US3814171A - Stationary heat exchanger - Google Patents

Stationary heat exchanger Download PDF

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Publication number
US3814171A
US3814171A US00211089A US21108971A US3814171A US 3814171 A US3814171 A US 3814171A US 00211089 A US00211089 A US 00211089A US 21108971 A US21108971 A US 21108971A US 3814171 A US3814171 A US 3814171A
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US
United States
Prior art keywords
heat exchanger
heat
plates
heat radiating
passages
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 - Lifetime
Application number
US00211089A
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English (en)
Inventor
K Nakamura
Y Kondo
M Kuroyanagi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Toyota Motor Corp
Toyota Central R&D Labs Inc
Original Assignee
Toyota Motor Corp
Toyota Central R&D Labs Inc
NipponDenso Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Toyota Motor Corp, Toyota Central R&D Labs Inc, NipponDenso Co Ltd filed Critical Toyota Motor Corp
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Publication of US3814171A publication Critical patent/US3814171A/en
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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
    • F28D9/00—Heat-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
    • F28D9/0012—Heat-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
    • F28D9/0018—Heat-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
    • Y—GENERAL 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/357—Plural plates forming a stack providing flow passages therein forming annular heat exchanger
    • Y10S165/358—Radially arranged plates

Definitions

  • the recuperative stationary heat exchanges which have commonly been used heretofore are classified into a tube bank type consisting only of tubes and a tube-fin type consisting of a combination of tubes and fins. These types of heat exchangers are further classitied into a parallel flow type, a perpendicular flow type and a counterflow type according to the flow directions of fluids.
  • the tube bank type and tube-fine type heat exchangers have the disadvantage that, because of a large restriction imposed on the inner and outer heat transfer areas, the types of the inner and outer fluids are subjected to a limitation.
  • the counterflow type heat exchanger has the disadvantage that, since different fluids are passed in opposite directions to each other, a complex and large-sized mechanism is required for preventing the fluids from mixing with each other and further much labor and time are required for manufacture.
  • the present invention has for its object the provision of a stationary heat exchanger which comprises an annular heat exchanger unit composed of a number of corrugated plates arranged radially in juxtaposed relation so as to define independent radial passages between each other, means for passing fluid in every other ones of said passages from the outer periphery toward the center of said annular heat exchanger unit and means for passing different fluid in the other every other ones of said passages from the center toward the outer periphery of said annular heat exchanger unit; and which, therefore, enables the heat transfer area of said corrugated plates to be freely adjusted, any combination of fluids to be used, the heat transfer capacity per unit area to be increased, and the incoming and outgoing fluids to-be positively separated by a very simple mechanism, and can be easily manufactured.
  • FIG. I is an overall view of an embodiment of the stationary heat exchanger according to the present invention. with the half portion in vertical section briefly showing the construction thereof;
  • FIG. 2 is an elevational view as viewed from the left side of FIG. 1;
  • FIG. 3 is a fragmentary perspective view showing the front portions of the heat exchanger unit and gas guide unit;
  • FIGS. 4(A 4(8), 4(C), 4(D) and 4(E) are fragmen-
  • FIG. 7 is a fragmentary perspective view of the protective ring member
  • FIG. 10 is a fragmentary perspective view of the rear portions of the heat exchanger unit and the gas guide unit;
  • FIG. 11 is a fragmentary enlarged transverse sectional view of the gas guide unit taken along the line XI- Xl of FIG. 1;
  • FIG. 12 is a fragmentary perspective view of another form of the connection between the heat exchanger unit and the gas guide unit;
  • FIGS. 13 and 14 are fragmentary vertical sectional views showing other forms of the gas guide unit respectively.
  • the heat exchanger comprises a heat exchanger unit 1 composed of a plurality of corrugated heat radiating plates having convexes and concaves of a rectangular sectional shape on both sides thereof and radially arranged in juxtaposed relation so as to define radial passages between each other, and a gas guide unit 2 for leading low temperature high pressure air into every other ones of said radial passages and leading to the outside high temperature low pressure gas emerging from the other every other ones of said passages.
  • the low temperature high pressure air is, for example, air supplied from the blower to the combustor of a gas turbine engine
  • the high temperature low pressure gas is, for example, the combustion gas generated in the combustor upon combustion of fuel with said low temperature high pressure air and discharged through the turbine.
