CN1979082A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
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- CN1979082A CN1979082A CN 200610164578 CN200610164578A CN1979082A CN 1979082 A CN1979082 A CN 1979082A CN 200610164578 CN200610164578 CN 200610164578 CN 200610164578 A CN200610164578 A CN 200610164578A CN 1979082 A CN1979082 A CN 1979082A
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Abstract
The invention provides a heat exchanger, condensed water generated by this heat exchanger which used as gas cooler flow swimmingly, thereby phenomena of ventilation resistance increased obviously enable be restrained. Wherein, flat heat condut pipes (4) are set as double-row multiple layer structure, set aslant relative to gas main flow, and adjacent heat condut pipes in two row are staggered each other. A drainage surface (8) connected in vertical direction is set on the surface of wing (1) between double-row flat heat condut pipes (4a,4b). In this way, condensed water generated on the surface of wing (1) flow to the upper surface of the flat heat condut pipes (4a,4b), then flow along with incline plane of the flat heat condut pipes (4a,4b), then flow along with the drainage surface (8) connected in vertical direction. Thereby, condensed water without flowing stop and unable make ventilation resistance increased obviously.
Description
Technical field
The present invention relates to the fin of a kind of use in air-conditioner and freezing equipment etc. and add the duct type heat exchanger, this heat exchanger makes at gases such as flow air between many tabular fins stacked together with between the water of flat heat-transfer pipe inner fluid or refrigerant etc. and carries out heat exchange.
Background technology
The general fin that is made of many tabular fins stacked together and flat heat-transfer pipe adds the duct type heat exchanger as shown in Fig. 9, Figure 10, comprising: many tabular fins 1 that gas W such as stacked together abreast and air flows betwixt with certain spacing; Roughly be with the spacing of regulation vertically be inserted in these fins 1, inside has fluid R such as water or refrigerant flowing and the outer rim in cross section is the heat-transfer pipe 4 of flat; And the two ends of heat-transfer pipe 4 are connected respectively, formed the tube head part 5 of refrigerant circuits with heat-transfer pipe 4.
In above-mentioned existing heat exchanger, it is on the horizontal direction that length direction on the cross section of heat-transfer pipe 4 is set at the direction parallel with the main flow direction A of gas, and heat-transfer pipe 4 is configured to weather side heat-transfer pipe row and two row of downwind side heat-transfer pipe row, be provided with a plurality of layer in each row, the heat-transfer pipe 4 in two row is configured to staggered.In addition, on the fin 1 between weather side heat-transfer pipe and the downwind side heat-transfer pipe, also be provided with the main flow direction of gas perpendicular that is the coconnected smooth draining face of vertical direction (example wherein can be opened flat 3-63499 communique 1-3 page or leaf, Fig. 1-2 and Fig. 4 and Japanese patent gazette 2624336 1-3 pages or leaves, Fig. 1-3 and Fig. 7 with reference to the open communique spy of Japan Patent).
But, exist following problem in the above-mentioned existing formation.Because the length direction of flat heat-transfer pipe 4 is set up in the horizontal direction, therefore, when heat exchanger is used as gas cooler, if though be directed between the weather side heat-transfer pipe that is arranged on fin 1 and the downwind side heat-transfer pipe attached to the condensed water L on the outer surface of the surface of fin 1 and heat-transfer pipe 4, words on the coconnected smooth draining face of vertical direction can flow down swimmingly, but, before this, condensed water L can keep, rest on the upper surface of flat heat-transfer pipe 4, be not easy to flow down very much, thereby can cause the flowing resistance of gas to increase significantly.
Summary of the invention
The present invention is intended to address the above problem, and its purpose is to provide a kind of like this heat exchanger, and this heat exchanger can make the condensed water that produces when using as gas cooler flow down swimmingly, thereby can suppress the increase significantly of the flowing resistance of gas.
In order to solve the above-mentioned problems in the prior art, in heat exchanger of the present invention, the flat heat-transfer pipe is set up the shape that is the staggered of biserial, multilayer or staggers mutually, and is inclined to set for the main flow direction of gas.In addition, the slope that descends takes place in the side leeward that the incline direction that is in the described flat heat-transfer pipe in the row of weather side of described gas at least is provided in described gas, and is being provided with at the coconnected draining face of vertical direction on the fin surface between two described flat heat-transfer pipes row.
By resembling in the above-mentioned formation, described flat heat-transfer pipe is arranged to be the shape of interlocking or staggering mutually of biserial multilayer, main flow direction for described gas is inclined to set, and on the fin surface between two described flat heat-transfer pipe row, be provided with at the coconnected draining face of vertical direction, heat exchanger of the present invention is when using as gas cooler, the condensed water that produces on the surface of described fin can flow on the upper surface of described flat heat-transfer pipe earlier, inclined plane along described flat heat-transfer pipe flows down then, thereafter again along the lip-deep of described fin is set, under the coconnected draining surface current of vertical direction.Therefore, condensed water can not stop, and flowing resistance does not have very big increase yet.
The technique effect that the present invention produces is as follows.Adopt after the present invention, the heat exchanger of increase significantly occurs thereby can provide a kind of condensed water that takes place when heat exchanger is used as gas cooler can flow down the flowing resistance that can suppress gas swimmingly.
The specific embodiment of the invention is summarized as follows.In the heat exchanger in the 1st scheme of the present invention, the heat-transfer pipe of flat is arranged to have the row of the weather side that is positioned at gas and is positioned at two row of row of the downwind side of described gas, the staggered shape of multilayer, is inclined to set with respect to the main flow direction of described gas; And the slope that descends takes place in leeward one side that the incline direction of described flat heat-transfer pipe of row that is in the weather side of described gas at least is provided in described gas; Simultaneously, on the fin surface between two described flat heat-transfer pipe row, be provided with at the coconnected draining face of vertical direction.Like this, when heat exchanger uses as gas cooler, can flow on the upper surface of described flat heat-transfer pipe earlier at the condensed water that produces on the surface of described fin, inclined plane along described flat heat-transfer pipe flows down then, thereafter again along be located on the described fin surface, under the coconnected draining surface current of vertical direction.Therefore, condensed water can not stop, and flowing resistance does not have too many increase yet.
The 2nd scheme is, in the heat exchanger of the 1st scheme, the incline direction of described flat heat-transfer pipe of row that is in the downwind side of described gas is provided in upwind side one side the slope that descends takes place.Like this, when heat exchanger uses as gas cooler, can flow on the upper surface of described flat heat-transfer pipe earlier at the condensed water that produces on the surface of described fin, inclined plane along described flat heat-transfer pipe flows down then, thereafter again along be located on the described fin surface, under the coconnected draining surface current of vertical direction.Therefore, condensed water can not stop, and flowing resistance does not have too many increase yet.
