US3818984A - Heat exchanger - Google Patents

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US3818984A
US3818984A US00324300A US32430073A US3818984A US 3818984 A US3818984 A US 3818984A US 00324300 A US00324300 A US 00324300A US 32430073 A US32430073 A US 32430073A US 3818984 A US3818984 A US 3818984A
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portions
disposed
fluid
heat exchanger
passages
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US00324300A
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K Nakamura
M Kuroyanagi
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Denso Corp
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Denso Corp
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Priority to JP1972012891U priority Critical patent/JPS5128703Y2/ja
Priority to JP4623372U priority patent/JPS5227710Y2/ja
Application filed by Denso Corp filed Critical Denso Corp
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Publication of US3818984A publication Critical patent/US3818984A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F28D9/0018Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form without any annular circulation of the heat exchange media
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0026Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion engines, e.g. for gas turbines or for Stirling engines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10Particular pattern of flow of the heat exchange media
    • F28F2250/108Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10STECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00Heat exchange
    • Y10S165/355Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356Plural plates forming a stack providing flow passages therein
    • Y10S165/357Plural plates forming a stack providing flow passages therein forming annular heat exchanger
    • Y10S165/358Radially arranged plates

Abstract

A heat exchanger for heat exchange between low-temperature and high-pressure air and high-temperature and low-pressure gas comprising a housing, a plurality of partition members disposed substantially radially in the housing for defining therebetween alternate air and gas passages for passing the air and gas in directions opposite to each other, a first corrugated fin disposed in each air passage, and a second corrugated fin disposed in each gas passage. The first fins are suitably cut out at one end thereof to communicate with an air inlet of the heat exchanger, and the second fins are suitably cut out at the end remote from the cut-out end of the first fins to communicate with a gas inlet of the heat exchanger so as to attain satisfactory heat exchange between the two fluids.

Description

United States Patent [191 Nakamura et al.

[ HEAT EXCHANGER [75] Inventors: Kenya Nakamura, Okazaki; Makoto Kuroyanagi, Hekinan, both of Japan [73] Assignee: Nippondenso Co., Ltd., Kariya-shi,

Japan Filed: Jan. 17, 1973 App]. No.: 324,300

[30] Foreign Application Priority Data Jan. 31, 1972 Japan 47-12891 Apr. l8, 1972 Japan 47-46233 [52] US. Cl. 165/166, 165/157 7 [51] Int. Cl. F28b 3/08 [58] Field of Search 165/166, 167, 60, 39.51, l65/141,l55, 157,164,165

[56] References Cited UNITED STATES PATENTS 2,368,732 2/1945 Wallgren 165/167 2,792,200 5/1957 Huggins et al. 165/148 X 3,198248 8/1965 Stack 165/166 June 25, 1974 3,228,464 l/1966 Stein et al 165/166 Primary Examiner-Charles J. Myhre Assistant ExaminerTheophil W. Streule, Jr.

Attorney, Agent, or Firm-Cushman, Darby & Cushman [57] ABSTRACT A heat exchanger for heat exchange between lowtemperature and high-pressure air and hightemperature and low-pressure gas comprising a housing, a plurality of partition members disposed substantially radially in the housing for defining therebetween alternate air and gas passages for passing the air and gas in directions opposite to each other, a first corrugated fin disposed in each air passage, and a second corrugated fin disposed in each gas passage. The first fins-are suitably cut out at one end thereof to communicate with an air inlet of the heat exchanger, and the second fins are suitably cut out at the end remote from the cut-out end of the first fins to communicate with a gas inlet of the heat exchanger so as to attain satisfactory heat exchangebetween the two fluids.

5 Claims, 9 Drawing Figures PATENTEUJUNZSIQH SHEU 1 (IF 8 PATENTEDJUNZSW v 3;a1a.9a4

' ISHEUEUFS I I FIG. 2

PATENTEDJUNZSIBH SHEET 6 [IF 8 FIG 4 FIG. 9

PATENTED JUNE 5 I974 SHEET 5 BF 8 FIG. 5

PATENTED JUNZS I974 SHEET 8 OF 8 PATENTEI] JUNZ 51974 shit? 7 [1F 8 FIG. 7

PATENTEDJUNZSISH SHEEI 8 OF 8 0 0 I o o 5 W O OIIIIIHIO 4 o o m o m IO 0 m 0 O 0 mm o I H I. O o k 8m ,o m mw m 0mm mm I @m l I nom nwm I mm 1 HEAT EXCHANGER This invention relates to heat exchangers, and more particularly to a heat exchanger of the kind preferably used with an engine such as a gas turbine engine for vehicles.

It is generally most important for a heat exchanger to accommodate the largest possible heat transfer area within a limited space, since the largeness of this heat transfer area is one of the greatest factors governing the performance of the heat exchanger. Recuperative heat exchangers known in the art include tube bundle tubefin heat exchangers employing solely tubes arranged in parallel and tube-fine type heat exchangers comprising the combination of tubes and fins. Plate-fin type heat exchangers comprising the combination of fluid conduits and corrugated fins manufactured by forming flat plates in the shape are especially widely employed for the reasons that such a heat exchanger is quite small in size and has a large heat transfer area. Further, these heat exchangers are classified into the parallel flow type, cross flow type and counter flow type depending on the directions of fluids placed in heat exchange relation. However, the conventional heat exchangers of the tube bundle type and tube-fin type have been defective in that there is a great restriction in the inner and outer effective heat transfer areas and the selection of working fluids is also subject to a limitation. Further, these heat exchangers have been defective in that a high heat exchange efficiency cannot be expected due to the fact that the working fluids must be inevitably passed in parallel flow or cross flow relation. The counterflow type heat exchanger in which working fluids are passed through adjoining conduits in counterflow relation has also been defective in that a complex arrangement is required for separating the different fluids from each other so that the fluids flowing into and out of the'adjoining conduits may not be mixed with each other. This type of heat exchanger has further been defective in that it is quite bulky due to the inclusion of many unnecessary dead spaces in the heat transfer zones and a very complex process and a long period of time are required for the manufacture.

