CA1230872A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- CA1230872A CA1230872A CA000430892A CA430892A CA1230872A CA 1230872 A CA1230872 A CA 1230872A CA 000430892 A CA000430892 A CA 000430892A CA 430892 A CA430892 A CA 430892A CA 1230872 A CA1230872 A CA 1230872A
- Authority
- CA
- Canada
- Prior art keywords
- fins
- plate
- heat exchanger
- elongated
- needle
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
- B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
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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
- 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
- F28D1/047—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 bent, e.g. in a serpentine or zig-zag
- F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
- F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
-
- 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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Abstract of the Disclosure:
A heat exchanger comprising a flat pipe for allowing a heat exchange medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip metal plate, the fins being arranged between the confronted flat surfaces and along their lengthwise direction, characterized in that the strip metal plate is modified structurally in a new manner whereby yield of a fin material, rigidity of the fins and performance of heat transfer are improved, and occurrence of reject articles is reduced.
A heat exchanger comprising a flat pipe for allowing a heat exchange medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip metal plate, the fins being arranged between the confronted flat surfaces and along their lengthwise direction, characterized in that the strip metal plate is modified structurally in a new manner whereby yield of a fin material, rigidity of the fins and performance of heat transfer are improved, and occurrence of reject articles is reduced.
Description
308~2 The present invention relates to a heat exchanger.
Ire present invention will ox illustrated by way of the accompanying drawings, in which:
Figs i and i to Figs I and I show a heat exchanger having conventional needle fins, Fig. l (a) is a front elevation Al view, Fig. i is a cross-sectional view, Fig. 2 is a partial perspective view, Fig. I is a lo partial cross-sectional view, and Fig. 3 (b) is a partial cross-sectional view of the needle fins;
Figs I, (b) and (c) and Fig. 5 show a first embodinlent of the heat exchanger according to the present invention, Fig. I is a partial cross-sectional view, Fig.
I is a partial cross-sectional view of the needle fins, Fig. I is a partial front elevation Al view, and Fig. 5 is an enlarged perspective view of the needle fins;
Fig. I and (b) and Fig. 7 show a second embody-mint of the heat exchanger according to the present invent lion, Fig. I and (b) are partial cross-sectional views, respectively, Fig. 7 is an enlarged perspective view of the fin portions;
Fig. I and (b) and Fig. 9 show a fourth embody-merit of the heat exchanger according to the present invent lion, Fig. I is a partial cross-sectional view of the needle fins, Fig. I is an enlarged perspective view of the needle fins, Fig. 9 is a diagram showing an air-side heat transfer rate according to the heat exchanger thus-treated in Fig. 8 for comparison with that of the previous heat exchanger.
The heat exchanger is a device for transnlitting heat energy from a high-temperature fluid to a low-tempera-; B I- 2 -~23~37~
lure fluid through a partition wall in order to accomplish heat-in or cooling. If the heat exchangers are classified struck rurally, there will be found a pipe type heat exchanger having fins. When a gas is caused to flow outside a heat transfer pipe, a heat transfer rate between the heat transfer pipe and the gas is small, therefore the pipe type heat exchanger having fins is employed in which the fins are fixed on the surfaces of the heat transfer pipe to increase heat fluxes.
lo As be definite from the foregoing, fitting a variety of fins on the heat transfer pipe is commonly carried out with the intention of improving the heat transfer performance of the heat exchanger, and various configurations of the fins have been sup-gusted. The inventors of the present invention have also pro-15 posed, in place of conventional corrugate fins, a high-perfor-mange heat exchanger having needle fins ~srltish Patents Nos.
15,689/l909 and 1,204,675).
This suggested heat exchanger equipped with the needle fins is excellent as a condenser in an elf conditioner for a car and a house, an evaporator or the like, and its structure is, for example, as shown in Figs l to 3.
- pa -12308~2 attached hereto. That is to say, as a heat transfer pipe, there is used an extruded flat pipe 1 having chambers therein defined by a plurality of partition walls lay flat surfaces lb of the flat pipe 1 are confronted with each other at an interval and disposed in parallel; and a needle fin group 2, which is formed by corrugating a strip metal plate, is disposed between the confronted flat surfaces lb of the flat pipe 1 in a manner normal to the lengthwise direction of the flat pipe 1. In operation, a heat exchange medium is fed into the flat pipe 1 through union joints 3 at opposite ends thereof, and a fluid such as air is caused to flow whereinto from outside in a direction normal to the lengthwise direction of the flat pipe 1 it in a direction along straight portions of lo the corrugate needle fins 2) in order to carry out heat exchange.
The needle fin group 2 can be prepared by forming numerous rectangular punched portions 2b in the strip metal plate (plate width h), slightly leaving opposite width direction end portions pa thereof, so that the plate is shaped into a ladder-like form. The thus formed needle fin group 2 is corrugated by causing it to meander along the lengthwise direction of the flat pipe at a meander width w, and the opposite width direction end portions of the needle fin group are brazed or caused to adhere to I
1230~72 the confronted flat surfaces lb of the flat pipe 1 by use of a brazing material or an adhesive previously applied on the flat surfaces lb. In this case, the needle fin group 2 having numerous needle fins 2c is arranged so that each fin pitch parallel to the flow direction of sir 4 may be PLY and each fin pitch normal to the flow direction of the air 4 may be PT.