  • the heat exchanger further comprises a gas guide unit 3 for leading the high pressure air.
  • the heat exchanger unit 1 is composed of a plurality of radial heat radiating elements radially arranged in juxtaposed relation as shown in FIG. 1.
  • Each heat radiating element is composed of heat radiating plates 10, 11, 13 and 14.
  • the heat radiating plates 10, 11 are corrugated by pressing was to form convexes and concaves of a rectangular sectional shape on both sides thereof and welded together with a reinforcing plate 12 interposed therebetween, in such a manner that the convexes of the respective plates 10, ll confronting each other.
  • the heat radiating plates 10, 11 are respectively welded to the heat radiating plates l3, 14 of the adjoining heat radiat- 3 ing elements.
  • the heat radiating plates 13, 14 are shaped in the same manner as theheat radiating plates 10, Hand the pitch or the interval l-I of the convexes thereof is equal to the interval H, of the convexes of the latter.
  • the heat radiating plates 10, ll, 13 and 14 when connected together in the manner described above have the appearance and cross section as shown in FIGS. 4(C) and 5. As seen, the heat radiating plates 10, 11 and the reinforcing plate 12 define air passages 15, and the heat radiating plates 10,11 and 13, 14 define gas passages 16.
  • the heat radiating element thus constructed further define gas passages 17 between it and the adjoining heat radiating element.
  • the radiallyoutward ends a, 11a of the heat radiating plates 10, 11 are tapered as shown in FIG. 4(B), thereby to determine the flow directions of the low temperature high pressure ai-r' and the high temperature low'pressure combustion gas passing through the heat'exchanger unit as will be described later.
  • the radially inward ends 100 lie of the heat radiating plates 10, ll
  • the gas guide unit 3 is composed of a plurality of adjoining guide elements.
  • Each guide element as shown in FIG. 4(E), is composed of a pair of guide plates 24,
  • the gas guide unit 2 is composed of a plurality of gas guide elements, each for each heat radiating element, arranged circularly in juxtaposed relation around the heat exchanger unit 1.
  • Each gas guide element is composed of a 'pair of trapezoidal guide plates 18, 19 welded at their lower edges 18a, 19a to the tapered edges 110b, llb-of the heat radiating plates 10, 11 by butt resistance welding.
  • the oblique edges 18b, 19b of the guide plates 18, 19 are bent outwardly of each other with a small curvature by pressing, while the other oblique edges 18c, 19c (FIG. -10) are bent inwardly of each other with a small curvature.
  • the guide plates 18, 19 are'gently corrugated such that each of them has a wavy sectional shape of a small curvature on the cross section taken on the line Vl-Vl of FIG. 1.
  • the guide plates 18, 19 are welded together at the oblique edges 18c, 190, the flat edges l8d,'l9d and'the end edges 18e, l9e and 18e, l9-'e, concurrently with the welding'of the heat radiating plates 10, 11, with an extension 12a of the reinforcing plate 12 interposed therebetween by butt resistance welding in such a manner that the recessed and projecting portions of the guide plate 18 register with the recessed and projecting portions of the guide plate 19 respectively as shown in FIGS. 3 and 4.
  • air inlet openings 20 and air inlet passages 21 of an elliptical cross section are formed as shown in FIG. 6.
  • the passagesZl extend obliquely downwardly toward the right as viewed in FIG. 3 and communicate with each other at their lower ends and also communicate with the air passage of a the heat exchanger unit 1.
  • the low temperature high pressure air flowing into the air inlet openings of the gas guide unit 2 passes in the passages 21 and then passes uniformly in the air passages 15 of the heat exchanger unit 1.
  • the gas guide unit 2 is closed at the oblique edges 18c, 19c ofthe guide plates l8, 19 as shown in FIG. 10.
  • FIGS. 3 and 10 show two of the heat radiating unit of the construction described previously. As seen, the heat radiating plate 13 of one element is slightly spaced from the heat radiating plate 14' of the adjacent element to form a passage 17, and the oblique edge 1&-
  • One edges 24a, 25a of the guide plates 24, 25 are welded to the edges 1011,1111 of the heat radiating plates-10, 11 respectively and'the opposite end edges 24b, 25b and 24c, 25c thereof are welded together respectively with the extension 12b of the reinforcing plate 12 interposed therebetween, by butt resistance welding (FIG. 10).
  • the guide plates 24, 25 are corrugated suchthat a wavy sectional shape ofa small curvature appears on the cross section-taken on the line B-B of FIG. 1. Therefore, it .willbeunderstood that elliptical spaces are formed between the guide plates 24, 25 as shown inFIGS. 4(E) and 11.
  • the air passages 1 5'of the heat exchanger unit l communicate with the spaces '26. This is the case forany heat radiating ele-' ment.
  • an outwardly bulged lower edge portion 24d of the guide plate 24 and an outwardly bulged lower edge portion 25'd of the adjacent guideplate 25' are welded together as shown in FIG. 9. Therefore, a space 27 is formed between the guide plates 24 and 25 asshown in FIGS. 3 and 4(E). This is the case for any adjacent heatradiating elements.