With a view to obviate such prior art defects, it is an object of the present invention to'provide a novel and improved heat exchanger which comprises a cylindrical housing, a plurality of core units disposed radially within said housing, each said core unit including a plurality of partition members arranged in parallel for defining therebetween alternate passages for passing a first fluid and a second fluid in directions opposite to each other, a first corrugated fin disposed in each of said first fluid passages, and a second corrugated fin disposed in each of said second fluid passages, and a plurality of first fluid admitting space portions defined between the inner wall of said housing and said core units for communication with said-first fluid passages in said core units. The heat exchanger having the features set forth in the above is quite small in size and the effective heat transfer area can be adjusted as desired by suitably selecting the number of the first and second fluid passages and the number of the core units.

Another object of the present invention is to provide a heat exchanger of the above character in which at least one of said first and second fins is provided with a cut-out at one or either end thereof so as to pass the first and second fluids in the directions opposite to each other.

A further object of the present invention is to provide a heat exchanger comprising a cylindrical housing,a heat exchange unit disposed within said housing, a plurality of partition members disposed radially in said heat exchange unit for defining alternate passages for a first fluid and a second fluid, a first corrugated fin disposed in each of said first fluid passages, and a second corrugated fin disposed in each of said second fluid passages, at least one of said first and second fins being provided with a cut-out at one or either end thereof so as to pass these two different fluids through said alternate passages in directions opposite to each other. The heat exchanger having the features set forth in the above possesses a large heat transfer area and is quite small in size due to the fact that unnecessary dead spaces are substantially eliminated.

The above and other objects, features and advantages of the present invention will be apparent from the following detailed description taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a partly sectional side elevation view showing the structure of an embodiment of the present invention;

FIG. 2 is a partly sectional front elevation of the heat exchanger shown in FIG. 1;

FIG. 3 is a partly cut-away, enlarged perspective view showing the structure of one of the core units in the heat exchanger shown in FIG. 1;

FIG. 4 is an enlarged section of parts'of the air and gas passages in the core unit shown in FIG. 3;

FIG. 5 is a partly cut-away perspective view showing a modification of the core unit shown in FIG. 3;

FIG. 6 is a longitudinal section showing the structure of another embodiment of the present invention;

FIG. 7 is a side elevation of the left-hand half of the heat exchanger shown in FIG. 6;

FIG. 8 is a partly sectional perspective view showing the structure of the heat change unit in the heat exchanger shown in FIG. 6; and

FIG. 9' is an enlarged sectional view of parts of the heat exchanger shown in FIG. 6.

An embodiment of the present invention will be described with reference to FIGS. I to 4.

Referring to FIGS. 1 and 2, a cylindrical housing 1 forms an outer shell of a heat exchanger. A plurality of core units 2 are disposed radially within the housing 1 for the heat exchange between air at a low temperature and high pressure and gas at a high temperature and low pressure. A plurality of radially spaced members 3 connect the radially arranged core units 2 with one another in such a manner that a space 4 is defined between anytwo adjacent core units 2. An arcuate space portion 5 is defined between the inner wall of the housing I and each of the radially outer connecting members 3 for admitting low-temperature and high-pressure air into each core unit 2. Each of these spaces 4 is closed gas-tight by the core units 2 disposed on opposite sides thereof and by the associated core unit connecting members 3. The heat exchanger is provided with a plurality of flange portions 5a for mounting on an apparatus such as a gas turbine engine. The lowtemperature and high-pressure air is supplied from a compressor (not shown) to be fed through an air inlet 6 of the heat exchanger into each arcuate air admitting space portion 5, thence into air inlet portions 2a of each core unit 2. The low-temperature and highpressure air is turned into high-temperature and highpressure air through the heat exchange with the hightemperature and low-pressure gas while passing through each core unit .2 and such air is discharged through air outlet portions 2b of each core unit 2, thence through an air outlet 7 of the heat exchanger to be supplied to a combustor (not shown). The hightemperature and low-pressure gas is supplied through a gas inlet 8 of the heat exchanger into gas inlet portions 20 of each core unit 2 to be subjected to heat exchange with the low-temperature and high-pressure air while passing through the core unit 2, and the lowtemperature and low-pressure gas produced by the heat exchange is discharged through gas outlet portions 2d of each core unit 2, thence through a gas outlet 9 of the heat exchanger to the exterior. The direction of flow of the air in each core unit 2 is opposite to the direction of flow of the gas. Freely expansible sealing means 10 and 11 are disposed between the radially outer connecting member 3 and a passage forming member 12 and between another passage forming member 13 and a seal supporting member 14 respectively for each core unit 2.