The 3rd scheme is, in the heat exchanger of the 2nd scheme, the described flat heat-transfer pipe of row that is in the weather side of described gas is inserted by the breach from the windward leading edge of described fin, and the described flat heat-transfer pipe of row that is in the downwind side of described gas is inserted by the breach from the leeward trailing edge of described fin.Like this, insert owing to be formed in the described flat heat-transfer pipe of the ramped shaped that leeward one side of row of the weather side of described gas descends and be from the breach of the windward leading edge of described fin, simultaneously, the described flat heat-transfer pipe that is formed in the slope that upwind side one side of row of the downwind side of described gas descends is that the breach from the leeward trailing edge of described fin inserts, therefore, when heat exchanger uses as gas cooler, can flow on the upper surface of described flat heat-transfer pipe earlier at the condensed water that produces on the surface of described fin, inclined plane along described flat heat-transfer pipe flows down then, thereafter again along being set in place on the described fin surface between the described flat heat-transfer pipe of biserial, under the coconnected draining surface current of vertical direction.Therefore, condensed water can not stop, and owing to be inserted with the upside that the breach of the leeward trailing edge of the breach of windward leading edge of described fin of described flat heat-transfer pipe and described fin is positioned at the slope of inclining that described flat heat-transfer pipe forms, not only condensate liquid can not stop, and flowing resistance does not have too big increase yet.In addition, owing to the breach insertion of the described flat heat-transfer pipe in the row of the weather side that is in described gas from the windward leading edge of described fin gets final product, being in described flat heat-transfer pipe in the row of downwind side of described gas inserts from the breach of the leeward trailing edge of described fin and gets final product, therefore, the assembling operation efficient of heat exchanger is very high.
The 4th scheme is, in the 1st～3 in the heat exchanger of arbitrary scheme, the width of described flat heat-transfer pipe of row that is in the downwind side of described gas be set to the weather side that is in described gas row described flat heat-transfer pipe width about 30%～60%.Like this, owing to can make the width ratio of described flat heat-transfer pipe of row of downwind side of the described flat heat-transfer pipe of row of weather side of described gas and described gas and the heat load between weather side and the downwind side or heat stream ratio almost equal, therefore, the ratio of flowing refrigerant flow equates substantially with heat load or heat stream ratio between weather side and the downwind side in each heat-transfer pipe of the described flat heat-transfer pipe of the row of the downwind side of the described flat heat-transfer pipe of the row of the weather side of described gas and described gas, in each heat-transfer pipe such as described flat heat-transfer pipe of the row of the downwind side of the described flat heat-transfer pipe of the row of the weather side of described gas and described gas the quantity of state of flowing refrigerant change also basic identical, thereby the performance of heat exchanger is brought into play to greatest extent.
The 5th scheme is that in the heat exchanger of arbitrary scheme, described flat heat-transfer pipe is configured to be about 5 °～30 ° with respect to the angle of inclination of horizontal direction in the 1st～4.Like this, not only can not make flowing resistance that too many increase is arranged, can not stop yet, can flow down swimmingly attached to the lip-deep condensed water of described fin and described flat heat-transfer pipe.When angle of inclination during less than about 5 °, condensed water will become and stop easily; And greater than about 30 ° of degree, flowing resistance can increase significantly.Therefore, the flat heat-transfer pipe serves as suitable with respect to the angle of inclination of horizontal direction with about 5 °～30 °.
The 6th scheme is, in the 1st～the 5th in the heat exchanger of arbitrary scheme, be located on two described fins between the described flat heat-transfer pipes row, be configured to be about 1mm～4mm at the row of the coconnected described draining face of vertical direction to width.Like this, the efficient of fin can not be subjected to too much influence, can flow down swimmingly attached to the lip-deep condensed water of described fin and described flat heat-transfer pipe yet.In addition, be located between the flat heat-transfer pipe of the flat heat-transfer pipe of windward row of described fin and leeward row, at the row of the coconnected draining face of vertical direction to width during less than 1mm, the phenomenon that stream deficiency, condensed water are difficult for flowing down can appear, and during greater than 4mm, fin efficiency will worsen.Therefore, the row of draining face are advisable with about 1mm～4mm to width.
The 7th scheme is, in the 1st～6 in the heat exchanger of arbitrary scheme, on the surface of described fin, and the main flow direction of described gas be in the zone between the described flat heat-transfer pipe of adjacency on meet at right angles direction that is the course, be provided with a plurality of vent windows of opening mouthful towards the main flow direction of described gas.Like this, the air that flow in the heat exchanger can pass a plurality of vent windows that are located on the described fin, the effect that produces the temperature boundary layer leading edge effect and the air-flow of the both sides that are positioned at described fin is mixed, stir, thus can obtain excellent heat transfer property.
The 8th scheme is, in the heat exchanger of the 7th scheme, the angle of described vent window is 20～40 °, described vent window the width on the main flow direction of described gas be configured to and described stacked fin between constant spacing about equally.Like this, air in the inflow heat exchanger can directly not pass from described fin, but can in a plurality of vent windows on being located at described fin suitable streaming take place, produce the temperature boundary layer leading edge effect and make the air-flow mixing that is positioned at described fin both sides, the effect that stirs, thereby can produce the effect that improves heat transfer property, increases heat-exchange capacity.
The 9th scheme is, in the heat exchanger of the 7th scheme, the height of described vent window is configured to greater than 0.8mm, and is essentially 1/3～2/3 of constant spacing between the described stacked fin.Like this, air in the inflow heat exchanger can directly not pass from described fin, but can in a plurality of vent windows on being located at described fin suitable streaming take place, produce the temperature boundary layer leading edge effect and make the air-flow mixing that is positioned at described fin both sides, the effect that stirs, thereby can produce the effect that improves heat transfer property, increases heat-exchange capacity.
The 10th scheme is, in the 1st～6 in the heat exchanger of arbitrary scheme, on the surface of described fin, and the rectangular direction of main flow direction of described gas that is course between the flat heat-transfer pipe of adjacency, be provided with the cocked part of a plurality of cut-outs towards gas main flow direction side opening, the height of the cocked part of described cut-out is essentially 1/4～3/4 of spacing between the stacked fin.Like this, the temperature boundary layer leading edge effect by means of the cocked part of described a plurality of cut-outs produces can obtain excellent ventilation characteristic and heat transfer property.
The 11st scheme is, in the heat exchanger of the 10th scheme, the width of the cocked part of described cut-out is set to about 1/3～1/2 of therebetween fin face width degree.Like this, the temperature boundary layer of the cocked part of described cut-out of the downwind side of described gas can not buried in the temperature boundary layer of the cocked part of described cut-out of the side of being in the wind, each cuts off cocked part all can produce very high temperature boundary layer leading edge effect, thereby can realize more excellent ventilation characteristic and heat transfer property.
