US2874940A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US2874940A
US2874940A US226582A US22658251A US2874940A US 2874940 A US2874940 A US 2874940A US 226582 A US226582 A US 226582A US 22658251 A US22658251 A US 22658251A US 2874940 A US2874940 A US 2874940A
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Prior art keywords
rotor
flow
fluid
channels
grooves
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US226582A
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English (en)
Inventor
Ahlen Karl Gustav
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Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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Priority to US226582A priority Critical patent/US2874940A/en
Priority to FR1060883D priority patent/FR1060883A/fr
Priority to US740017A priority patent/US2980403A/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
    • F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
    • F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/006—Feed-water heaters, i.e. economisers or like preheaters with heating tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L15/00—Heating of air supplied for combustion
    • F23L15/02—Arrangements of regenerators
    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
    • 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
    • Y10S165/135—Movable heat exchanger
    • Y10S165/139—Fully rotatable
    • Y10S165/156—Hollow cylindrical member, e.g. drum
    • Y10S165/159—Hollow cylindrical member, e.g. drum with particular flow path or defined fluid chamber, e.g. annulus, spiral

Definitions

  • the present invention relates to heatxtransfer "and-in its broader aspects has reference toheat transfer between ,heat. exchange at high rates of transfer per unit area' of heat exchanging surface, to provide forsuch transfer with minimum expenditure of power for eflecting relative movement between the heat exchanging bodies and in certain of. its aspects to utilize movement of the solid heat exchanging body to create, in whole or ,in part, there- I quired flow of the fluid or fluids with which the solid body is inheat exchange relation.
  • the invention contemplates the provision of Qrotating solid body in the form of a rotor having a multiplicity of circular fins or ribs with intervening channels inthe -form of grooves concentric with the axis of rotation of the rotor, with which'there is associated a rotationally stationary structure having bafile members projecting into the grooves and cover means for.
  • the grooves for controlling flow of fluid in the grooves such structure further being combined with means providing transfer passages for conducting fluid to and from diflerent grooves inac- 'cordance with novel principles hereinafter more fully described, which result in a novel character of flow which is productive of the improved results sought by the invention.
  • the invention is particularly adapted for heat exchange between two gaseousfiuids'for purposes such as-the pre- .heating of air to be used for combustion, by waste heat extracted from combustion-gases exhausted from; apparatus such as power boilers and internal combustion engines and-gas turbines.
  • the invention will therefore be described hereinafter, by wayof example but Without limitation, as applied to air preheating structure, but it will be understood that the principles of the invention are susceptible of use in many other applications andthat for certain of such applications, the principles of the inven* tion in its broader aspects may be carriedout with only certain features of the structure hereinafter .describedin connection with the air preheater apparatus chosen by way of example.
  • Fig.1 is a more or less diagrammatic longitudinal secof member 30.
  • Fig. 4 is a fragmentary perspective view of part of the structure shown in the precedingzfigures and with certain elements omitted for the sake of clarity;
  • Fig. 5 is a view, similar to' Fig. 3, showing a different structural arrangement of certain of the parts. for producing. an. altered character of. fluid flow;
  • Fig. 6 is afragmentary crosssection taken on the line 6-6 of Fig. 5;
  • Fig. 7 is .afragmentary; perspective view, similar to Fig. 4, of the arrangement shown in Fig 5;
  • Fig. 8 is a view similar to Figs. 3 and. 5 showing an other arrangement of structure for producing fluid flow of different character than that shown in Figs. 3 and 5;
  • Fig. 9 is a fragmentary cross section taken on line 99 ofFig. 8;
  • Fig.. 10' is a. fragmentary longitudinal. section. taken on line 10--.-10 of Fig. 8; I
  • Figill' is a view, similar to Fig. 8, showing structure providing an altered character'of fluid flow as compared with that of Fig. 8;
  • Fig. 12 is a longitudinal.sectionsimilar to'. Fig. lshowing apparatus embodyingthe invention arid having adifplicity of external axially spacedv radialifins or ribs 22,
  • the drum further carries'a multiplicity of similar internal ribs 26 providing a multiplicity of internal annular grooves 28.
  • a rotationally stationary s'tructure comprising a' hollow drumlike internal casing memberindicate'd generally at 30.
  • Member '30 is mounted “coaxiallywiththe' rotor and has a cylindrical casing wall 32 radially spaced'from the inner ends of the internal ribs26. "It further is provided with an inlet 34 at one end and outlets 36 at the other end.
  • the stationary structure further comprises an outer drumlike casing'wall 38surrounding the rotor'and radially spaced from the external ribs 22.
  • the stationary structure further has end walls 40 and 42,-the former extending inwardly past the end wall 16 offtherotor to shaft part 12 of the rotor where aseal 41may' be employed, and the latter extending inwardly to the inlet portion 34
  • An inlet duct 44; for fluid communicates by way of opening 46' at one end of the rotor withthe space 48 between rotor wall 18 and the outer casing 38. This space communicates 'at'the other end of the rotor by way-of an opening 4? with the outlets 50 'and 52.
  • the wall'54 extends inwardly to a seal diagrammatically indicated at '56 and with wall 42 providing an outlet duct ber30 through theinlet 34 and nows in'the direction of arrows 62 through member30. From this space'the'air flows -generallyfrom right to left as vie'wedinFig-l,
  • Hot fluid such as spent combustion gases enters in the direction indicated by arrow 64 through inlet duct 44 and opening 46 to the space 48 between the rotor drum 18 and the outer casing Wall 33.
  • the gas flows generally from left to right as viewed in Fig. 1 through this space in a manner hereinafter to be described and through opening 50 to the outlet duct 52.
  • the wall 32 of member 30 carries a plurality of battle members 66 extending axially of the rotor and peripherally spaced around the circumference of wall 32.
  • These members are of comb-like form having a multip- I licity of fingers 68 projecting into and substantially filling the cross sections of the grooves 28.
  • Similar comb-like bafile members 70 extend inwardly from the outer casing wall 38 and are provided with fingers 72 substantially filling the cross sections of the external rotor grooves 24.
  • a plurality of cover members 74 extend axially in closely spaced relation to the crests of the ribs 22. These cover members are supported by means of partition or guide plates 76 carried by the casing wall 38, as will be more clearly seen from Fig. 3. These partitions extend peripherally from one baffle 70 to the next and comprise oblique central portions 78 overlying the cover members 74 and transverse end portions 80. The end portions 80 of these partitions extend beyond the edges of the cover members to the adjacent baflles and divide the spaces between the edges of the cover plates and the baffles into two series of axially aligned ports between each two adjacent bafiles.
  • ports 82, 82a, 82b and 82c are indicated at 82, 82a, 82b and 82c, and the other is indicated at 84, 84a, 84b and 840, in Figs. 3 and 4.
  • These ports provide communication between the sectors of the grooves 24 between the adjacent battles and the space between the bafiles which lies radially outside the cover 'members or plates 74, the latter space being divided by the partitions into a series of oblique transfer passages as indicated at 86, 86a, 86b and 860 in Figs. 3 and 4,
  • cover plates 88 disposed adjacent to the crests of the inner ribs 26 and series of partitions or guide plates 90 for supporting the cover plates and forming series of ports 92'and 94, and together with the cover plates 88, the inner casing wall 32 and adjacent inner bafiles 66 providing oblique transfer passages 96 Transfer passages 86 and 96 respect to the rotor axis.
  • this gas enters radially a group of grooves 24 through inlet ports 82 distributed around the periphery of the structure. It being assumed that the rotor is turning in the direction indicated by arrow 98 in Fig. 4, friction between the gas and the surface of the moving ribs causes the gas streams in the grooves to move pcripherally in the direction of rotation of the rotor under the cover plate 74 until they are forced radially out of 1 the grooves by the fingers 72 of the bafile members 70, which substantially block or dam the grooves.
  • the character of the flow can be controlled so as to produce a high rate of heat transfer not only because of high relative velocity, but also because of the fact that the absolute velocity of the fluid can be maintained at a sufiiciently low value to prevent turbulence of an undesired nature. If the velocity is sufliciently low, generally laminar flow can be maintained except at the surface layers where small secondary eddies rotating about axes normal to the general line of flow are produced.
  • eddies are desirable from the standpoint of heat transfer and do not create much resistance to flow, and since the grooves are preferably generally relatively deep and narrow, the eddy like turbulence of the surface layers is sufficient to bring most of the fiuid the rate of heat transfer accordingly reduced, but also there may be induced a rotary turbulence in the plane of rotation, which is undesirable. Further, by ejecting the fluid from the grooves after a predetermined length of travel and transferring the fluid to another set of grooves, it is further ensured that all of the fluid in a t given stream or ct-numb is brought into intimate heat exchange relation with heat transfer surfce.
  • the number, spacing and cross sectional shape and area of the grooves may vary widely depending upon the nature of the heat exchange conditions to be met, the character of the fluid or fluids involved, entering temperatures and desired leaving temperatures, volumes to be handled, pressures and other specific factors. These factors will also aifect the length of the paths of flow of the streams in individual grooves, the grouping of the grams, which may, for example be such in an extreme ease, that each group may consist of but a single groove. In the embodiment being described the grooves have, for the sake of simplicity, been shown of equal cross section between equally spaced ribs. It will be evident, however,
  • the ribs may be spaced closer together at the colder end than at. the hot end to compensate for the contraction. 7 h v Also, in apparatus where the path of flow isrelatively long and through a large number of groove sectors, the cumulative eitect of the friction may result in a higher than desired velocity through the apparatus when n a given fluid column travels in all cases through the grooves in the direction ofmovement of the rotor, as illustrated for xample" in Fig. 4.
  • the grooves are preferably relatively deep and narrow and the ratio of depth to width of the grooves may in many, instances be, as much as tengto one, or even materially greater.
  • thejrate of heat transfer in the grooves is improved by the provision of auxiliary guide fingers shown at 102 and .104 in Fig. 2, which fingers extend only partially oi the full depth of the groovesand are located so that they serve to divide and guide the fluid entering and leaving the groove sectors through the respective. inlet and outlet ports.
  • These fingers may beparts er saint, like member similar a; the berfle menses 70 aaaslrpporteatn anysui tablefashidn semis 6 as parish: the siatieaary lsfrncfiire, it being noted that in the present embodiment these guide members rnust be radially spaced m the cylindrical walls 32 an as re; spectively, of the stationary structure since the fluid must flow" across the tops of these guide members :in its flow' between the several ports and the transfer passages.
  • these guide members have been shown, in phantom viewin Fig. 3 and have been omitted from the showing in Fig. 4
  • the number and specific arrangements of the guide fingers at any particular port or series of ports may be varied to suit the individual conditions required in order to obtain a more advan tageous distribution of flow of the fluid throughout the a depth or the groove.
  • inlet ports of greater peripheral extent than that of theoiitlet ports rather than ports of equal area as shown in the apparatus illustrated.
  • the apparatus may also provide all of the power required to create the flow of the fluid media and for example when used as an air preheater may provide the only means required to produce the necessary forced draftflow of the combustion air and also the force required to exhaust the spent combustion gases".
  • Thii's th apparatus may enable separate forced draft and exhaust fans to be eliminated entirely, or 'meterially reduce the power requirements 'for such fans by acting as a compound "fan for both purposes.
  • the stationarystrlicture is arranged so that the fluid columns flow in generan' axial directionfromendto endof the rotors.
  • This arrangement may be varied and in rigs; s to 10, another embodiment is'illustrated in which a different path of flow -forthe air columns is provided.
  • the general arrangement of rotor and stationary structure are as shown in Fig. 1, and corresponding parts are similarly designated.
  • the bafiie members providing the fingers extending into the grooves do not extend from end to end of the rotor but are peripherally offset as indicated at 7021-, 7%, 700-, 7021 and a in Fig. '8.
  • Each of these offset bafiles is coextensive with a group of grooves, the number of which may be chosen at Will, axially coextensive with the baffles.
  • the end walls 110 and 112 of these box like rnernbers define peripherally the limits of the inlet outlet ports communicating with the groove sectors while tite -side walls 1'14'and 11 6 define the aXial extent or ports.
  • auxiliary. guide fingers 10' end 104 are shdw'nand it win be noted that in the present construction these guide fingers can be extended support by the casing parts 38 and 32, respectively,
  • sinee the fl ow through the transfer passage is lengthwise of these guide members rather than across the tops of them, as in the previously described embodiments.
  • the fluid flow iii the grooves is always in the direction of movement of the rotor and for reasons previously explained it may be desirable to provide for counter flow of the fluid in one or more groups of grooves.
  • An arrangement for effecting this is shown in Fig. 11, wherein certain of the baflie members 70 and box members 106 are shown in offset relation such that the direction of flow of the fluid columns is peripherally reversed as indicated by arrows 122.
  • Figs. 12 and 13 the invention is shown embodied in a rotor of different form than that shown in the previously described embodiments.
  • the rotor shaft 200 carries a radially extending disc 202 which in turns supports a multiplicity of radially spaced concentric cylindrical ribs 204 and 206 on the opposite sides of the disc respectively and providing a multiplicity of annular cylindrical channels of groove like form 208 and 210, respectively.
  • the stationary structure indicated at 212 comprises an outer cylindrical shell 214 between which and disc 202 a seal diagrammatically indicated at 216 is provided, and end walls 218 and 220.
  • the structure forms an inlet duct 222 for fluid such as air to be heated, which communicates with the annular space 224 immediately around the rotorshaft on one side of the disc 202.
  • the structure further provides an outlet duct 226 having an annular portion 228 extending around the periphery of the casing adjacent to the end wall 220 and the flow of-air from duct 222 to 226 is generally outward from the central inlet space 224 to the periphery of the rotor duct and the annular duct 228.
  • the end wall 220 carries a plurality of sets of bafile members 230 which provide fingers 232 extending into and substantially damming the grooves 208, the sets of baflles at the same radius being peripherally offset with respect to adjacent sets of baflles at greater radius, as seen more clearly in Fig. 13, and between adjacent baflles of each set are box like cover members 234 which are likewise in sets, with adjacent sets of different radius peripherally offset relative to each other.
  • the structure provides an inlet duct 244 for fluid, such as combustion gases, this duct having an annular portion 246 for distributing the gas to the radially outermost grooves.
  • the casing wall 218 carries baffles 248 provided with fingers 250 extending into grooves 210 and box like cover members 252, similar to the cover members 234 carried by the end wall 220.
  • the arrangement of these baflles and cover members is similar to thatof the structure shown in Fig, 13 and need not be described in detail, the dif ference between the arrangement at the two sides of the disc 202 being that in one case the fluid flow is in generally outward direction while in the other case the flow is in. generally spiral inward direction to the outlet duct 254.
  • this arrangement provides for counter flow.
  • the fluid to be heated, which exands flows outwardly, while the heating fluid which contracts due to being cooled, flows inwardly.
  • the arrangement of the baflles and the cover members may be made so as to provide flow of fluid counter to the direction of rotation of the rotor in as many of the sectors as is desired in order to provide the desired rate of flow.
  • Variation in relative size of inlet and outlet ports and the provision of auxiliary guide fingers are, for the sakepof clarity, omitted from the figures.
  • Other features of design previously described may equally well be applied to the embodiment under con sideration.
  • movement of the rotating body is utilized to induce flow of the fluid or fluids and the rotary movement of the fluid and solid bodies is concurrent.
  • Heat exchange apparatus comprising a rotor having a pluralityof transverse parallel ribs providing a multiplicity of open peripherally continuous circular groovelike channels concentric with the axisof rotation of the rotor for flow of fluid in paths of flow in said channels lying in planes normal to said axis and stationary strueture including inlet and outlet openings for fluid and having a wall concentric with and cooperating with'said rotor to provide for flow of said fluid between said open ings through said channels inheat exchange relation with said rotor, said structure including a plurality of peripherally spaced longitudinal balfles, each baflle having one longitudinal edge abutting said wall and the opposite longitudinal edge having fingers extending into and obstructing said channels to provide a plurality of channel sections in each channel, longitudinally extending cover meahs fors a'id channels disposed peripherally between adjacent baflles, means forming transfer passages connecting different sections of diiierent channelsjat places adjacent to said balfles and at opposite sides of said cover means
  • Heat exchange apparatus comprising a rotor having a "plurality of transverse parallel ribs providing a multiplicity of op'en peripherally continuous circular groovelike channels concentric withthe axis of rotationof the rotor for flow of fluid in paths of flow in said channels lying in planes normal to said axis and stationary structure including inlet and outlet openings for fluid and having a wall concentric with and cooperating with said rotor to provide for flow of said fluid between said openings through said channels in heat exchange relation with the rotor, said structure including longitudinal baffle members, each baifle member having one longitudinal edge abutting said Wall and the opposite longitudinal edge having a series of axial aligned fingers providing bafiles extending into and obstructing a series of said channels, longitudinally extending cover means for said channels disposed peripherally between and peripherally spaced from adjacent baflies to provide ports communicating with the channels adjacent the baflles, means forming transfer passages defined in part by said cover means, connecting ports with diflierent channels at opposite sides of said
  • Heat exchange apparatus comprising a rotor having a plurality of transverse parallel ribs providing a multiplicity of open peripherally continuous circular groovelike channels concentric with the axis of rotation of the rotor for flow of fluid in paths of flow in said channels lying in planes normal to said axis and stationary struceerie-r6 ture including inlet an outlet opening; forfluid and ing a wall concentric with and coeperating with said ro' tor to provide for flow or said fluid between said openings through said channels in heat exchange relation with the rotor, said structure including a plurality of longitudinally peripherally spaced baifles, each bane liav ing one longitudinal edge abutting said wall and the op: posite, longitudinal edge having axially aligned fingers providing baflles extending into and obstructing said chan: nels, longitudinally extending cover means for said chan nels disposed peripherally between and peripherally spaced from adjacent baflles to provide ports communi catingwith
  • Heat exchange apparatus comprising a rotor having a plurality of transverse parallel ribs providing a multiplicity of open peripherally continuous circular groovelikechannels concentric with the axis of rotation of the rotor for flow of fluid in paths of flow in said channels lying in planes normal to said axis and stationary structure including inlet and outlet openings for fluid and having a wall concentric with and cooperating with said rotor to provide for flow of said fluid between said openings through said channels inheat exchange relation with said rotor, said structure including a plurality of longitudinal peripherally spaced sets of baffles, said baffle having one longitudinal edge abutting said wall and the opposite longitudinal edge having fingers extending into and obstructing said channels, the baflles of one set being peripherally offset with respect to the baflies of the adjacent sets, longitudinally extending cover means for said channel's disposed peripherally between andperipherally spaced from adjacent battles of each set to provide port's communicating with the channels adjacent the baflies, means forming transfer passages connecting ports corn
  • Heat exchange apparatus comprising a rotor having a plurality of transverse parallel ribs providing a multiplicity of open peripherally continuous circular groove-hire channels concentric with the axis of rotation of the rotor for flow of fluidin paths of flow in said channels lying in planes normal to said axis and stationary structure including inlet and outlet openings for fluid and having a wall concentric with and cooperating with said rotor to provide for flow of said fluid between said opening through said channels in heat exchange relation with said rotor, said structure including a plurality of longitudinal peripherally spaced sets of bafiles, said baffies having one longitudinal edge abutting said wall and the opposite longitudinal edge having fingers extending into and obstructing said channels, the baffles of one set being peripherally olfset with respect to the baflles of the adjacent sets, longitudinally extending cover means for said channels disposed peripherally between and peripherally spaced from adjacent baflles of each set' to provide ports communicating with the channels adjacent the baflles, means forming transfer passages
  • Heat exchange apparatus comprising a rotor having a wall and a plurality of transverse ribs extending from the opposite sides of said wall to provide on each side. of the wall a series of peripherally vcontinuous open groove-like circular channels concentric with the axis of rotation of the rotor, stationary means including inlet and outlet openings for fluid and having walls concentric with and cooperating with said rotor to provide for flow of fluid in paths of flow in said channels between said openings lying in planes normal to said axis, said stationary means including longitudinal baflles, certain of said baflles having one longitudinal edge abutting one of said last named walls and the other of said baflles having one longitudinal edge abutting the other of said last named walls and the opposite longitudinal edges of said baflles having fingers extending into and obstructing said channels, longitudinally extending cover means for said channels disposed between adjacent bafiles, means forming transfer passages connecting difierent channels at places adjacent to said baflles and at opposite sides of said cover means for
  • Heat exchange apparatus comprising a rotor hav ing a wall and a plurality of transverse ribs extending from the opposite sides of said wall to provide on each side of the wall a series of peripherally continuous open groove-like circular channels concentric with the axis of rotation of the rotor, stationary means including inlet and outlet openings for fluid and having walls concentric with and cooperating with said rotor to provide for flow of fluid in paths of flow in said channels between said openings lying in planes normal to said axis, said stationary means including a plurality of longitudinal peripherally spaced baffles, certain of said baffles having one longitudinal edge abutting one of said last named walls and the other of said bafiies having one longitudinal edge abutting the other of said last named walls and the opposite longitudinal edges of said baflies having fingers extending into and obstructing each of said channels to divide the same into a plurality of sections, longitudinally extending cover means for said channels disposed between adjacent baflles, means forming transfer passages connecting different sections of said
  • Heat exchange apparatus comprising a rotor drum having a plurality of transverse open circular groovelike channels concentric with the axis of rotation of the drum and providing for flow of fluid in paths of flow 12 in said channels lying in planes normally to said axis, said channels comprising a first series of inner channels extending radially inwardly from the wall of the drum and a second series of outer channels extending radially outwardly from the wall of the drum with said wall defining the bottoms of both series of channels, stationary structure including inlet and outlet openings for fluid and having inner and outer walls concentric with and cooperating with said drum to provide for flow of fluid in paths of flow in said inner and outer channels between said openings, said stationary structure including longitudinal inner and outer bafiles, said inner baflles having one longitudinal edge abutting said inner wall and the opposite longitudinal edge having fingers extending into and obstructing said inner channels, said outer baflles having one longitudinal edge abutting said outer wall and the opposite longitudinal edge having fingers extending into and obstructing said outer channels
  • a structure as defined in claim 9 in which said transfer passages are arranged for flow of each of the fluids from channel to channel progressively of the length of the drum and in countercurrent relation with respect to each other lengthwise of the drum.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US226582A 1951-05-16 1951-05-16 Heat exchanger Expired - Lifetime US2874940A (en)

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US226582A US2874940A (en) 1951-05-16 1951-05-16 Heat exchanger
FR1060883D FR1060883A (fr) 1951-05-16 1952-05-15 Dispositif de transfert de chaleur
US740017A US2980403A (en) 1951-05-16 1958-06-05 Heat transfer

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2995344A (en) * 1959-02-12 1961-08-08 Parsons C A & Co Ltd Plate type heat exchangers
US3027314A (en) * 1956-11-28 1962-03-27 Parsons C A & Co Ltd Heat transfer surfaces
US3137637A (en) * 1957-10-21 1964-06-16 Parsons C A & Co Ltd Fuel elements for nuclear reactors
US3179570A (en) * 1959-08-13 1965-04-20 Commissariat Energie Atomique Thermal exchange of the fuel elements in nuclear reactor
US3207673A (en) * 1957-09-27 1965-09-21 Parsons C A & Co Ltd Nuclear reactor fuel element having improved fin structure
US20170072766A1 (en) * 2015-09-11 2017-03-16 Denso International America, Inc. Air conditioning system having cylindrical heat exchangers

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3260652A (en) * 1955-10-25 1966-07-12 Parsons C A & Co Ltd Tubular heat exchange element

Citations (9)

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GB252373A (en) * 1925-05-19 1927-04-14 Simmon Maschf Hans Process and apparatus for the exchange of heat between gaseous, vapour like or liquid bodies
US1639051A (en) * 1925-12-05 1927-08-16 Munday Reginald Luther Heat-exchange apparatus
US1698313A (en) * 1927-03-04 1929-01-08 Firm G Polysius Device for utilizing the heat radiated from kilns
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US1897613A (en) * 1930-03-12 1933-02-14 Jensen Aage Apparatus for treating liquids
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US2369993A (en) * 1943-12-17 1945-02-20 Gen Electric Fluid heater
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US1914084A (en) * 1931-03-18 1933-06-13 Ellis Herbert Walter Apparatus for cooling oils or other fluids
GB500389A (en) * 1937-11-16 1939-02-08 British Leyland Motor Corp Improvements in and relating to tubular heat exchangers for fluids
US2402307A (en) * 1942-04-28 1946-06-18 Vannerus Torbjorn Recuperative heat exchanger for gaseous media
US2369993A (en) * 1943-12-17 1945-02-20 Gen Electric Fluid heater

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US3027314A (en) * 1956-11-28 1962-03-27 Parsons C A & Co Ltd Heat transfer surfaces
US3207673A (en) * 1957-09-27 1965-09-21 Parsons C A & Co Ltd Nuclear reactor fuel element having improved fin structure
US3137637A (en) * 1957-10-21 1964-06-16 Parsons C A & Co Ltd Fuel elements for nuclear reactors
US2995344A (en) * 1959-02-12 1961-08-08 Parsons C A & Co Ltd Plate type heat exchangers
US3179570A (en) * 1959-08-13 1965-04-20 Commissariat Energie Atomique Thermal exchange of the fuel elements in nuclear reactor
US20170072766A1 (en) * 2015-09-11 2017-03-16 Denso International America, Inc. Air conditioning system having cylindrical heat exchangers
US10086674B2 (en) * 2015-09-11 2018-10-02 Denso International America, Inc. Air conditioning system having cylindrical heat exchangers

Also Published As

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