Referring to FIGS. 3 and 4 showing in detail the structure of each core unit 2, a plurality of rectangular partition members 15 of, for example, stainless steel are arranged in parallel to define therebetween alter- 'nate air and gas passages 17 and 18. A first fin 16a in corrugated form consisting of a series of rectangular portions is disposed in each air passage 17 and a second fin 16b in corrugated form consisting of a series of rectangular portions is disposed in each gas passage 18 as shown. The first fins 16a. disposed in the air passages 17 defined between the associated partition members 15 are cut out in the form of a triangle at one end thereof to provide the air inlet portions 2a and are not cut to remain in the original rectangular shape at the other end thereof to provide the air outlet portions 2b. Similarly, the second fins 16b disposed in the gas passages 18 defined between the associated partition members 15 are cut out in the form ofa triangle at the end remote from the cut-out end of the first fins 16a to provide the gas inlet portions and are not cut out to remain in the original rectangular shape at the other end thereof to provide the gas outlet portions 2d. An L-shaped gas sealing member 19 is interposed gas-tight at its upstanding and horizontal portions between the corresponding opposite surface portions of each pair of the partition members 15 defining the gas passage 18 therebetween. Similarly, an L-shaped air sealing member 20 is interposed air-tight at its upstanding and horizontal portions between the corresponding opposite surface portions of each pair of the partition members 15 defining the air passage 17 therebetween. These sealing members 19 and 20 are alternately disposed in a confronting relationship as shown. The seal supporting member 14 of, for example, L-like cross section is fixed gas-tight at a position at which the horizontally extending portions of the air sealing members 20 inter-.

sect the upstanding portions of the gas sealing members 19. Another supporting member 14' is fixedly disposed gas-tight at a position at which the upstanding portions of the air sealing members'20 intersect the horizontally In operation, referring to FIG. 2, air at a low temperature and high pressure supplied from the compressor (not shown) passes through the air inlet 6 of the heat exchanger into each arcuate space portion 5, and after changing the direction of flow by 180, the air flows into the air inlet portions 2a of each core unit 2 to pass through the air passages 17 in the core unit 2. Thus, the air flows in a direction X X shown by the solid line. On the other hand, gas at high temperature and low pressure flows through the gas inlet 8 of the heat exchanger into the gas inlet portions 20 of each core unit 2 to passthrough the gas passages 18 in the core unit 2 in a direction Y Y shown by the dotted line Thus, the low-temperature and high-pressure air 'passing through the air passages 17 having the first fins 16a therein is brought into a satisfactory heat exchange relation with the high-temperature and low-pressure gas 7 which passes through the gas passages 18 having the pressure gas turns into low-temperature and lowextending portions of the gas sealing members 19. The

15 insuch a manner asto provide the airand gas inlet 2 portions Zaand 2cof the core. unit 2. f

' changer is small in size, has a large effective heat transpressure gas. Then, the high-temperature and highpressure air passes through the air outlet portions 2b of each core unit 2 to be supplied to the combustor (not shown) from the air outlet 7 of theheat exchanger while the low-temperature and low-pressure gas passes through the gas outlet portions 2d of each core unit 2 to be discharged to the exterior from the gas outlet 9 of the heat exchanger.

In the embodiment above described, the first and second fins 16a and 16b in each core unit 2 are cut out in a triangular form at one end thereof to provide the air inlet portions 2a and gas inlet portions 2c respectively. Referring to FIG. 5 showing a modification of the core unit 2 shown in FIG. 3, the first fins 16a disposed in the air passages 17 are cut out in a triangular form at opposite ends thereof as shown, while the second fins 16b disposed in the gas passages 18 are not cut out and have a rectangular shape. The first and second fins 16a and 16b are alternately fixed between the partition members l5 defining the air and gas passages 17 and 18 so that the cut-out ends of the first fins 16a provide the air inlet and outlet portions 2a and 2b, while the rectangular ends of the second fins 16b provide the gas inlet and outlet portions 2c and 2d in each core unit 2. Further, although the closed space portions 4 are provided between the core units 2 in the embodiment above described, these space portions 4 may be eliminated and additional core units 2 may be disposed in these spaces so as to increase the effective heat transfer area;

It will be understood from the above description that, in the first embodimentof the heat exchanger according to the present invention, a plurality of partition members are parallelly disposed to define therebetween a plurality of alternate air and gas passages for passing air and gasin directions opposite to each other and are combined with heat transfer fins to constitute a core unit, a plurality of such core units being disposed radially within a cylindrical housing, and the air passages in eachcore unit communicate with an air admitting space portion defined between the inner wall of the cylindrical housing. and the core .unit. The structure,

above described is advantageous in-that the heat exfer area and can be very simply manufactured due to the fact that the air admitting space portion can be formed by mere disposition of each core unit in the radial portion within the cylindrical housing, thereby eliminating the need for provision of any especial air supply conduit for supplying air into the air passages of the core unit. Further, by virtue of the fact that the core units disposed within the housing are independent of each other, leakage of air and gas can be easily detected and leaking parts can be repaired during the steps of manufacture and assembling. Thus, heat exchanger is from any air or gas leakage and the gas and air passages can be easily cleaned. The present invention is further advantageous in that the effective heat transfer area of the heat exchanger can be easily adjusted by suitably increasing or decreasing the number of the core units and also by increasing or decreasing the heat transfer area of the partition members and fins. Furthermore, by virtue of the fact that air and gas pass through the alternate air and gas passages in directions opposite to each other, satisfactory heat exchange between the air and the gas can be attained. Moreover, any especial means are not required for causing flow of the air and gas in the opposite directions and the heat exchanger has a simplified structure. Further, the heat exchanger has a satisfactory mechanical strength due to the fact that the core units are housed within the cylindrical housing.

Another embodiment of the present invention will be described with reference to FIGS. 6 to 9. Referring to FIG. 6, a heat exchange unit 22 is housed within a cylindrical housing 21. The heat exchange unit 22 is provided with an annular portion or ring 23 which is bolted to the cylindrical housing 21 for fixing the heat exchange unit 22 to the housing 21. The heat exchange unit 22 is supported within the housing 21 by a plurality of stays 24 welded to the heat exchange unit 22. The heat exchange unit 22 and housing 21 are mounted to the body of an apparatus such as a gas turbine engine (not shown) by a flange portion 25 and a ring 26. The heat exchange unit 22 includes an inner casing 27 which is closed at one end thereof. A plurality of first fins 280, second fins 28b and partition members 29 are alternately radially disposed around the inner casing 27. The first and second fins 28a and 28b are corrugated and have a width which is gradually enlarged from the inner toward the outer end. The assembly consisting of these fins 28a, 28b and partition members 29 is in the form of a thick-walled cylinder. As seen in FIGS. 6 and 8, the first fins 28a are cut out at one or right-hand end thereof, while the second fins 28b are cut out at the left-hand end remote from the cut-out end of the first fins 28a, and these first and second fins 28a and 28b are alternately arranged with the partition members 29 interposed therebetween. A first L-shaped sealing member 30a is in sealing engagement with the radially inner end edges and right-hand end edges of the partition members 29 disposed on opposite sides of each of the first fins 280 as seen in FIGS. 6 to 8. Similarly, a second L-shaped sealing member 30b is in sealing engagement with the radially outer end edges and left-hand end edges of the partition members 29 disposed on opposite sides of each of the second fins 28b. Further, these first and second sealing members 30a and 30b intersect at the opposite ends thereof and the rings 23 and 26 are welded to these intersecting portions to serve as a sealing means for these intersecting portions. An outer casing 31 is secured as by soldering to the second L-shaped sealing members 30b, and the flange portion 25 is formed at the left-hand end of the outer casing 31 as seen in FIGS. 6 to 8. The right-hand end of the outer casing 31 registers with the starting position of the cut-out at the right-hand end of the first fins 28a, and the left-hand end of the inner casing 27 registers with the starting portion of the cut-out at the left-hand end of the second fins 28b as best shown in FIG. 6.

In operation, air at a low temperature and high pressure is supplied from a compressor (not shown) to pass through the space between the housing 21 and the outer casing 31 in a direction as shown by the arrow A. On the other hand, combustion gas at a high temperature and low pressure is supplied through the opening of the ring 26 in a direction as shown by the arrow B. The low-temperature and high-pressure air flows then in a direction as shown by the arrow C to enter the triangular spaces defined by the cut-out ends of the first fins 28a, partition members 29 and first L-shaped sealing members 30a, thence into the air passages defined between the partition members 29 and containing the first fins 28a therein to be discharged through the space between the ring 26 and the outer casing 31 in a direction as shown by the arrow D. On the other hand, the high-temperature and low-pressure combustion gas flows in a direction as shown by the arrow E to enter the triangular spaces defined by the cut-out ends of the second fins 28b, partition members 29 and second L- shaped sealing members 30b, thence into the gas passages defined between the partition members 29 and containing the second fins 28b therein to be discharged through the space between the ring 23 and the inner casing 27 in a direction as shown by the arrow F. In the heat exchanger, heat exchange between the lowtemperature and high-pressure air and the hightemperature and low-pressure combustion gas occurs through the medium of the first and second fins 28a, 28b and partition members 29. As a result, the air supplied in the low-temperature and high-pressure state is turned into high-temperature and high-pressure air and such air is fed in the direction of the arrow D to be supplied into the combustor in the gas turbine engine (not shown) for combustion, while the combustion gas supplied in the high-temperature and low-pressure state is turned into low-temperature and low-pressure gas and such gas is discharged to the exterior in the direction of the arrow F.

' In the second embodiment of the present invention, the first fins 28a and second fins 28b are cut out at their right-hand and left-hand ends in the manner shown in FIG. 6 so as to provide the air and combustion gas inlet portions respectively. However, the first fins 28a may be cut out at the left-hand end thereof as shown by the two-dot chain line in FIG. 6 in addition to the cut-out at the right-hand end thereof, while the second fins 28b may not be cut out at either end thereof, and the shape of the first and second L-shaped sealing members 30a and 30b may be slightly modified. In such a modification, the air and combustion gas flow in respective directions as shown by the two-dot chain lines and satisfactory heat exchange between the air and the combustion gas can be similarly effectively attained.

What is claimed is:

l. A heat exchanger comprising a cylindrical housing, a plurality of partition members disposed within said housing for defining alternate passages for a first fluid and a second fluid, first corrugated fins are each disposed in each of said first fluid passages, second corrugated fins are each disposed in each of said second fluid passages, at least one of said first and second fins being formed with oblique cut out portions at at least one end thereof so as to provide inlet portions for introducing said two fluids into said alternate passages in directions opposite to each other.

2. A heat exchanger comprising a cylindrical housing, a plurality of core units disposed radially'within said housing, each of said core units having a square cross section and including a plurality of partition members arranged substantially parallel to one another for defining therebetween alternate passages for passing first and second fluids in opposite directions, first corrugated fins one each disposedin each of said first fluid passages, second corrugated fins one each disposed in each of said second fluid passages, one of said first and second corrugated fins being formed with oblique cut out portions at their radially outer ends so as to provide inlet portions to introduce said first or second fluid into said first or second fluid passages, a plurality of fluid admitting space portions defined between the inner wall of said housing and radially outer surfaces of said core units for communication with said first or second fluid passages in said core units through said cut out portions,and a cylindrical space defined by the radially inner surfaces of said core units at a center portion in said housing for communication with the other of said first and second fluid passages.

3. A heat exchanger as defined in claim 2, wherein oblique cut out portions are formed also at the radially and second fluid passages being opened to said fluid admitting space portions, said cut out portions of the corrugated fins disposed in the other of said passages being opened to said cylindrical space.

4. A heat exchanger comprising a cylindrical housing, a heat exchanger unit disposed within said housing, said heat exchanger unit including a plurality of partition members disposed radially for defining alternate passages for a first fluid and a second fluid, first corru- V gated fins each having a wedge-shaped cross section and being disposed in each of said first fluid passages, second corrugated fins each having a wedge-shaped cross section and being disposed in each of said second inner endsof the corrugated fins disposed in the other i of said first and second fluid passages, said cut out portions of the corrugated fins disposed in one of said first inner periphery of said heat exchanger unit at a center portion in said housing for communication with the other of said first and second fluid passages.

