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5 tor 12 between its parallel upper and lower end faces. The latter are in sliding contact with the seals 13 and 14. Because of the multitude of tiny gas passages, a com paratively smooth but foraminous ‘contact surface for the rubbingportionsoftheseals13and14-isprovided. The brazingmaterial32comprisesacopperalloy. However, the advantages of the present invention are not con?ned to the use of copper brazed stainless steel sheet material. Other sheet matrix material similarly fused or bonded 6 thearrangementshowninFIGURE 3,sothattheshort ends 30'}; would extend radially and the long sides 30’a would extend circumferentially, then if the short ends 30’b of one convoluted layer should intersect the mid regions of the long sides 30’a of the next radially ad jacent layer, the long sides 30’a thus intersected would be deformedcomparativelyeasily. The long sides 30a in FIGURE 3 are primarily sub jecttotensionloads. Forthisreasontherim20must such as heat resistant ceramic or glass, can be employed. The short ends 3012 reinforced by the ?at strip material 31 and the braZing material 32 serve as short beams inter connecting the ends of the long sides or spoke portions Stla to effect a multitude of thin spokes extending from hub19totherim20. Byvirtueofthestubbycharacter of the beams 3012, the fact that the individual elements 30:: of the radial spokes are discontinuous and slightly offset circumferentially from each other is rendered im or forces tending to bend it out of round will be trans ferred to its circumferentially adjacent parts, somewhat inthenatureofabicyclerim. However,thelongsides 38a also must withstand limited compressional loads, so that in the present instance their length as compared to thelengthoftheshortend3% isapproximatelyinthe ratioof6:1. Asmorefullyexplainedintheabovemen tioned Huebner application, the greater the ratio, the better will be the heat transfer characteristics of the heat 3,276,515 to provide the con?guration illustrated in FIGURE 3, 10 be su?iciently rigid and resilient so that localized loads material when the spoke elements 30a are subject to 20 passage. In no case would the structure illustrated have radial forces. The above is true because of the small leverage effec tive to cause deformation of the beam portions 30!) con~ necting the radial spoke portions 30a in FIGURE 3. Thus, even in extreme cases where the long sides 30a of one convoluted layer intersect the mid~regions of the shortsides3% ofthenextradialadjacentlayer,asinthe upper portion of FIGURE 3, the tension or compres sional forces are transmitted radially from the long side a long side to short side ratio of less than 3:1 because then the total amount of the flat strip material 31 and braze or weld material 32 would ‘be too large in propor tion to the total gas passage area, with resulting loss of compactness and heat transfer ei?ciency. Another advantage of the structure shown is that the pressure gradient across the cross [arm portion 13a of the seal will be carried by a large number of radially elongated‘gaspassagesarrangedsidebyside,FIGURE 5. 30a of each convoluted layer to the long sides 30a of 30 Hence the pressure differential across the long sides of thenextlayerwithoutdistortingthematrix. Inconse quence supplemental reinforcing spokes, which are not ef?cient heat transfer element, and a reinformed rim capable by itself of withstanding the forces acting on the regenerator, are rendered unnecessary. anygaspassagewillbecomparativelysmall,FIGURE 6, and will not deform or rupture the gas passage. In contrast, FIGURE 8 illustrates the pressure distri bution that exists across the cross arm seal 13a when the 35 cross sectional elongations of individual gas passages is The ability of the regenerator to withstand deforma— tion as a result of radial loads transmitted along the long sides 30a can be more readily appreciated when it is understood that the .02" spacing between a pair of cir cumferentiallyadjacentlongsides30aissoslightthatata40 sides3tl’barelong,DP isappreciableandeffectiveto radial distance of r1 of ?ve inches from the regenerator axis of rotation, the angle t9 subtended by the pair of circumferentially adjacent long sides 30a will be .02"/5"=.004 radians. As aforesaid, these circumfer entially adjacent long sides 30a extend radially, so that their deviation from true parallelism will be measured by the equation: wherein 0 is the angle between circumferentially adja cent long sides 3tla, and r1 and r2 are the radial distances from the axis of rotation to the radially inner and radially outerendsofthelongsides30abeingcompared. Sub stituting the value calculated for 0:.004 in Equation 1 deform the re‘generator matrix. At the circumferential portions of the seal there is where11:5"andr2:5.l2",becausetheradiallengthof55 volutionsofthestrip30terminateseverallapsshortof the long sides 39a are on the order of .12 as aforesaid, we have: (2) This deviation of less than ?ve ten-thousandths of an 60 inch from true parallelism cannot be detected by the eye alone and is appreciably less than the thickness of .002" for the thin sheet stock 3t) and 31, and is in fact appre ciably less than can be obtained with normal production tolerances. Hence,foralpracticalpurposesthecircum ferentially adjacent radial long sides 30a are so close together that they may be considered to be parallel to eachother. Inconsequencethemaximumcircumferen tial offset of one long side Pitafrom the radially adjacent the strip 31, which then winds several times around the circumference of the regenerator 12 and forms the rim 20. I claim: 1. Ina rotary counter flow regenerator for a gas turbine engine, a disc-type matrix rotatable about a central axis and comprising a plurality of ‘gas passages. extending parallel to said axis and arranged side-by-side in layers extending circumferentially around said axis, said gas pas sages in cross section transverse to said axis being elongat ed radially of said axis and being de?ned by substantially parallel circumferentially spaced long thin sidewalls and radially spaced short end walls, the end walls of the gas passages of each layer abutting the end walls of the gas long side 30a, connected by the comparatively stubby and 70 passages in the radially adjacent layers, means having rigid triple thickness beam 30b, 31, 32, will be negligible and at maximum, will be not greater than one-sixth the radial spacing between successive spirals of the layer 31. By way of comparison if the elongation of the gas passages is aligned as in FIGURE 7 at right angles to a radial dimension of the order of magnitude of the thickness of said long thin sidewalls connecting the abutting end walls to comprise rigid beams for trans mitting the radial forces in the long sidewalls of each layer of gas passages to the long sidewalls of the gas arranged circumferentially. DP represents the pressure differential acting across the portion of the long side 30'a separating two radially adjacent gas passages, where in the ends 30'b are not aligned radially. Where the substantially no pressure ‘gradient circumferentially across the long sides 3% of FIGURES 2 and 5. A compara tively large pressure differential will occur across the short ends 30!) of the radially adjacent gas passages, but these short ends or beams 36b are much more resistant to deformation because of their shortness and readily carry the force of the pressure differential tthereacross without beingdeformed. Furthermore,thecircumferentialpor tions of the matrix which underlie the seal portion 135 are not employed for heat transfer purposes and may accordingly be of triangular cross sectional shape, as il lustratedinFIGURE 4. InthisviewthetriangularconPDF Image | WHITFIELD GAS TURBINE REGENERATOR
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