EP2778593B1 - Fin-tube heat exchanger - Google Patents

Fin-tube heat exchanger Download PDF

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Publication number
EP2778593B1
EP2778593B1 EP12848344.3A EP12848344A EP2778593B1 EP 2778593 B1 EP2778593 B1 EP 2778593B1 EP 12848344 A EP12848344 A EP 12848344A EP 2778593 B1 EP2778593 B1 EP 2778593B1
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EP
European Patent Office
Prior art keywords
heat transfer
fin
heat exchanger
tube
protruding
Prior art date
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Active
Application number
EP12848344.3A
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German (de)
English (en)
French (fr)
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EP2778593A4 (en
EP2778593A1 (en
Inventor
Atsunori Hashimoto
Kazuhiro Taniguchi
Shoichi Yokoyama
Michihito OZAKI
Kaoru Hosokawa
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Panasonic Corp
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Panasonic Corp
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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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the present invention relates to a fin-tube heat exchanger and a heat pump device including the fin-tube heat exchanger.
  • the present invention also relates to a heat transfer fin suitable for use in a fin-tube heat exchanger.
  • heat exchangers serving as evaporators or condensers are used in air conditioning units such as household air conditioners, automobile air conditioners, and industrial packaged air conditioners, and heat pump devices such as refrigerators and heat pump water heaters.
  • air conditioning units such as household air conditioners, automobile air conditioners, and industrial packaged air conditioners
  • heat pump devices such as refrigerators and heat pump water heaters.
  • fin-tube heat exchangers are most commonly used.
  • FIG. 13 is a partial cross-sectional view of a fin-tube heat exchanger 100 used in a household air conditioner, an industrial packaged air conditioner, or the like.
  • This heat exchanger 100 includes a stack of heat transfer fins 120 and a heat transfer tube 110 penetrating the stack of heat transfer fins 120.
  • Each of the heat transfer fins 120 has a cylindrical collar portion 123 (having a uniform cross-sectional shape) extending upwardly from a base portion 121.
  • a bottom portion 122 and a flared portion 124 extend radially outwardly in a curved manner from the bottom of the collar portion 123 and the upper end thereof, respectively.
  • the flared portion 124 is in contact with the flat portion 121 of the adjacent heat transfer fin 120 in the vicinity of the bottom portion 122.
  • the heat transfer tube 110 having an outer diameter smaller than the inner diameter of the collar portion 123 is inserted into the collar portions 123 through the stack of the heat transfer fins 120, and then the heat transfer tube 110 is expanded. Thus, the heat transfer tube 110 is brought into close contact with the collar portions 123.
  • gaps 130 are formed between the flared portions 124 and the adjacent bottom portions 122. Since the portions of the heat transfer tube 110 corresponding to these gaps 130 are not in contact with the heat transfer fins 120, the performance of heat transfer from the heat transfer tube 110 to the heat transfer fins 120 cannot be improved by conventional, commonly used mechanical tube expansion techniques.
  • Patent Literature 1 has proposed a method for improving the performance of heat transfer from the heat transfer tube 110 to the heat transfer fins 120.
  • a filler such as a silicone resin is put into the gaps 130 and cured so as to fill the gaps 130.
  • Patent Literature 2 forming the closest prior art from which the present invention starts, discloses a fin for a hat exchanger, which consists essentially of a matrix of tubes and of fins disposed transversely to the latter.
  • the fin has pass-through elements to receive tubes, which are to be joint mechanically, while a first liquid medium flows through the tubes and the fin is acted on by a second gaseous medium.
  • Multiple fins are positioned in their fin pitch by integral spaces, wherein the spaces are in the form of noses stamped out of the pass-through elements and distributed over the periphery of the latter.
  • Patent Literature 1 since the method proposed in Patent Literature 1 requires a step of putting the filler in addition to the conventionally required common steps, improvements in the production process are needed, resulting in a significant increase in man hours.
  • the heat exchanger when the heat exchanger is discarded, not only metals commonly used for the heat transfer fins 120 and the heat transfer tube 110 but also the filler, a different type of material, must be disposed of. Therefore, it is difficult to separate the materials from one another. As a result, the recycling efficiency is reduced and the environmental impact is increased.
  • a fin-tube heat exchanger as defined in independent claim 1 attached.
  • the present disclosure provides a heat transfer fin including: a base portion; a cylindrical collar portion extending upwardly from the base portion; a protruding portion protruding radially outwardly from a part of an upper end of the collar portion; and a wall portion extending upwardly from a part of the upper end of the collar portion other than the part of the upper end from which the protruding portion protrudes, wherein a height from the base portion to a top of the wall portion is greater than a height from the base portion to a top of the protruding portion.
  • the present disclosure can provide a heat transfer fin suitable for use in a fin-tube heat exchanger.
  • a first aspect of the present disclosure provides a fin-tube heat exchanger as defined in independent claim 1 attached, wherein the fin-tube heat exchanger comprises a stack of heat transfer fins and a heat transfer tube penetrating the stack of heat transfer fins.
  • each of the heat transfer fins comprises a base portion; a cylindrical collar portion extending upwardly from the base portion; a protruding portion protruding radially outwardly from a part of an upper end of the collar portion; and a wall portion extending upwardly from a part of the upper end of the collar portion other than the part of the upper end from which the protruding portion protrudes, wherein a height from the base portion to a top of the wall portion is greater than a height from the base portion to a top of the protruding portion.
  • the protruding portions serve to support the adjacent heat transfer fins when they are stacked.
  • a part of the upper end of each collar portion other than the part of the upper end on which the protruding portion is provided, that is, the wall portion comes into contact with the heat transfer tube. Therefore, it is possible to ensure a larger contact area between each heat transfer fin and the heat transfer tube, and accordingly it is possible to reduce the gap between the adjacent heat transfer fins as much as possible. Therefore, it is possible to reduce the gap between the adjacent heat transfer fins as much as possible as a whole, with the adjacent heat transfer fins being stably stacked.
  • the adjacent heat transfer fins are brought into contact with each other when they are stacked. Therefore, the heat transfer fins in the stack are integrated into a single unit and the performance of heat transfer of the entire stack is improved. As a result, heat of a fluid flowing in the heat transfer tube can be transferred more efficiently
  • the adjacent heat transfer fins in the stack may not be in complete contact with each other, but the heat transfer fins in the stack are integrated into a single unit and the performance of heat transfer of the entire stack is improved.
  • a second aspect of the present disclosure provides the fin-tube heat exchanger according to the first aspect, wherein the number of the protruding portions provided is at least two. According to this configuration, it is possible to stack the adjacent heat transfer fins stably while reducing the number of the protruding portions. As the number of the protruding portions is reduced, the contact area between the heat transfer fin and the heat transfer tube can be increased accordingly.
  • a third aspect of the present disclosure provides the fin-tube heat exchanger according to the second aspect, wherein one of the at least two protruding portions extends in a specific direction, and another of the at least two protruding portions extends in a direction opposite to the specific direction. According to this configuration, it is possible to ensure sufficiently stable stacking of the heat transfer fins even if the number of the protruding portions is two.
  • a fourth aspect of the present disclosure provides the fin-tube heat exchanger according to the third aspect, wherein the specific direction is perpendicular to a longitudinal direction of the heat transfer fin. According to this configuration, it is possible to ensure sufficiently stable stacking of the heat transfer fins even if the number of the protruding portions is two.
  • a fifth aspect of the present disclosure provides the fin-tube heat exchanger according to the third aspect, wherein the specific direction is within an angular range of ⁇ 30 degrees with respect to a straight line extending in a transverse direction perpendicular to a longitudinal direction of the heat transfer fin from a center of the collar portion. According to this configuration, it is possible to ensure sufficiently stable stacking of the heat transfer fins even if the number of the protruding portions is two.
  • a sixth aspect of the present disclosure provides the fin-tube heat exchanger according to any one of the first to fifth aspects, wherein the protruding portion is bent radially outwardly with distance from the upper end of the collar portion.
  • a stepped portion is provided that is curved and extends from the bottom portion down to the base portion to form a recess. According to this configuration, when the heat transfer fins are stacked, each stepped portion forms a recess into which the protruding portion of the adjacent heat transfer fin enters. Thereby, when the heat transfer fins are stacked during the production of the heat exchanger, even if the lower heat transfer fin is loaded by the weight of the upper heat transfer fin in the stack and the protruding portion of the lower heat transfer fin is deformed radially outwardly from the collar portion, the range in which the protruding portion is deformed is limited by the recess formed by the stepped portion.
  • the present disclosure provides a fin-tube heat exchanger wherein the wall portion of one of the heat transfer fins in the stack enters a space beneath a bottom of the collar portion of another heat transfer fin that is stacked on the one heat transfer fin. According to this configuration, it is possible to reduce the gap formed between one of the heat transfer fins in the stack and another heat transfer fin that is stacked on the one heat transfer fin as much as possible. Thereby, it is possible to increase the heat transfer area and thus enhance the heat exchange efficiency.
  • FIG. 1 shows a fin-tube heat exchanger 1 according to the first embodiment of the present invention.
  • This heat exchanger 1 includes a stack of heat transfer fins 3A, a pair of side plates 20 disposed on both sides of the stack of transfer fins 3A, and a plurality of U-shaped heat transfer tubes 2 penetrating the heat transfer fins 3A and the side plates 20.
  • Each of the heat transfer fins 3A extends in a specific direction, and the straight portions of the heat transfer tubes 2 are arranged at a constant pitch in the longitudinal direction of the heat transfer fins 3A.
  • the straight portions of each heat transfer tube 2 are connected by a bent portion on the side of one of the side plates 20, and both ends of the heat transfer tube 2 protrude from the other side plate 20, and one end of the heat transfer tube 2 and one end of the adjacent heat transfer tubes 2 are connected by a bent pipe 21.
  • Each of the heat transfer tubes 2 is made of a metal such as copper having a high thermal conductivity
  • Each of the heat transfer fins 3A has a plate shape obtained by press-forming a thin aluminum plate, and is rectangular in plane view.
  • the shape of the heat transfer fins 3A is not particularly limited as long as they have a shape extending in the specific direction. For example, it may be a polygonal shape extended in the specific direction, such as a rhombus or a trapezoid, or may be an elliptical shape.
  • each of the heat transfer fins 3A includes a base portion 4 spreading around the straight portion of the heat transfer tube 2 and a cylindrical collar portion 5 extending upwardly from the base portion 4 along the straight portion of the heat transfer tube 2.
  • the direction in which the collar portion 5 extends is referred to as an upward direction and the direction opposite to the upward direction is referred to as a downward direction.
  • the collar portion 5 forms an insertion hole into which the heat transfer tube 2 is to be inserted.
  • the heat transfer tube 2 has an initial outer diameter smaller than the inner diameter of the collar portion 5. After the heat transfer fins 3A are stacked so that their insertion holes coincide with each other, the heat transfer tube 2 is inserted through the insertion holes. That is, a clearance is provided between the initial heat transfer tube 2 and the collar portions 5 so as to facilitate the insertion of the heat transfer tube 2. Then, the heat transfer tube 2 is expanded by a mechanical tube expanding technique in which a tube expanding billet is inserted into the heat transfer tube 2. Thereby, the heat transfer tube 2 comes into contact with the collar portions 5, and the collar portions 5 are coaxially fixed together.
  • the collar portion 5 is provided with, on its lower end, a bottom portion 55 that is curved and extends radially outwardly from the bottom of the collar portion 5 down to the base portion 4.
