WO2012102053A1 - Échangeur de chaleur à tube à ailettes - Google Patents

Échangeur de chaleur à tube à ailettes Download PDF

Info

Publication number
WO2012102053A1
WO2012102053A1 PCT/JP2012/000521 JP2012000521W WO2012102053A1 WO 2012102053 A1 WO2012102053 A1 WO 2012102053A1 JP 2012000521 W JP2012000521 W JP 2012000521W WO 2012102053 A1 WO2012102053 A1 WO 2012102053A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
leeward
windward
rib
fin
Prior art date
Application number
PCT/JP2012/000521
Other languages
English (en)
Japanese (ja)
Inventor
勝志 谷口
横山　昭一
富之 野間
高橋　正敏
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to JP2012554699A priority Critical patent/JPWO2012102053A1/ja
Publication of WO2012102053A1 publication Critical patent/WO2012102053A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present invention is used in air conditioners such as room air conditioners, packaged air conditioners, and car air conditioners, heat pump water heaters, refrigerators, freezers, and the like, and gas such as air flowing between a plurality of stacked flat fins.
  • the present invention relates to a finned tube heat exchanger that transfers heat to and from a fluid such as water or refrigerant flowing in a heat transfer tube.
  • a fin-and-tube heat exchanger (hereinafter referred to as a “fin-tube heat exchanger”) composed of a plurality of laminated flat plate-shaped heat transfer fins and heat transfer tubes is shown in FIG.
  • a large number of plate-like fins 101 are stacked in parallel at a constant pitch, and a gas W such as air flows between them, and inserted into these fins 101 at a predetermined pitch at a substantially right angle.
  • a heat transfer tube 104 through which a fluid R such as a refrigerant flows.
  • the heat transfer tube 104 is tightly joined to a cylindrical fin collar 102 that rises perpendicularly to the outer periphery of the through hole of the fin 101.
  • the slit forming portion 103 of the fin 101 of this heat exchanger is provided with a notch 113 as shown in FIGS. 8, 9 and 10, and the upwind fin 101 is raised with respect to the gas flow 1 of the notch.
  • a peak 115 having an opening 114 formed by a notch 113 is provided on the leeward side.
  • ridges 115 are formed, when the gas flows along the ridges 115 and passes through the opening 114 on the leeward side, a vertical vortex is generated, from which the leeward heat transfer fin surface There are some which improve the heat exchanger efficiency by disturbing the temperature boundary layer and improving the heat transfer efficiency (see, for example, Patent Document 1).
  • FIG. 12 and FIG. 13 it is called “corrugated” in which the fin 201 is bent at an angle of ⁇ 1 about a straight line in a direction substantially perpendicular to the gas flow 1 or in the longitudinal direction of the heat transfer fin 201. It is known that heat transfer efficiency is improved by making the shape (for example, see Patent Document 2).
  • the fin strength can be increased by bending the fin into a corrugated shape. There are problems such as an increase and an increase in air pressure loss during operation.
  • the present invention has been made in view of such conventional problems, and while achieving high heat exchanger efficiency, it improves fin strength, reduces manufacturing and transportation man-hours and costs, and is also in operation.
  • the purpose is to minimize the increase in air pressure loss.
  • the finned tube heat exchanger according to the present invention is formed by providing notches in the heat transfer fins, raising the heat transfer fins on the windward side of the cut gas, and cutting the leeward side.
  • a first corrugated rib provided further on the windward side of the plurality of mountain parts, and the windward side of the mountain part that is the most upwind among the plurality of mountain parts.
  • a straight line connecting the apex and the portion of the first corrugated rib that is on the most windward side is arranged so as to be substantially parallel to the gas flow direction.
  • the finned tube heat exchanger of the present invention by providing the wave-shaped ribs, it is possible to improve the heat exchange efficiency while suppressing the increase in air-side pressure loss, improve the fin strength and reduce the cost. It is possible to simultaneously improve manufacturability and handling properties while suppressing the increase.
  • FIG. 1 of the present invention The bottom view of the heat-transfer fin in Embodiment 1 of this invention
  • Front view of heat transfer fin in embodiment 2 of the present invention Front view of heat transfer fin in embodiment 3 of the present invention
  • Front view of heat transfer fin in embodiment 4 of the present invention The bottom view of the heat-transfer fin in Embodiment 4 of this invention
  • Front view of conventional heat transfer fin Bottom view of conventional heat transfer fin Enlarged perspective view of the main part of a conventional heat transfer fin
  • a perspective view of a conventional finned tube heat exchanger Front view of another conventional heat transfer fin Bottom view of another conventional heat transfer fin
  • the first invention includes a plurality of heat transfer fins laminated substantially in parallel at a predetermined interval, and a plurality of heat transfer tubes penetrating the heat transfer fins in a direction substantially orthogonal to the planar direction of the heat transfer fins.
  • a substantially cylindrical fin collar extending in a direction substantially orthogonal to the plane direction of the heat transfer fin is formed around a through hole of the heat transfer fin through which the heat transfer tube passes,
  • a fin tube type heat exchange that is inserted into the through hole in close contact with the fin collar and performs heat exchange between the gas flowing in the plane direction of the heat transfer fin and the thermal refrigerant flowing inside the heat transfer tube.
  • the heat transfer fins are provided with cuts, the heat transfer fins on the windward side of the cuts are raised, and a ridge having an opening formed by the cuts on the leeward side;
  • the mountain part provided And a first corrugated rib provided on the windward side, and the windward apex of the peak portion of the plurality of peak portions on the windward side and the windward side of the first corrugated rib.
  • a straight line connecting the portions is arranged so as to be substantially parallel to the gas flow direction.
  • the longitudinal strength of the heat transfer fin can be increased. Therefore, the heat transfer fin can be bent and caught in the depression of the press machine during the feed process at the time of heat transfer fin press, etc., thereby reducing the machine failure or the heat transfer fin buckling and causing a production loss.
  • the strength of the heat transfer fin in the gas flow direction can be increased. Therefore, for example, in the process of bending the heat exchanger about 90 degrees around the straight line in the vertical direction of the heat exchanger, called L-bending when manufacturing a heat exchanger for a room air conditioner outdoor unit, the phenomenon that the heat transfer fins bend is caused. Can be reduced.
  • the straight line connecting the most windward portion of the corrugated rib and the apex of the mountain portion is arranged so as to be substantially parallel to the wind flow direction. Therefore, the gas divided into the left and right toward the wind flow at the most windward part of the corrugated rib flows smoothly along the slope of the mountain, so it is excellent while minimizing the increase in pressure loss Heat transfer performance can be obtained.
  • the windward apex of the mountain portion that is on the leeward side of the mountain portion that is most windward, and the portion that is the most downstream side of the first corrugated rib is arranged so as to be substantially parallel to the gas flow direction. That is, a configuration is adopted in which the apex of the second and subsequent peaks is provided on the downstream side in the wind flow direction from the most leeward side of the corrugated rib.
  • a line segment connecting a portion of the first corrugated rib that is closest to the leeward side and each of the two windward ridges adjacent to each other on the windward side. are arranged so that their midpoints are substantially parallel to the gas flow direction.
  • a configuration is adopted in which the midpoint of the apex of the first adjacent mountain part counted from the windward is installed in the part of the wave-shaped rib on the downstream side in the wind flow direction from the part on the most leeward side.
  • the air is sent evenly to the peaks arranged in the heat transfer fins, and excellent heat transfer characteristics can be obtained while minimizing the increase in pressure loss, and the frosting condition in cold regions is also achieved. Since it can equalize, the capability fall by frost formation can also be suppressed.
  • a second corrugated rib is provided further on the leeward side of the mountain part that is most leeward, and the windward side of the mountain part that is most leeward.
  • the straight line connecting the apex and the end of the opening of the peak portion is the most windward part of the second corrugated rib, and the most leeward side part adjacent to the windward part. It is arranged to pass between.
  • the second corrugated rib is provided further downstream than the most downstream peak portion, the longitudinal strength of the heat transfer fins is further increased, and machine failure and production loss are further reduced. Can do.
  • the strength of the heat transfer fin in the gas flow direction is further increased, and the problem that the heat transfer fin is bent in the L bending process can be solved.
  • the windward apex and the leeward apex (the end of the opening) of the most downstream peak portion between the most windward side portion and the most leeward side portion of the corrugated rib provided on the downstream side ) Are intersected (passed between). Therefore, since the vertical vortex generated on the downstream side of the peak portion flows smoothly along the second corrugated rib, excellent heat transfer characteristics can be obtained while minimizing an increase in pressure loss. Can do.
  • the height of the first corrugated rib or the second corrugated rib is one third of the stacking interval of the heat transfer fins.
  • the above is 2/3 or less. According to this, since the height of the wave-shaped rib in the heat transfer fin stacking direction is not less than one third and not more than two thirds of the heat transfer fin stacking interval, an increase in pressure loss is suppressed. Fin strength and heat transfer acceleration effect can be obtained.
  • an angle formed by a corrugated tangent of the first corrugated rib or the second corrugated rib and the gas flow direction is It is 45 degrees or more. According to this, since the acute angle formed by the corrugated tangent of the corrugated rib and the wind flow is 45 degrees or more, when the heat exchanger is used as an evaporator, in particular, before the windward side of the heat transfer fin. Condensed water adhering in a large amount in the vicinity of the edge is dripped and drained quickly without staying in the heat transfer fins, so that it is possible to prevent the draft resistance from increasing abnormally. The same applies to the drainage during the defrosting operation.
  • the finned tube heat exchanger according to the present invention penetrates through heat transfer fins in a direction orthogonal to the plane direction of the plurality of heat transfer fins and laminated in parallel at a predetermined interval. And a plurality of heat transfer tubes.
  • a heat medium such as a refrigerant passes through the inside of each heat transfer tube and exchanges heat with a gas (generally air) flowing in the plane direction of the heat transfer fins between the heat transfer fins.
  • FIG. 1 is a front view of a heat transfer fin of the present embodiment
  • FIG. 2 is a bottom view thereof
  • FIG. 3 is an enlarged perspective view of a main part.
  • FIG. 1 shows one of the plurality of heat transfer fins 10, and FIG. 2 penetrates the four heat transfer fins 10 and the heat transfer fins 10 among the plurality of stacked heat transfer fins 10.
  • One of the plurality of heat transfer tubes 12 is shown.
  • each heat transfer fin 10 is formed with a plurality of through holes 11a through which the heat transfer tubes 12 pass (only two through holes are shown in FIG. 1).
  • a substantially cylindrical fin collar 11 is formed extending in a plane direction of the heat transfer fin 10 or a direction substantially perpendicular to the flow direction of the airflow 1.
  • the heat transfer tube 12 is inserted into the through hole 11 a while being in close contact with the fin collar 11.
  • all the fin collars 11 extend from the heat transfer fins 10 in the same direction and have substantially the same height.
  • the diameter expansion of the heat transfer tube 12 will be described in detail.
  • the heat transfer fins 10 are stacked and the heat transfer tubes 12 are inserted into the fin collars 11.
  • the inner diameter of the fin collars 11 at the time of fin pressing is set to the heat transfer tubes.
  • the outer diameter is slightly larger than 12.
  • the heat transfer tube 12 is expanded in diameter using a hydraulic pressure or by a mechanical method, and the heat transfer tube 12 and the fin collar 11 are brought into close contact with each other to perform heat transfer performance. Has improved.
  • the heat transfer fin 10 includes a heat exchanger stage direction (a direction in which the heat transfer fins 10 are stacked) that is substantially perpendicular to the flow direction of the airflow 1 to the heat transfer fin 10.
  • the heat transfer fin 10 on the windward side where the gas flows with respect to the cut 13 is raised on the front side (the front side in FIG. 1 and the upper side in FIG. 2), and the cut 13 is formed on the leeward side.
  • a crest 15 having a substantially triangular opening 14 is formed.
  • the cuts 13 are formed so as to penetrate the heat transfer fins 10 and are formed so as to extend in a direction substantially perpendicular to the flow direction of the airflow 1 and along the surface of the heat transfer fins 10.
  • a plurality of crests 15 having openings 14 on the leeward side are formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent in the step direction, and a group of crests (hereinafter referred to as the most crests) provided on the most leeward side.
  • the windward mountain portion 15 a is a contact point between the windward mountain portion windward vertex 15 a 1 that is the highest windward vertex of the contact points between the mountain portion 15 and the heat transfer fin 10, and the opening portion 14 and the heat transfer fin 10. It has a windward mountain top leeward apex (not shown).
  • the second tier mountain portion 15b is the second tier mountain portion upwind vertex 15b1, the second tier mountain portion leeward vertex (not shown), and the leeward mountain portion 15c is the leeward mountain top windward vertex. 15c1 and the leeward side mountain part leeward side vertex 15c2.
  • a sawtooth-shaped first corrugated rib 20 is provided between the windward front edge 10a of the heat transfer fin 10 and the windward mountain portion 15a.
  • the first corrugated ribs 20 are provided in the step direction of the heat exchanger, and are formed by raising the heat transfer fins 10 on the surface (the front side in FIG. 1, the upper side in the figure).
  • the first corrugated rib 20 includes a first rib windward convex portion 20a which is the most windward portion of the sawtooth shape, and first rib leeward convex portions 20b1 and 20b2 which are the most leeward portions. It has.
  • the straight line 21, 25 connecting the first rib leeward convex part 20b2 adjacent to the first rib leeward convex part 20b1 and the leeward mountain top windward vertex 15c1 is substantially parallel to the wind flow.
  • a second corrugated rib 27 similar to the first corrugated rib 20 is also provided between the leeward side front edge 10b of the heat transfer fin 10 and the leeward side peak portion 15c.
  • the height H2 of the first wave-shaped rib 20 and the second wave-shaped rib 27 in the stacking direction of the heat transfer fins 10 is not less than one third and not more than two thirds of the stacking interval H1 of the heat transfer fins 10. It has become.
  • the first corrugated ribs 20 and the second corrugated ribs 27 are not limited to being raised on the front side, and may be raised on the back side or mixed. Also good. A plurality of them may be provided.
  • the strength of the heat transfer fin 10 is particularly affected when the heat transfer fin 10 is pressed, transported after the press process, and L-bending.
  • a fin-like shape is formed by sandwiching a sheet-like metal material (for example, aluminum material) from above and below with a mold, and simultaneously cut into a required size.
  • a sheet-like metal material for example, aluminum material
  • the strength in the direction substantially orthogonal to the longitudinal direction of the heat transfer fin 10 or the wind flow direction is sufficient. Become. Therefore, it is possible to sufficiently reduce the deflection of the heat transfer fin 10 in the surface direction, and it is possible to sufficiently reduce the occurrence of being caught or caught in the press machine when the mold is slid after pressing. As a result, it is possible to eliminate loss of the heat transfer fins 10 and damage to the mold.
  • the heat exchanger fins 10 are laminated, the heat transfer tubes 12 are inserted, the diameter is expanded, and the heat exchanger fins 10 and the heat transfer tubes 12 are brought into close contact with each other, and the entire heat exchanger is pressed into an L-shaped mold.
  • the heat exchanger is bent in an L shape.
  • the strength of the wind flow direction is sufficient. It can be prevented from buckling by the force received in the direction.
  • the straight line 22 or 24 connecting the first rib windward convex portion 20a and the windward mountain portion windward vertex 15a1 is arranged so as to be substantially parallel to the wind flow.
  • the gas divided into right and left by the 1st rib windward convex part 20a toward the flow of a wind can flow smoothly along the slope of the windward mountain part 15a.
  • a vertical vortex is effectively generated, from which the temperature boundary layer on the surface of the heat transfer fin 10 on the leeward side is disturbed to improve the heat transfer coefficient, Excellent heat transfer performance can be obtained while minimizing the increase in loss.
  • the air is sent evenly to the second ridge portion 15b arranged in the heat transfer fin 10, and excellent heat transfer characteristics can be obtained while suppressing an increase in pressure loss, and frost formation in a cold region. Since a state can also be equalized, the capability fall by frost formation can also be suppressed.
  • the vertical vortex generated by the first corrugated rib 20 is concentrated by providing the second-step mountain-side upwind vertex 15b1 at the downstream side of the first rib leeward convex portion 20b1 in the wind flow direction.
  • the resulting flow hits the second-step mountain-side upwind vertex 15b1. Therefore, it is possible to obtain excellent heat transfer characteristics by promoting heat transfer due to the collision with the slope of the second hill portion 15b while minimizing an increase in pressure loss.
  • a leeward mountain top windward vertex 15c1 is provided at a portion downstream of the first rib leeward convex portion 20b2 adjacent to the first rib leeward convex portion 20b1 in the wind flow direction.
  • the height H2 of the first wave-shaped rib 20 or the second wave-shaped rib 27 in the heat transfer tube direction is at least one third of the stacking interval H1 of the stacked heat transfer fins 10. It is less than 2 minutes. Therefore, the resistance of the wind flow can be kept low, and a sufficient heat transfer fin strength and heat transfer acceleration effect can be obtained while suppressing an increase in pressure loss.
  • the shape of the first wave-shaped rib 20 or the second wave-shaped rib 27 is a wave shape, the strength of the heat transfer fin 10 in the wind flow direction is increased. Furthermore, the acute angle ⁇ formed by the corrugated tangent line 26 and the wind flow is set to 45 degrees or more. Therefore, particularly when the heat exchanger is used as an evaporator, the condensed water adhering in a large amount in the vicinity of the windward front edge 10a of the heat transfer fin 10 is quickly dropped and drained without staying in the heat transfer fin 10. Ventilation resistance does not increase abnormally. The same applies to the drainage during the defrosting operation.
  • FIG. 4 is a front view of the heat transfer fin in the second embodiment.
  • a third wave-shaped rib 30 that is a wave-shaped (for example, sine curve) rib having a smooth curve without a straight portion is provided.
  • Straight lines 32, 34 connecting the third rib windward convex portion 30 a that is the most windward portion of the third corrugated rib 30 and the windward mountain top windward vertex 15 a 1, the most of the third corrugated rib 30.
  • Straight lines 31 and 35 connecting the leeward mountain top windward vertex 15c1 are substantially parallel to the wind flow direction.
  • a fourth corrugated rib 37 similar to the third corrugated rib 30 is also provided between the leeward front edge 10 b of the heat transfer fin 10 and the leeward mountain peak portion 15 c.
  • the straight wave portion is not used for the wave shape of the third wave-shaped rib 30 or the fourth wave-shaped rib 37, and a smooth curve (for example, a sine curve) is used.
  • a smooth curve for example, a sine curve
  • FIG. 5 is a front view of the heat transfer fin in the third embodiment.
  • first corrugated ribs 20 a plurality of “dog-shaped” ribs 40, 41 that form an angle with the wind flow are provided.
  • second corrugated ribs 27 a plurality of “shaped” ribs 47 and 48 are provided in the same manner.
  • the “shaped” ribs 40 and 41 adjacent to each other in the longitudinal direction of the heat transfer fin 10 pass through the center of the tangent line connecting the furthest windward portions 40a and 41a of the ribs and are substantially parallel to the wind flow direction. Are arranged symmetrically with respect to the straight line 44. And between the adjacent rib-shaped ribs 40 and 41, the ribless parts 50 and 51 which are not raising the heat-transfer fin 10 are provided.
  • a straight line 43 connecting the furthest windward portion 40a of the dog-shaped rib 40 and the windward mountain top windward vertex 15a1 is substantially parallel to the wind flow direction.
  • An upwind vertex 15b1 is installed.
  • the straight lines 42 and 46 which connected the ribless part 51 and the leeward side mountain part upwind vertex 15c1 are substantially parallel to the flow direction of a wind.
  • Rib-free portions 50 and 51 are provided, and the rib-free portions 50 and 51 are in the vicinity of the most leeward side portions of the “shaped” ribs 40 and 41. Further, since the second ridge portion 15b is installed on the leeward side of the ribless portion 50, the most leeward portions 40a and 41a of the " ⁇ "-shaped "ribs 40 and 41 face the wind flow. Thus, the gas divided into right and left can smoothly pass through the ribless portion 50 and smoothly flow along the slope of the second hill portion 15b.
  • the leeward side mountain portion 15c is installed on the leeward side of the rib-free portion 51, the furthest portions 40a and 41a of the dog-shaped ribs 40 and 41 are divided into left and right toward the wind flow.
  • the generated gas can smoothly pass through the ribless portion 51 and smoothly flow along the slope of the leeward mountain portion 15c. Therefore, when passing through the leeward opening 14 of the leeward mountain portion 15c, a vertical vortex is effectively generated, from which the temperature boundary layer on the surface of the leeward heat transfer fin 10 is disturbed and the heat transfer coefficient is increased. By improving, it is possible to obtain excellent heat transfer performance while minimizing an increase in pressure loss.
  • FIGS. 6 is a front view of the heat transfer fin 10 according to the fourth embodiment
  • FIG. 7 is a bottom view thereof.
  • FIG. 6 similarly to the first embodiment, there is a peak 65a having an opening 64a on the leeward side, a peak 65b having an opening 64b on the leeward side, and a peak 65c having an opening 64c on the leeward side.
  • a plurality of heat transfer fins 10 are formed between the fin collars 11 adjacent to each other in the step direction. These are arranged in the order of the mountain parts 65a, 65b, 65c from the windward side.
  • a fifth corrugated rib 70 is provided between the windward front edge 10a of the heat transfer fin 10 and the peak portion 65a.
  • the fifth corrugated rib 70 includes a fifth rib upwind convex portion that is the most windward portion and a fifth rib leeward convex portion 70b that is the most leeward portion of the fifth corrugated rib 70.
  • Each has a plurality.
  • a straight line 75 connecting the fifth rib leeward convex portion 70b and the midpoint of two adjacent fifth rib leeward convex portions 70a is substantially parallel to the wind flow direction.
  • the mountain portion 65c has a windward vertex 65c1 that is the most windward vertex of the contact points between the mountain portion 65c and the heat transfer fin 10, and a leeward vertex 65c2 that is a contact point between the opening 64c and the heat transfer fin 10. is doing.
  • a sixth corrugated rib 71 is also provided between the leeward front edge 10b of the heat transfer fin 10 and the peak portion 65c.
  • a straight line 66 connecting the leeward apex 65c1 and the leeward apex 65c2 of the mountain portion 65c is the sixth rib upwind convex portion 71a which is the furthest windward part of the sixth corrugated rib 71 and the most leeward part. It is configured to pass between a certain sixth rib leeward convex portion 71b.
  • the fifth rib leeward convex portion 70b and the sixth rib leeward convex portion 71b are arranged on a straight line passing through the center of the heat transfer tube 12 and parallel to the wind flow direction. Moreover, the space
  • the flow of the wind that hits the fifth rib windward convex portion 70a, which is the most windward part of the fifth corrugated rib 70, is divided into right and left in the wind direction. Therefore, a large amount of wind flows into the fifth rib leeward convex portion 70b, which is the most leeward portion of the fifth corrugated rib 70. Since the fifth rib leeward convex portion 70b is in the leeward direction from the middle of the two adjacent fifth rib leeward convex portions 70a, many winds may pass between the mountain portions 65a located on the most leeward side. it can. For this reason, it is possible to improve the fin strength while suppressing an increase in pressure loss.
  • a straight line 66 connecting the windward vertex 65c1 and the leeward vertex 65c2 of the mountain 65c is between the sixth rib windward convex portion 71a and the sixth rib leeward convex portion 71b of the sixth corrugated rib 71. It is configured to pass. Therefore, the gas that has passed through the mountain part 65c on the most leeward side generates a vertical vortex when passing through the opening 64c, thereby disturbing the temperature boundary layer on the surface of the heat transfer fin 10 on the leeward side and increasing the heat transfer coefficient. While improving, since it can flow smoothly along the wave fin on the leeward side, excellent heat transfer characteristics can be exhibited while suppressing an increase in pressure loss.
  • the angle formed by the tangent line of the corrugation of the fifth corrugated rib and the wind flow direction is gentler in the portion located on the windward side of the mountain portion 65a than in the portion located on the windward side of the heat transfer tube 12. Excellent heat transfer characteristics can be achieved while suppressing an increase in pressure loss.
  • the angle formed by the corrugated tangent of the sixth corrugated rib and the wind flow direction is gentler in the portion located on the leeward side of the peak portion 65c than in the portion located on the leeward side of the heat transfer tube 12. Excellent heat transfer characteristics can be achieved while suppressing an increase in pressure loss.
  • the second step mountain portion 15b is provided between the windward mountain portion 15a and the leeward mountain portion 15c.
  • a plurality of mountain groups may be provided.
  • the finned tube heat exchanger according to the present invention provides a corrugated rib having a shape suitable for the shape of the peak portion while forming a peak portion having an opening on the leeward side to improve heat exchange efficiency.
  • a heat exchanger used in air conditioners, heat pump water heaters, refrigerators, freezers, etc. it can increase the strength of the fins in all directions while suppressing an increase in pressure loss, and solve manufacturing problems. Useful.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur à tube à ailettes dans lequel une partie nervurée comprenant une ouverture sur le côté de vent arrière de celle-ci est formée. Ledit échangeur de chaleur est également doté d'une première nervure ondulée (20) en amont de la partie nervurée susmentionnée (15), qui correspond à la forme de ladite partie nervurée (15). Le présent échangeur de chaleur présente une excellente efficacité de transfert de chaleur tout en présentant une solidité d'ailettes suffisante, ce qui permet de réduire les coûts de fabrication et d'expédition. En outre, les augmentations des pertes de compression du côté exposé à l'air pendant le fonctionnement sont réduites à un minimum.
PCT/JP2012/000521 2011-01-27 2012-01-27 Échangeur de chaleur à tube à ailettes WO2012102053A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2012554699A JPWO2012102053A1 (ja) 2011-01-27 2012-01-27 フィンチューブ型熱交換器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-014954 2011-01-27
JP2011014954 2011-01-27

Publications (1)

Publication Number Publication Date
WO2012102053A1 true WO2012102053A1 (fr) 2012-08-02

Family

ID=46580627

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/000521 WO2012102053A1 (fr) 2011-01-27 2012-01-27 Échangeur de chaleur à tube à ailettes

Country Status (2)

Country Link
JP (1) JPWO2012102053A1 (fr)
WO (1) WO2012102053A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014016107A (ja) * 2012-07-09 2014-01-30 Mitsubishi Electric Corp フィンアンドチューブ型熱交換器及びこれを備えた空気調和機
EP2784426A1 (fr) * 2013-03-27 2014-10-01 GEA Batignolles Technologies Thermiques Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées
CN105806125A (zh) * 2016-05-26 2016-07-27 珠海格力电器股份有限公司 翅片和空调换热器
WO2021020592A1 (fr) * 2019-07-26 2021-02-04 株式会社アタゴ製作所 Élément de promotion d'échange de chaleur et échangeur de chaleur
CN113834129A (zh) * 2020-06-08 2021-12-24 青岛海信日立空调系统有限公司 一种空调器
WO2023190378A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Échangeur de chaleur et unité intérieure

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0448192A (ja) * 1990-06-18 1992-02-18 Toshiba Corp 熱交換器のフィン形状
JPH0534470U (ja) * 1991-10-07 1993-05-07 東洋ラジエーター株式会社 空調用熱交換器のプレートフイン
JPH08170890A (ja) * 1994-12-16 1996-07-02 Daikin Ind Ltd クロスフィン熱交換器
JP2006138503A (ja) * 2004-11-10 2006-06-01 Denso Corp 熱交換器
JP2008215737A (ja) * 2007-03-06 2008-09-18 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル
JP2010008034A (ja) * 2008-05-26 2010-01-14 Panasonic Corp フィンチューブ型熱交換器
JP2010210188A (ja) * 2009-03-11 2010-09-24 Panasonic Corp フィンチューブ熱交換器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0448192A (ja) * 1990-06-18 1992-02-18 Toshiba Corp 熱交換器のフィン形状
JPH0534470U (ja) * 1991-10-07 1993-05-07 東洋ラジエーター株式会社 空調用熱交換器のプレートフイン
JPH08170890A (ja) * 1994-12-16 1996-07-02 Daikin Ind Ltd クロスフィン熱交換器
JP2006138503A (ja) * 2004-11-10 2006-06-01 Denso Corp 熱交換器
JP2008215737A (ja) * 2007-03-06 2008-09-18 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル
JP2010008034A (ja) * 2008-05-26 2010-01-14 Panasonic Corp フィンチューブ型熱交換器
JP2010210188A (ja) * 2009-03-11 2010-09-24 Panasonic Corp フィンチューブ熱交換器

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014016107A (ja) * 2012-07-09 2014-01-30 Mitsubishi Electric Corp フィンアンドチューブ型熱交換器及びこれを備えた空気調和機
EP2784426A1 (fr) * 2013-03-27 2014-10-01 GEA Batignolles Technologies Thermiques Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées
WO2014154398A1 (fr) * 2013-03-27 2014-10-02 Gea Batignolles Technologies Thermiques Échangeur de chaleur à tubes avec caractéristiques thermohydrauliques optimisées
CN105806125A (zh) * 2016-05-26 2016-07-27 珠海格力电器股份有限公司 翅片和空调换热器
WO2021020592A1 (fr) * 2019-07-26 2021-02-04 株式会社アタゴ製作所 Élément de promotion d'échange de chaleur et échangeur de chaleur
CN114556041A (zh) * 2019-07-26 2022-05-27 株式会社爱拓制作所 热交换促进部件以及热交换器
CN114556041B (zh) * 2019-07-26 2024-06-25 株式会社爱拓制作所 热交换促进部件以及热交换器
CN113834129A (zh) * 2020-06-08 2021-12-24 青岛海信日立空调系统有限公司 一种空调器
CN113834129B (zh) * 2020-06-08 2022-11-29 青岛海信日立空调系统有限公司 一种空调器
WO2023190378A1 (fr) * 2022-03-31 2023-10-05 ダイキン工業株式会社 Échangeur de chaleur et unité intérieure
JP2023149884A (ja) * 2022-03-31 2023-10-16 ダイキン工業株式会社 熱交換器及び室内機
JP7401802B2 (ja) 2022-03-31 2023-12-20 ダイキン工業株式会社 熱交換器及び室内機

Also Published As

Publication number Publication date
JPWO2012102053A1 (ja) 2014-06-30

Similar Documents

Publication Publication Date Title
CN104285119B (zh) 换热器及空气调节机
US9671177B2 (en) Heat exchanger, method for fabricating heat exchanger, and air-conditioning apparatus
WO2012102053A1 (fr) Échangeur de chaleur à tube à ailettes
EP2236972B1 (fr) Ailette pour échangeur thermique et échangeur thermique utilisant l'ailette
WO2009153985A1 (fr) Échangeur de chaleur
JP4775429B2 (ja) フィンチューブ型熱交換器
US20110036550A1 (en) Fin and heat exchanger having the same
US20090308585A1 (en) Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby
JP5523495B2 (ja) フィンチューブ型熱交換器及び冷凍サイクル装置
WO2013001744A1 (fr) Échangeur de chaleur à tubes à ailettes
EP2699867B1 (fr) Échangeur de chaleur
JP5608478B2 (ja) 熱交換器及びそれを用いた空気調和機
EP1832832A1 (fr) Échangeur de chaleur
JPH08247678A (ja) アルミニウム製熱交換器
JP5020886B2 (ja) 熱交換器
JP5138408B2 (ja) フィン・アンド・チューブ式熱交換器
CN107990598B (zh) 微通道换热器
JP2009121708A (ja) 熱交換器
JP2008215670A (ja) 伝熱フィン、フィンチューブ型熱交換器および冷凍サイクル装置
JP5084304B2 (ja) フィンチューブ型熱交換器及び冷凍サイクル
JP5958917B2 (ja) フィンチューブ型熱交換器
JP2015014397A (ja) 熱交換器
JP2009204278A (ja) 熱交換器
JP2015001307A (ja) フィンチューブ熱交換器
JP5815128B2 (ja) 熱交換器、及び空気調和機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12739493

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2012554699

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12739493

Country of ref document: EP

Kind code of ref document: A1