  • the aforesaid spaces 26 communicate with the central hollow ,portion 8 of the. heat exchanger and the spaces 27 communicate with the low pressure high temperature gas inlet opening 7 at one endsand with the gas passages 16,17 of the heat exchangerunit 1 at the other ends thereof.
  • a continuous flange 41 formed by projecting portions 39 (FIGS. 3 and 4) of the respective guide elements of the gas guide unit 2 is shaped by pressing into a flange 41 shown in FIG. 7 and an annular protective ring 43 is secured to said flange 41' by resistance welding. Further, O-rings 44, 45 (FIG.
  • Reference numeral 46 designates an annular bellows made from a sheet of a heat resisting material, e.g., a thin sheet of stainless steel, and having one end secured to the sealing plate 32 as by welding, with the other end secured to a flange 6a of the conduit 6 by means of bolts or welding. This bellows 46 serves to prevent a leakage of the low temperature high pressure air passing in the conduit 6 toward the gas guide unit 2.
  • Reference numeral 47 designates anotherannular bellows also made from a thin sheet of stainless steel having one end secured to the sealing ring 38 as by welding, with the other end secured a flange member 49 which is connected to the conduit 4 through a packing 48.
  • This annular bellows 47 serves to prevent a leakage of the high temperature low pressure combustion gas, passing in the gas inlet 7 toward the spaces 27 of the gas guide unit 3, into the conduits 4, 6 and the hollow portion 8.
  • Reference numeral 51 designates still another annular bellows made, for example, from a thin sheet of stainless steel and having one end secured to the sealing plate 34 as by welding, with the other end secured to a flange member 54 by welding, which flange memberis connected to a conduit 52 through a packing 56.
  • This annular bellows 51 serves to prevent a leakage of the heated high pressure air, flowing into the hollow portion 8, into the-conduit 5 and a leakage of the low pressure high temperature combustion gas,
  • the heat exchanger of the invention constructed as described above operates as follows: Namely, when the low temperature high pressure air generated by the compresser of the gas turbine engine is supplied into the conduit 6, it flows obliquely into the air inlet openings 20 from the outer periphery of the gas guide unit 2 and thence into the passages 21.
  • the air inlet openings 20 are formed slantingly between the oblique edges 18!). .1917 of the guide plates 18, 19 and said oblique edges 18h. 1912 are expanded outwardly of each other as stated above. Therefore, the air inlet openings 20 have a relatively large area and the introduction of the high pressure air is facilitated.
  • the guide plates 18, 19 respectively have a wavy cross section and are welded to the extension 12a of the reinforcing plate 12. Therefore, these guide plates have a large mechanical strength and will not be subjected to a deformation under the pressure of the low temperature high pressure air.
  • the low temperature high pressure air passing in the passages 21 flows into the air passages 15 in the heat exchange unit 1 while being guided by the tapered edges 10a, 11a of the heat radiating plates 10, 11 and, after passing through said air passages 15, flows into the spaces 26 in the gas guide unit 3 while being guided by the tapered edges 10c, 11c on the downstream side of the heat exchanger unit 1, and then flows into the central hollow portion 8 to be discharged axially in the direction opposite to the cover 9.
  • Such flow of the low temperature high pressure air is indicated by the arrows C in FIG. 1.
  • the high temperature low pressure combustion gas passes in the gas passages 16, 17 of the heat exchanger unit 1 in the opposite direction to the flow direction of the air as described later, and gives the heat possessed thereby to said air.
  • the so-called heat exchange takes place between the low temperature high pressure air and the high temperature low pressure combustion gas through the heat radiating plates 10, 11, 13, 14.
  • the heat exchanging ratio in this case is extremely high because the low temperature high pressure air and the high temperature low pressure combustion gas flow adjacent each other and in opposite directions to each other.
  • the high temperature low pressure combustion gas discharged from the gas turbine engine flows axially into the spaces 27 in the gas guide unit 3 as indicated by the arrow F in FIG. 1. Since one end of the gas guide unit 3 is closed by the annular plate 34, the combustion gas passing in the spaces 27 is directed into the gas passages 16, 17 in the heat exchanger unit 1 by being guided by the tapered edges 10c, of the heat radiating plates 10, 11. The combustion gas thus passing in the gas passages 16, 17 gives the heat to the air passing in the air passages 15 as described above and then flows into the spaces 22 in the gas guide unit 2 by being guides by the tapered edges 10a, 11a of the heat radiating plates 10, 11, to be discharged to the outside from the discharge openings 23. Such flow of the high temperature low pressure combustion gas is indicated by the arrows F in FIG. 1.
  • the high pressure air and the combustion gas respectively flow along independent paths completely isolated from each other and pass through the heatexchange unit 1 in the opposite directions to each other and in adjacent relation to each other. Therefore, the low temperature high pressure air is heated very effectively and the heated air is supplied the combustor of the gas turbine engine provided, for example, in the central hollow portion 8 of the heat exchanger.
  • the tapered edges 10b, 11b of the heat radiating plates 10, 11 of the heat exchanger unit are connected with the edges 18a, 19a of the guides plates 18, 19 of the gas guide unit 2, and the tapered edges 10d, 11d of the former tov the edges 24a, 25a of the guide plates 24, 25 of the gas guide unit 3 respectively, by but resistance welding.
  • the corrugation of the heat radiating plates 10, ll, 13, 14 is not necessarily restricted to a rectangular shape but an arcuate shape in cross section.
  • the guide plates l8, 19 of the gas-guide unit 2 may be combined with the extension 12a of the reinforcing plate interposed therebetween such that the convexes and concaves thereof are respectively parallel to each other as shown in FIG. 13, and obviously the guide plates 24, 25 of the gas guide unit 3 may be combined likewise as shown in FIG. 14.
  • a method may be employed which comprises preparing a die ofa shape complementary to the unitary piece forming a metal layer on said die by electric casting which is a sort of plating method and removing the metal layer from said die when the thickness of said metal layer has reached a desired value.
  • brazing or soldering may be used, instead of resistance welding, for mechanically coupling the gas guide unit 2, the heat exchanger unit 1 and the gas guide unit 3 with each other. The resistance welding is preferably carried out continuously, for example, by using the discharge current of a capacitor.
  • the heat exchanger unit is composed of a plurality of corrugated plates radially arranged in juxtaposed relation so as to form independent radial passages between each other, and fluid is passed in every other ones of said passages radially inwardly from the outer periphery of the heat exchanger unit, while different fluid ispassed in the other every other ones of said passage radially outwardly from the center of the heat exchanger unit.
  • the heat transfer area can be freely adjusted. Therefore, the heat exchanger of the invention can be used with any combination of fluids and particularly advantageously used for the heat exchange between air and air such, for example, as in a gas turbine engine, which requires a large heat transfer area on each side of a heat radiating plate.
  • two kinds of fluid between which it is desired to exchange heat are passed counterflowwise on both sides of one corrugated heat radiating plate.
  • corrugated heat radiating plates are radially arranged in juxtaposed relation, enables such a remarkable advantage to be obtained that the heat transfer effect per unit area of the heat radiating plate can be increased far greater than in the conventional parallel flow type and perpendicular flow type ones of tube bank type and tubefin type heat exchangers, and consequently the heat exchanger of the invention can be very small in size with a minimum dead 'space therein, as compared with the conventional ones for the same heat exchanging capacity.
  • the radially opposite ends of the corrugated heat radiating plates are respectively tapered to form flat portions which define the radially opposite ends of the independent radial passages between each other. Therefore, the fluid flowing into one passage and the fluid flowing out of the adjacent passage can be separated positively and by a simple structure. Further, the aforesaid tapered flat portions give no resistance to thefluid flowing into or out of the passages, providing for a smooth uniform flow of fluid.
  • the tapered flat portions at the radially opposite ends of the corrugated heat radiating plate can be shaped by a single pressing operation, which makes the fabrication of the plate very simple and easy.
  • a stationary heat exchanger comprising a heat exchanger unit mounted in a housing having means for passing fluids therethrough for a gas turbine engine, said heat exchanger unit including a plurality of heat radiating elements arranged in juxtaposed relation, each said element being composed of space corrugated heat radiating plates forming convexes and concaves of rectangular section and a reinforcing plate interposed therebetween, said heat radiating plates defining independent and adjacent passages between each other, means for leading fluid into every other ones of said passages from the outer periphery of said heat exchanger unit to pass it radially inwardly therein including a plurality of first guide plates, each attached to said heat radiating plates and means for leading another fluid into the rest of said passages from the central portion of said heat exchanger-unit to pass it radially outwardly therein including a plurality of second guide plates, each attached to said heat radiating plates the opposite ends of said corrugated plates respectively being tapered to form flat portions for separating two kinds of fluids.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00211089A 1970-12-26 1971-12-22 Stationary heat exchanger Expired - Lifetime US3814171A (en)