5. A heat exchanger as defined in claim 4, wherein oblique cut out portions are formed also at the radially inner ends of the corrugated fins disposed in the other of said first and second fluidpassages, said cut out portions of the corrugated fins disposed in one of said first and second fluid passages being opened to said fluid admitting portion, saidcut out portionsof the corrugated fins disposed in the other of said passages being opened to said cylindrical space.

Claims (5)

1. A heat exchanger comprising a cylindrical housing, a plurality of partition members disposed within said housing for defining alternate passages for a first fluid and a second fluid, first corrugated fins are each disposed in each of said first fluid passages, second corrugated fins are each disposed in each of said second fluid passages, at least one of said first and second fins being formed with oblique cut out portions at at least one end thereof so as to provide inlet portions for introducing said two fluids into said alternate passages in directions opposite to each other.
2. A heat exchanger comprising a cylindrical housing, a plurality of core units disposed radially within said housing, each of said core units having a square cross section and including a plurality of partition members arranged substantially parallel to one another for defining therebetween alternate passages for passing first and second fluids in opposite directions, first corrugated fins one each disposed in each of said first fluid passages, second corrugated Fins one each disposed in each of said second fluid passages, one of said first and second corrugated fins being formed with oblique cut out portions at their radially outer ends so as to provide inlet portions to introduce said first or second fluid into said first or second fluid passages, a plurality of fluid admitting space portions defined between the inner wall of said housing and radially outer surfaces of said core units for communication with said first or second fluid passages in said core units through said cut out portions, and a cylindrical space defined by the radially inner surfaces of said core units at a center portion in said housing for communication with the other of said first and second fluid passages.
3. A heat exchanger as defined in claim 2, wherein oblique cut out portions are formed also at the radially inner ends of the corrugated fins disposed in the other of said first and second fluid passages, said cut out portions of the corrugated fins disposed in one of said first and second fluid passages being opened to said fluid admitting space portions, said cut out portions of the corrugated fins disposed in the other of said passages being opened to said cylindrical space.
4. A heat exchanger comprising a cylindrical housing, a heat exchanger unit disposed within said housing, said heat exchanger unit including a plurality of partition members disposed radially for defining alternate passages for a first fluid and a second fluid, first corrugated fins each having a wedge-shaped cross section and being disposed in each of said first fluid passages, second corrugated fins each having a wedge-shaped cross section and being disposed in each of said second fluid passage, one of said first and second fins being formed with oblique cut out portions at their radially outer ends so as to provide inlet portions to introduce said first or second fluid into said first or second fluid passages, respectively, a plurality of fluid admitting space portions defined between the inner wall of said housing and the outer periphery of said heat exchanger unit for communication with said first or second fluid passages in said heat exchanger unit through said cut out portions, and a cylindrical space defined by the inner periphery of said heat exchanger unit at a center portion in said housing for communication with the other of said first and second fluid passages.
5. A heat exchanger as defined in claim 4, wherein oblique cut out portions are formed also at the radially inner ends of the corrugated fins disposed in the other of said first and second fluid passages, said cut out portions of the corrugated fins disposed in one of said first and second fluid passages being opened to said fluid admitting portion, said cut out portions of the corrugated fins disposed in the other of said passages being opened to said cylindrical space.
US00324300A 1972-01-31 1973-01-17 Heat exchanger Expired - Lifetime US3818984A (en)

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JP1972012891U JPS5128703Y2 (en) 1972-01-31 1972-01-31
JP4623372U JPS5227710Y2 (en) 1972-04-18 1972-04-18

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Cited By (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4085588A (en) * 1976-04-05 1978-04-25 Ford Motor Company Concentric crossflow recuperator for stirling engine
US4098330A (en) * 1976-07-23 1978-07-04 General Motors Corporation Annular metal recuperator
US4213297A (en) * 1977-10-06 1980-07-22 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Vehicular propulsion gas turbine motor
US4321964A (en) * 1978-02-11 1982-03-30 Kernforschungsanlage Julich Gesellschaft Mit Berschrankter Haftung, Rosenthal Technik Ag Recuperative heat exchanger of ceramic material
EP0071781A1 (en) * 1981-08-06 1983-02-16 Klöckner-Humboldt-Deutz Aktiengesellschaft Annular recuperative heat exchanger
EP0097726A1 (en) * 1982-06-24 1984-01-11 Rockwell International Corporation A heat exchanger
EP0127683A1 (en) * 1982-11-04 1984-12-12 Matsushita Electric Industrial Co., Ltd. Heat exchanger
US4993223A (en) * 1989-09-11 1991-02-19 Allied-Signal Inc. Annular recuperator
US5004044A (en) * 1989-10-02 1991-04-02 Avco Corporation Compact rectilinear heat exhanger
US5050668A (en) * 1989-09-11 1991-09-24 Allied-Signal Inc. Stress relief for an annular recuperator
US5065816A (en) * 1990-05-29 1991-11-19 Solar Turbines Incorporated Sealing system for a circular heat exchanger
US5081834A (en) * 1990-05-29 1992-01-21 Solar Turbines Incorporated Circular heat exchanger having uniform cross-sectional area throughout the passages therein
EP0796986A1 (en) * 1995-09-08 1997-09-24 Honda Giken Kogyo Kabushiki Kaisha Gas-turbine engine
US5878590A (en) * 1998-02-25 1999-03-09 General Motors Corporation Dehumidifying mechanism for auto air conditioner with improved space utilization and thermal efficiency
US6293338B1 (en) 1999-11-04 2001-09-25 Williams International Co. L.L.C. Gas turbine engine recuperator
GB2360577A (en) * 1999-12-23 2001-09-26 Framo Developements As Heat exchanger construction
US6357113B1 (en) 1999-11-04 2002-03-19 Williams International Co., L.L.C. Method of manufacture of a gas turbine engine recuperator
US6438936B1 (en) 2000-05-16 2002-08-27 Elliott Energy Systems, Inc. Recuperator for use with turbine/turbo-alternator
US6474408B1 (en) * 2000-08-31 2002-11-05 Honeywell International Inc. Heat exchanger with bypass seal allowing differential thermal expansion
US20020179296A1 (en) * 1999-12-02 2002-12-05 Jassens Jean Paul Heat exchanger
US20030164233A1 (en) * 2002-02-19 2003-09-04 Wu Alan K. Low profile finned heat exchanger
US20030173068A1 (en) * 2000-12-21 2003-09-18 Davies Michael E. Finned plate heat exchanger
US20030196782A1 (en) * 2001-08-10 2003-10-23 Otter James W. Black layer coated heat exchanger
US20040067414A1 (en) * 2002-10-02 2004-04-08 Ronghua Wei Thermal control device and method of use therefor
US20040069441A1 (en) * 2002-06-04 2004-04-15 Burgers Johny G. Lateral plate finned heat exchanger
US20040069474A1 (en) * 2002-07-05 2004-04-15 Alan Wu Baffled surface cooled heat exchanger
US20040188078A1 (en) * 2003-03-24 2004-09-30 Wu Alan Ka-Ming Lateral plate surface cooled heat exchanger
US20040238162A1 (en) * 2003-04-11 2004-12-02 Seiler Thomas F. Heat exchanger with flow circuiting end caps
US20050087330A1 (en) * 2003-10-28 2005-04-28 Yungmo Kang Recuperator construction for a gas turbine engine
US20050098309A1 (en) * 2003-10-28 2005-05-12 Yungmo Kang Recuperator assembly and procedures
US20050115701A1 (en) * 2003-11-28 2005-06-02 Michael Martin Low profile heat exchanger with notched turbulizer
US6935416B1 (en) * 2000-12-25 2005-08-30 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
NL1025958C2 (en) * 2004-04-15 2005-10-18 Nefit Buderus B V Heat exchanger transmits heat from relatively hot fluid to relatively cold fluid and comprises cylindrical body in which several plates extend
US20060243429A1 (en) * 2005-04-29 2006-11-02 Stanley Chu Heat exchangers with turbulizers having convolutions of varied height
WO2010139329A3 (en) * 2009-06-05 2011-03-10 Danfoss Compressors Gmbh Heat exchanger arrangement and stirling refrigerator
US20120199335A1 (en) * 2011-02-04 2012-08-09 Lockheed Martin Corporation Radial-flow heat exchanger with foam heat exchange fins
US20120205086A1 (en) * 2011-02-14 2012-08-16 Denso Corporation Heat exchanger
US20140124179A1 (en) * 2012-11-08 2014-05-08 Delio Sanz Heat Exchanger
US20140260178A1 (en) * 2013-03-14 2014-09-18 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
EP2910765A1 (en) * 2014-02-21 2015-08-26 Rolls-Royce Corporation Single phase micro/mini channel heat exchangers for gas turbine intercooling
US20160122024A1 (en) * 2014-11-03 2016-05-05 Hamilton Sundstrand Corporation Heat exchanger
US20160123230A1 (en) * 2013-06-14 2016-05-05 United Technologies Corporation Curved plate/fin heater exchanger
US20160177829A1 (en) * 2014-02-21 2016-06-23 Rolls-Royce Corporation Microchannel heat exchangers for gas turbine intercooling and condensing
US9395122B2 (en) 2011-02-28 2016-07-19 Pratt & Whitney Canada Corp. Diffusing gas turbine engine recuperator
US9394828B2 (en) 2011-02-28 2016-07-19 Pratt & Whitney Canada Corp. Gas turbine engine recuperator with floating connection
US9464847B2 (en) 2011-02-04 2016-10-11 Lockheed Martin Corporation Shell-and-tube heat exchangers with foam heat transfer units
US20170089647A1 (en) * 2014-05-12 2017-03-30 Fraunhofer Gesellschaft zur Förderung der angewandten Forschung e.V. Heat transfer device and use thereof
US9766019B2 (en) 2011-02-28 2017-09-19 Pratt & Whitney Canada Corp. Swirl reducing gas turbine engine recuperator
US9951997B2 (en) 2011-02-04 2018-04-24 Lockheed Martin Corporation Staged graphite foam heat exchangers
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
US20190212074A1 (en) * 2018-01-08 2019-07-11 Hamilton Sundstrand Corporation Method for manufacturing a curved heat exchanger using wedge shaped segments

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368732A (en) * 1939-11-18 1945-02-06 Bolinder Munktell Cooler for engines
US2792200A (en) * 1952-03-15 1957-05-14 Modine Mfg Co Toroidal type heat exchanger
US3198248A (en) * 1963-04-10 1965-08-03 Minnesota Mining & Mfg Corrugated heat transfer exchangers
US3228464A (en) * 1963-08-09 1966-01-11 Avco Corp Corrugated plate counter flow heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2368732A (en) * 1939-11-18 1945-02-06 Bolinder Munktell Cooler for engines
US2792200A (en) * 1952-03-15 1957-05-14 Modine Mfg Co Toroidal type heat exchanger
US3198248A (en) * 1963-04-10 1965-08-03 Minnesota Mining & Mfg Corrugated heat transfer exchangers
US3228464A (en) * 1963-08-09 1966-01-11 Avco Corp Corrugated plate counter flow heat exchanger

Cited By (84)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4085588A (en) * 1976-04-05 1978-04-25 Ford Motor Company Concentric crossflow recuperator for stirling engine
US4098330A (en) * 1976-07-23 1978-07-04 General Motors Corporation Annular metal recuperator
US4213297A (en) * 1977-10-06 1980-07-22 Kernforschungsanlage Julich Gesellschaft Mit Beschrankter Haftung Vehicular propulsion gas turbine motor
US4321964A (en) * 1978-02-11 1982-03-30 Kernforschungsanlage Julich Gesellschaft Mit Berschrankter Haftung, Rosenthal Technik Ag Recuperative heat exchanger of ceramic material
US4527622A (en) * 1981-08-06 1985-07-09 Klockner-Humboldt-Deutz Aktiengesellschaft Ring-shaped recuperative heat exchanger
EP0071781A1 (en) * 1981-08-06 1983-02-16 Klöckner-Humboldt-Deutz Aktiengesellschaft Annular recuperative heat exchanger
EP0097726A1 (en) * 1982-06-24 1984-01-11 Rockwell International Corporation A heat exchanger
EP0127683A1 (en) * 1982-11-04 1984-12-12 Matsushita Electric Industrial Co., Ltd. Heat exchanger
EP0127683A4 (en) * 1982-11-04 1985-06-10 Matsushita Electric Ind Co Ltd Heat exchanger.
US4993223A (en) * 1989-09-11 1991-02-19 Allied-Signal Inc. Annular recuperator
US5050668A (en) * 1989-09-11 1991-09-24 Allied-Signal Inc. Stress relief for an annular recuperator
US5004044A (en) * 1989-10-02 1991-04-02 Avco Corporation Compact rectilinear heat exhanger
US5081834A (en) * 1990-05-29 1992-01-21 Solar Turbines Incorporated Circular heat exchanger having uniform cross-sectional area throughout the passages therein
WO1991019152A1 (en) * 1990-05-29 1991-12-12 Solar Turbines Incorporated A sealing system for a circular heat exchanger
US5065816A (en) * 1990-05-29 1991-11-19 Solar Turbines Incorporated Sealing system for a circular heat exchanger
EP0796986A1 (en) * 1995-09-08 1997-09-24 Honda Giken Kogyo Kabushiki Kaisha Gas-turbine engine
EP0796986A4 (en) * 1995-09-08 1998-02-11 Honda Motor Co Ltd Gas-turbine engine
US5855112A (en) * 1995-09-08 1999-01-05 Honda Giken Kogyo Kabushiki Kaisha Gas turbine engine with recuperator
US5878590A (en) * 1998-02-25 1999-03-09 General Motors Corporation Dehumidifying mechanism for auto air conditioner with improved space utilization and thermal efficiency
USRE38181E1 (en) 1998-02-25 2003-07-15 Delphi Technologies, Inc. Dehumidifying mechanism for auto air conditioner with improved space utilization and thermal efficiency
US6293338B1 (en) 1999-11-04 2001-09-25 Williams International Co. L.L.C. Gas turbine engine recuperator
US6357113B1 (en) 1999-11-04 2002-03-19 Williams International Co., L.L.C. Method of manufacture of a gas turbine engine recuperator
US20020179296A1 (en) * 1999-12-02 2002-12-05 Jassens Jean Paul Heat exchanger
GB2360577A (en) * 1999-12-23 2001-09-26 Framo Developements As Heat exchanger construction
US6837419B2 (en) 2000-05-16 2005-01-04 Elliott Energy Systems, Inc. Recuperator for use with turbine/turbo-alternator
US6438936B1 (en) 2000-05-16 2002-08-27 Elliott Energy Systems, Inc. Recuperator for use with turbine/turbo-alternator
US6474408B1 (en) * 2000-08-31 2002-11-05 Honeywell International Inc. Heat exchanger with bypass seal allowing differential thermal expansion
US20030173068A1 (en) * 2000-12-21 2003-09-18 Davies Michael E. Finned plate heat exchanger
US7011142B2 (en) 2000-12-21 2006-03-14 Dana Canada Corporation Finned plate heat exchanger
US6935416B1 (en) * 2000-12-25 2005-08-30 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
US20030196782A1 (en) * 2001-08-10 2003-10-23 Otter James W. Black layer coated heat exchanger
US6959757B2 (en) * 2001-08-10 2005-11-01 Carrier Corporation Black layer coated heat exchanger
US20060243431A1 (en) * 2002-02-19 2006-11-02 Martin Michael A Low profile finned heat exchanger
US20030164233A1 (en) * 2002-02-19 2003-09-04 Wu Alan K. Low profile finned heat exchanger
US20040069441A1 (en) * 2002-06-04 2004-04-15 Burgers Johny G. Lateral plate finned heat exchanger
US6889758B2 (en) 2002-06-04 2005-05-10 Dana Canada Corporation Lateral plate finned heat exchanger
US7025127B2 (en) 2002-07-05 2006-04-11 Dana Canada Corporation Baffled surface cooled heat exchanger
US20040069474A1 (en) * 2002-07-05 2004-04-15 Alan Wu Baffled surface cooled heat exchanger
US20040067414A1 (en) * 2002-10-02 2004-04-08 Ronghua Wei Thermal control device and method of use therefor
US6938686B2 (en) * 2003-03-24 2005-09-06 Dana Canada Corporation Lateral plate surface cooled heat exchanger
US20040188078A1 (en) * 2003-03-24 2004-09-30 Wu Alan Ka-Ming Lateral plate surface cooled heat exchanger
US20040238162A1 (en) * 2003-04-11 2004-12-02 Seiler Thomas F. Heat exchanger with flow circuiting end caps
US7213638B2 (en) 2003-04-11 2007-05-08 Dana Canada Corporation Heat exchanger with flow circuiting end caps
US20060137868A1 (en) * 2003-10-28 2006-06-29 Yungmo Kang Recuperator assembly and procedures
US20050098309A1 (en) * 2003-10-28 2005-05-12 Yungmo Kang Recuperator assembly and procedures
US20050087330A1 (en) * 2003-10-28 2005-04-28 Yungmo Kang Recuperator construction for a gas turbine engine
US7065873B2 (en) 2003-10-28 2006-06-27 Capstone Turbine Corporation Recuperator assembly and procedures
US7415764B2 (en) 2003-10-28 2008-08-26 Capstone Turbine Corporation Recuperator assembly and procedures
US7147050B2 (en) 2003-10-28 2006-12-12 Capstone Turbine Corporation Recuperator construction for a gas turbine engine
US20050115701A1 (en) * 2003-11-28 2005-06-02 Michael Martin Low profile heat exchanger with notched turbulizer
US7182125B2 (en) 2003-11-28 2007-02-27 Dana Canada Corporation Low profile heat exchanger with notched turbulizer
NL1025958C2 (en) * 2004-04-15 2005-10-18 Nefit Buderus B V Heat exchanger transmits heat from relatively hot fluid to relatively cold fluid and comprises cylindrical body in which several plates extend
US20060243429A1 (en) * 2005-04-29 2006-11-02 Stanley Chu Heat exchangers with turbulizers having convolutions of varied height
US7686070B2 (en) * 2005-04-29 2010-03-30 Dana Canada Corporation Heat exchangers with turbulizers having convolutions of varied height
WO2010139329A3 (en) * 2009-06-05 2011-03-10 Danfoss Compressors Gmbh Heat exchanger arrangement and stirling refrigerator
US20120199335A1 (en) * 2011-02-04 2012-08-09 Lockheed Martin Corporation Radial-flow heat exchanger with foam heat exchange fins
US9464847B2 (en) 2011-02-04 2016-10-11 Lockheed Martin Corporation Shell-and-tube heat exchangers with foam heat transfer units
US9951997B2 (en) 2011-02-04 2018-04-24 Lockheed Martin Corporation Staged graphite foam heat exchangers
US9513059B2 (en) * 2011-02-04 2016-12-06 Lockheed Martin Corporation Radial-flow heat exchanger with foam heat exchange fins
US20120205086A1 (en) * 2011-02-14 2012-08-16 Denso Corporation Heat exchanger
US9472489B2 (en) * 2011-02-14 2016-10-18 Denso Corporation Heat exchanger
US9394828B2 (en) 2011-02-28 2016-07-19 Pratt & Whitney Canada Corp. Gas turbine engine recuperator with floating connection
US9766019B2 (en) 2011-02-28 2017-09-19 Pratt & Whitney Canada Corp. Swirl reducing gas turbine engine recuperator
US10550767B2 (en) 2011-02-28 2020-02-04 Pratt & Whitney Canada Corp. Gas turbine engine recuperator with floating connection
US9395122B2 (en) 2011-02-28 2016-07-19 Pratt & Whitney Canada Corp. Diffusing gas turbine engine recuperator
US20140124179A1 (en) * 2012-11-08 2014-05-08 Delio Sanz Heat Exchanger
US20140260178A1 (en) * 2013-03-14 2014-09-18 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
US9724746B2 (en) * 2013-03-14 2017-08-08 Pratt & Whitney Canada Corp. Aerodynamically active stiffening feature for gas turbine recuperator
US10100740B2 (en) * 2013-06-14 2018-10-16 United Technologies Corporation Curved plate/fin heater exchanger
US20160123230A1 (en) * 2013-06-14 2016-05-05 United Technologies Corporation Curved plate/fin heater exchanger
US10371053B2 (en) * 2014-02-21 2019-08-06 Rolls-Royce North American Technologies, Inc. Microchannel heat exchangers for gas turbine intercooling and condensing
US20150240722A1 (en) * 2014-02-21 2015-08-27 Rolls-Royce Corporation Single phase micro/mini channel heat exchangers for gas turbine intercooling
EP2910765A1 (en) * 2014-02-21 2015-08-26 Rolls-Royce Corporation Single phase micro/mini channel heat exchangers for gas turbine intercooling
US10316750B2 (en) * 2014-02-21 2019-06-11 Rolls-Royce North American Technologies, Inc. Single phase micro/mini channel heat exchangers for gas turbine intercooling
US20160177829A1 (en) * 2014-02-21 2016-06-23 Rolls-Royce Corporation Microchannel heat exchangers for gas turbine intercooling and condensing
US10605543B2 (en) * 2014-05-12 2020-03-31 Fraunhofer Gesellschaft zur Förderung der angewandten Forschung e.V. Heat transfer device having channels
US20170089647A1 (en) * 2014-05-12 2017-03-30 Fraunhofer Gesellschaft zur Förderung der angewandten Forschung e.V. Heat transfer device and use thereof
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
US20160122024A1 (en) * 2014-11-03 2016-05-05 Hamilton Sundstrand Corporation Heat exchanger
US20190204012A1 (en) * 2018-01-04 2019-07-04 Hamilton Sundstrand Corporation Curved heat exchanger
EP3722722A1 (en) * 2018-01-04 2020-10-14 Hamilton Sundstrand Corporation Curved heat exchanger
US10670346B2 (en) * 2018-01-04 2020-06-02 Hamilton Sundstrand Corporation Curved heat exchanger
US10551131B2 (en) * 2018-01-08 2020-02-04 Hamilton Sundstrand Corporation Method for manufacturing a curved heat exchanger using wedge shaped segments
US20190212074A1 (en) * 2018-01-08 2019-07-11 Hamilton Sundstrand Corporation Method for manufacturing a curved heat exchanger using wedge shaped segments

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