  • a plurality of protruding portions 51 and a plurality of wall portions 52 are alternately arranged in the circumferential direction.
  • the number of the protruding portions 51 is equal to the number of the wall portions 52.
  • the base portion 4 may be flat, but in the present embodiment, it has a corrugated shape having folds parallel to the longitudinal direction of the heat transfer fins 3A.
  • the folds of the corrugated shape need not necessarily be parallel to the longitudinal direction of the heat transfer fins 3A. They may be inclined with respect to the longitudinal direction.
  • the base portion 4 includes a corrugated portion 41 having ridges and grooves, a flat ring portion 43 surrounding the heat transfer tube 2 at the same level as the grooves of the corrugated portion 41, and a peripheral wall portion 42 extending in a tapered manner from the outer edge of the ring portion 43 to the ridges of the corrugated portion 41.
  • the above-mentioned bottom portion 55 extends down to the inner edge of the ring portion 43.
  • each of the protruding portion 51 protrudes radially outwardly from a part of the upper end of the collar portion 5.
  • the wall portion 52 extends upwardly from a part of the upper end of the collar portion 5 other than the part of the upper end from which the protruding portion 51 protrudes.
  • the wall portion 52 is formed by extending the collar portion 5 to a region between the protruding portions 51.
  • the protruding portion 51 of one heat transfer fin 3A is in contact with the ring portion 43 of the adjacent heat transfer fin 3A in the vicinity of the bottom portion 55.
  • a stepped portion that is curved and extends from the bottom of the collar portion 5 down to the base portion 4 to form a recess is provided.
  • the ring portion 43 is provided with the stepped portion 6 so as to form a recess, into which the protruding portions 51 can be fitted, around the bottom portion 55. That is, the stepped portion 6 has an inner diameter larger than the diameter of a circle circumscribing the protruding portions 51.
  • the cross-sectional shape of the stepped portion 6 may be a straight line parallel or oblique to the axial direction of the collar portion 5, or may be a curved line.
  • the protruding portions 51 serve to support the adjacent heat transfer fins 3A when they are stacked. Therefore, it is desirable that the heights from the ring portion 43 to the tops of all the protruding portions 51 be equal. Furthermore, it is preferable that the protruding portions 51 be arranged at regular angular intervals in the circumferential direction.
  • the number of the protruding portions 51 is not particularly limited, but it is desirable that at least two protruding portions 51 be provided. From the viewpoint of the stability of the stack of the heat transfer fins 3A in the transverse direction perpendicular to the longitudinal direction of the heat transfer fins 3A (the heat transfer fins 3A are supported more stably by two or more protruding portions 51 in the longitudinal direction), it is preferable that at least two protruding portions 51 be respectively disposed in two separate regions within a specific angular range spreading in the transverse direction of the heat transfer fin 3A from the center of the collar portion 5 (for example, in two separate regions within an angular range of ⁇ 30 degrees with respect to a straight line extending in the transverse direction).
  • three protruding portions 51 may be disposed in such a manner that one of them is disposed in one region within the angular range and the other two are disposed in the other region within the angular range and that the center lines of these three protruding portions 51 form a Y-shaped configuration in plane view (as viewed from the axial direction of the collar portion 5).
  • two protruding portions 51 may be respectively disposed in two separate regions within the specific angular range, that is, at two separate positions deviated from a straight line passing through the center of the collar portion 5 and extending in the transverse direction.
  • the best configuration is that only two protruding portions 51 protruding in the opposite directions along the transverse direction of the heat transfer fin 3A are provided.
  • one of these two protruding portions 51 extends in a specific direction.
  • the other one of the two protruding portions 51 extends in a direction opposite to the specific direction.
  • the specific direction is a direction (transverse direction) perpendicular to the longitudinal direction of the heat transfer fin 3A.
  • each protruding portion 51 is bent radially outwardly with distance from the upper end of the collar portion 5 and finally bent at 90 degrees with respect to the collar portion 5.
  • the protruding portion 51 need not necessarily be curved.
  • the protruding portion 51 may be formed of a linear gradient portion extending obliquely upward from the collar portion 5 and a flange portion provided on the upper end of the linear gradient portion. The bending angle also is not limited to 90 degrees.
  • each protruding portion 51 is smaller than the circumferential width of each protruding portion 51.
  • the circumferential width of each protruding portion 51 is about one twelfth to one fifth the perimeter of the collar portion 5.
  • each protruding portion 51 has sharp corners and its plane view is a circular arc shape with a certain width.
  • the corners of the protruding portion 51 may be rounded, as shown in FIG. 7 , to prevent the sharp corners from damaging something when the heat transfer fins 3A are stacked.
  • the protruding portion 51 may have a crescent shape in plane view.
  • the wall portions 52 come into contact with the heat transfer tube 2, although they do not serve to support the adjacent heat transfer fins 3A.
  • the inner diameter of a circle connecting the wall portions 52 is equal to the inner diameter of the collar portion 5, and the wall portions 52 and the collar portion 5 form a continuous wall surface.
  • a gap 7 is formed between the protruding portion 51 and the bottom portion 55 of the upper heat transfer fin 3A, as shown in FIG. 4A , but a much smaller gap is formed between the wall portion 52 and the bottom portion 55 of the upper heat transfer fin 3A, as shown in FIG. 4B .
  • the height B from the ring portion 43 (base portion 4) to the top of the wall portion 52 is greater than the height A from the ring portion 43 (base portion 4) to the top of the protruding portion 51. That is, the top of the wall portion 52 is located higher than the top of the protruding portion 51 by the difference ⁇ h between the height B from the ring portion 43 (base portion 4) to the top of the wall portion 52 and the height A from the ring portion 43 (base portion 4) to the top of the protruding portion 51.
  • the heat transfer area increases and thus the heat exchange efficiency improves. If the height B from the ring portion 43 (base portion 4) to the top of the wall portion 52 is smaller than the height A from the ring portion 43 (base portion 4) to the top of the protruding portion 51, the lateral surface of the heat transfer tube 2 is exposed between the adjacent heat transfer fins 3A when the heat transfer fins 3A are stacked. This is an undesirable tendency in terms of the heat transfer efficiency.
  • the wall portions 52 are formed on the upper end of the collar portion 5, the adjacent heat transfer fins 3A are brought into contact with each other when they are stacked. Therefore, the heat transfer fins 3A in the stack are integrated into a single unit and the performance of heat transfer of the entire stack is improved. As a result, heat of a fluid flowing in the heat transfer tube 2 can be transferred more efficiently.
  • the wall portion 52 of one of the heat transfer fins 3A in the stack may be in contact with the back side of the bottom of the collar portion 5 of another heat transfer fin 3A that is stacked on the one heat transfer fin 3A.
  • the wall portion 52 of one of the heat transfer fins 3A in the stack need not be in contact with the back side of the bottom of the collar portion 5 of another heat transfer fin 3A that is stacked on the one heat transfer fin 3A.
  • some of the wall portions 52 may be in contact with the back sides of the bottoms of the collar portions 52, and the other wall portions 52 may not be in contact with the back sides of the bottoms of the collar portions 52.
  • the wall portion 52 is more likely to come into contact with the back side of the bottom of the adjacent collar portion 5 by the weight thereof.
  • the wall portion 52 may not come into contact with the back side of the bottom of the adjacent collar portion 5.
  • the stacked heat transfer fins 3A are integrated into a single unit and the performance of heat transfer of the entire stack is improved.
  • the protruding portion 51 of one of the heat transfer fins 3A in the stack enters the recess formed by the stepped portion 6 of another heat transfer fin 3A that is stacked on the one heat transfer fin 3A.
  • the wall portion 52 of one of the heat transfer fins 3A in the stack enters the space beneath the bottom of the collar portion 5 of another heat transfer fin 3A that is stacked on the one heat transfer fin 3A.
  • the height B from the base portion 4 to the top of the wall portion 52 need only be greater than the height A from the base portion 4 to the top of the protruding portion 51.
  • a thin linear slit is provided between the protruding portion 51 and the wall portion 52.
  • a notch 53 an example of a notched portion having an arc-shaped bottom with a certain width and smoothly connecting the protruding portion 51 and the wall portion 52, as shown in FIG. 8 .
  • the heat of a fluid flowing in the heat transfer tube 110 is transferred from the outer peripheral surface of the heat transfer tube 110 to the inner peripheral surface of the collar portion 123, and then is conducted to the outer peripheral surface of the collar portion 123 and the upper surface and the lower surface of the base portion 121.
  • the heat thus conducted to the outer peripheral surface of the collar portion 123 and the upper surface and the lower surface of the base portion 121 is transferred to a fluid that is to flow between the base portions 121.
  • K the thermal contact conductance (W/m 2 ⁇ K)
  • ⁇ 1 is the surface roughness ( ⁇ m) of one of two members in contact at the interface
  • ⁇ 2 is the surface roughness ( ⁇ m) of the other one of the members in contact at the interface
  • ⁇ 1 is the thermal conductivity (W/m ⁇ K) of the one of the members in contact at the interface
  • ⁇ 2 is the thermal conductivity (W/m ⁇ K) of the other one of the members in contact at the interface
  • P is the contact pressure (MPa)
  • H is the hardness (Hb) of a softer one of
  • the thermal contact resistance Rc is calculated from the following equation 2 using the thermal contact conductance K obtained by the above equation 1.
  • Rc 1 / K ⁇ S
  • Rc is the thermal contact resistance (K/W) and S is the contact area (m 2 ).
  • the materials of the heat exchanger 100 include not only the materials of the heat transfer fins 120 and the heat transfer tube 110 but also the filler as a different type of material. Therefore, it is difficult to separate the materials from one another for recycling when the product is discarded. As a result, the recycling efficiency decreases, which leads to a decrease in the recycling rate, an increase in the energy required for recycling, etc., and consequently in an increase in the environmental impact.
  • thermal contact conductance K there are many other ways to increase the thermal contact conductance K.
  • a method of reducing the surface roughnesses ⁇ 1 and ⁇ 2 of the surfaces of the heat transfer tube 110 and the collar portion 123 in contact a method of increasing the contact pressure P, a method of increasing the thermal conductivities ⁇ 1 and ⁇ 2 of the heat transfer tube 110 and the heat transfer fin 120, and a method of reducing the hardness H of the softer one of the heat transfer tube 110 and the heat transfer fin 120.
  • the present invention focuses on the method of increasing the contact area S.
  • An increase in the contact area between the heat transfer tube 110 and the heat transfer fin 120 makes it possible to reduce the thermal contact resistance Rc without changing the thermal contact conductance K, and thus to improve the performance of heat transfer from the heat transfer tube 110 to the heat transfer fin 120.
  • the heat exchanger 1 of the present embodiment not only the collar portions 5 but also the wall portions 52 between the protruding portions 51 come into contact with the heat transfer tube 2. Therefore, the performance of heat transfer from the heat transfer tube 2 to the heat transfer fins 3A can be improved more than in conventional heat exchangers. Thereby, the heat exchange efficiency of the heat exchanger 1 can be improved.
  • the heat exchanger 1 does not require a filler. Therefore, it is easy to separate the materials from one another when the heat exchanger is discarded, and the recycling efficiency does not decrease.
  • a refrigerant circuit 10C is configured to pass through both an indoor unit 10A and an outdoor unit 10B.
  • a compressor 11 for example, a rotary compressor
  • a four-way valve 12 for example, an outdoor heat exchanger 13
  • a throttling device 14 for example, an expansion valve
  • An indoor heat exchanger 15 is disposed in the indoor unit 10A.
  • the outdoor unit 10B is provided with an outdoor fan 16 (for example, a propeller fan) for supplying outdoor air to the outdoor heat exchanger 13
  • the indoor unit 10A is provided with an indoor fan 17 (for example, a cross flow fan) for supplying indoor air to the indoor heat exchanger 15.
  • a high-temperature and high-pressure refrigerant compressed by the compressor 11 is directed through the four-way valve 12 to the indoor heat exchanger 15 in heating operation and to the outdoor heat exchanger 13 in cooling operation.
  • the indoor heat exchanger 15 serves as a condenser, into which the high-temperature refrigerant is introduced through the four-way valve 12.
  • the indoor heat exchanger 15 allows the high-temperature refrigerant introduced thereinto to transfer its heat to the indoor air supplied by the indoor fan 17 through heat exchange between the refrigerant and the air so as to condense and liquefy the refrigerant.
  • the liquefied refrigerant is adiabatically expanded by the throttling device 14, and the resulting low-temperature and low-pressure refrigerant is supplied to the outdoor heat exchanger 13.
  • the outdoor heat exchanger 13 serves as an evaporator, and allows the vapor-liquid two-phase low-temperature refrigerant to absorb the heat of the outdoor air supplied by the outdoor fan 16 through heat exchange between the refrigerant and the air so as to evaporate and vaporize the refrigerant.
  • the evaporated low-pressure vapor refrigerant is again compressed by the compressor 11.
  • the indoor air is heated by repeating this cycle continuously Thus, the room is heated.
  • the refrigerant is caused to flow in the reverse direction by switching the four-way valve 12 so as to cool the indoor air.
  • the room is cooled. That is, in both the heating operation and the cooling operation, the refrigerant circulating in the refrigerant circuit 10C passes through the compressor 11, the condenser, the throttling device 14, and the evaporator in this order.
  • the heat exchanger 1 of the present embodiment When the heat exchanger 1 of the present embodiment is used as at least one of the condenser and the evaporator in the room air conditioner 10 as described above or any other heat pump device, the heat exchange efficiency of the condenser and/or the evaporator can be improved. As a result, the COP (coefficient of performance) of the heat pump device can be improved.
  • FIG. 9 a fin-tube heat exchanger is described with reference to FIG. 9 .
  • the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof may be omitted. This also applies to the third embodiment described later.
  • a heat transfer fin 3B having a shape shown in FIG. 9 is used.
  • This heat transfer fin 3B has the same configuration as the heat transfer fin 3A used in the first embodiment, except for the shape of the protruding portions 51.
  • the height from the base portion 4 to the top of the wall portion 52 is greater than the height from the base portion 4 to the top of the protruding portion 51.
  • each protruding portion 51 is formed continuously from the wall portions 52 on both sides thereof, and has a shape in which the circumferential center thereof is gradually raised with distance from the upper end of the collar portion 5.
  • each protruding portion 51 has a spout-like shape with a pointed arch-shaped cross section (such as a bird's beak-shaped or V-shaped cross section).
  • the protruding portions 51 serve to support the adjacent heat transfer fins 3B. Therefore, the protruding portions 51 need to support the weight of all the upper located heat transfer fins 3B.
  • the spout-like protruding portions 51 of the present embodiment can have a higher section modulus. Therefore, the strength of the protruding portions 51 themselves can be increased.
  • the wall portions 52 have the same effect as in the first embodiment.
  • the protruding portion 51 has a pointed arch-shaped cross section with a sharp corner at the center thereof, but the center of the protruding portion 51 may be smoothly curved as shown in FIG. 10 to prevent the sharp corner from damaging something when the heat transfer fins 3B are stacked.
  • a fin-tube heat exchanger is described with reference to FIG. 11 .
  • a heat transfer fin 3C having a shape shown in FIG. 11 is used.
  • This heat transfer fin 3C has the same configuration as the heat transfer fin 3A used in the first embodiment, except for the shape of the protruding portions 51.
  • the height from the base portion 4 to the top of the wall portion 52 is greater than the height from the base portion 4 to the top of the protruding portion 51.
  • each protruding portion 51 is a protrusion provided on the outer peripheral surface of a continuous cylindrical body including the collar portion 5 and the wall portion 52.
  • the protrusion has a linear tab-like shape extending in the axial direction of the collar portion 5. This configuration also produces the same effects as in the first embodiment.
  • the fin-tube heat exchanger of the present invention is applicable to heat pump devices for use in air conditioning units such as household air conditioners, automobile air conditioners, and industrial packaged air conditioners, refrigerators, heat pump water heaters, etc.

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  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP12848344.3A 2011-11-10 2012-11-09 Fin-tube heat exchanger Active EP2778593B1 (en)

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JP2011246711 2011-11-10
PCT/JP2012/007197 WO2013069299A1 (ja) 2011-11-10 2012-11-09 伝熱フィン、フィンチューブ型熱交換器及びヒートポンプ装置

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EP2778593A1 EP2778593A1 (en) 2014-09-17
EP2778593A4 EP2778593A4 (en) 2014-10-15
EP2778593B1 true EP2778593B1 (en) 2017-05-10

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EP2778593B1 (en) * 2011-11-10 2017-05-10 Panasonic Corporation Fin-tube heat exchanger
US20160079639A1 (en) * 2014-09-15 2016-03-17 James O. Pinon Cooling fin for a battery cell
JP6548729B2 (ja) * 2015-07-10 2019-07-24 三菱電機株式会社 熱交換器および空気調和装置
JP6831206B2 (ja) * 2016-10-20 2021-02-17 リンナイ株式会社 フィンチューブ型熱交換器及びこの熱交換器を備える燃焼装置
WO2018139162A1 (ja) * 2017-01-24 2018-08-02 三菱電機株式会社 熱交換器
JP2019052829A (ja) 2017-09-19 2019-04-04 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 熱交換器及び空気調和機

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JPS5624869Y2 (ja) * 1976-07-21 1981-06-11
JPS56162486U (ja) * 1980-04-29 1981-12-03
JPS5761377U (ja) * 1980-09-25 1982-04-12
JPS58127092A (ja) * 1982-01-25 1983-07-28 Nippon Denso Co Ltd 熱交換器及びその製法
JPS6071880U (ja) * 1983-10-18 1985-05-21 宇野金属工業株式会社 放熱板
JPH0482570U (ja) * 1990-11-20 1992-07-17
JPH04198691A (ja) * 1990-11-29 1992-07-20 Toshiba Corp 熱交換器
JPH05141889A (ja) * 1991-11-22 1993-06-08 Rinnai Corp 熱交換器
DE4404837A1 (de) * 1994-02-16 1995-08-17 Behr Gmbh & Co Rippe für Wärmetauscher
JPH09119792A (ja) * 1995-10-25 1997-05-06 Hidaka Seiki Kk 熱交換器用フィン
JP2010169344A (ja) 2009-01-26 2010-08-05 Fujitsu General Ltd 熱交換器
JP5140051B2 (ja) * 2009-09-17 2013-02-06 三菱電機株式会社 熱交換器および熱交換器用フィンとその製造方法
EP2778593B1 (en) * 2011-11-10 2017-05-10 Panasonic Corporation Fin-tube heat exchanger

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Publication number Publication date
CN103105089B (zh) 2017-03-01
CN202885630U (zh) 2013-04-17
EP2778593A4 (en) 2014-10-15
EP2778593A1 (en) 2014-09-17
JPWO2013069299A1 (ja) 2015-04-02
CN103105089A (zh) 2013-05-15
WO2013069299A1 (ja) 2013-05-16
JP6115783B2 (ja) 2017-04-19

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