However, it has been found that the heat exchanger equipped with such needle fins has the following faults:
(1) Since the punched portions 2b are provided in the strip metal plate in order to leave the needle fins 2c, an amount of the plate material corresponding to the punched portions is wasteful, which is undesirable from the viewpoints of resources saving and material cost, and particularly when aluminum is employed as the strip metal plate source, its wastage is serious.
Ire present invention will ox illustrated by way of the accompanying drawings, in which:
Figs i and i to Figs I and I show a heat exchanger having conventional needle fins, Fig. l (a) is a front elevation Al view, Fig. i is a cross-sectional view, Fig. 2 is a partial perspective view, Fig. I is a lo partial cross-sectional view, and Fig. 3 (b) is a partial cross-sectional view of the needle fins;
Figs I, (b) and (c) and Fig. 5 show a first embodinlent of the heat exchanger according to the present invention, Fig. I is a partial cross-sectional view, Fig.
I is a partial cross-sectional view of the needle fins, Fig. I is a partial front elevation Al view, and Fig. 5 is an enlarged perspective view of the needle fins;
Fig. I and (b) and Fig. 7 show a second embody-mint of the heat exchanger according to the present invent lion, Fig. I and (b) are partial cross-sectional views, respectively, Fig. 7 is an enlarged perspective view of the fin portions;
Fig. I and (b) and Fig. 9 show a fourth embody-merit of the heat exchanger according to the present invent lion, Fig. I is a partial cross-sectional view of the needle fins, Fig. I is an enlarged perspective view of the needle fins, Fig. 9 is a diagram showing an air-side heat transfer rate according to the heat exchanger thus-treated in Fig. 8 for comparison with that of the previous heat exchanger.
The heat exchanger is a device for transnlitting heat energy from a high-temperature fluid to a low-tempera-; B I- 2 -~23~37~
lure fluid through a partition wall in order to accomplish heat-in or cooling. If the heat exchangers are classified struck rurally, there will be found a pipe type heat exchanger having fins. When a gas is caused to flow outside a heat transfer pipe, a heat transfer rate between the heat transfer pipe and the gas is small, therefore the pipe type heat exchanger having fins is employed in which the fins are fixed on the surfaces of the heat transfer pipe to increase heat fluxes.
lo As be definite from the foregoing, fitting a variety of fins on the heat transfer pipe is commonly carried out with the intention of improving the heat transfer performance of the heat exchanger, and various configurations of the fins have been sup-gusted. The inventors of the present invention have also pro-15 posed, in place of conventional corrugate fins, a high-perfor-mange heat exchanger having needle fins ~srltish Patents Nos.
15,689/l909 and 1,204,675).
This suggested heat exchanger equipped with the needle fins is excellent as a condenser in an elf conditioner for a car and a house, an evaporator or the like, and its structure is, for example, as shown in Figs l to 3.
- pa -12308~2 attached hereto. That is to say, as a heat transfer pipe, there is used an extruded flat pipe 1 having chambers therein defined by a plurality of partition walls lay flat surfaces lb of the flat pipe 1 are confronted with each other at an interval and disposed in parallel; and a needle fin group 2, which is formed by corrugating a strip metal plate, is disposed between the confronted flat surfaces lb of the flat pipe 1 in a manner normal to the lengthwise direction of the flat pipe 1. In operation, a heat exchange medium is fed into the flat pipe 1 through union joints 3 at opposite ends thereof, and a fluid such as air is caused to flow whereinto from outside in a direction normal to the lengthwise direction of the flat pipe 1 it in a direction along straight portions of lo the corrugate needle fins 2) in order to carry out heat exchange.
The needle fin group 2 can be prepared by forming numerous rectangular punched portions 2b in the strip metal plate (plate width h), slightly leaving opposite width direction end portions pa thereof, so that the plate is shaped into a ladder-like form. The thus formed needle fin group 2 is corrugated by causing it to meander along the lengthwise direction of the flat pipe at a meander width w, and the opposite width direction end portions of the needle fin group are brazed or caused to adhere to I
1230~72 the confronted flat surfaces lb of the flat pipe 1 by use of a brazing material or an adhesive previously applied on the flat surfaces lb. In this case, the needle fin group 2 having numerous needle fins 2c is arranged so that each fin pitch parallel to the flow direction of sir 4 may be PLY and each fin pitch normal to the flow direction of the air 4 may be PT.
However, it has been found that the heat exchanger equipped with such needle fins has the following faults:
(1) Since the punched portions 2b are provided in the strip metal plate in order to leave the needle fins 2c, an amount of the plate material corresponding to the punched portions is wasteful, which is undesirable from the viewpoints of resources saving and material cost, and particularly when aluminum is employed as the strip metal plate source, its wastage is serious.
(2) The needle fin group 2 is structurally weak in stiffness in the direction of a plate width (height) h.
Therefore, when the application of pressure is carried out to secure the needle fin group on the flat surfaces lb, the needle fins 2c are prone to curve, so that the fin pitches PLY PUT would be uninformed and many reject articles would be manufactured.
Therefore, when the application of pressure is carried out to secure the needle fin group on the flat surfaces lb, the needle fins 2c are prone to curve, so that the fin pitches PLY PUT would be uninformed and many reject articles would be manufactured.
