figure 12) the temperature difference separately of cold-producing medium, set the eccentric amplitude with respect to center line 21a between row of grooving 10a.
When the temperature constant of heat-transfer pipe 13a of the 1st row or constant, for example as shown in Figure 3, connecting portion 11 is configured near heat-transfer pipe 13a intersegmental central authorities of the 1st row, thereby the distance from connecting portion 11 to two adjacent heat-transfer pipe 13a is equated.Thus, the impact of heat conduction also equates.But according to the environment for use of reheater 6b, the refrigerant temperature that might cross cold territory reduces gradually, and the temperature of the cold-producing medium of two the adjacent heat-transfer pipe 13a that flow through is different as mentioned above.Therefore, be positioned at the impact of heat conduction of heat-transfer pipe 13a4 in downstream of flow of refrigerant large.
Obvious when temperature difference is large to the heat conduction of the heat-transfer pipe 13a of the 1st row from the heat-transfer pipe 13b of the 2nd row.Therefore, near the heat-transfer pipe 13a1 of temperature difference little (that is, because the temperature of the cold-producing medium of flowing through is the highest, so the most approaching with the fin temperature of the 2nd row), preferably make eccentric amplitude less between row.By like this, can more suitably guarantee heat transfer area.Therefore, in reheater 6bD, the closer to the downstream (heat-transfer pipe 13a4) of crossing the cold-producing medium in cold territory, between row, temperature difference is larger, so make eccentric amplitude larger the closer to the downstream.
That is, in reheater 6bD, little and be not vulnerable to make the eccentric amplitude of grooving 10a1 less near the heat-transfer pipe 13a1 of heat conduction impact in temperature difference.On the other hand, larger in temperature difference, easily be subject to setting the eccentric amplitude of the grooving 10a2 heat-transfer pipe 13a2 and heat-transfer pipe 13a3 near larger near heat-transfer pipe 13a2, the 13a3 of heat conduction impact.Large especially in temperature difference, especially easily be subject near the heat-transfer pipe 13a4 of heat conduction impact, be configured in the larger mode of eccentric amplitude of the grooving 10a3 heat-transfer pipe 13a4 near.If these are summarized, for to set as follows: heat-transfer pipe 13a(13a1,13a2,13a3,13a4 flow through) the temperature of cold-producing medium and the temperature difference between the temperature of the cold-producing medium of the heat-transfer pipe 13b that flows through larger, grooving 10a(10a1,10a2,10a3) with respect to center line 21a between row eccentric amplitude larger.
Like this, the little zone of temperature difference, make the eccentric amplitude of grooving little between row.Thus, in the little zone of the impact of heat conduction, can avoid the heat transfer area of the 1st row to become too small.Its result can be kept high heat transfer property.And the large zone of temperature difference, make the eccentric amplitude of grooving large between row.Thus, reduce heat transfer area and improve the inhibition of heat conduction, realizing the raising of heat transfer property.
According to above structure, can improve the heat transfer property as heat exchanger integral body, can improve the high air conditioner of energy saving.That is, improved energy saving.So, by being used as the reheater of indoor set, reheater 6bD consists of air conditioner 100, can improve the condensation performance, can turn round efficiently when heating running.
5. the 5th embodiment
Next, with reference to Figure 13, illustrate the 5th embodiment the structure of reheater 6bE.Should illustrate, in the following description, the difference between the described reheater 6b such as main explanation and Fig. 3, the explanation of omitting identical content in order to simplify.And the parts identical with reheater 6b shown in Figure 3 are given identical symbol, omit its detailed explanation.And the structure of the air conditioner beyond reheater 6bE is identical with above-mentioned content.
In reheater 6bE, the position of connector 11a1 is different from reheater 6b.Particularly, in reheater 6b, near intersegmental apart from being provided with connecting portion 11a central authorities at heat-transfer pipe 13a, but in reheater 6bE is to the paper left to eccentric a little and arrange.Namely, connecting portion 11a2 is arranged on the straight line that the mind-set direction vertical with flow of refrigerant extended from heat-transfer pipe 13b2, but the straight line that the direction that connecting portion 11a1 is vertical with flow of refrigerant with respect to mind-set from heat-transfer pipe 13b1 is extended arranges to paper left side bias.Should illustrate, also identical with the 4th embodiment in the 5th embodiment, cold-producing medium flows through successively from heat-transfer pipe 13a1 lateral heat transfer pipe 13a4 side, and temperature reduces gradually.
When the temperature constant of the heat-transfer pipe 13a that is assumed to the 1st row, connecting portion 11 is configured near the intersegmental central authorities of the 1st row, thereby the distance from connecting portion 11 to two adjacent heat-transfer pipe 13a is equated.Thus, the impact of heat conduction also equates.But according to the environment for use of reheater 6b, the refrigerant temperature that might cross cold territory reduces gradually, and is different in the temperature of the mobile cold-producing medium of two adjacent heat-transfer pipe 13a.Therefore, be positioned at the impact of heat conduction of heat-transfer pipe 13a4 in downstream of flow of refrigerant large.
Therefore, in reheater 6bE, in heat-transfer pipe 13a1, the 13a2 of the 1st row close to the connecting portion 11a, in the heat-transfer pipe 13a1 side of the upstream side of flow of refrigerant, from intersegmental eccentric and configure apart from central portion.That is, connecting portion 11a is from the central part of heat-transfer pipe 13a1,13a2 to the heat-transfer pipe 13a1 lateral deviation heart at the upstream side of the flow of refrigerant of heat-transfer pipe 13a1,13a2 internal flow.Thus, suppress the impact that brings because of the heat conduction to the heat-transfer pipe 13a2 in temperature difference larger downstream, can consist of and more easily realize cold heat exchanger.
And, in reheater 6bE, only make connecting portion 11a1 eccentric, do not make connecting portion 11a2 eccentric.The refrigerant temperature of crossing cold territory under the high condition of refrigerant temperature and the temperature difference between air large, the heat radiation quantitative change is large, so the variations in temperature of cold-producing medium also becomes large.On the other hand, if refrigerant temperature reduces, and the temperature difference between air diminish, so heat dissipation capacity diminishes, variations in temperature also diminishes.
Each temperature difference of two heat-transfer pipe 13a1,13a2 close to the connecting portion 11a1 of the upstream side that is configured in flow of refrigerant is larger than each temperature difference of two heat-transfer pipe 13a3,13a4 close to connecting portion 11a2.Therefore, do not make temperature difference little zone, namely connecting portion 11a2 is eccentric, but makes temperature difference large zone, and namely connecting portion 11a1 is eccentric.
Adopt above structure, can improve the heat transfer property as heat exchanger integral body, can improve the high air conditioner of energy saving.That is, improve energy saving.So, by being used as the reheater of indoor set, reheater 6bE consists of air conditioner 100, can improve the condensation performance, can turn round efficiently when heating running.
6. the 6th embodiment
Next, with reference to Figure 14, the 6th embodiment is described.The 1st above-mentioned embodiment ~ the 5th embodiment is all the embodiment about reheater 6b, but has on the heat exchanger this point of temperature difference between row, and cooler is identical with reheater, so the structure of cooler 6aA is described in the 6th embodiment.As mentioned above, flow into the refrigerant gas of high temperature at cooler 6aA, cold-producing medium is discharged with gas and liquid two-phase state.
Cold-producing medium flows into gaseous state from the 3rd row (row 6a3) of downwind side.And, flow through successively, and be condensed to the 2nd row (row 6a2), the 1st row (row 6a1) while cold-producing medium dispels the heat.The 2nd row and the 1st row are two-phase states, and what become gaseous state is that the 3rd when flowing into is listed as.Therefore, between the cold-producing medium of the cold-producing medium of the 2nd row of flowing through and the 3rd row of flowing through, produce large temperature difference between row.
And in cooler 6aA, make the grooving 10b that is arranged between the 2nd row and the 3rd row to adjacent with the connecting portion 11b 12d of the section lateral deviation heart of having cut.Thus, make grooving 10b and the distance of having cut between the 12d of section narrows down, can suppress the heat conduction from the heat-transfer pipe 13c of the 3rd row to the heat-transfer pipe 13b of the 2nd row.
And, extend the heat conduction distance between heat-transfer pipe 13b and heat-transfer pipe 13c, suppress heat conduction.And, the heat transfer area of the 2nd row is increased, and the heat dissipation capacity of the 2nd row is increased.And, by enlarging grooving 10b and having cut distance between the 12c of section, can promote fin heat conduction, improve fin efficiency, further make the heat dissipation capacity increase of fin 9.
Adopt above structure, can improve the heat transfer property as heat exchanger integral body, can improve the high air conditioner of energy saving.That is, improve energy saving.So, by being used as the cooler of indoor set, cooler 6aA consists of air conditioner 100, can improve the condensation performance, can turn round efficiently when heating running.
7. variation
Above, with reference to the accompanying drawings of present embodiment, but present embodiment is not limited to above content.For example, above explanation mainly is illustrated as example take when running of heating of air conditioner, but also applicable identical explanation during cooling operation.
In addition, for example, can between the 2nd row and the 3rd row, grooving 10b be set yet, can realize thus the further raising of fin strength.
In addition, the section of having cut 12 of not adjacent with each connecting portion 11 (not opposed) is parts not necessarily, can delete as required.
In addition, in the 3rd embodiment with reference to Figure 11 explanation, the rugosity of heat-transfer pipe how difference can.That is, in the 3rd embodiment, heat-transfer pipe 13a chap, but also can make heat-transfer pipe 13a thin.At this moment, make accordingly grooving 10a eccentric with thin heat-transfer pipe 13a, make and cut distance between the 12a of section and narrow down and get final product.
In addition, in the 4th embodiment with reference to Figure 12 explanation, what also connecting portion 11a can be configured in the 2nd biographies heat pipe 13b is intersegmental near central authorities (namely between row on center line 21a), makes the alee lateral deviation heart of grooving 10a1.At this moment, the eccentric amplitude of heat-transfer pipe 13a1 side diminishes, and the eccentric amplitude of heat-transfer pipe 13a4 side becomes large.
And in the 4th embodiment, flowing of the cold-producing medium of the 1st row can be 2 systems or its above system's number.At this moment, along flow of refrigerant, suitably change eccentric amplitude and get final product.
In addition, in the 5th embodiment of reference Figure 13 explanation, also can make connecting portion 11a2 eccentric with respect to the mode that connecting portion 11a1 diminishes with eccentric amplitude.
In addition, in the 6th embodiment of reference Figure 14 explanation, also connecting portion 11b can be configured near the intersegmental central authorities of the 2nd heat-transfer pipe 13b that is listed as, make the grooving 10b windward lateral deviation heart.In addition, identical with the situation that is applicable to reheater 6b, will apart from the eccentric amplitude of center line between the row of grooving 10b, apart from the intersegmental eccentric amplitude apart from central authorities of connecting portion corresponding to the flow direction of Exhaust Gas cold-producing medium suitably change get final product.Thus, can obtain to improve the effect of heat transfer property.
In addition, in each embodiment, fin 9 is 3 row, but can be also 2 row, or more than 4 row.And in the scope of not appreciable impact effect of the present invention, structure that also can each embodiment of appropriate combination is implemented.
And, as above-mentioned change, also can access the effect identical with the effect of present embodiment.
Claims (13)
1. air conditioner, the intersection fin-and-tube type heat exchanger that it possesses and have fin, connects described fin and be set to staggered a plurality of heat-transfer pipes and be arranged on the grooving of described fin surface and cut section,
Described air conditioner is characterised in that,
In described heat exchanger,
More than the 1st heat-transfer pipe that is equipped on the weather side of described fin is arranged on roughly the same direction with more than the 2nd heat-transfer pipe that is equipped on the downwind side of described fin,
Be provided with the section of having cut between described more than the 1st heat-transfer pipe,
Be provided with grooving between described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe, be provided with connecting portion between this grooving and adjacent other grooving,
Length between adjacent two heat-transfer pipes in described more than the 1st heat-transfer pipe of the Length Ratio of this connecting portion is short,
Be adjacent to be provided with the cut section longer than the length of described connecting portion with described connecting portion,
The described grooving that is arranged between described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe sets as follows: with respect to linking the line between the center of described more than the 1st heat-transfer pipe and linking center line between the 1st row of centre of the line between the center of described more than the 2nd heat-transfer pipe, be eccentric in described more than the 1st heat-transfer pipe or described more than the 2nd heat-transfer pipe side.
2. air conditioner according to claim 1, is characterized in that,
Described connecting portion is arranged on the substantial middle between two adjacent heat-transfer pipes in described more than the 1st heat-transfer pipe,
The described grooving that is arranged between described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe sets as follows: with respect to center line between described the 1st row, be eccentric in described more than the 1st heat-transfer pipe side.
3. air conditioner according to claim 1, is characterized in that,
Described connecting portion is arranged on the substantial middle between two adjacent heat-transfer pipes in described more than the 2nd heat-transfer pipe,
The described grooving that is arranged between described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe sets as follows: with respect to center line between described the 1st row, be eccentric in described more than the 2nd heat-transfer pipe side.
4. air conditioner according to claim 1, is characterized in that,
More than the 3rd heat-transfer pipe connects described fin and is arranged on the downwind side of described more than the 2nd heat-transfer pipe,
Described more than the 1st heat-transfer pipe, described more than the 2nd heat-transfer pipe and described more than the 3rd heat-transfer pipe are provided on roughly the same direction,
Be provided with between described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe as the 1st grooving of grooving with as the 1st connecting portion of connecting portion,
Be provided with between described more than the 2nd heat-transfer pipe and described more than the 3rd heat-transfer pipe as the 2nd grooving of grooving with as the 2nd connecting portion of connecting portion,
Described the 1st grooving arranges with respect to center line bias between described the 1st row,
And described the 2nd grooving is arranged on and is linking the line between the center of described more than the 2nd heat-transfer pipe and linking between the 2nd row of centre of the line between the center of described more than the 3rd heat-transfer pipe on center line.
5. air conditioner according to claim 4, is characterized in that,
The distance that 1st grooving adjacent with described the 1st connecting portion and the adjacent with the 1st grooving the 1st cut between section is shorter than 2nd grooving adjacent with described the 2nd connecting portion and 2nd distance of having cut section between adjacent with the 2nd grooving.
6. air conditioner according to claim 4, is characterized in that,
The length of described the 1st connecting portion of the Length Ratio of described the 2nd connecting portion is long.
7. air conditioner according to claim 1, is characterized in that,
The described a plurality of heat-transfer pipes that consist of described heat exchanger comprise the different heat-transfer pipe of internal diameter.
8. air conditioner according to claim 1, is characterized in that,
Temperature difference between the temperature of the cold-producing medium of the heat-transfer pipe of the temperature of the cold-producing medium of the heat-transfer pipe of described more than the 1st heat-transfer pipe of the formation of flowing through and described more than the 2nd heat-transfer pipe of formation of flowing through is larger, and grooving is set greatlyr with respect to the eccentric amplitude of center line between described the 1st row.
9. air conditioner according to claim 1, is characterized in that,
Described connecting portion is eccentric in the heat-transfer pipe side of the upstream side of the cold-producing medium stream that becomes this heat-transfer pipe inside of flowing through from the central part of two adjacent heat-transfer pipes of consisting of described more than the 1st heat-transfer pipe.
10. air conditioner according to claim 1, is characterized in that,
Set as follows the above-mentioned section of having cut, link to consist of described more than the 1st heat-transfer pipe heat-transfer pipe the center and be arranged on described more than the 1st heat-transfer pipe and described more than the 2nd heat-transfer pipe between the straight line of end of grooving intersect with the section of having cut that is arranged between described more than the 1st heat-transfer pipe.
11. air conditioner according to claim 1 is characterized in that,
The length of described connecting portion is W1, adjacent with this connecting portion and the length section of having cut that arranges is W2, when being equipped on distance between the heat-transfer pipe of these both sides of having cut section and being W3, set described connecting portion, described section of section and the described heat-transfer pipe cut in the mode that satisfies following formula (1)
12. air conditioner according to claim 1 is characterized in that,
The length of described connecting portion is W1, and when being provided in distance between the heat-transfer pipe of both sides of and the section of having cut that arranges adjacent with this connecting portion and being W3, setting as follows described connecting portion and described heat-transfer pipe: W1 is below 0.6 divided by the value of W3.
13. air conditioner according to claim 12 is characterized in that,
Setting as follows described connecting portion and described heat-transfer pipe: W1 is below 0.2 divided by the value of W3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-267038 | 2011-12-06 | ||
| JP2011267038A JP5519624B2 (en) | 2011-12-06 | 2011-12-06 | Air conditioner |
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| Publication Number | Publication Date |
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| CN103148643A true CN103148643A (en) | 2013-06-12 |
| CN103148643B CN103148643B (en) | 2015-06-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210304282.5A Active CN103148643B (en) | 2011-12-06 | 2012-08-24 | Air conditioner |
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| CN (1) | CN103148643B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345044A (en) * | 2019-07-05 | 2019-10-18 | 华北电力大学 | A kind of compression carbon dioxide energy-storage system that double underground gas storage rooms are recycled with heat accumulation |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03194370A (en) * | 1989-12-22 | 1991-08-26 | Hitachi Ltd | Heat exchanger for air conditioner |
| JPH09133488A (en) * | 1995-11-09 | 1997-05-20 | Matsushita Electric Ind Co Ltd | Heat exchanger with fin |
| JP2003279282A (en) * | 2002-03-20 | 2003-10-02 | Toshiba Kyaria Kk | Heat exchanger |
| JP2004085139A (en) * | 2002-08-28 | 2004-03-18 | Toshiba Kyaria Kk | Indoor unit for air conditioner |
| JP2011122819A (en) * | 2009-11-04 | 2011-06-23 | Daikin Industries Ltd | Heat exchanger and indoor unit including the same |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3256634B2 (en) * | 1994-08-10 | 2002-02-12 | 三菱電機株式会社 | Heat exchanger |
| JP2000234886A (en) * | 1999-02-17 | 2000-08-29 | Matsushita Electric Ind Co Ltd | Finned heat exchanger |
| JP2001091183A (en) * | 1999-07-21 | 2001-04-06 | Matsushita Refrig Co Ltd | Fin tube type heat exchanger |
-
2011
- 2011-12-06 JP JP2011267038A patent/JP5519624B2/en active Active
-
2012
- 2012-08-24 CN CN201210304282.5A patent/CN103148643B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03194370A (en) * | 1989-12-22 | 1991-08-26 | Hitachi Ltd | Heat exchanger for air conditioner |
| JPH09133488A (en) * | 1995-11-09 | 1997-05-20 | Matsushita Electric Ind Co Ltd | Heat exchanger with fin |
| JP2003279282A (en) * | 2002-03-20 | 2003-10-02 | Toshiba Kyaria Kk | Heat exchanger |
| JP2004085139A (en) * | 2002-08-28 | 2004-03-18 | Toshiba Kyaria Kk | Indoor unit for air conditioner |
| JP2011122819A (en) * | 2009-11-04 | 2011-06-23 | Daikin Industries Ltd | Heat exchanger and indoor unit including the same |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345044A (en) * | 2019-07-05 | 2019-10-18 | 华北电力大学 | A kind of compression carbon dioxide energy-storage system that double underground gas storage rooms are recycled with heat accumulation |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013119977A (en) | 2013-06-17 |
| JP5519624B2 (en) | 2014-06-11 |
| CN103148643B (en) | 2015-06-10 |
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Effective date of registration: 20160812 Address after: Hongkong, China Patentee after: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. Address before: Tokyo, Japan, Japan Patentee before: Hitachi Appliances Inc. |
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Effective date of registration: 20180614 Address after: Tokyo, Japan, Japan Patentee after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong, China Patentee before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |