WO2013183136A1 - 空気熱交換器 - Google Patents
空気熱交換器 Download PDFInfo
- Publication number
- WO2013183136A1 WO2013183136A1 PCT/JP2012/064631 JP2012064631W WO2013183136A1 WO 2013183136 A1 WO2013183136 A1 WO 2013183136A1 JP 2012064631 W JP2012064631 W JP 2012064631W WO 2013183136 A1 WO2013183136 A1 WO 2013183136A1
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- WO
- WIPO (PCT)
- Prior art keywords
- water guide
- heat transfer
- guide groove
- groove
- heat exchanger
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
- F25D21/14—Collecting or removing condensed and defrost water; Drip trays
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Definitions
- the present invention relates to an air heat exchanger including a flat tube and a heat transfer fin.
- the air heat exchanger includes two tubular headers through which a refrigerant flows, a plurality of flat tubes arranged to connect the two headers, and a plurality of heat transfer fins provided between each of the plurality of flat tubes. Is provided. Each flat tube is orthogonal to the header, and each heat transfer fin is orthogonal to the flat tube. A plurality of thin flow paths communicating from the header are formed inside the flat tube. The refrigerant flows from the header to the flat tube through this flow path.
- a header, a flat tube, and a heat-transfer fin are formed with a metal material with high heat conductivity, for example, aluminum. These members are joined to each other by a brazing material or an adhesive. Air is introduced into the air heat exchanger having such a structure by using a fan.
- heat is exchanged between the refrigerant and air.
- the refrigerant is introduced into the header and then distributed to the flat tube through the flow path.
- the heat or cold of the refrigerant introduced into the flat tube is transferred from the flat tube to the heat transfer fins that expand the heat transfer area, and exchanges heat with the air flowing between the heat transfer fins.
- the air heat exchanger when used as an evaporator, the temperature of the flat tube and the surface of the heat transfer fin is lower than the temperature of the air, so when the air passes between the heat transfer fins, Water condenses on the surface of the heat transfer fin.
- the condensed water formed on the surface of the heat transfer fins is mostly moved by the action of gravity. There is no drainage. If condensation further proceeds and a large amount of condensed water stays between the heat transfer fins, the heat transfer fins may be blocked.
- Patent Document 1 discloses an air heat exchanger in which an opening is provided in a heat transfer fin and the condensed water on the surface of the heat transfer fin is drained.
- Patent Document 2 discloses an air heat exchanger that drops condensed water by inclining heat transfer fins.
- the fixing position of the heat transfer fin is likely to shift due to expansion and deformation of the flat tube, and contact between the flat tube and the heat transfer fin tends to be uneven.
- the opening is provided in the heat transfer fin, not only the heat transfer area of the heat transfer fin is decreased, but also the contact area between the heat transfer fin and the flat tube is reduced. There is a problem that resistance increases.
- the present invention can prevent an increase in ventilation resistance and a decrease in heat exchange efficiency due to condensed water generated on the surface of the heat transfer fin without increasing the thermal resistance of the flat tube and the heat transfer fin.
- An object of the present invention is to provide an air heat exchanger capable of preventing water droplets from scattering from the heat transfer fins to the leeward.
- the air heat exchanger according to the present invention has the following features.
- An air heat exchanger comprising a plurality of flat tubes and heat transfer fins provided between the flat tubes, wherein air is blown, wherein the flat tubes are drained on a side surface on which the heat transfer fins are provided.
- the heat transfer fin includes a water guide groove communicating with the drainage groove.
- the groove walls constituting the water guide groove at least the groove wall on the windward side in the air blowing direction is provided from the position on the windward side of the drainage groove toward the drainage groove, and the water guide groove is The cross-sectional area that extends toward the drainage groove along the groove wall on the windward side becomes smaller toward the drainage groove.
- the present invention without increasing the thermal resistance of the flat tube and the heat transfer fin, it is possible to prevent an increase in ventilation resistance due to condensed water generated on the surface of the heat transfer fin and a decrease in heat exchange efficiency, Furthermore, it is possible to provide an air heat exchanger that can prevent water droplets from being scattered from the heat transfer fins to the leeward side.
- Example 1 It is a fragmentary perspective view of the air heat exchanger by Example 1, and is a figure which shows a flat tube and a heat-transfer fin. It is a fragmentary perspective view of the air heat exchanger by Example 1 when a heat-transfer fin is seen from the bottom. It is a perspective view which shows the whole air heat exchanger by Example 1.
- FIG. It is a fragmentary perspective view of the conventional air heat exchanger, and is a figure which shows a flat tube and a heat-transfer fin. It is the partial side view which looked at the conventional air heat exchanger from the ventilation direction.
- Example 1 it is a partial top view of a heat-transfer fin explaining the principle of drainage of the condensed water produced on the surface of the heat-transfer fin.
- Example 2 It is a fragmentary perspective view of the air heat exchanger by Example 2, and is a figure which shows the case where one drainage groove is formed in each single side
- Example 4 it is a partial side view of a heat-transfer fin explaining the principle of drainage of the condensed water produced on the surface of the heat-transfer fin. It is a fragmentary perspective view of the air heat exchanger by Example 5, and is a figure which shows a flat tube and a heat-transfer fin. It is a fragmentary perspective view of the air heat exchanger by Example 6, and is a figure which shows a flat tube and a heat-transfer fin. It is a fragmentary perspective view of another air heat exchanger by Example 6, and is a figure which shows a flat tube and a heat-transfer fin.
- the air heat exchanger according to the present invention drains condensed water generated on the surface of the heat transfer fins by utilizing not only gravity but also surface tension and fluid force (fan wind force). For this reason, without increasing the thermal resistance of the flat tube and the heat transfer fin, it is possible to prevent an increase in ventilation resistance due to condensed water and a decrease in heat exchange efficiency, and to prevent water droplets from scattering from the heat transfer fin to the leeward. Is possible.
- the air heat exchanger according to the present invention includes a flat tube provided with a drainage groove in the length direction, and a heat transfer fin provided with a water guide groove.
- the groove wall on the windward side in the blowing direction is provided from the position on the windward side with respect to the drainage groove toward the communication portion communicating with the drainage groove.
- the groove wall on the leeward side in the air blowing direction is provided from the position on the leeward side to the drainage groove with respect to the drainage groove, but from the position on the leeward side toward the drainage groove. It may be provided and may be in the same position as the drainage groove in the blowing direction. In this way, the water guide groove extends along the groove wall on the windward side toward the communication part with the drainage groove, and is formed to communicate with the drainage groove.
- the water guide groove has a cross-sectional area perpendicular to the extending direction (hereinafter, simply referred to as “cross-sectional area”) that decreases toward the communicating portion with the drain groove.
- cross-sectional area perpendicular to the extending direction
- the cross-sectional area of the water guide groove may be reduced smoothly (gradually) or may be reduced stepwise.
- a force proportional to the radius of curvature of the water droplet acts on the water droplet in the water guide groove due to the surface tension. Therefore, a force acts on the water droplet from the side with the larger radius of curvature to the side with the smaller radius of curvature, that is, from the larger cross-sectional area of the water guide groove to the smaller side. Therefore, when the cross-sectional area of the water guide groove is reduced toward the communicating part with the drainage groove, the water droplets in the water guide groove are directed toward the drainage groove due to the force acting from the larger cross-sectional area to the smaller one. I get wet.
- the cross-sectional area of the water guide groove is reduced by gradually reducing the width of the water guide groove toward the communicating portion with the drainage groove.
- FIG. 1 is a partial perspective view of the air heat exchanger 1 according to the first embodiment, and shows a flat tube 2 and heat transfer fins 5. Air is blown to the air heat exchanger 1 by a fan (not shown).
- the X axis indicates the width direction of the air heat exchanger 1.
- the X-axis direction is also the width direction of the heat transfer fins 5.
- the positive direction of the Y axis indicates the direction of gravity
- the positive direction of the Z axis indicates the air blowing direction 10 by the fan.
- the terms “windward” and “windward” used below indicate the direction with respect to the blowing direction 10. That is, the windward side represents the negative direction side of the Z axis, and the leeward side represents the positive direction side of the Z axis.
- the air heat exchanger 1 includes a plurality of flat tubes 2 and a plurality of heat transfer fins 5 provided between the flat tubes 2 so as to be orthogonal to the flat tubes 2.
- FIG. 1 only one flat tube 2 is shown for easy understanding of the display.
- positioned at the upper and lower sides (both ends of a Y-axis direction) of the flat tube 2 is abbreviate
- the heat transfer fins 5 may have a corrugated shape.
- a plurality of thin flow paths 3 through which the refrigerant flows are formed inside.
- drainage grooves 4 extending in the length direction (Y-axis direction) are formed on both side surfaces in the X-axis direction (surfaces on which the heat transfer fins 5 are provided).
- the drainage groove 4 communicates from the upper end to the lower end in the Y-axis direction, and opens toward the positive or negative direction of the X-axis and the positive and negative directions of the Y-axis. That is, the drainage groove 4 opens toward the heat transfer fin 5 and opens in the vertical direction.
- the position of the drainage groove 4 in the blowing direction 10 (Z-axis direction) of the flat tube 2 may be arbitrary, but is preferably formed at one end on the leeward side (one end in the positive direction of the Z-axis).
- the heat transfer fin 5 is connected to the flat tube 2 at both side surfaces in the width direction (X-axis direction) and is orthogonal to the flat tube 2. Further, the heat transfer fin 5 has a water guide groove 6 communicating with the drain groove 4 of the flat tube 2.
- the groove wall 40 on the windward side (the negative direction side of the Z-axis) is directed from the position on the windward side of the drainage groove 4 to the communication portion 30 communicating with the drainage groove 4.
- the groove wall 50 on the leeward side (the positive direction side of the Z axis) is directed toward the drainage groove 4 from a position on the windward side of the drainage groove 4. Is provided. In this way, the water guide groove 6 extends toward the communication portion with the drainage groove 4 and communicates with the drainage groove 4.
- the portion on the most windward side (the negative direction side of the Z axis) of the water guide groove is referred to as “windward end portion 20”. Therefore, the communication portion 30 of the water guide groove 6 with the drain groove 4 is located on the leeward side (the positive direction side of the Z axis) with respect to the wind upper end portion 20 of the water guide groove 6.
- the position of the wind upper end portion 20 of the water guide groove 6 in the width direction (X-axis direction) of the heat transfer fin 5 can be arbitrarily determined.
- drainage grooves 4 of the flat tube 2 are present on both side surfaces of the heat transfer fin 5 in the width direction (X-axis direction). Since the heat transfer fin 5 is sandwiched between the two flat tubes 2, the water guide groove 6 includes two communication portions 30 that communicate with the respective drainage grooves 4. Therefore, the water guide groove 6 has a V shape extending from the wind upper end portion 20 toward the two communication portions 30.
- the water guide groove 6 has a function of discharging condensed water generated on the surface of the heat transfer fin 5 to the drain groove 4. Condensed water generated on the surface of the heat transfer fin 5 is pushed away to the water guide groove 6 by the wind of the fan, flows to the drain groove 4 through the water guide groove 6 due to surface tension, and is discharged from the drain groove 4. The principle of the condensed water flowing in the water guide groove 6 due to the surface tension will be described later with reference to FIG.
- a preferable position of the wind upper end portion 20 of the water guide groove 6 can be determined according to the wind speed blown by the fan, the area of the heat transfer fins 5 and the like.
- the position of the wind upper end portion 20 of the water guide groove 6 in the blowing direction 10 is preferably on the leeward side (the positive direction side of the Z-axis) as much as possible (however, on the windward side (Z The negative side of the shaft)).
- the windward upper end portion 20 of the water guide groove 6 needs to be positioned as leeward as possible.
- condensed water is mainly generated on the leeward side (the negative direction side of the Z axis), and little condensed water is generated on the leeward side (the positive direction side of the Z axis). Accordingly, most of the condensed water can be discharged by setting the position of the windward end 20 of the water guide groove 6 to the leeward side as much as possible. In addition, the position of the lee end portion 20 of the water guide groove 6 can be determined so that the region of the surface of the heat transfer fin 5 where much condensed water is not generated is located on the leeward side of the water guide groove 6.
- the width of the water guide groove 6 gradually decreases from the wind top part 20 toward the communication part 30 with the drainage groove 4. That is, in the water guide groove 6, the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 have a relationship of r 1 > r 2 , and the width gradually increases from the wind upper end portion 20 toward the communication portion 30. It gets smaller. Preferably, r 1 > 2r 2 . Specific sizes of the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 can be determined according to the wind speed blown by the fan, the hydrophilicity of the heat transfer fins 5, and the like.
- the depth of the water guide groove 6 can be arbitrarily determined according to the wind speed blown by the fan, the thickness and hydrophilicity of the heat transfer fins 5 and the like.
- the water guide groove 6 communicates from the wind upper end portion 20 to the drainage groove 4 of the flat tube 2 connected to both side surfaces of the heat transfer fin 5 by the communication portion 30 with the drainage groove 4. Yes. Further, the wind upper end portion 20 of the water guide groove 6 is located at the center in the width direction (X-axis direction) of the heat transfer fin 5. That is, the water guide groove 6 is a V-shaped groove that spreads from the windward end 20 toward the leeward side (the positive direction of the Z axis).
- FIG. 2 is a partial perspective view of the air heat exchanger 1 when the heat transfer fins 5 are viewed from below (the positive direction of the Y axis). 2, the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- the water guide groove 6 of the heat transfer fin 5 When the heat transfer fin 5 is viewed from below (the positive direction of the Y axis), the water guide groove 6 of the heat transfer fin 5 has a convex shape. That is, the water guide groove 6 protrudes downward (in the positive direction of the Y axis) from the lower surface of the heat transfer fin 5.
- FIG. 3 is a perspective view showing the entire air heat exchanger 1 according to the first embodiment of the present invention.
- the air heat exchanger 1 includes two headers 11 through which refrigerant flows, a plurality of flat tubes 2 fixed so as to connect the headers 11, and a plurality of heat transfer fins 5 provided between the flat tubes 2. .
- Each flat tube 2 is formed with a plurality of flow paths through which the refrigerant flows, and the refrigerant is distributed from the header 11. Air is blown to the air heat exchanger 1 in the blowing direction 10 by a fan (not shown).
- the air heat exchanger 1 heat is exchanged between the refrigerant and air.
- the heat or cold heat of the refrigerant flowing in the flow path inside the flat tube 2 is transferred from the flat tube 2 to the heat transfer fin 5 that expands the heat transfer area, and exchanges heat with the air flowing between the heat transfer fins 5. Do it efficiently.
- the condensed water that has flowed from the heat transfer fin 5 through the water guide groove 6 to the drain groove 4 of the flat tube 2 is drained to the header 11 provided at the lower portion of the flat tube 2 using gravity.
- the flat tube 2 at both ends in the width direction (X-axis direction) of the air heat exchanger 1 may have drainage grooves 4 formed only on one side where the heat transfer fins 5 are provided. Drainage grooves 4 may be formed on both side surfaces of.
- FIG. 4 is a partial perspective view of a conventional air heat exchanger 100 showing a flat tube 200 and heat transfer fins 500.
- FIG. 4 as in FIG. 1, only one flat tube 200 is shown, and the header is not shown.
- the direction indicated by the coordinate axes is the same as in FIG.
- the heat transfer fins 500 are attached so as to be orthogonal to the flat tube 200 and have a corrugated shape. Air is blown into the air heat exchanger 100 in the blowing direction 10 by a fan (not shown).
- the discharge path of the condensed water generated on the surface of the heat transfer fin 500 will be described.
- the heat exchanger 100 is used as an evaporator, the surface temperature of the flat tube 200 becomes lower than the temperature of the air. Therefore, water in the air condenses on the surfaces of the flat tube 200 and the heat transfer fins 500 and water droplets are formed. Arise.
- FIG. 5 is a partial side view of the conventional air heat exchanger 100 shown in FIG. 4 as viewed from the air blowing direction 10 (Z-axis direction).
- the conventional air heat exchanger 100 there is no path through which the condensed water 22 is drained, and it tends to stay in the form of water droplets on the surface of the heat transfer fins 500. Further, water droplets (condensed water 22) generated on the surface of the heat transfer fins 500 gradually grow and block part of the gaps between the heat transfer fins 500.
- the gap between the heat transfer fins 500 is closed, there is a problem that the pressure loss on the air side increases, the ventilation resistance of the air heat exchanger 100 increases, and the heat exchange efficiency decreases. Further, there is a problem that the condensed water 22 pushed away by the air scatters to the leeward side of the heat transfer fins 500 and blows out from the air heat exchanger 100.
- FIG. 6 is a view for explaining the principle of drainage of the condensed water 22 generated on the surface of the heat transfer fin 5, and is a top view schematically showing a part of the water guide groove 6 formed in the heat transfer fin 5. .
- FIG. 6 is a view of the heat transfer fin 5 as viewed from above (the negative direction of the Y axis).
- the width of the water guide groove 6 becomes narrower from the right side to the left side of the figure. That is, the wind upper end portion 20 of the water guide groove 6 is on the right side of FIG. 6, and the communication portion 30 of the water guide groove 6 with the drain groove 4 is on the left side.
- condensed water 22 exists in the form of water droplets as shown in FIG. 6. The water droplets of the condensed water 22 are generated on the surface of the heat transfer fins 5 and then pushed into the water guide groove 6 by the wind of the fan.
- FIG. 6 also shows capillary forces f 1 and f 2 generated in the condensed water 22 due to surface tension.
- f 1 is a force applied to the condensed water 22 from the communicating portion 30 side of the water guiding groove 6 with the drain groove 4
- f 2 is a force applied to the condensed water 22 from the wind upper end portion 20 side of the water guiding groove 6.
- R 1 indicates the radius of curvature of the end of the water droplet of the condensed water 22 on the side of the communication part 30, and R 2 indicates the radius of curvature of the end on the side of the windward end 20. Since the width of the water guide groove 6 becomes narrower from the wind upper end portion 20 side toward the communication portion 30 side, R 1 ⁇ R 2 is satisfied.
- ⁇ indicates a taper angle of the water guide groove 6 (an angle representing a rate at which the width of the water guide groove 6 becomes narrower).
- Capillary forces f 1 and f 2 generated in the condensed water 22 are obtained by the equations (1) and (2).
- ⁇ is the surface tension acting on the condensed water 22
- ⁇ is the contact angle formed by the water guide groove 6 and the condensed water 22.
- the surface of the heat transfer fin 5 is processed to be hydrophilic
- the surface of the water guide groove 6 is also hydrophilic.
- the contact angle ⁇ formed by the water guide groove 6 and the condensed water 22 is very small and can be considered to be close to zero. Therefore, since R 1 ⁇ R 2 , f 1 ⁇ f 2 from the formulas (1) and (2). For this reason, a force directed from the wind upper end 20 side toward the communication portion 30 side acts on the condensed water 22, and the condensed water 22 wets from the wider width of the water guide groove 6 to the narrower (communication portion 30 side). move on.
- the condensed water 22 generated on the surface of the heat transfer fin 5 is forced to flow into the water guide groove 6 by the wind of the fan, and then the principle based on the surface tension acting on the condensed water 22 is used. Accordingly, the wetted portion 30 is wetted toward the communicating portion 30 with the drainage groove 4 and efficiently drained through the drainage groove 4 formed in the flat tube 2.
- the water guide groove 6 protrudes downward (in the positive direction of the Y axis) from the lower surface of the heat transfer fin 5.
- Condensed water 22 generated on the lower surface of the heat transfer fin 5 is pushed down to the protruding water guide groove 6 by the wind of the fan, and then pushed down to the drain groove 4 along the water guide groove 6. For this reason, the condensed water 22 generated on the surface of the heat transfer fin 5 is also efficiently discharged from the drain groove 4 on the lower surface of the heat transfer fin 5.
- the condensed water generated on the surface of the heat transfer fin 5 is efficiently discharged on both the upper surface and the lower surface of the heat transfer fin 5. Therefore, it is possible to prevent an increase in ventilation resistance and a decrease in heat exchange efficiency of the air heat exchanger 1, and it is possible to prevent scattering of water droplets from the heat transfer fins 5 to the leeward.
- the water guide groove 6 protrudes downward (in the positive direction of the Y axis). However, the water guide groove 6 does not have to protrude downward on the lower surface of the heat transfer fin 5. Whether the water guide groove 6 protrudes downward can be determined according to the manufacturing conditions of the heat transfer fin 5 such as the thickness of the heat transfer fin 5 and the processing method of the water guide groove 6. Moreover, in the Example described below, although the lower surface of the heat-transfer fin 5 is not demonstrated, a water guide groove may protrude toward the downward direction (positive direction of a Y-axis).
- Example 2 of the present invention An air heat exchanger according to Example 2 of the present invention will be described.
- the present embodiment is an example in the case where the heat transfer fin 5 includes a plurality of water guide grooves 6 in the air heat exchanger 1 of the first embodiment.
- the number of the water guide grooves 6 formed in the heat transfer fins 5 is not limited to one and may be plural.
- the air heat exchanger 1 including the heat transfer fins 5 having the plurality of water guiding grooves 6 will be described by taking the air heat exchanger 1 in the case where the number of the water guiding grooves 6 is two as an example. The following description is applicable also when the number of the water guide grooves 6 is three or more.
- FIG. 7 and 8 are partial perspective views of the air heat exchanger 1 including the heat transfer fins 5 having the two water guide grooves 6, and show the flat tubes 2 and the heat transfer fins 5.
- the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- one drainage groove 4 is formed on each side surface in the X-axis direction of the flat tube 2.
- Two drain grooves 4 are formed on each side of the direction.
- two water guide grooves 6a and 6b are formed in the air blowing direction 10 (Z-axis direction), and the two water guide grooves 6a and 6b are common to each other. It communicates with the drainage groove 4.
- the widths of the two water guide grooves 6a and 6b are gradually reduced from the wind upper end parts 20a and 20b toward the communication part 30a and the communication part 30b with the drainage groove 4.
- the positions of the wind upper end portions 20a and 20b of the water guide grooves 6a and 6b in the air blowing direction 10 (Z-axis direction) are both on the windward side (the negative direction side of the Z-axis) of the drainage groove 4.
- the principle of discharging condensed water generated on the surface of the heat transfer fin 5 is the same as that of the first embodiment. That is, the condensed water generated on the surface of the heat transfer fin 5 is forced to flow into the water guide groove 6a and the water guide groove 6b by the wind of the fan, and flows to the drain groove 4 through the water guide groove 6a and the water guide groove 6b due to surface tension. It is discharged from the groove 4.
- two water guide grooves 6a and 6b are formed in the blowing direction 10 (Z-axis direction).
- Two drain grooves 4a and 4b are formed on each side surface of the flat tube 2 in the X-axis direction.
- the water guide groove 6a communicates with the drainage groove 4a from the wind upper end portion 20a
- the water guide groove 6b communicates with the drainage groove 4b from the wind upper end portion 20b.
- the widths of the two water guide grooves 6a and 6b are gradually reduced from the wind upper end portions 20a and 20b toward the communication portions 30a and 30b with the drain grooves 4a and 4b, respectively.
- the position of the wind upper end portion 20a of the water guide groove 6a in the blowing direction 10 (Z-axis direction) is on the windward side (the negative direction side of the Z axis) of the drain groove 4a, and the wind upper end portion 20b of the water guide groove 6b is The position in the blowing direction 10 is on the windward side of the drainage groove 4b.
- the principle of discharging condensed water generated on the surface of the heat transfer fin 5 is the same as that of the first embodiment. That is, the condensed water generated on the surface of the heat transfer fin 5 is forced to flow into the water guide groove 6a and the water guide groove 6b by the wind of the fan, and flows to the drain grooves 4a and 4b through the water guide groove 6a and the water guide groove 6b by surface tension. The water is discharged from the drainage grooves 4a and 4b.
- the distance that the condensed water generated on the surface of the heat transfer fin 5 reaches the water guide grooves 6a and 6b can be shortened.
- the condensed water can be discharged from the drain grooves 4 (or the drain grooves 4a and 4b) more efficiently.
- Example 3 of the present invention An air heat exchanger according to Example 3 of the present invention will be described.
- the present embodiment is an example in which the cross-sectional area of the water guide groove is reduced by gradually reducing the width of the water guide groove toward the communicating portion with the drainage groove.
- FIG. 9 is a partial perspective view of the air heat exchanger 1 according to the third embodiment, and shows a flat tube 2 and heat transfer fins 5.
- the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- the heat transfer fin 5 has a water guide groove 7 communicating with the drainage groove 4.
- the width of the water guide groove 7 is gradually reduced from the wind upper end portion 20 toward the communication portion 30 with the drainage groove 4 (in the example of FIG. 9, three steps).
- the position of the wind upper end portion 20 of the water guide groove 7 in the air blowing direction 10 (Z-axis direction) is on the windward side (the negative direction side of the Z-axis) of the drainage groove 4.
- the water guide grooves 7 formed in the heat transfer fins 5 may have a shape in which the width gradually decreases from the wind upper end portion 20 toward the communication portion 30, as illustrated in FIG. 1. It does not have to be a tapered shape like the water guide groove 6 of the first embodiment.
- the width of the water guide groove 7 is narrowed in three stages, but is not limited to three stages.
- the stage where the width of the water guide groove 7 is narrowed can be arbitrarily determined.
- the condensed water generated on the surface of the heat transfer fin 5 is pushed into the water guide groove 7 by the wind force of the fan, and then the surface tension acting on the condensed water as shown in FIG.
- the water advances toward the communicating portion 30 with the drainage groove 4 and is efficiently drained through the drainage groove 4 formed in the flat tube 2. Therefore, the air heat exchanger according to the present embodiment also has the same effect as the air heat exchanger according to the first embodiment.
- Example 4 of the present invention An air heat exchanger according to Example 4 of the present invention will be described.
- the present embodiment is an example in which the cross-sectional area of the water guide groove is reduced by gradually reducing the depth of the water guide groove toward the communicating portion with the drainage groove.
- FIG. 10 is a partial perspective view of the air heat exchanger 1 according to the fourth embodiment, and shows a flat tube 2 and heat transfer fins 5.
- the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- the heat transfer fin 5 is formed with a water guide groove 8 communicating with the drainage groove 4 from the wind upper end portion 20.
- the depth of the water guide groove 8 gradually decreases from the wind upper end portion 20 toward the communication portion 30 with the drainage groove 4.
- the position of the wind upper end portion 20 of the water guide groove 8 in the air blowing direction 10 (Z-axis direction) is on the windward side (the negative direction side of the Z-axis) of the drainage groove 4.
- FIG. 11 is a partial side view of the air heat exchanger 1 shown in FIG. 10 as viewed from the blowing direction 10 (Z-axis direction).
- the depth at the wind upper end portion 20 is represented by d 1 and the depth at the communicating portion 30 with the drainage groove 4 is represented by d 2 , d 1 > d 2 , the depth gradually decreases from the wind upper end portion 20 toward the communication portion 30.
- Specific sizes of the depth d 1 at the wind upper end portion 20 and the depth d 2 at the communication portion 30 can be determined according to the wind speed blown by the fan, the hydrophilicity of the heat transfer fins 5, and the like.
- the taper angle ⁇ of the water guide groove indicates an angle representing the ratio of the depth of the water guide groove 8 becoming shallower.
- FIG. 12 is a view for explaining the principle of drainage of the condensed water 22 generated on the surface of the heat transfer fin 5 in this embodiment, and schematically shows a part of the water guide groove 8 formed in the heat transfer fin 5.
- FIG. FIG. 12 shows the air heat exchanger 1 viewed from the air blowing direction 10 (Z-axis direction) as in FIG.
- the taper angle ⁇ of the water guide groove 8 indicates an angle representing the rate at which the depth of the water guide groove 8 becomes shallower.
- the depth of the water guide groove 8 may be reduced stepwise from the wind top part 20 toward the communication part 30 with the drainage groove 4.
- the stage where the depth of the water guide groove 8 is narrowed can be arbitrarily determined.
- the width of the water guide groove 8 can be arbitrarily determined according to the wind speed blown by the fan or the hydrophilicity of the heat transfer fins 5.
- the width of the water guide groove 8 may be constant, or may be made smaller from the wind upper end portion 20 toward the communication portion 30 as shown in FIGS. 1 and 9.
- the water guide groove 8 protrudes downward (in the positive direction of the Y axis) from the lower surface of the heat transfer fin 5.
- Condensed water 22 generated on the lower surface of the heat transfer fin 5 is pushed down to the protruding water guide groove 8 by the wind of the fan, and then pushed down to the drain groove 4 along the water guide groove 8.
- the water guide groove 8 may not protrude downward from the lower surface of the heat transfer fin 5. Whether the water guide groove 8 protrudes downward can be determined according to the manufacturing conditions of the heat transfer fin 5 such as the thickness of the heat transfer fin 5 and the processing method of the water guide groove 8.
- the condensed water 22 generated on the surface of the heat transfer fin 5 is pushed into the water guide groove 8 by the wind of the fan and then acts on the condensed water 22 as shown in FIG.
- the surface tension wets toward the communication portion 30 with the drainage groove 4 and is efficiently drained through the drainage groove 4 formed in the flat tube 2. Therefore, the air heat exchanger according to the present embodiment also has the same effect as the air heat exchanger according to the first embodiment.
- the present embodiment is an example of an air heat exchanger in which a water guide groove formed in a heat transfer fin communicates with a drainage groove of a flat tube at one communication portion.
- FIG. 13 is a partial perspective view of the air heat exchanger 1 according to the fifth embodiment, and shows the flat tubes 2 and the heat transfer fins 5. 13, the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- the flat tube 2 has a drain groove 4 formed on one side surface in the X-axis direction.
- the drainage groove 4 is open toward the positive direction of the X axis and the positive and negative directions of the Y axis.
- the heat transfer fin 5 has a water guide groove 9 communicating with the drainage groove 4 provided in the flat tube 2.
- the water guide groove 9 extends from the wind upper end part 20 to the communication part 30 with the drainage groove 4.
- the communication part 30 with the drainage groove 4 of the water guide groove 9 is only one place.
- the wind upper end portion 20 of the water guide groove 9 is on the windward side (the Z axis negative direction side) in the air blowing direction 10 (Z axis direction) than the communication portion 30 of the water guide groove 9 with the drain groove 4.
- the position of the wind upper end portion 20 of the water guide groove 9 in the width direction (X-axis direction) of the heat transfer fin 5 is the opposite side of the communication portion 30 in the width direction (X-axis direction). It is a connection part.
- the water guide groove 9 is directed from the wind upper end 20 at one end in the width direction (X-axis direction) of the heat transfer fin 5 to the communication portion 30 with the drain groove 4 at the other end, and in the air blowing direction 10 (Z From the windward side (the negative direction side of the Z axis) in the axial direction toward the leeward side (the positive side of the Z axis). Therefore, as shown in FIG. 13, the water guide groove 9 is inclined with respect to the width direction (X-axis direction) of the heat transfer fin 5 and the blowing direction 10 (Z-axis direction).
- the width of the water guide groove 9 is gradually reduced from the wind top part 20 toward the communication part 30 with the drainage groove 4. That is, in the water guide groove 9, the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 have a relationship of r 1 > r 2 , and the width gradually increases from the wind upper end portion 20 toward the communication portion 30. It gets smaller. Preferably, r 1 > 2r 2 . Specific sizes of the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 can be determined according to the wind speed blown by the fan, the hydrophilicity of the heat transfer fins 5, and the like.
- the depth of the water guide groove 9 can be arbitrarily determined according to the wind speed blown by the fan, the thickness and hydrophilicity of the heat transfer fins 5 and the like.
- the air heat exchanger 1 also has the same effect as the air heat exchanger according to the first embodiment.
- the width of the water guide groove 9 gradually decreases toward the communication portion 30 is shown, but the depth may decrease toward the communication portion 30. Further, the width and depth of the water guide groove 9 may be gradually reduced toward the communication portion 30. In any case, the cross-sectional area of the water guide groove 9 only needs to decrease from the wind upper end portion 20 toward the communication portion 30.
- the flat tube 2 has the drainage grooves 4 formed on one side surface in the X-axis direction, but the drainage grooves 4 may be formed on both side surfaces in the X-axis direction.
- the water guide groove 9 may communicate with the drainage groove 4 of the flat tube 2 at the wind upper end portion 20. That is, the water guide groove 9 may communicate with the drainage groove 4 at both ends (the wind upper end portion 20 and the communication portion 30).
- FIG. 14 is a partial perspective view of the air heat exchanger 1 according to the sixth embodiment, and shows the flat tubes 2 and the heat transfer fins 5. 14, the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- the heat transfer fin 5 has a water guide groove 12 communicating with the drainage groove 4.
- the water guide groove 12 has a groove wall 50 on the leeward side (the positive direction side of the Z axis) among the groove walls constituting the water guide groove 12. 4 is in the same position. Therefore, the overall shape of the water guide groove 12 as viewed from above (the negative direction of the Y axis) is a triangle composed of the groove wall 50 and the two groove walls 40 on the windward side (the negative direction side of the Z axis). is there.
- the groove wall 50 on the leeward side may or may not be parallel to the X axis.
- FIG. 15 is a partial perspective view of another air heat exchanger 1 according to the sixth embodiment, and shows a flat tube 2 and heat transfer fins 5.
- the same reference numerals as those in FIG. 1 denote the same elements as those in FIG. 1, and the description of these elements is omitted.
- a water guide groove 13 communicating with the drain groove 4 is formed.
- the water guide groove 13 has a groove wall 50 on the leeward side (the positive direction side of the Z axis) among the groove walls constituting the water guide groove 13, which is leeward than the drainage groove 4.
- the entire shape of the water guide groove 13 as viewed from above (the negative direction of the Y axis) is composed of two groove walls 50 and two groove walls 40 on the windward side (the negative direction side of the Z axis). Convex square.
- the position of the wind upper end portion 20 in the blowing direction 10 (Z-axis direction) is on the windward side of the drainage groove 4 (on the negative direction side of the Z-axis). ).
- the widths of the water guide groove 12 and the water guide groove 13 are gradually reduced from the wind upper end portion 20 toward the communication portion 30 with the drainage groove 4. That is, in the water guide groove 12 and the water guide groove 13, the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 are in a relationship of r 1 > r 2 , and are directed from the wind upper end portion 20 toward the communication portion 30. The width gradually decreases. Preferably, r 1 > 2r 2 . Specific sizes of the width r 1 at the wind upper end portion 20 and the width r 2 at the communication portion 30 can be determined according to the wind speed blown by the fan, the hydrophilicity of the heat transfer fins 5, and the like.
- the condensed water can be formed according to the same principle as described in the first embodiment with reference to FIG. 6, Formula (1), and Formula (2). Can be discharged from the water guide groove 12 or the water guide groove 13 to the drain groove 4.
- the condensed water generated on the surface of the heat transfer fin 5 is swept away by the wind of the fan into the water guide groove 12 or the water guide groove 13 and then the surface tension acting on the condensed water. It progresses wet toward the communication part 30 with the drainage groove 4 and is efficiently drained through the drainage groove 4 formed in the flat tube 2. For this reason, the air heat exchanger according to the present embodiment also has the same effect as the air heat exchanger according to the first embodiment.
- the water guide groove 13 shown in FIG. is formed so that the portion on the leeward side of the drainage groove 4 is as small as possible (that is, the groove wall 50 is not located on the leeward side of the drainage groove 4 as much as possible). A decrease in the efficiency of drainage of the groove 13 can be suppressed, and condensed water can be discharged from the water guide groove 13 to the drainage groove 4.
- the water guide groove extends linearly from the wind upper end portion 20 toward the communication portion 30 on the surface (ZX plane) of the heat transfer fin 5 (for example, the water guide groove is In FIG. 1, it extends in two straight lines from the windward end 20 and in FIG. 13 extends from the windward upper part 20 by one straight line).
- the water guide groove does not need to extend in a straight line, and may extend in a polygonal line or a curved line.
- the part from the leeward side to the windward side (the part going from the positive side of the Z axis to the negative side) is in the water guide groove, the condensed water in the water guide groove does not advance against the wind force of the fan. Therefore, drainage efficiency is lowered, which is not preferable.
- the shape of the cross section perpendicular to the extending direction of the water guide groove is arbitrary.
- the cross-sectional shape may be a polygonal shape such as a quadrangle or a triangle, or a curved shape such as a circle or an ellipse.
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Abstract
Description
Claims (8)
- 複数の扁平管と、前記扁平管の間に設けられた伝熱フィンとを備え、空気が送風される空気熱交換器であって、
前記扁平管は、前記伝熱フィンが設けられる側面に排水溝を備え、
前記伝熱フィンは、前記排水溝へ連通する導水溝を備え、
前記導水溝を構成する溝壁のうち、少なくとも前記空気の送風方向の風上側にある溝壁は、前記排水溝よりも風上側の位置から、前記排水溝へ向けて設けられ、
前記導水溝は、前記風上側にある溝壁に沿って前記排水溝へ向かって延在し、延在方向に垂直な断面積が前記排水溝へ向かって小さくなっていくことを特徴とする空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記伝熱フィンは、前記伝熱フィンを間に設けた2つの前記扁平管のそれぞれの前記排水溝へ連通する導水溝を備える空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記導水溝は、幅が前記排水溝へ向かって小さくなっていく空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記導水溝は、深さが前記排水溝へ向かって小さくなっていく空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記導水溝は、前記断面積が前記排水溝へ向かって滑らかに小さくなっていく空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記導水溝は、前記断面積が前記排水溝へ向かって段階的に小さくなっていく空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記伝熱フィンは、前記導水溝を前記送風方向に複数備える空気熱交換器。 - 請求項1記載の空気熱交換器であって、
前記導水溝は、前記伝熱フィンの前記導水溝を備える面とは反対側の面で、前記伝熱フィンから突出する空気熱交換器。
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US14/405,408 US9534827B2 (en) | 2012-06-07 | 2012-06-07 | Air heat exchanger |
JP2014519757A JP5799382B2 (ja) | 2012-06-07 | 2012-06-07 | 空気熱交換器 |
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CN108253834A (zh) * | 2016-12-28 | 2018-07-06 | 丹佛斯微通道换热器(嘉兴)有限公司 | 用于换热器的扁管和具有该扁管的换热器 |
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CN108716790B (zh) * | 2018-04-24 | 2020-09-15 | 安徽春辉仪表线缆集团有限公司 | 一种传热效率高的蒸发器 |
CN109668450A (zh) * | 2018-11-29 | 2019-04-23 | 金阿益 | 一种石油炼制用翅片式板式交叉组合换热器装置 |
CN109668450B (zh) * | 2018-11-29 | 2020-10-30 | 浙江天旭机电设备有限公司 | 一种石油炼制用翅片式板式交叉组合换热器装置 |
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JP5799382B2 (ja) | 2015-10-28 |
JPWO2013183136A1 (ja) | 2016-01-21 |
US9534827B2 (en) | 2017-01-03 |
US20150211781A1 (en) | 2015-07-30 |
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