(3) Further, with regard to heat transfer performance, since the needle fins 2c are arranged in a straight line ~23~)872 along the direction of the air flow 4, the downstream needle fins 2c get into a boundary layer flow formed by the upstream needle fins 2c. This leads to deterioration in efficiency of the fins.
(4) Furthermore, in the case of the heat exchanger equipped with such fins 2c as mentioned above, the entrance of the air flow 4 into the needle fin group 2 is accom-polished through the curved portions of the corrugated plate, i.e. top and bottom portions of the group, and the discharge of the air flow is also done through the same curved portions. Therefore, inflow and outflow of the air 4 are greatly obstructed by the needle phony. As a result, a flow velocity vector pa of the air 4 at the curved portions of the corrugated plate is small and a flow velocity vector 4b at the straight portions of the corrugated plate is large. Finally, pressure loss at the inlet and outlet sides of the heat exchanger is great, and heat transfer rate is lowered due to the uninformed flow velocity, which facts lead to the deterioration in heat transfer performance.
(5) Still further, since a sectional shape of the needle fins is rectangular and their edge portions are sharp, a gas which is streaming near the edge portions brings about turbulence. In consequence, pressure loss is large and noise occurs, and additionally the flow I I
velocity of the gas is reduced due to the pressure loss and heat transfer rate is thus deteriorated. Moreover, since the needle portions 2c are arranged in a straight line along the direction of the air flow 4, contact of the downstream needle portions 2c with the air flow 4 is obstructed by the upstream needle portions 2c. As a result, the air-side heat transfer rate at the down-stream needle portions 2c is poor, and it is accordingly impost-isle to improve the heat transfer rate to an enough extent.
lo The present invention provides a heat exchanger which can eliminate conventional drawbacks described above, and improves yield of a fin material, rigidity of fin and performance of heat transfer and is hard to become a reject article.
According to the present invention there is provided a heat exchanger comprising an elongated flat plate adapted to pass a heat exchange medium there through, said flat plate having a pelf of oppositely disposed flat surfaces, said flat plate being bent along the elongated direction thereof in a meandering lash-ion into a plurality of generally rectilinear sections lntercon-netted by curved sections with the flat surfaces of adjacent fee-tllinear sections disposed in spaced facing generally parallel relation, fins extending between said facing flat surfaces of adjacent said rectilinear sections, said fins comprising an eon-grated sheet material plate corrugated to form alternating curved sections and straight sections, said plate having a pair of fat-orally spaced elongated edges with each said edge connected to a different one of said facing flat surfaces, said plate being slit in the direction between the elongated edges between locations adjacent to and spaced inwardly from said elongated edges, said plates being slit so that no portion of said plate is punched out and removed, said slitted plate forming adjacent fins extending for the ~23~87~
length of the slits in said plate, and said curved sections of said plate being punched out between locations adjacent said elongated edges whereby said fins extend along said straight section of said plate with said curved sections being free of said fins and being open.
Thus, the heat exchanger comprises a flat pipe for allowing a heat exchange medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins take the configuration of a needle fin group which is prepared by lo punching out the strip metal plate in the portions ZOO
- pa -~L23~87~
corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; forming numerous width direction notches in portions corresponding to straight portions of the corrugated plate in order to provide fins there between;
and causing the respective adjacent fins to alternately oppo-Seattle project.
The present invention again provides a heat exchanger which can overcome the aforementioned conventional drawbacks and has less pressure loss and high heat transfer performance. In accordance with the present invention the heat exchanger come proses a flat pipe for allowing a heat exchange medium to pass there through, flat surface of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins take the configure-lion of a ladder-like fin group which is formed by punching out the strip metal plate in the portions corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; and punching out the strip metal plate in the portions corresponding to straight portions of the corrugated plate in order to form numerous slits therein.
The present invention again provides a heat exchanger adapted to have great heat transfer rate and to generate less noise. Thus, the invention provides a heat exchanger comprising a flat pipe for allowing a heat exchanger medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins are removed partially to form portions for allowing a fluid to pass there through, and outer peripheral surfaces of the fins are made in the state of a smooth curvy surface.
~23087Z
Jo The present invention further provides a heat exchanger which can further improve an air-side heat transfer rate.
According to the present invention the heat exchanger comprises a flat pipe, in cross-section, meanderlngly arranged so that its flat surfaces may be parallel to each other at a predetermined interval, and a ladder-like needle corrugate fin meanderingly arranged in a space defined by the flat surfaces above so as to be parallel to each other in the width direction of the flat pipe, in which the needle portions of the corrugate fin are shaped into a circular form in I
cross section, and the respective adjacent needle portions are caused to alternately oppositely project from a standard plane.
Now, the present invention will be described with regard to its first embodiment on the basis of Figs 4 to 5:
A heat exchanger of the present invention makes use of an extruded flat pipe 1, by way of a heat transfer pipe, in which partition walls lo are installed therein in its lengthwise direction, as in a conventional one. The one extruded flat pipe 1 may be caused to meander so that its flat surfaces lb may be confronted with each other at an interval and disposed in parallel, alternatively many extruded flat pipes lay be connected to each other with the interposition of headers. In the spaces defined by the flat surfaces lb, there is secured a needle fin group 20 in a manner normal to the lengthwise direction of the flat plate I by use of a brazing material or adhesive, the needle fin group 20 being formed by corrugating a strip metal plate.
B
123~7~:
The needle fin group 20 can be formed from the strip metal plate as follows: The strip metal plate having a wall thickness of T and a width of h is employed; the strip metal plate is punched out in the portions correspond-in to curved portions R of the corrugated plate, slightly leaving opposite width direction end portions ~230872 aye thereof, in order to form punched portions 20b; the strip metal plate is formed with width direction notches in the portions corresponding to straight portions L of the corrugated plate at an interval substantially equal to the wall thickness T in order to form needle fins 20c between the respective notches; and the adjacent needle fins 20c are caused to alternately project in order to obtain a needle fin group 20 as shown enlargedly in FIG. 5.
The thus formed needle fin group 20 is corrugated so that a corrugation width and a fin pitch of the straight portions L may be w and PUT, respectively and the eon-rugated needle fin group 20 is inserted between the flat surfaces lb of the flat pipe 1. Then, the fin group is secured on the flat surfaces lb by the aid of the brazing material or adhesive which is previously affixed on the flat surfaces lb. In the case of the thus secured needle fin group 20, a fin pitch parallel to the flow direction of air 4 is PLY a fin pitch, normal to the flow direction of the air 4, of the straight portions L of the corrugated plate is PUT, a fin pitch between the needle fins 20c on the straight line L is Pi, a height of the fins (plate width) is h, and a wave height of the fins (meander width) lo W.
With regard to the heat exchanger including the thus formed needle fin group 20, the portions 20b corresponding ~30872 to the curved portions after completion of corrugation are only punched out in forming the needle fin group 20, therefore the yield of the used material can be improved to a great degree. Further, in the needle fin group 20, the notches are provided and the respective adjacent needle fins 20c are caused to alternately project, therefore the fin rigidity can be improved noticeably. As a result, even if a pressure is applied at the time of securing the needle fin group on the flat surfaces lb, it will not be deformed. This makes it possible to obtain a stable heat exchanger without any deformation. Furthermore, since being different from the conventional constitution that the punched portions are alternately provided to form the ladder-like structure, the needle fin group of the present invention can increase the fins by the number correspond-in to the punched portions. In consequence, a heat transfer area can be enlarged and a heat transfer per-pheromones can thus be enhanced. Additionally, when it is attempted to obtain the same performance as in the con-ventional one, the heat exchanger according to the present invention can be miniaturized. Moreover, since the needle fins are arranged so as to project alternately oppositely, the development of boundary layers can be restrained and the heat transfer performance can thus be improved.
FIGS. 6 and 7 attached hereto show a second embodiment ~:301372 of the present invention.
In this embodiment, as a heat transfer, there is used an extruded flat pipe l in which partition walls lo (which may be disposed along a longer axis, in cross section, of the pipe, though FIG. 1 (b) shows its arrangement along a shorter axis) are installed therein in its lengthwise direction as in the case of the conventional one. The one flat pipe l may be caused to meander so that its flat surfaces lb may be confronted with each other at an inter-vet and disposed in parallel, as shown in FIG. 1, alterna-lively many flat pipes 1 may be connected to each other with the interposition of headers. In the space defined by the flat surfaces lb, there is arranged a needle fin group 30 in a securing manner by use of the brazing material or adhesive, the needle fin group 30 being formed by corrugating a strip metal plate and being disposed there in a style normal to the lengthwise direction of the flat pipe 1 or in an inclined style.
When the conventional needle fin group (see FIGS. 3 (a) and 3 by was reviewed in detail, it has been found that the increase in pressure loss and the decrease in heat transfer rate are attributed to the fact the inflow and outflow of the air 4 are obstructed by the needle fins 2c at the curved portions of the corrugated plate, i.e. at the tops and bottoms of the meander. Therefore, the needle ~3087~
fin group 30 of this embodiment is formed as follows:
The strip metal thin plate which is a fin material is extensively punched out in the portions corresponding to the curved portions R of the corrugated plate, slightly leaving opposite width direction end portions aye thereof, in order to form punched portions 30b; and the portions, of the strip metal plate, corresponding to the straight portions L of the corrugated plate are formed with numerous rectangular slits 30c, slightly leaving the opposite width direction end portions aye thereof, in order to leave ladder-like needle fins 30d which constitute the needle fin group 30. The thus formed group 30 is corrugated by meandering it along the lengthwise direction of the flat surfaces lb of the flat pipe 1. And, securing the needle fin group 30 on the flat surfaces lb of the flat pipe 1 as a heat transfer pipe can be carried out by brazing or bonding the opposite width direction end portions of the corrugated needle fin group 30 to the flat surfaces lb with the aid of the brazing material or adhesive which is previously applied on the flat surfaces, but at this securing operation, the straight portions L of the eon=
rugated plate may be arranged so as to be parallel to the width direction of the flat pipe 1 or to be inclined as much as an angle I.
In the heat exchanger equipped with such a needle fin 12~087~
group 30, the curved portions R of the corrugated plate have no needle fins dry therefore the inflow and outflow of the air 4 can smoothly and uniformly carried out without any obstruction. As a result, the flow velocity vector pa of the air 4 at the curved portions R is equal to the flow velocity vector 4b of the air 4 at the straight portions L, and thus the pressure loss of the air is reduced and the heat transfer rate is improved. Therefore, when it is contemplated to obtain the same performance as in the conventional one, the heat exchanger according to the present invention can be miniaturized.
FIG. 8 shows a third embodiment of the present invent lion, and it is directed to an improved heat exchanger of the second embodiment illustrated.
This heat exchanger, as shown in FIG. 8 (a), comprises a flat pipe in cross section and a corrugate fin 50 meander-tingly arranged in a space defined by the flat surfaces lb of the flat pipe 1. As shown in FIG. 8 (b), in the case of this corrugate fin 50, needle portions 50b are formed in a ladder-like form between opposite end portions aye, aye, and the respective needle portions 50b are shaped into a substantially circular form in cross section. Further, between the respective needle portions 50b, there are formed openings 50c, and at the curved portions aye' of the end portions aye, there are formed fin-free portions 50d 1~30872 in order to facilitate the inflow and outflow of the air flow 4. Furthermore, bending portions eye are formed between the needle portions 50b and the opposite end portions aye, aye so that the respective adjacent needle portions 50b, 50b may be caused to alternately oppositely project by a predetermined distance from a plane comprising the opposite end portions aye, aye.
The thus prepared corrugate fins 50 are arranged so that they may be in parallel with each other in the width lo direction of the flat surfaces lb of the flat pipe 1, and the fin pitch of the needle portions 50b is Puts.
According to the heat exchanger above, the needle port lions 50b are caused to alternately project from the plane of the opposite end portions aye, therefore the downstream needle portions 50b can efficiently be heat exchanged with the air flow 4, which improves the air-side heat transfer rate. In the case of PUTS = TAO tin the case that the needle portions of the previous heat exchanger are caused to project without any processing), an effect on the improvement in a kcal/m.C.hr aroused heat transfer rate) has been investigated, and obtained results are set forth in FIG. 9. In this drawing, an abscissa axis repro-sets an air flow velocity (TV < m/sec) and an ordinate axis represents an improvement ratio of the air-side heat transfer rate of the heat exchanger regarding this 1 ~3087;~
embodiment with respect to that of the previous heat exchanger.
According to the results in FIG. 9, it is definite that the heat exchanger of this embodiment is better in the pa than the previous one. Further, the improvement ratio of the pa tends to decrease with the increase in the air flow velocity, but within the range usually employed (TV < 3 m/sec), it improves as much as 35% or more.
Since improving in the air-side heat transfer rate, the aforesaid heat exchanger can be miniaturized and lightened, if it is attempted to have the same performance as in the conventional one. Therefore, when this heat exchanger is applied as an air conditioner for a car, effects such as saving of a car fuel and expansion of a car space can be obtained.
In addition, the ladder-like needle corrugate fin 50 can be formed by in-line punching and circularization in cross section, and its punching pitch is a fin pitch for permitting acquisition of a maximum air-side heat transfer rate aye. In the case of the corrugate fin of this embody-mint, the maximum value of the air-side heat transfer rate aye can be obtained at a position where the fin pitch PUTS is narrower than TAO. For this reason, the fin pitch PUTS is to be narrowed, which serves to improve the yield of a used material.
i2~0872 Since the needle portions are circularized in cross section and are caused to project alternately normal to the direction of the air flow as described above, the heat exchanger having such needle portions can obtain noticeable effects of improvement in the air-side heat transfer rate, miniaturization and lightening of the heat exchanger body, betterment in the yield of the material, and the like.
velocity of the gas is reduced due to the pressure loss and heat transfer rate is thus deteriorated. Moreover, since the needle portions 2c are arranged in a straight line along the direction of the air flow 4, contact of the downstream needle portions 2c with the air flow 4 is obstructed by the upstream needle portions 2c. As a result, the air-side heat transfer rate at the down-stream needle portions 2c is poor, and it is accordingly impost-isle to improve the heat transfer rate to an enough extent.
lo The present invention provides a heat exchanger which can eliminate conventional drawbacks described above, and improves yield of a fin material, rigidity of fin and performance of heat transfer and is hard to become a reject article.
According to the present invention there is provided a heat exchanger comprising an elongated flat plate adapted to pass a heat exchange medium there through, said flat plate having a pelf of oppositely disposed flat surfaces, said flat plate being bent along the elongated direction thereof in a meandering lash-ion into a plurality of generally rectilinear sections lntercon-netted by curved sections with the flat surfaces of adjacent fee-tllinear sections disposed in spaced facing generally parallel relation, fins extending between said facing flat surfaces of adjacent said rectilinear sections, said fins comprising an eon-grated sheet material plate corrugated to form alternating curved sections and straight sections, said plate having a pair of fat-orally spaced elongated edges with each said edge connected to a different one of said facing flat surfaces, said plate being slit in the direction between the elongated edges between locations adjacent to and spaced inwardly from said elongated edges, said plates being slit so that no portion of said plate is punched out and removed, said slitted plate forming adjacent fins extending for the ~23~87~
length of the slits in said plate, and said curved sections of said plate being punched out between locations adjacent said elongated edges whereby said fins extend along said straight section of said plate with said curved sections being free of said fins and being open.
Thus, the heat exchanger comprises a flat pipe for allowing a heat exchange medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins take the configuration of a needle fin group which is prepared by lo punching out the strip metal plate in the portions ZOO
- pa -~L23~87~
corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; forming numerous width direction notches in portions corresponding to straight portions of the corrugated plate in order to provide fins there between;
and causing the respective adjacent fins to alternately oppo-Seattle project.
The present invention again provides a heat exchanger which can overcome the aforementioned conventional drawbacks and has less pressure loss and high heat transfer performance. In accordance with the present invention the heat exchanger come proses a flat pipe for allowing a heat exchange medium to pass there through, flat surface of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins take the configure-lion of a ladder-like fin group which is formed by punching out the strip metal plate in the portions corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; and punching out the strip metal plate in the portions corresponding to straight portions of the corrugated plate in order to form numerous slits therein.
The present invention again provides a heat exchanger adapted to have great heat transfer rate and to generate less noise. Thus, the invention provides a heat exchanger comprising a flat pipe for allowing a heat exchanger medium to pass there through, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, in which the fins are removed partially to form portions for allowing a fluid to pass there through, and outer peripheral surfaces of the fins are made in the state of a smooth curvy surface.
~23087Z
Jo The present invention further provides a heat exchanger which can further improve an air-side heat transfer rate.
According to the present invention the heat exchanger comprises a flat pipe, in cross-section, meanderlngly arranged so that its flat surfaces may be parallel to each other at a predetermined interval, and a ladder-like needle corrugate fin meanderingly arranged in a space defined by the flat surfaces above so as to be parallel to each other in the width direction of the flat pipe, in which the needle portions of the corrugate fin are shaped into a circular form in I
cross section, and the respective adjacent needle portions are caused to alternately oppositely project from a standard plane.
Now, the present invention will be described with regard to its first embodiment on the basis of Figs 4 to 5:
A heat exchanger of the present invention makes use of an extruded flat pipe 1, by way of a heat transfer pipe, in which partition walls lo are installed therein in its lengthwise direction, as in a conventional one. The one extruded flat pipe 1 may be caused to meander so that its flat surfaces lb may be confronted with each other at an interval and disposed in parallel, alternatively many extruded flat pipes lay be connected to each other with the interposition of headers. In the spaces defined by the flat surfaces lb, there is secured a needle fin group 20 in a manner normal to the lengthwise direction of the flat plate I by use of a brazing material or adhesive, the needle fin group 20 being formed by corrugating a strip metal plate.
B
123~7~:
The needle fin group 20 can be formed from the strip metal plate as follows: The strip metal plate having a wall thickness of T and a width of h is employed; the strip metal plate is punched out in the portions correspond-in to curved portions R of the corrugated plate, slightly leaving opposite width direction end portions ~230872 aye thereof, in order to form punched portions 20b; the strip metal plate is formed with width direction notches in the portions corresponding to straight portions L of the corrugated plate at an interval substantially equal to the wall thickness T in order to form needle fins 20c between the respective notches; and the adjacent needle fins 20c are caused to alternately project in order to obtain a needle fin group 20 as shown enlargedly in FIG. 5.
The thus formed needle fin group 20 is corrugated so that a corrugation width and a fin pitch of the straight portions L may be w and PUT, respectively and the eon-rugated needle fin group 20 is inserted between the flat surfaces lb of the flat pipe 1. Then, the fin group is secured on the flat surfaces lb by the aid of the brazing material or adhesive which is previously affixed on the flat surfaces lb. In the case of the thus secured needle fin group 20, a fin pitch parallel to the flow direction of air 4 is PLY a fin pitch, normal to the flow direction of the air 4, of the straight portions L of the corrugated plate is PUT, a fin pitch between the needle fins 20c on the straight line L is Pi, a height of the fins (plate width) is h, and a wave height of the fins (meander width) lo W.
With regard to the heat exchanger including the thus formed needle fin group 20, the portions 20b corresponding ~30872 to the curved portions after completion of corrugation are only punched out in forming the needle fin group 20, therefore the yield of the used material can be improved to a great degree. Further, in the needle fin group 20, the notches are provided and the respective adjacent needle fins 20c are caused to alternately project, therefore the fin rigidity can be improved noticeably. As a result, even if a pressure is applied at the time of securing the needle fin group on the flat surfaces lb, it will not be deformed. This makes it possible to obtain a stable heat exchanger without any deformation. Furthermore, since being different from the conventional constitution that the punched portions are alternately provided to form the ladder-like structure, the needle fin group of the present invention can increase the fins by the number correspond-in to the punched portions. In consequence, a heat transfer area can be enlarged and a heat transfer per-pheromones can thus be enhanced. Additionally, when it is attempted to obtain the same performance as in the con-ventional one, the heat exchanger according to the present invention can be miniaturized. Moreover, since the needle fins are arranged so as to project alternately oppositely, the development of boundary layers can be restrained and the heat transfer performance can thus be improved.
FIGS. 6 and 7 attached hereto show a second embodiment ~:301372 of the present invention.
In this embodiment, as a heat transfer, there is used an extruded flat pipe l in which partition walls lo (which may be disposed along a longer axis, in cross section, of the pipe, though FIG. 1 (b) shows its arrangement along a shorter axis) are installed therein in its lengthwise direction as in the case of the conventional one. The one flat pipe l may be caused to meander so that its flat surfaces lb may be confronted with each other at an inter-vet and disposed in parallel, as shown in FIG. 1, alterna-lively many flat pipes 1 may be connected to each other with the interposition of headers. In the space defined by the flat surfaces lb, there is arranged a needle fin group 30 in a securing manner by use of the brazing material or adhesive, the needle fin group 30 being formed by corrugating a strip metal plate and being disposed there in a style normal to the lengthwise direction of the flat pipe 1 or in an inclined style.
When the conventional needle fin group (see FIGS. 3 (a) and 3 by was reviewed in detail, it has been found that the increase in pressure loss and the decrease in heat transfer rate are attributed to the fact the inflow and outflow of the air 4 are obstructed by the needle fins 2c at the curved portions of the corrugated plate, i.e. at the tops and bottoms of the meander. Therefore, the needle ~3087~
fin group 30 of this embodiment is formed as follows:
The strip metal thin plate which is a fin material is extensively punched out in the portions corresponding to the curved portions R of the corrugated plate, slightly leaving opposite width direction end portions aye thereof, in order to form punched portions 30b; and the portions, of the strip metal plate, corresponding to the straight portions L of the corrugated plate are formed with numerous rectangular slits 30c, slightly leaving the opposite width direction end portions aye thereof, in order to leave ladder-like needle fins 30d which constitute the needle fin group 30. The thus formed group 30 is corrugated by meandering it along the lengthwise direction of the flat surfaces lb of the flat pipe 1. And, securing the needle fin group 30 on the flat surfaces lb of the flat pipe 1 as a heat transfer pipe can be carried out by brazing or bonding the opposite width direction end portions of the corrugated needle fin group 30 to the flat surfaces lb with the aid of the brazing material or adhesive which is previously applied on the flat surfaces, but at this securing operation, the straight portions L of the eon=
rugated plate may be arranged so as to be parallel to the width direction of the flat pipe 1 or to be inclined as much as an angle I.
In the heat exchanger equipped with such a needle fin 12~087~
group 30, the curved portions R of the corrugated plate have no needle fins dry therefore the inflow and outflow of the air 4 can smoothly and uniformly carried out without any obstruction. As a result, the flow velocity vector pa of the air 4 at the curved portions R is equal to the flow velocity vector 4b of the air 4 at the straight portions L, and thus the pressure loss of the air is reduced and the heat transfer rate is improved. Therefore, when it is contemplated to obtain the same performance as in the conventional one, the heat exchanger according to the present invention can be miniaturized.
FIG. 8 shows a third embodiment of the present invent lion, and it is directed to an improved heat exchanger of the second embodiment illustrated.
This heat exchanger, as shown in FIG. 8 (a), comprises a flat pipe in cross section and a corrugate fin 50 meander-tingly arranged in a space defined by the flat surfaces lb of the flat pipe 1. As shown in FIG. 8 (b), in the case of this corrugate fin 50, needle portions 50b are formed in a ladder-like form between opposite end portions aye, aye, and the respective needle portions 50b are shaped into a substantially circular form in cross section. Further, between the respective needle portions 50b, there are formed openings 50c, and at the curved portions aye' of the end portions aye, there are formed fin-free portions 50d 1~30872 in order to facilitate the inflow and outflow of the air flow 4. Furthermore, bending portions eye are formed between the needle portions 50b and the opposite end portions aye, aye so that the respective adjacent needle portions 50b, 50b may be caused to alternately oppositely project by a predetermined distance from a plane comprising the opposite end portions aye, aye.
The thus prepared corrugate fins 50 are arranged so that they may be in parallel with each other in the width lo direction of the flat surfaces lb of the flat pipe 1, and the fin pitch of the needle portions 50b is Puts.
According to the heat exchanger above, the needle port lions 50b are caused to alternately project from the plane of the opposite end portions aye, therefore the downstream needle portions 50b can efficiently be heat exchanged with the air flow 4, which improves the air-side heat transfer rate. In the case of PUTS = TAO tin the case that the needle portions of the previous heat exchanger are caused to project without any processing), an effect on the improvement in a kcal/m.C.hr aroused heat transfer rate) has been investigated, and obtained results are set forth in FIG. 9. In this drawing, an abscissa axis repro-sets an air flow velocity (TV < m/sec) and an ordinate axis represents an improvement ratio of the air-side heat transfer rate of the heat exchanger regarding this 1 ~3087;~
embodiment with respect to that of the previous heat exchanger.
According to the results in FIG. 9, it is definite that the heat exchanger of this embodiment is better in the pa than the previous one. Further, the improvement ratio of the pa tends to decrease with the increase in the air flow velocity, but within the range usually employed (TV < 3 m/sec), it improves as much as 35% or more.
Since improving in the air-side heat transfer rate, the aforesaid heat exchanger can be miniaturized and lightened, if it is attempted to have the same performance as in the conventional one. Therefore, when this heat exchanger is applied as an air conditioner for a car, effects such as saving of a car fuel and expansion of a car space can be obtained.
In addition, the ladder-like needle corrugate fin 50 can be formed by in-line punching and circularization in cross section, and its punching pitch is a fin pitch for permitting acquisition of a maximum air-side heat transfer rate aye. In the case of the corrugate fin of this embody-mint, the maximum value of the air-side heat transfer rate aye can be obtained at a position where the fin pitch PUTS is narrower than TAO. For this reason, the fin pitch PUTS is to be narrowed, which serves to improve the yield of a used material.
i2~0872 Since the needle portions are circularized in cross section and are caused to project alternately normal to the direction of the air flow as described above, the heat exchanger having such needle portions can obtain noticeable effects of improvement in the air-side heat transfer rate, miniaturization and lightening of the heat exchanger body, betterment in the yield of the material, and the like.
Claims (5)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A heat exchanger comprising an elongated flat plate adapted to pass a heat exchange medium therethrough said flat plate having a pair of oppositely disposed flat surfaces, said flat plate being bent along the elongated direction thereof in a meandering fashion into a plurality of generally rectilinear sec-tions interconnected by curved sections with the flat surfaces of adjacent rectilinear sections disposed in spaced facing generally parallel relation, fins extending between said facing flat sur-faces of adjacent said rectilinear sections, said fins comprising an elongated sheet material plate corrugated to form alternating curved sections and straight sections, said elongated sheet mate-rial plate having a pair of laterally spaced elongated edges with each said edge connected to a different one of said facing flat surfaces, said elongated sheet material plate being salt in the direction between the elongated edges between locations adjacent to and spaced inwardly from said elongated edges, said elongated sheet material plates being slit so that no portion of said plate is punched out and removed, said slitted plate forming adjacent fins extending for the length of the slits in said plate, and said curved sections of said elongated sheet material plate being punched out between locations adjacent said elongated edges whereby said fins extend along said straight section of said plate with said curved sections being free of said fins and being open.
2. A heat exchanger, as set forth in claim 1, wherein said fins are shaped to provide a smooth curved peripheral sur-face.
3. A heat exchanger, as set forth in claim 2, wherein said fins have a circular transverse cross section.
4. A heat exchanger, as set forth in claim 1, wherein said elongated edges are located in a common plane, and adjacent said fins are displaced laterally outwardly on opposite sides of the plane containing said elongated edges.
5. A heat exchanger, as set forth in claim 1, wherein said fins have an outside peripheral surface exten-ding in the direction between said elongated edges, said peripheral surface being circular in transverse cross-sec-tion, said elongated edges located in a common plane, and adjacent said fins extending in the direction between said elongated edges being displaced outwardly from the common plane containing the elongated edges whereby adjacent said fins define there between an opening through said plate.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9146582U JPS58194384U (en) | 1982-06-21 | 1982-06-21 | Heat exchanger |
| JP91465/1982 | 1982-06-21 | ||
| JP15901782U JPS5965275U (en) | 1982-10-22 | 1982-10-22 | Heat exchanger |
| JP173312/1982 | 1982-11-16 | ||
| JP17331282U JPS5976885U (en) | 1982-11-16 | 1982-11-16 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1230872A true CA1230872A (en) | 1987-12-29 |
Family
ID=27306751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000430892A Expired CA1230872A (en) | 1982-06-21 | 1983-06-21 | Heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0097612B1 (en) |
| AU (1) | AU1599483A (en) |
| CA (1) | CA1230872A (en) |
| DE (1) | DE3377666D1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01111965U (en) * | 1988-01-21 | 1989-07-27 | ||
| US8177932B2 (en) | 2009-02-27 | 2012-05-15 | International Mezzo Technologies, Inc. | Method for manufacturing a micro tube heat exchanger |
| DE102017217568A1 (en) * | 2017-10-04 | 2019-04-04 | Mahle International Gmbh | Heat exchanger |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH219262A (en) * | 1939-08-28 | 1942-01-31 | Ungarische Radiatoren Fabriks | Lamella heat exchange device. |
| FR1119126A (en) * | 1954-02-20 | 1956-06-15 | Escher Wyss Ag | Tube bundle for heat exchangers and method for its manufacture |
| FR1526316A (en) * | 1967-04-14 | 1968-05-24 | Chausson Usines Sa | Improvements to secondary heat sinks for radiators and unit heaters |
| US3776015A (en) * | 1970-12-01 | 1973-12-04 | Chausson Usines Sa | Process for manufacturing expanded and corrugated heat exchanger cores from metal strip material |
| AU556955B2 (en) * | 1981-09-09 | 1986-11-27 | Mulock-Bentley, D. And Associates Pty. Ltd. | Heat exchanger |
-
1983
- 1983-06-21 AU AU15994/83A patent/AU1599483A/en not_active Abandoned
- 1983-06-21 EP EP19830730057 patent/EP0097612B1/en not_active Expired
- 1983-06-21 CA CA000430892A patent/CA1230872A/en not_active Expired
- 1983-06-21 DE DE8383730057T patent/DE3377666D1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| AU1599483A (en) | 1984-01-05 |
| EP0097612A2 (en) | 1984-01-04 |
| DE3377666T2 (en) | 1988-09-15 |
| EP0097612B1 (en) | 1988-08-10 |
| EP0097612A3 (en) | 1985-01-23 |
| DE3377666D1 (en) | 1988-09-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |