US3910344A - Regenerator matrix - Google Patents

Regenerator matrix Download PDF

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Publication number
US3910344A
US3910344A US455047A US45504774A US3910344A US 3910344 A US3910344 A US 3910344A US 455047 A US455047 A US 455047A US 45504774 A US45504774 A US 45504774A US 3910344 A US3910344 A US 3910344A
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United States
Prior art keywords
strip
corrugations
matrix
axis
strips
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
US455047A
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English (en)
Inventor
Robert J Hagen
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.)
Motors Liquidation Co
Original Assignee
Motors Liquidation Co
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.)
Filing date
Publication date
Application filed by Motors Liquidation Co filed Critical Motors Liquidation Co
Priority to US455047A priority Critical patent/US3910344A/en
Priority to CA218,630A priority patent/CA999288A/en
Priority to DE19752512358 priority patent/DE2512358A1/de
Priority to GB1167175A priority patent/GB1440748A/en
Priority to IT48771/75A priority patent/IT1032448B/it
Priority to JP50035661A priority patent/JPS50130047A/ja
Application granted granted Critical
Publication of US3910344A publication Critical patent/US3910344A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28D19/041—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 with axial flow through the intermediate heat-transfer medium
    • F28D19/042—Rotors; Assemblies of heat absorbing masses

Definitions

  • ABSTRACT A matrix disk for a rotary regenerator is made up of 52 U.S. c1. 165/10 Spiral mm of a first strip having Spaced apart Comb [51] Int.
  • This invention relates to a matrix disk for a rotary regenerator heat exchange apparatus and, in particular, to a regenerator matrix of the axial-flow or disk type.
  • Rotary regenerators particularly of the axial-flow type, utilize heat transfer means in the form of a porous 1 metal or ceramic disk matrix which is rotated so that each element thereof passes successively through two aeriform fluid flow paths, absorbing heat from a hotter fluid and releasing it to a cooler fluid in these flow paths.
  • Metal matrices ordinarily are made up of a crimped or corrugated metal sheets spirally wound into a disk and then brazed or otherwise bonded together so as to provide a rigid cellular or porous structure.
  • regenerators of the sort to which this invention is particularly applicable the major portion of the disk is heated to relatively high temperatures of the order of up to l450F. or higher, whereas the rim or radially outermost portion of the disk is contacted around the perimeter by the relatively cool air and thus is at substantially lower temDerature.
  • Other factors may cause temperature gradients but, in general, whatever the reasons for the difference in temperature between different radial zones of the matrix, the result is differential expansion with attendant overstressing and yielding of the parts and resulting cracking.
  • substantial separation in a generally radial plane has been observed in operation of metallic rotary regenerator matrices.
  • the corrugations will not match uniformly and the successive layers of the matrix will not stack in a proper spiral path.
  • the peaks of the corrugations of the sheets will be aligned to provide a large separation where at its other points the peaks of one sheet will fall into the valleys of the other so that the separation is insufficient and, of course, the winding is not close to a uniform spiral.
  • a still further object of this invention is to provide a matrix structure with circumferentially orientated rectangular flow passages thereby reducing stresses in matrix flow passage walls caused by pressure differentials between flow passages, as well as by seal contact loads.
  • FIG. 1 is a schematic view of an axial-flow rotary regenerator taken in a plane containing the axis of rotation of the matrix thereof;
  • FIG. 2 is an enlarged, end face view of a portion of the heat exchange material of the matrix of FIG. 1 constructed in accordance with the invention with the stack of spirally wound sheets forming the heat exchange material straightened to more clearly show the configuration of these sheets;
  • FIG. 3 is an end face view of the heat exchange material of the matrix of FIG. 1 showing the spiral winding of the sheet layers thereof;
  • FIGS. 4, 4a and 4b show the various configurations assumed by a corrugation of a sheet layer of the matrix, FIG. 4 showing the corrugation as manufactured, FIG. 4a showing the corrugation under compressive load and FIG. 4b showing the corrugation under tensile load.
  • a rotary regenerator heat exchange apparatus which includes a housing 10, generally drum-shaped, to enclose an axialflow matrix 12 which is of such construction so as to define a multiplicity of pores or passages 14, greatly enlarged in FIG. 1, extending from face to face of the matrix generally parallel to the axis of rotation defined by a matrix locating and driving shaft 16.
  • Shaft 16 is suitably journalled in the boss 18 of the housing 10 and terminates in a spider 20 which is coupled to the matrix by means, not illustrated, which may be of the type described in U.S. Pat. No. 3,476,173 entitled Rotary Regenerator Matrix Mount and Drive issued Nov. 4, 1969 to Joseph W. Bracken, .Ir., and William S. Hubble, so that the matrix may be rotated slowly.
  • the matrix could alternately be driven through a rim drive, not shown.
  • the matrix preferably includes a non-porous hub or inner rim 22 and an outer, non-porous, cylindrical rim 24, but such rims are not essential, and a body of heat exchange material 26 made up of metal strips wound to form a disk having parallel faces and pervious to flow generally parallel to the axis of the disk.
  • a generally cylindrical space 28 is defined within the interior of the matrix and a space 30 extends around the periphery of the matrix within the housing 10.
  • An inlet 32 for cool high pressure air enters one face of the housing and, opposite to it, an outlet 34 is provided for the discharge of compressed air which is heated after having passed through the matrix.
  • I-Iot low pressure exhaust gases enter through an inlet 36 and leave the regenerator through an outlet 38, the two streams being thus in counterflow relation in the embodiment of the regenerator illustrated.
  • the hot gas passage is of larger area than the cool air passage because of the difference in density between these fluids. Since the exhaust gases entering through the inlet 36 engage first the upper face of the matrix, as seen in FIG. 1, this is the hot side, while the lower face of the matrix is then referred to as the cold side.
  • a sealing means or seal assembly 40 is provided be tween each face of the matrix and the housing to confine the cold and hot fluids to the desired flow paths through the matrix from inlet to outlet and to minimize leakage between the paths.
  • the heat exchange body 26 of matrix disk 12 is, in accordance with the invention, made up of alternating corrugated strips 50 and 60 wrapped spirally around the hub 22, this spiral wrapping being shown in FIG. 3, to form, in effect, a spirally wound stack of alternating corrugated strip layers 50 and 60, the corrugations in adjacent layer strips being orientated at different angles.
  • the corrugations on each of the strips extend out from one side only thereof, the opposite side of each strip presenting substantially a flat surface against which the peaks of the corrugations of the adjacent strip abut to define the flow passages 14 through the matrix disk.
  • the strip 50 is formed with spaced apart, deep, narrow ribs or corrugations 52 with flat sheet or non-corrugated portions 54 therebetween.
  • the corrugations 52 typically are substantially triangular in cross section with an open gap S at the base and each of these corrugations are inclined in the same direction relative to the edges of the strip and thus to the faces of the finished matrix disk.
  • Strip 50 as seen in FIG. 2, can be considered to have left-hand corrugations 52.
  • Strip 60 is also formed with spaced apart ribs or corrugations 62 with flat or non-corrugated portions 64 therebetween.
  • Corrugations 62 are also typically substantially triangular in cross section with a gap S at the base thereof with each corrugation inclined in the same direction relative to the edges of the strip, but in the opposite direction to those of strip 50, and thus this strip 60 can be considered to have right-hand corrugations, as viewed in FIG. 2.
  • both the corrugations 52 and 62 of strips 50 and 60 are inclined at an acute angle to the axis of the matrix disk.
  • the corrugations 52 and 62 of the strips 50 and 60 may be formed at any desired acute angle relative to the axis of the matrix, but opposite each other, and preferably this angle should be chosen so as not to greatly restrict the flow of the fluid in a direction generally parallel to the axis of the matrix disk. However, the angle should be sufficiently large to ensure that the peak of a corrugation of one sheet cannot enter the valley of a corrugation of the next adjacent sheet in the event that these corrugations are somewhat radially aligned as a result of spiral winding of the strips. Of course, by maintaining the gap S at the base of a corrugation as small as possible, the chance that this will occur is also greatly reduced.
  • opposite orientation of the corrugations in adjacent strips serves to prevent nesting of the elements which would result if the corrugations in each were parallel, particularly if the gap S is substantial. Maintaining a minimum gap 5 is also desirable as this will produce more perfect rectangular flow passages 14 between adjacent strips.
  • the angular orientation of the corrugations of the strips 50 and 60 serves to reduce the effective unsupported span of the adjacent strip with which it cooperates, a result which would occur if the corrugations of these strips were parallel to the axis of the matrix.
  • This angular orientation of the corrugations provides a degree of radial rigidity in the resulting structure and will provide support for the previously spiraled sheets during assembly.
  • the distance for pitch P between corrugations may be selected, as desired, but it should be realized that this pitch distance should be chosen so that when the strips are spirally wound, the sheet does not traverse a full convolution pitch P so that a degree of radial flexibility is maintained. However, it has been found that a measure of radial flexibility can be maintained even if ribs traverse more than a full convolution pitch since alignment of the ribs in subsequent wraps is random.
  • the peaks of the corrugations on one sheet should engage the flat portions of the adjacent sheet, but since these sheets are spirally wound to form the matrix disk, which may be about 2 feet overall in diameter and about 3 inches thick, with the individual sheets forming the heat exchange portion being, for example, of stainless steel, approximately 0.002 inch thick with corrugations in the order of, for example, about 0.13 inch deep, the possibility of a circumferential leak between adjacent flow passages exists.
  • the depth of the corrugations refers to the radial dimension of the corrugation relative to the flat portion of the strip from which it extends.
  • Some measurable gap S is necessary particularly if a brazing compound is used to bond the spiral wound sheets together to maintain the circumferential flexibility provided by the corrugated sheets 50 and 60, as shown. Bonding without the aid of a brazing compound allows the possibility of near zero gap S. However, some minimum gap S is desired since, as shown in FIGS. 4, 4a and 4b, with a gap S as seen in FIG. 4 for the corrugation as manufactured, this gap as seen in FIG. 4a under compressive load will reduce to a gap size S and, under tensile load, this gap will increase in width to a gap size S" as seen in FIG. 41;.
  • the corrugations of a single formed convolution would vary in configuration from that shown in FIG. 4a to that shown in FIG.
  • the sheets 50 and 60 are shown with their corrugations uniformly spaced apart, it is to be realized that, if desired, the spacing of the corrugations could be varied from the inner periphery to the outer periphery of the matrix disk to correspond to the variation in the distance around the matrix from turn to turn because of the spiral winding of the strips 50 and 60.
  • the depth of the corrugations in the final turn or course of the strips adjacent to the rim 24 can be gradually decreased to maintain a cylindrical outer surface of the heat exchange body adapted to fit into the cylindrical rim 24.
  • Sheets 50 and 60 may be made of any suitable mate rial such as, for example, a ferritic stainless steel or an austinitic stainless steel, with a material thickness of, for example, 0.001 inch to 0.006 inch thick, typically 0.002 inch thick.
  • the heighth and spacing or pitch P of the ribs or corrugations on these sheets would be preferably 0.012 inch to 0.025 inch, typically 0.018 inch and 0.050 inch to 0.150 inch, typically 0.130 inch, respectively.
  • the rib or corrugation angle is preferably 12 to 4 and typically 1.
  • any suitable method can be used to fabricate the corrugated strips 50 and 60.
  • One suitable method of producing these strips if made, for example, of stainless steel, is by feeding a flat metal strip to a pair of forming rolls, one of which is equipped with appropriately spaced, radial extending, high strength, forming teeth, while the other roll is of a resilient compound which would conform to the forming teeth of the first roll to thereby produce the desired shape in the strip, the original flat strip from which these strips are to be fabricated being fed into the bite of the forming rolls at a skew angle corresponding to the desired angle of the corrugations relative to the edges of the strip.
  • the strips may be fabricated by reciprocating machine forming, not shown, in a conventional manner.
  • a rotary regenerator matrix structure of annular form porous to flow of fluid generally parallel to the axis of the matrix and effective to block fluid flow circumferentially around the axis, the matrix structure comprising first and second spiral wound strips with each turn of the first strip disposed between adjacent turns of the second strip and with the strips abutting face to face and fixed together into a rigid, elastic structure, the first strip being provided with spaced apart corrugations inclined at a relatively small angle of approximately /z to 4 in one direction relative to the axis of the matrix, the portion of said first strip between said spaced apart corrugations thereon being substantially flat sheet stock material, the second strip being formed with spaced apart corrugations inclined in the opposite direction and at an equivalent angle to the axis of the matrix from the corrugations of the first strip, the portion of said second strip between said spaced apart corrugations thereon being substantially flat sheet stock material, the corrugations of the first strip and of the second strip having substantial depth radially of the matrix to separate radially the turns of the other strip, the first strip

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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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
US455047A 1974-03-27 1974-03-27 Regenerator matrix Expired - Lifetime US3910344A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US455047A US3910344A (en) 1974-03-27 1974-03-27 Regenerator matrix
CA218,630A CA999288A (en) 1974-03-27 1975-01-24 Regenerator matrix
DE19752512358 DE2512358A1 (de) 1974-03-27 1975-03-18 Ringfoermiger speicher fuer axial durchstroemte drehspeicher-waermetauscher
GB1167175A GB1440748A (en) 1974-03-27 1975-03-20 Regenerator matrix
IT48771/75A IT1032448B (it) 1974-03-27 1975-03-25 Perfezionamento nei recuperatori di calore a matrice
JP50035661A JPS50130047A (ja) 1974-03-27 1975-03-26

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US455047A US3910344A (en) 1974-03-27 1974-03-27 Regenerator matrix

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US3910344A true US3910344A (en) 1975-10-07

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US455047A Expired - Lifetime US3910344A (en) 1974-03-27 1974-03-27 Regenerator matrix

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US (1) US3910344A (ja)
JP (1) JPS50130047A (ja)
CA (1) CA999288A (ja)
DE (1) DE2512358A1 (ja)
GB (1) GB1440748A (ja)
IT (1) IT1032448B (ja)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2347638A1 (fr) * 1976-04-05 1977-11-04 Ltg Lufttechnische Gmbh Echangeur de chaleur a regeneration
US4200441A (en) * 1976-06-29 1980-04-29 Ltg Lufttechnische Gmbh Regenerative heat exchanger
US5735158A (en) * 1996-10-10 1998-04-07 Engelhard Corporation Method and apparatus for skew corrugating foil
US5899261A (en) * 1997-09-15 1999-05-04 Abb Air Preheater, Inc. Air preheater heat transfer surface
NL1013232C2 (nl) * 1999-10-06 2001-04-09 Ursus Bv Platenpakket voor warmteregenerator.
US20030010473A1 (en) * 2001-07-10 2003-01-16 Mitchell Matthew P. Foil structure for regenerators
US6745822B1 (en) * 1998-05-22 2004-06-08 Matthew P. Mitchell Concentric foil structure for regenerators
US20060254756A1 (en) * 2003-03-03 2006-11-16 Jack Kaser Heat exchanger having powder coated elements
US7841390B1 (en) * 2003-03-03 2010-11-30 Paragon Airheater Technologies, Inc. Heat exchanger having powder coated elements
US20140090822A1 (en) * 2009-08-19 2014-04-03 Alstom Technology Ltd Heat transfer element for a rotary regenerative heat exchanger
US20180216897A1 (en) * 2017-01-27 2018-08-02 Airxchange, Inc. Rotary heat regenerator using parallel plate media

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE8206246L (sv) * 1981-11-12 1983-05-13 Northern Solar Systems Inc Roterande vermevexlare

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1808921A (en) * 1927-08-01 1931-06-09 Philipp August Weydmann Metallic filling for cold accumulators
US3183963A (en) * 1963-01-31 1965-05-18 Gen Motors Corp Matrix for regenerative heat exchangers
US3252506A (en) * 1965-07-20 1966-05-24 Chrysler Corp Rotary heat exchanger

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1808921A (en) * 1927-08-01 1931-06-09 Philipp August Weydmann Metallic filling for cold accumulators
US3183963A (en) * 1963-01-31 1965-05-18 Gen Motors Corp Matrix for regenerative heat exchangers
US3252506A (en) * 1965-07-20 1966-05-24 Chrysler Corp Rotary heat exchanger

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2347638A1 (fr) * 1976-04-05 1977-11-04 Ltg Lufttechnische Gmbh Echangeur de chaleur a regeneration
US4200441A (en) * 1976-06-29 1980-04-29 Ltg Lufttechnische Gmbh Regenerative heat exchanger
US5735158A (en) * 1996-10-10 1998-04-07 Engelhard Corporation Method and apparatus for skew corrugating foil
US5899261A (en) * 1997-09-15 1999-05-04 Abb Air Preheater, Inc. Air preheater heat transfer surface
US6745822B1 (en) * 1998-05-22 2004-06-08 Matthew P. Mitchell Concentric foil structure for regenerators
NL1013232C2 (nl) * 1999-10-06 2001-04-09 Ursus Bv Platenpakket voor warmteregenerator.
WO2001025710A1 (en) * 1999-10-06 2001-04-12 Ursus B.V. Set of plates for a heat-regenerator
US6854509B2 (en) 2001-07-10 2005-02-15 Matthew P. Mitchell Foil structures for regenerators
US20030010473A1 (en) * 2001-07-10 2003-01-16 Mitchell Matthew P. Foil structure for regenerators
US20060254756A1 (en) * 2003-03-03 2006-11-16 Jack Kaser Heat exchanger having powder coated elements
US7819176B2 (en) 2003-03-03 2010-10-26 Paragon Airheater Technologies, Inc. Heat exchanger having powder coated elements
US7841390B1 (en) * 2003-03-03 2010-11-30 Paragon Airheater Technologies, Inc. Heat exchanger having powder coated elements
US8316924B2 (en) 2003-03-03 2012-11-27 Paragon Airheater Technologies Heat exchanger having powder coated elements
US20140090822A1 (en) * 2009-08-19 2014-04-03 Alstom Technology Ltd Heat transfer element for a rotary regenerative heat exchanger
US9448015B2 (en) * 2009-08-19 2016-09-20 Arvos Technology Limited Heat transfer element for a rotary regenerative heat exchanger
US20180216897A1 (en) * 2017-01-27 2018-08-02 Airxchange, Inc. Rotary heat regenerator using parallel plate media

Also Published As

Publication number Publication date
IT1032448B (it) 1979-05-30
JPS50130047A (ja) 1975-10-14
DE2512358A1 (de) 1975-10-09
CA999288A (en) 1976-11-02
GB1440748A (en) 1976-06-23

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