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JP45128995A JPS4828189B1 (fr) 1970-12-26 1970-12-26

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5060721A (en) * 1990-05-29 1991-10-29 Solar Turbines Incorporated Circular heat exchanger
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
US20050129593A1 (en) * 2002-03-26 2005-06-16 Masatoshi Hotta Reaction appparatus with a heat-exchanger
WO2005045345A3 (fr) * 2003-10-28 2005-11-03 Capstone Turbine Corp Construction d'un recuperateur pour moteur a turbine a gaz
US20130199152A1 (en) * 2012-02-03 2013-08-08 Pratt & Whitney Canada Corp. Turbine engine heat recuperator plate and plate stack

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3131091A1 (de) * 1981-08-06 1983-02-24 Klöckner-Humboldt-Deutz AG, 5000 Köln Ringfoermiger rekuperativer waermetauscher

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1811455A (en) * 1926-04-10 1931-06-23 George C Cook Regenerative air preheater
US3203455A (en) * 1961-02-20 1965-08-31 Marryat & Place Ltd Syringe for injecting small measured volumes of liquid

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1811455A (en) * 1926-04-10 1931-06-23 George C Cook Regenerative air preheater
US3203455A (en) * 1961-02-20 1965-08-31 Marryat & Place Ltd Syringe for injecting small measured volumes of liquid

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5060721A (en) * 1990-05-29 1991-10-29 Solar Turbines Incorporated Circular heat exchanger
US20050129593A1 (en) * 2002-03-26 2005-06-16 Masatoshi Hotta Reaction appparatus with a heat-exchanger
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
WO2005045345A3 (fr) * 2003-10-28 2005-11-03 Capstone Turbine Corp Construction d'un recuperateur pour moteur a turbine a gaz
US7065873B2 (en) 2003-10-28 2006-06-27 Capstone Turbine Corporation Recuperator assembly and procedures
US20060137868A1 (en) * 2003-10-28 2006-06-29 Yungmo Kang Recuperator assembly and procedures
US7147050B2 (en) 2003-10-28 2006-12-12 Capstone Turbine Corporation Recuperator construction for a gas turbine engine
US7415764B2 (en) 2003-10-28 2008-08-26 Capstone Turbine Corporation Recuperator assembly and procedures
US20130199152A1 (en) * 2012-02-03 2013-08-08 Pratt & Whitney Canada Corp. Turbine engine heat recuperator plate and plate stack
US9359952B2 (en) * 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack

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Publication number Publication date
DE2162888A1 (de) 1972-07-06
JPS4828189B1 (fr) 1973-08-30

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