The 12nd scheme is, in the 1st～6 in the heat exchanger of arbitrary scheme, in the zone on the surface of described fin and on rectangular direction of the main flow direction of described gas that is the course between the described heat-transfer pipe of adjacency, be provided with by crest line and be the mutual relief part that forms of arranging in top and paddy portion that course is extended, like this, can realize excellent heat transfer property.In addition, when the heat exchanger of this programme uses as the outdoor heat converter of air-conditioner, the lower words of temperature degree outside when heating process, though frosting can take place on the surface of described fin, be difficult for to take place rely on the temperature boundary layer leading edge effect can realize the cocked part of high performance cut-out etc. go up the white concentrated area that occurs attached to the leading edge of the cocked part of well behaved cut-out, the frost that attaching make hole on the described fin block, ventilate and become very soon almost can't to carry out, the problem of the rapid decline of heating performance.
The 13rd scheme is, in the heat exchanger of the 12nd scheme, be arranged on described fin lip-deep, and the described heat-transfer pipe of the rectangular direction of main flow direction of described gas that is course adjacency between the zone in described relief part in, the crest line of at least one side in the described paddy portion that crest line is that described top that course extends and crest line be that course extends is provided with otch.Like this, when using as evaporimeter under with the condition of the frost-free on condenser and fin surface of the heat exchanger in the 13rd scheme, the described otch that is located on the crest line can produce temperature boundary layer leading edge leading edge effect, is expected to improve performance.On the other hand, when under the condition of frosting, using as evaporimeter, under the effect of temperature boundary layer leading edge leading edge effect, though be arranged on office can very fast frosting on the described otch on the very high crest line of hot reception and registration rate, even but described otch is blocked, still can keep its performance by the mutual described relief part that forms of arranging in top and paddy portion that crest line is derived on course, so heating performance can sharply not descend.
The 14th scheme is that in the heat exchanger of arbitrary scheme, the refrigerant of portion's circulation is within it selected HFC refrigerant, HC refrigerant and CO for use in the 1st～13
2Among arbitrary in the refrigerant or its mixed cooling medium.Like this, can not damage the ozone layer, and because HC refrigerant and CO
2The greenhouse effects of the earth coefficient of refrigerant etc. is little, can make commodity such as the air-conditioner that is beneficial to environmental protection and refrigerator.Simultaneously, because use is the flat heat-transfer pipe, the use amount of refrigerant also can reduce.
Description of drawings
Fig. 1 is front view in the heat exchanger of the embodiment of the invention 1, that be inserted with the fin of flat heat-transfer pipe,
Fig. 2 is the sectional view of the arrow A-A direction in Fig. 1,
Fig. 3 is front view in the heat exchanger of the embodiment of the invention 2, that be inserted with the fin of flat heat-transfer pipe,
Fig. 4 is the sectional view of the arrow B-B direction in Fig. 3,
Fig. 5 is front view in the heat exchanger of the embodiment of the invention 3, that be inserted with the fin of flat heat-transfer pipe,
Fig. 6 is the sectional view of the arrow C-C direction along Fig. 5,
Fig. 7 is front view in the heat exchanger of the embodiment of the invention 4, that be inserted with the fin of flat heat-transfer pipe,
Fig. 8 is the sectional view along the arrow D-D direction of Fig. 7,
Fig. 9 adds the oblique view of the basic comprising of duct type heat exchanger for representing existing fin,
Figure 10 is the front view of existing fin.
In the above-mentioned accompanying drawing, label 1 is a fin, and 4 is the flat heat-transfer pipe, 4a is the flat heat-transfer pipe of windward row, 4b is the flat heat-transfer pipe of leeward row, and 3a is a breach of keeping supplying the flat heat-transfer pipe 4a windward leading edge that insert, that be positioned at fin of wind row, and 3b is the breach for the flat heat-transfer pipe 4b leeward trailing edge that insert, that be positioned at fin of leeward row, 8 are draining face, 5 is the tube head part, and 6 is vent window, and 7 for cutting off cocked part, 9 is relief part, and 10 is otch.
The specific embodiment
Come with reference to the accompanying drawings some embodiments of the present invention are elaborated.It is pointed out that such embodiment does not have the effect that limits the scope of the invention.
In addition, it is identical that conventional fin described in the essential structure of the heat exchanger among each embodiment of the present invention and " background technology " of the front part adds the duct type heat exchanger, promptly is made of stacked many tabular fins and the flat heat-transfer pipe that is biserial, sandwich construction.In addition, when heat exchanger of the present invention uses as evaporimeter, to add the duct type heat exchanger identical with general fin, the main flow direction of described gas that is " row to " described below are provided with in the horizontal direction, and the direction vertical with the main flow direction of described gas that is " course " described below are arranged on the vertical direction.Therefore, no longer be described here for these structures.Because the shape and being obliquely installed of flat heat-transfer pipe of fin are feature of the present invention places, thus under regard to these characteristics and be described in detail.
(embodiment 1)
Fig. 1 is the front view of fin 1 in the heat exchanger of the embodiment of the invention 1, that be inserted with flat heat-transfer pipe 4.Fig. 2 is the sectional view of the arrow A-A direction in Fig. 1, a plurality of fins 1 in the heat exchanger of the embodiment of the invention 1, that be inserted with flat heat-transfer pipe 4 has been shown among Fig. 2 has been in schematic diagram under the stacked state.
In Fig. 1, Fig. 2, when heat exchanger used as evaporimeter, the main flow direction of gas that is " row to " were set up in the horizontal direction, and direction that is " course " perpendicular with the main flow direction of gas are set up in vertical direction.
Column pitch and interlamellar spacing that the heat-transfer pipe 4 that the outer rim in cross section is flat roughly is vertically with regulation are inserted in the fin 1, heat-transfer pipe 4 is arranged in the biserial sandwich construction, and the windward row (refer to be positioned at the row of windward one side, (refer to be positioned at the row of leeward one side) flat heat-transfer pipe 4b all is formed on the slope that leeward one side descends with about 5 °～30 ° tilt angle alpha with respect to the main flow direction of gas down together for flat heat-transfer pipe 4a down together) and leeward row.Multilayer in the heat-transfer pipe 4 is the formation that staggers mutually, that is, from the upper right side of Fig. 1 during along the surface observation of heat-transfer pipe 4, heat-transfer pipe adjacent in 2 row is not on sustained height.
Be about 1mm～4mm what row made progress apart from E between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row.In addition, on the surface of the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of the row of being in the wind and leeward row, be provided with at the coconnected draining face 8 of vertical direction.On the surface of the fin 1 in the zone between the flat heat-transfer pipe 4 adjacent on course, be provided with at a plurality of vent windows 6 of opening mouth towards the main flow direction of gas.The inclination angle [theta] of these vent windows 6 is set as 20～40 °, the width W on the main flow direction of gas 1 be configured to and stacked fin 1 between constant spacing Pf about equally.In addition, the height H 1 of these vent windows 6 is more than or equal to 0.8mm, and is set at 1/3～2/3 of constant spacing between the stacked fin basically.
The operational circumstances and the effect that regard to down in the heat exchanger with above formation are described.
As mentioned above, in the present embodiment, biserial, the multilayer flat heat-transfer pipe 4 of flat heat-transfer pipe 4b that is in the row of the flat heat-transfer pipe 4a of row of weather side of gas and side at a disadvantage is configured to mutually staggered, main flow direction with respect to gas is inclined to set, and is in leeward one side that flat heat-transfer pipe 4b in the row of downwind side of flat heat-transfer pipe 4a in the row of weather side of gas and gas all is formed in gas the slope that descends takes place.In addition, on the surface of the fin 1 between the flat heat-transfer pipe 4b that flat heat-transfer pipe 4a and leeward at the windward row are listed as, also be provided with at the coconnected draining face 8 of vertical direction.Like this, when heat exchanger is used as the gas cooler use, part in the condensed water that produces on the surface of fin 1 can flow to the upper surface of the flat heat-transfer pipe 4a of windward row earlier, can flow down along the inclined plane of the flat heat-transfer pipe 4a of windward row then, thereafter again along be provided with fin 1 lip-deep, flow down at the coconnected draining face 8 of vertical direction.In addition, remainder in the condensed water that produces on the surface of fin 1 can flow to earlier on the upper surface of flat heat-transfer pipe 4b of leeward row, thereafter, inclined plane along the flat heat-transfer pipe 4b of leeward row flows down, thereafter again along the hinder marginal part of the downwind side that is positioned at fin 1, flow down at the coconnected planar section of vertical direction.Like this, condensed water can not stop, and can not make flowing resistance that too big increase is arranged.
In addition, in the present embodiment, after making flat heat-transfer pipe 4 be arranged to be about 5 °～30 ° with respect to the tilt angle alpha of horizontal direction, not only can not make flowing resistance that too big increase is arranged, and can not stop, but can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.If the tilt angle alpha here is less than 5 °, condensed water will stop easily; And if greater than 30 °, flowing resistance will increase significantly.It is the most suitable when therefore, flat heat-transfer pipe 4 is set to about 5 °～30 ° with respect to the tilt angle alpha of horizontal direction.
In addition, though will be provided with that the off-premises station as air-conditioner of the heat exchanger in the present embodiment is arranged under the level is best state, but this off-premises station is arranged on respect to the words in the place of inclined degree within about 5 ° of horizontal direction and also allows.Under such occasion, for condensed water also can be flowed down swimmingly, the flat heat-transfer pipe 4a of windward row preferably is configured to be about 10 °～30 ° with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row with respect to the angle of inclination of the main flow direction of air-flow.
For instance, if the flat heat-transfer pipe 4a of the windward in the heat exchanger of present embodiment row is set up into about 10 ° with respect to the angle of inclination of the main flow direction of air-flow with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row, the air-conditioner outdoor unit that is provided with above-mentioned heat exchanger be set at again with respect to horizontal direction have an appointment 5 ° inclination the place in, then the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row also has an appointment 5 ° with respect to the minimum cant of horizontal direction, thereby condensed water is flowed down swimmingly.
In addition, the upper limit (about 30 °) that is provided with for the purpose that significantly increases of the flowing resistance that suppresses air-flow under the above-mentioned situation also be to and the main flow direction of gas between the restriction carried out of relation, this and air conditioner outdoor unit etc. orientation independent is set.
In addition, in the present embodiment, be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, be configured to be about 1mm～4mm at the row of the coconnected draining face 8 of vertical direction to width E.Like this, the efficient of fin can not be subjected to very big influence, and can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.Here, if be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, narrower to width E than 1mm at the row of the coconnected draining face 8 of vertical direction, the situation that can cause stream deficiency, condensed water to be difficult for flowing down; And wideer than 4mm, the efficient of fin will worsen.Therefore, the row of draining face 8 are best to width E setting into about 1mm～4mm.
In addition, in the surf zone of the fin 1 between the flat heat-transfer pipe 4 in the course adjacency, be provided with a plurality of vent windows 6 of opening mouth at described main flow direction in the present embodiment towards gas.Like this, the air that flow in the heat exchanger can pass a plurality of vent windows 6 that are located on the fin 1, can cross the effect that produces the temperature boundary layer leading edge effect and the air-flow of fin 1 both sides is mixed, stirs, thereby can obtain the heat transfer property of excellence.
In addition, in the present embodiment, the inclination angle [theta] of vent window 6 is set to 20～40 °, vent window 6 the width W on the main flow direction of gas 1 be configured to and stacked fin 1 between constant spacing Pf about equally.In addition, the height H 1 of vent window 6 is configured to 0.8mm or more than the 0.8mm, and be between the stacked fin 1 constant spacing Pf 1/3～2/3.Like this, the air that flow in the heat exchanger is not directly to pass between fin 1, but can suitably pass in a plurality of vent windows 6 on being located at fin 1, produce the temperature boundary layer leading edge effect and will be positioned at the effect that the air-flow of described fin both sides mixes, stirs, thereby can improve heat transfer property, increase heat-exchange capacity.
(embodiment 2)
Fig. 3 is the front view of fin 1 in the heat exchanger of the embodiment of the invention 2, that be inserted with flat heat-transfer pipe 4, Fig. 4 is the sectional view of the arrow B-B direction along Fig. 3, wherein shows the schematic diagram of the folded fin 1 of multilayer in the heat exchanger of the embodiment of the invention 2, that be inserted with flat heat-transfer pipe 4.
As shown in Fig. 3, Fig. 4, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, form to have the column pitch of regulation and biserial, the multi-ply construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.In addition, the flat heat-transfer pipe 4a that is in windward row is formed in respect to the main flow direction of gas that leeward one side descends and tilt angle alpha is about 5 °～30 ° slope, and the flat heat-transfer pipe 4b of row at a disadvantage then constitutes with respect to the be in the wind decline of direction one side, inclination angle beta of the main flow direction of gas and is about 5 °～30 ° slope.
Row between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row are about 1mm～4mm to distance E.In addition, and, be provided with at the coconnected draining face 8 of vertical direction on the surface of the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row.On the surface of the fin 1 in the zone on being located at course between the flat heat-transfer pipe 4 of adjacency, be provided with the cocked part 7 of a plurality of cut-outs of opening mouth towards the main flow direction of gas.These height H s that cut off cocked part 7 are constant spacing Pf about 1/4～3/4 between the stacked fin 1, and these width Ws of cutting off cocked part 7 are about 1/3～1/2 of the width W b of therebetween fin surface.
Below operational circumstances in the heat exchanger with above formation and effect are described.
As mentioned above, in the present embodiment, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, constitute to have the column pitch of regulation and the biserial sandwich construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.And the flat heat-transfer pipe 4a of windward row is formed on the slope that decline takes place leeward one side, and the flat heat-transfer pipe 4b of leeward row is formed on the slope that the generation of upwind side one side descends.In addition, on the surface of the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, be provided with at the coconnected draining face 8 of vertical direction.Like this, when heat exchanger is used as the gas cooler use, the condensed water that produces on the surface of fin 1 can flow to earlier on the upper surface of flat heat-transfer pipe 4b of the upper surface of flat heat-transfer pipe 4a of windward row or leeward row, then along the inclined plane of the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row or leeward row to dirty, thereafter again along be arranged on fin 1 lip-deep, at the coconnected draining face 8 of vertical direction to dirty.Therefore, condensed water can not stop, and can not make flowing resistance that too big increase is arranged.
In addition, in the present embodiment, the flat heat-transfer pipe 4a of windward row is configured to be about 5 °～30 ° with respect to the flat heat-transfer pipe 4b of the tilt angle alpha of horizontal direction and leeward row with respect to the inclination angle beta of horizontal direction.Like this, can not make flowing resistance that too big increase is arranged, can not stop, can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.The angle of inclination is during less than 5 °, and condensed water just stops easily, and during greater than about 30 °, flowing resistance will increase significantly.Therefore, flat heat-transfer pipe 4 is more suitable into about 5 °～30 ° with respect to the angle of inclination setting of horizontal direction.
In addition, though will be provided with that the off-premises station as air-conditioner of the heat exchanger in the present embodiment is arranged under the level is best state, but this off-premises station is arranged on respect to the words in the place of inclined degree within about 5 ° of horizontal direction and also allows.Under such occasion, for condensed water also can be flowed down swimmingly, the flat heat-transfer pipe 4a of windward row preferably is configured to be about 10 °～30 ° with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row with respect to the angle of inclination of the main flow direction of air-flow.
For instance, if the flat heat-transfer pipe 4a of the windward in the heat exchanger of present embodiment row is set up into about 10 ° with respect to the angle of inclination of the main flow direction of air-flow with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row, the air-conditioner outdoor unit that is provided with above-mentioned heat exchanger be set at again with respect to horizontal direction have an appointment 5 ° inclination the place in, then the side among the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row is about 5 ° with respect to the angle of inclination of horizontal direction, and the opposing party is about 15 ° with respect to the angle of inclination of horizontal direction.Like this, also have an appointment 5 °, thereby condensed water is flowed down swimmingly with respect to the minimum cant of horizontal direction.
In addition, the upper limit (about 30 °) that is provided with for the purpose that significantly increases of the flowing resistance that suppresses air-flow under the above-mentioned situation also be to and the main flow direction of gas between the restriction carried out of relation, this and air conditioner outdoor unit etc. orientation independent is set.
In addition, in the present embodiment, be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, be configured to be about 1mm～4mm at the row of the coconnected draining face 8 of vertical direction to width E.Like this, the efficient of fin can not be subjected to very big influence, and can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.Here, if be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, narrower to width E than 1mm at the row of the coconnected draining face 8 of vertical direction, the situation that can cause stream deficiency, condensed water to be difficult for flowing down; And wideer than 4mm, the efficient of fin will worsen.Therefore, the row of draining face 8 are best to width E setting into about 1mm～4mm.
In addition, in the present embodiment, on the surface of the fin 1 in the zone between the described flat heat-transfer pipe in adjacency on the course, in the cocked part 7 of a plurality of cut-outs of the main flow direction upper shed of gas, and these height H s that cut off cocked part 7 be between the stacked fin 1 constant spacing Pf about 1/4～3/4.Like this, cut off cocked part 7 by these and can produce the temperature boundary layer leading edge effect, thereby can obtain excellent ventilation characteristic and heat transfer property.
In addition, in the present embodiment, the width Ws of cutting off cocked part 7 be set to fin surface therebetween width W b about 1/3～1/2.Like this, the temperature boundary layer of the cocked part 7 of the cut-out of the downwind side of gas can not bury in the temperature boundary layer of the cocked part 7 of cut-out of the side of being in the wind, each cuts off cocked part 7 and all has very high temperature boundary layer leading edge effect, thereby can obtain excellent more ventilation characteristic and heat transfer property.
(embodiment 3)
Fig. 5 is the front view of fin 1 in the heat exchanger of the embodiment of the invention 3, that be inserted with flat heat-transfer pipe 4, Fig. 6 is for along the view of seeing of the arrow C-C among Fig. 5, wherein shows the schematic diagram of fin 1 in the heat exchanger of the embodiment of the invention 3, that be inserted with flat heat-transfer pipe 4.
In Fig. 5, Fig. 6, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, constitute to have the column pitch of regulation and the biserial sandwich construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.And the flat heat-transfer pipe 4a of windward row is inserted by the breach 3a on the windward leading edge of fin 1, and the flat heat-transfer pipe 4b of leeward row is inserted by the breach 3b from the leeward trailing edge of fin 1.In addition, the flat heat-transfer pipe 4a of windward row constitute with respect to the main flow direction of gas leeward a side slope that descends takes place, its tilt angle alpha is set to about 5 °～30 °; The flat heat-transfer pipe 4b of leeward row then constitutes with respect to the main flow direction of gas direction one side of being in the wind the slope that descends takes place, and its inclination angle beta is set as about 5 °～30 °.
Row between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row are about 1mm～4mm to distance E.In addition, on the surface of the fin 1 between the flat heat-transfer pipe 4b that flat heat-transfer pipe 4a and leeward at the windward row are listed as, be provided with at the coconnected draining face 8 of vertical direction.On the surface of the fin 1 in the zone on being located at course between the flat heat-transfer pipe 4 of adjacency, be provided with its crest line (crestal line) in the mutual relief part 9 that forms of arranging in upwardly extending top of layer and paddy portion.
Below operational circumstances in the heat exchanger with above formation and effect are described.
As mentioned above, in the present embodiment, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, form to have the column pitch of regulation and biserial, the sandwich construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.In addition, the flat heat-transfer pipe 4a of windward row is formed in the slope that decline takes place leeward one side, and the flat heat-transfer pipe 4b of leeward row is formed in the slope that the generation of upwind side one side descends.And, on the surface of the fin 1 between the flat heat-transfer pipe 4b that flat heat-transfer pipe 4a and leeward at the windward row are listed as, be provided with at the coconnected draining face 8 of vertical direction.Like this, when heat exchanger is used as the gas cooler use, the condensed water that produces on the surface of fin 1 can flow to earlier on the upper surface of flat heat-transfer pipe 4b of the upper surface of flat heat-transfer pipe 4a of windward row or leeward row, inclined plane along the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row or leeward row flows down then, thereafter again along be arranged on fin 1 lip-deep, flow down at the coconnected draining face 8 of vertical direction.Therefore, condensed water can not stop, and can not make flowing resistance that too big increase is arranged.
In addition, in the present embodiment, the flat heat-transfer pipe 4a of windward row is inserted by the breach 3a from the windward leading edge of fin 1, and the flat heat-transfer pipe 4b of leeward row is inserted by the breach 3b from the leeward trailing edge of fin 1.Like this, the breach 3b that is inserted with the leeward trailing edge of the breach 3a of windward leading edge of fin 1 of flat heat-transfer pipe 4a and fin 1 all is arranged in the upside on the slope of flat heat-transfer pipe 4.Therefore, when heat exchanger was used as the gas cooler use, the condensate liquid that produces on the surface of fin 1 can not stop, thereby flowing resistance is increased.In addition, because the flat heat-transfer pipe 4a of windward row is inserted, the flat heat-transfer pipe 4b of leeward row is inserted from the breach 3b of the leeward trailing edge of fin 1 gets final product from the breach 3a of the windward leading edge of fin 1, so the packaging efficiency of heat exchanger will be very high.
In addition, in the present embodiment, the flat heat-transfer pipe 4a of windward row is configured to be about 5 °～30 ° with respect to the flat heat-transfer pipe 4b of the tilt angle alpha of horizontal direction and leeward row with respect to the inclination angle beta of horizontal direction.Like this, not only can not make flowing resistance that too big increase is arranged, can not stop attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4, but can flow down swimmingly.The tilt angle alpha here is during less than about 5 °, and condensed water stops easily, and when greater than about 30 °, flowing resistance will increase significantly.It is the most suitable when therefore, flat heat-transfer pipe 4 is about 5 °～30 ° with respect to the tilt angle alpha of horizontal direction.
In addition, though will be provided with that the off-premises station as air-conditioner of the heat exchanger in the present embodiment is arranged under the level is best state, but this off-premises station is arranged on respect to the words in the place of inclined degree within about 5 ° of horizontal direction and also allows.Under such occasion, for condensed water also can be flowed down swimmingly, the flat heat-transfer pipe 4a of windward row preferably is configured to be about 10 °～30 ° with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row with respect to the angle of inclination of the main flow direction of air-flow.
For instance, if the flat heat-transfer pipe 4a of the windward in the heat exchanger of present embodiment row is set up into about 10 ° with respect to the angle of inclination of the main flow direction of air-flow with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row, the air-conditioner outdoor unit that is provided with above-mentioned heat exchanger be set at again with respect to horizontal direction have an appointment 5 ° inclination the place in, then the side among the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row is about 5 ° with respect to the angle of inclination of horizontal direction, and the opposing party is about 15 ° with respect to the angle of inclination of horizontal direction.Like this, also have an appointment 5 °, thereby condensed water is flowed down swimmingly with respect to the minimum cant of horizontal direction.
In addition, the upper limit (about 30 °) that is provided with for the purpose that significantly increases of the flowing resistance that suppresses air-flow under the above-mentioned situation also be to and the main flow direction of gas between the restriction carried out of relation, this and air conditioner outdoor unit etc. orientation independent is set.
In addition, in the present embodiment, be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, be configured to be about 1mm～4mm at the row of the coconnected draining face 8 of vertical direction to width E.Like this, the efficient of fin can not be subjected to very big influence, and can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.Here, if be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, narrower to width E than 1mm at the row of the coconnected draining face 8 of vertical direction, the situation that can cause stream deficiency, condensed water to be difficult for flowing down; And wideer than 4mm, the efficient of fin will worsen.Therefore, the row of draining face 8 are best to width E setting into about 1mm～4mm.
In addition, in the present embodiment, on the surface of the fin 1 in the zone on being located at course between the heat-transfer pipe 4 of adjacency, be provided with its crest line and be the mutual relief part 9 that forms of arranging in top and paddy portion that course is extended, thus can excellent heat transfer property.In addition, when the heat exchanger of present embodiment uses as the outdoor heat converter of air-conditioner, if it is lower in the temperature that heats process China and foreign countries gas, though can frosting on the surface of fin 1, be difficult for taking place by the temperature boundary layer leading edge effect reach the cocked part of high performance cut-out etc. go up the frost meeting concentrated area that occurs attached to the leading edge of the cocked part of well behaved cut-out, the frost that attaching with the hole on the fin 1 block, ventilation almost can't be carried out with regard to making in the short time, heating performance sharply descends the degradation problem.
(embodiment 4)
Fig. 7 in the heat exchanger of the embodiment of the invention 4, be inserted with the front view of the fin 1 of flat heat-transfer pipe 4, the schematic diagram of Fig. 8 for seeing along the arrow D-D of Fig. 7 wherein shows schematic diagram in the heat exchanger of the embodiment of the invention 4, that be inserted with the state of flat heat-transfer pipe 4 in the fin 1.
In Fig. 7, Fig. 8, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, constitute to have the column pitch of regulation and biserial, the sandwich construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.In addition, the flat heat-transfer pipe 4a of windward row is inserted by the breach 3a from the windward leading edge of fin 1, the flat heat-transfer pipe 4b of leeward row is inserted by the breach 3b from the leeward trailing edge of fin 1, and the width Lb of the flat heat-transfer pipe 4b of leeward row be the windward row flat heat-transfer pipe 4a width La about 30%～60%.And, the flat heat-transfer pipe 4a of windward row be configured to respect to the main flow direction of gas leeward side the slope that descends takes place, its tilt angle alpha is configured to be about 5 °～30 °; The flat heat-transfer pipe 4b of leeward row then constitutes with respect to the main flow direction of the gas direction side of being in the wind the slope that descends takes place, and its inclination angle beta is configured to be about 5 °～30 °.
The row of the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row are about 1mm～4mm to distance E.In addition, on the surface of the fin 1 between the flat heat-transfer pipe 4b that flat heat-transfer pipe 4a and leeward at the windward row are listed as, be provided with at the coconnected draining face 8 of vertical direction.On the surface of the fin 1 in the zone on being located at course between the flat heat-transfer pipe 4 of adjacency, be provided with crest line and be the mutual relief part 9 that forms of arranging in top and paddy portion that course is extended.In addition, on the crest line at the top of relief part 9, be provided with otch 10.
Below operational circumstances in the heat exchanger with above formation and effect are described.
As mentioned above, in the present embodiment, the heat-transfer pipe 4 that the cross section outer rim is flat roughly is and vertically is inserted in the fin 1, constitute to have the column pitch of regulation and biserial, the multi-ply construction of interlamellar spacing, and the adjacent heat-transfer pipe 4 in the biserial staggers mutually.In addition, the flat heat-transfer pipe 4a of windward row is configured to the slope that side generation leeward descends, and the flat heat-transfer pipe 4b of leeward row is provided in the slope that the generation of upwind side one side descends.And, on the surface of the fin 1 between the flat heat-transfer pipe 4b that flat heat-transfer pipe 4a and leeward at the windward row are listed as, be provided with at the coconnected draining face 8 of vertical direction.Like this, when heat exchanger is used as the gas cooler use, the condensed water that produces on the surface of fin 1 can flow to earlier on the upper surface of flat heat-transfer pipe 4b of the upper surface of flat heat-transfer pipe 4a of windward row or leeward row, then along the inclined plane of the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row or leeward row to dirty, thereafter again along be arranged on fin 1 lip-deep, flow down at the coconnected draining face 8 of vertical direction.Therefore, condensed water can not stop, and flowing resistance does not have too big increase.
In addition, in the present embodiment, the flat heat-transfer pipe 4a of windward row is inserted by the breach 3a from the windward leading edge of fin 1, and the flat heat-transfer pipe 4b of leeward row is inserted by the breach 3b from the leeward trailing edge of fin 1.Like this, because the breach 3b that is inserted with the leeward trailing edge of the breach 3a of windward leading edge of fin 1 of flat heat-transfer pipe 4a and fin 1 is positioned at the upside of the incline direction of flat heat-transfer pipe 4, therefore, the condensate liquid that takes place from the surface of fin 1 when heat exchanger uses as gas cooler can not stop, and flowing resistance can not increase too much yet.In addition, because the flat heat-transfer pipe 4a of windward row inserts from the breach 3a of the windward leading edge of fin 1, the flat heat-transfer pipe 4b of leeward row is inserted by the breach 3b towards the leeward trailing edge of fin 1, so the assembling operation efficient of heat exchanger will be very high.
In addition, in the present embodiment, the width Lb of the flat heat-transfer pipe 4b of leeward row be set to the windward row flat heat-transfer pipe 4a width La about 30%～60%.Because this ratio and downwind side equate substantially for about 40%～about 50% of the heat load of weather side or heat stream ratio, therefore, being in the wind in the flat heat-transfer pipe 4b heat-transfer pipe separately of the flat heat-transfer pipe 4a of row and leeward row respectively, the ratio of flowing refrigerant flow also equates substantially with the heat load of weather side and downwind side or the ratio of heat stream, the quantity of state of flowing refrigerant of being in the wind in the flat heat-transfer pipe 4b heat-transfer pipe separately of the flat heat-transfer pipe 4a of row and leeward row changes also the same basically, thereby can give play to the performance of heat exchanger to greatest extent.
In addition, in the present embodiment, the flat heat-transfer pipe 4a of windward row is configured to be about 5 °～30 ° with respect to the flat heat-transfer pipe 4b of the tilt angle alpha of horizontal direction and leeward row with respect to the inclination angle beta of horizontal direction.Like this, not only can not make flowing resistance that too big increase is arranged, and can not stop, can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.Tilt angle alpha is during less than about 5 °, and condensed water just stops easily, and during greater than about 30 °, flowing resistance can increase significantly.Therefore, flat heat-transfer pipe 4 serves as suitable with respect to the tilt angle alpha of horizontal direction with about 5 °～30 °.
In addition, though will be provided with that the off-premises station as air-conditioner of the heat exchanger in the present embodiment is arranged under the level is best state, but this off-premises station is arranged on respect to the words in the place of inclined degree within about 5 ° of horizontal direction and also allows.Under such occasion, for condensed water also can be flowed down swimmingly, the flat heat-transfer pipe 4a of windward row preferably is configured to be about 10 °～30 ° with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row with respect to the angle of inclination of the main flow direction of air-flow.
For instance, if the flat heat-transfer pipe 4a of the windward in the heat exchanger of present embodiment row is set up into about 10 ° with respect to the angle of inclination of the main flow direction of air-flow with respect to the flat heat-transfer pipe 4b of the angle of inclination of the main flow direction of air-flow and leeward row, the air-conditioner outdoor unit that is provided with above-mentioned heat exchanger be set at again with respect to horizontal direction have an appointment 5 ° inclination the place in, then the side among the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row is about 5 ° with respect to the angle of inclination of horizontal direction, and the opposing party is about 15 ° with respect to the angle of inclination of horizontal direction.Like this, also have an appointment 5 °, thereby condensed water is flowed down swimmingly with respect to the minimum cant of horizontal direction.
In addition, the upper limit (about 30 °) that is provided with for the purpose that significantly increases of the flowing resistance that suppresses air-flow under the above-mentioned situation also be to and the main flow direction of gas between the restriction carried out of relation, this and air conditioner outdoor unit etc. orientation independent is set.
In addition, in the present embodiment, be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, be configured to be about 1mm～4mm at the row of the coconnected draining face 8 of vertical direction to width E.Like this, the efficient of fin can not be subjected to very big influence, and can flow down swimmingly attached to the lip-deep condensed water of fin 1 and flat heat-transfer pipe 4.Here, if be located on the fin 1 between the flat heat-transfer pipe 4b of the flat heat-transfer pipe 4a of windward row and leeward row, narrower to width E than 1mm at the row of the coconnected draining face 8 of vertical direction, the situation that can cause stream deficiency, condensed water to be difficult for flowing down; And wideer than 4mm, the efficient of fin will worsen.Therefore, the row of draining face 8 are best to width E setting into about 1mm～4mm.
In addition, in the present embodiment, on the surface of the fin 1 in the zone on being located at course between the heat-transfer pipe 4 of adjacency, be provided with the mutual relief part 9 that forms of arranging in top and paddy portion that is the course extension by crest line, thus can excellent heat transfer property.In addition, when the heat exchanger of present embodiment uses as the outdoor heat converter of air-conditioner, if it is lower in the temperature that heats process China and foreign countries gas, though can frosting on the surface of fin 1, be difficult for taking place having reached by the temperature boundary layer leading edge effect the concentrated leading edge of frost of appearance in the structure such as the cocked part of high performance cut-out, the frost that attaching attached to the cocked part of well behaved cut-out with the hole on the fin 1 block, ventilation almost can't be carried out with regard to making in the short time, heating performance sharply descends the degradation problem.
In addition, in the present embodiment, be provided with relief part 9 in the zone between the heat-transfer pipe 4 of fin 1 lip-deep adjacency on course, the crest line at the top in the relief part 9 is provided with otch 10.Like this, when the heat exchanger of present embodiment does not take place on as condenser or fin surface under the condition of frosting to use as evaporimeter, the otch 10 that is located on the crest line at top of relief part 9 can produce the temperature boundary layer leading edge effect, thereby can improve the performance of heat exchanger.In addition, when under the condition of frost-free, using as evaporimeter, though can be very fast on the otch 10 that localized heat reception and registration rate is very high under the effect of temperature boundary layer leading edge effect frost, but, even otch 10 is blocked by frost, still can keep its performance by crest line in the mutual relief part 9 that forms of arranging in top and paddy portion that course is extended, so heating performance can sharply not descend.
In addition, though in the heat exchanger of present embodiment, just be provided with otch 10 on the crest line at the top in relief part 9, but, only be provided in a side of words on the crest line of the paddy portion in the relief part 9 also can reach with the crest line that only is provided in a side of the top on the time identical effect.In addition, also can upper cut 10 all be set on the two at the crest line of the crest line at the top of relief part 9 and paddy portion, can obtain better effect this moment.
In addition, in embodiment 1～4, can suitably select HFC refrigerant, HC refrigerant and CO for use at the refrigerant of heat exchanger internal flow
2In the refrigerant any or its mixed cooling medium.Like this, can not damage ozone layer, and HC refrigerant and CO
2The greenhouse effects of the earth coefficient of refrigerant is very little, so can make products such as the air-conditioner that benefits environmental protection and refrigerator.In addition, owing to used the flat heat-transfer pipe, the use amount of refrigerant also can reduce.
As mentioned above, in heat exchanger of the present invention, the heat-transfer pipe of flat is configured to be the staggered shape of biserial multilayer, and the main flow direction with respect to gas is inclined to set, and the incline direction of the described flat heat-transfer pipe in the row of the weather side of described at least gas descends for leeward one side at described gas, form the slope, simultaneously, on the fin surface between two described flat heat-transfer pipe row, also be provided with at the coconnected draining face of vertical direction.Adopt after such formation, when heat exchanger of the present invention uses as gas cooler, the condensed water that produces on the outer surface of the surface of described fin and flat heat-transfer pipe can flow on the upper surface of described flat heat-transfer pipe earlier, inclined plane along described flat heat-transfer pipe flows down then, thereafter again along be arranged on described fin lip-deep, under the coconnected draining surface current of vertical direction.Therefore, condensed water can not stop, and flowing resistance does not have very big increase yet.
In sum, the heat exchanger among the present invention is when using as gas cooler, and the condensed water that produces on the surface of fin can not stop, and can flow down swimmingly, can not make flowing resistance that very big increase is arranged.Therefore, the present invention can be useful in widely and be used for fin air-conditioner and refrigerator etc., carry out exchange heat between the fluids such as gas such as flow air and water that flows and refrigerant in the flat heat-transfer pipe between many tabular fins of stacked setting and add in the duct type heat exchanger.
Claims (14)
1. heat exchanger is characterized in that comprising:
Carry out stacked, many tabular fins of flowing betwixt of gas such as air simultaneously abreast with certain spacing; With
Roughly be with the spacing of regulation vertically be inserted in the described fin, combine closely with described fin, inside has fluid to flow and the outer rim in cross section is the heat-transfer pipe of flat,
Described flat heat-transfer pipe be configured to have the row of the weather side that is in gas and be in two row of row of downwind side of gas and a plurality of layer and two row in described flat heat-transfer pipe be the structure that staggers mutually, described flat heat-transfer pipe is tilted configuration with respect to the main flow direction of gas
The slope that descends takes place in leeward one side that the incline direction of flat heat-transfer pipe of row that is in the weather side of gas is provided in gas, is being provided with draining face on the fin surface between two flat heat-transfer pipes row.
2. the heat exchanger described in claim 1 is characterized in that: the incline direction of flat heat-transfer pipe of row that is in the downwind side of gas is provided in the slope that upwind side one side descends.
3. the heat exchanger described in claim 2, it is characterized in that: the flat heat-transfer pipe of row that is in the weather side of gas is inserted by the breach from the windward leading edge of fin, and the flat heat-transfer pipe of row that is positioned at the downwind side of gas is inserted by the breach from the leeward trailing edge of fin.
4. the heat exchanger described in each of claim 1～3 is characterized in that: the width of flat heat-transfer pipe of row that is in the downwind side of gas be configured to be in gas weather side row the flat heat-transfer pipe width 30%～60%.
5. the heat exchanger described in each of claim 1～4, it is characterized in that: described flat heat-transfer pipe is configured to be about 5 °～30 ° with respect to the angle of inclination of horizontal direction.
6. the heat exchanger described in each of claim 1～5, it is characterized in that: the row of described draining face are configured to be about 1mm～4mm to width.
7. the heat exchanger described in each of claim 1～6 is characterized in that: between the flat heat-transfer pipe of adjacency on the course, be provided with towards a plurality of vent windows of the main flow direction side opening of gas.
8. the heat exchanger described in claim 7, it is characterized in that: the angle of described vent window is 20～40 °, and vent window the width on the main flow direction of gas be configured to and stacked fin between spacing basic identical.
9. the heat exchanger described in claim 7, it is characterized in that: the height of described vent window is configured to more than or equal to 0.8mm, and is essentially 1/3～2/3 of spacing between the stacked fin.
10. the heat exchanger described in each of claim 1～6, it is characterized in that: between the flat heat-transfer pipe of adjacency on the course, be provided with the cocked part of a plurality of cut-outs towards gas main flow direction side opening, the height of the cocked part of described cut-out is essentially 1/4～3/4 of spacing between the stacked fin.
11. the heat exchanger described in claim 10 is characterized in that: the width of the cocked part of described cut-out is set 1/3～1/2 of the width that is essentially fin surface therebetween.
12. the heat exchanger described in each of claim 1～6 is characterized in that: between the flat heat-transfer pipe of adjacency on the course, be provided with by crest line and be the mutual relief part that forms of arranging in top and paddy portion that course is extended.
13. the heat exchanger described in claim 12 is characterized in that: be provided with otch on the crest line of at least one side in top or paddy portion.
14. the heat exchanger described in each of claim 1～13, it is characterized in that: portion's flowing refrigerant is selected HFC refrigerant, HC refrigerant and CO for use within it
2At least a in the refrigerant.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005352979 | 2005-12-07 | ||
| JP2005352979 | 2005-12-07 | ||
| JP2006299918 | 2006-11-06 |
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| Publication Number | Publication Date |
|---|---|
| CN1979082A true CN1979082A (en) | 2007-06-13 |
| CN100513977C CN100513977C (en) | 2009-07-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101645786A Active CN100513977C (en) | 2005-12-07 | 2006-12-07 | Heat exchanger |
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| CN (1) | CN100513977C (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101995115A (en) * | 2009-08-07 | 2011-03-30 | 江森自控科技公司 | Multi-channel heat exchanger fins |
| CN101694360B (en) * | 2009-09-30 | 2012-03-28 | 天津三电汽车空调有限公司 | Parallel flow heat exchanger and wing band structure thereof |
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| CN101995115A (en) * | 2009-08-07 | 2011-03-30 | 江森自控科技公司 | Multi-channel heat exchanger fins |
| CN102483313A (en) * | 2009-09-16 | 2012-05-30 | 开利公司 | Free-draining finned surface architecture for a heat exchanger |
| CN101694360B (en) * | 2009-09-30 | 2012-03-28 | 天津三电汽车空调有限公司 | Parallel flow heat exchanger and wing band structure thereof |
| WO2014107877A1 (en) * | 2013-01-11 | 2014-07-17 | General Electric Company | Gas turbine inlet having integrated coils and mist reducing vanes |
| CN105518405A (en) * | 2013-09-11 | 2016-04-20 | 大金工业株式会社 | Heat exchanger, air conditioner, and heat exchanger manufacturing method |
| CN104567108A (en) * | 2013-10-12 | 2015-04-29 | 杭州三花微通道换热器有限公司 | Heat exchanger and fin thereof |
| CN104567108B (en) * | 2013-10-12 | 2018-12-11 | 杭州三花微通道换热器有限公司 | A kind of heat exchanger and its fin |
| WO2017042645A1 (en) * | 2015-09-08 | 2017-03-16 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン） リミテッド | Outdoor unit for air conditioner |
| CN106918261A (en) * | 2015-12-25 | 2017-07-04 | 浙江盾安热工科技有限公司 | A kind of fin and heat exchanger |
| CN106918261B (en) * | 2015-12-25 | 2022-03-08 | 浙江盾安热工科技有限公司 | Fin and heat exchanger |
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| CN110603419A (en) * | 2017-05-11 | 2019-12-20 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
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