[0001] This invention relates to a heat exchange channel element having a multiplicity of
wall projection portions disposed on its surface and to a heat exchanger comprising
channel elements formed from such wall members.
[0002] , U. S. Patent No. 3,757,856 issued September 11, 1973 to L. C. Kun discloses a thin-walled,
light-weight heat exchange channel element having on a portion of its wall surface
isostress contours with substantially uniformly disposed unidirectional wall supporting
projections. The isostress surface disclosed in the Kun patent is a continuously curved
surface having a multi-
plicity of" isostress countours wherein each contour has a multiplicity of radii with
theoretically no flat segments and resembles the curved contour of a shear-free "soap
bubble" membrane. The isostress contoured heat exchange channel element may suitably
be formed as a longitudinally extending channel open at its extremities, whereby a
first heat exchange fluid may be flowed through the interior of the channel element
in heat exchange with a second heat exchange medium flowed over the exterior surface
of the channel element. Such heat exchange channel elements may usefully be employed
in any application where there is substantial pressure difference between the respective
first and second heat exchange media and has particular utility as incorporated in
an automotive radiator.
[0003] As employed in an automotive radiator or heater, a multiplicity of the Kun heat exchange
channel elements are serially stacked in an array and arranged so that the wall projections
on one channel element mate with and abut against corresponding wall projections on
an adjacent channel element. A heat exchanger fabricated in this manner has a first
set of passages defined by and bound within the channel wall members and a second
set of passages defined by and disposed between the channel elements. During operation,
high internal coolant pressures (of the first heat exchange medium flowed through
the interior passages of the channel elements) on the order of 20 psig and higher
may be accommodated, since in the stacked array the internal pressure is balanced
by the support function of the adjacent channel element projections. The heat exchanger
can thus be economically and quickly fabricated, with the stacked channel element
assembly (heat exchanger core) being disposed within a mechanically simple load-bearing
structural frame assembly.
[0004] The provision of the isostress-contoured surface in the manner of the aforementioned
Kun patent permits the channel element to be readily formed of thin and lightweight
materials of construction such as aluminum. For example, the channel element may be
stamped from thin aluminum sheet stock having a thickness of for example on the order
of 8 - 10 mils. This ability to use thin sheet metal material in fabricating channel
elements has several inherent advantages, particularly in application to automotive
radiators and heaters. First, the use of low material thicknesses for the heat exchanger
channel elements is associated with reduced material costs and reduced material weight
for the fabricated heat exchanger. The reduction in weight permits a given automobile
power plant (internal combustion engine) to provide increased transportation fuel
efficiency, with obvious advantage in our present economic and energy climate. Second,
the use of thin wall members for the heat exchange channel element permits high heat
transfer performance of the heat exchanger to be achieved. Such result is attributable
at least in part to a short heat conduction path normal to the surface of the heat
exchange channel element. Third, the increase in heat transfer capability of the thin-walled
channel elements permits a substantial reduction in size of the fabricated heat exchanger
to be achieved.
[0005] Notwithstanding the above-identified advantages of heat exchange channel elements
and heat exchangers constructed in accordance with the teachings of the aforementioned
Kun patent, automotive heat exchangers of such type have not yet been widely implemented
in the construction of automobiles and other motor vehicles. A primary reason for
this lack of implementation is associated with the characteristic external heat exchange
medium pressure drop in the fabricated heat exchanger. In the normal automobile configuration,
wherein air (the external heat exchange medium) flows successively through the front
grill panel, the air conditioner condenser (if present), the radiator, the fan, and
then by the engine block, the radiator represents a principal resistance to air flow.
In this configuration, radiators constructed in accordance with the Kun teachings
typically have a higher air-side pressure drop than conventional radiator designs.
As a result, the Kun radiator will operate with a lower gas velocity at the primary
surface of the channel element than is characteristic of conventional radiators. Such
lowered air-side gas velocity in turn reduces the air-side heat transfer. Inasmuch
as air-side heat transfer represents the controlling or limiting resistance to heat
transfer in the radiator, the lower air-side gas velocity and heat transfer disadvantageously
reduce the advantages otherwise achieved by the radiator in employing thin wall members.
[0006] Accordingly, it is an object of the present invention to provide a heat exchange
wall member which may be employed to form a thin-walled, light-weight heat exchange
channel element possessing the advantages of the channel element disclosed in the
aforementioned Kun patent which when employed in a heat exchanger assembly, such as
an automobile radiator, has more favorable air-side pressure drop performance than
the heat exchanger disclosed in the Kun patent.
[0007] In its broadest aspect, the invention relates to a heat exchange wall member of thermally
conductive material having a multiplicity of wall projection portions distributed
across the wall member surface and extending therefrom with load-bearing end segments
at their extremities, whereby the wall member may be supported abuttingly against
an adjacent structural member by the load-bearing end segments of the wall projection
portions.
[0008] In the improvement of the invention, the wall projection portions extend elongately
on the wall member surface with the load-bearing segments thereof having an aspect
ratio (d
2/d
1) of at least 10, wherein d
2 = length of the major axis of the wall projection portion load-bearing end segment
measured in the base plane of the wall member and d
1 = length of the minor axis of the wall projection portion load-bearing end segment
measured in the base plane of the wall member. The wall projection portions are oriented
on the wall member surface with the major axes of the load-bearing end segments of
the wall projection portions aligned substantially parallel to one another. In addition,
the wall projection portions have a dimensional size and a dimensional relationship
therebetween defined by a D dimension of between about 0.2 and 3.0 inch, a H/D ratio
of between about 0.05 and 0.5, and D/d
1 ratio of betweenabout 1.5 and 50, wherein: H = the maximum height measured perpendicularly
from the base plane of the wall member to the innermost point on the wall member surface
between adjacent wall surface projections; between D = the spacing/the rajor axes
of load-bearing end segments of adjacent wall projection portions, as measured perpendicularly
to said major axes in the base plane of the wall member; and the base plane of the
wall member is a plane containing the extremities of wall surface projections extending
outwardly from the wall member surface to a uniform extent.
[0009] In preferred practice, the above-described heat exchange wall member is suitably
employed in a heat channel element including two spaced exchange channel element including
two spaced apart wall members of such type, wherein the heat exchange channel element
extends longitudinally and hasan elongated cross section bound by the aforementioned
two spaced-apart wall members as side walls spaced apart by edge walls, the channel
element having a first fluid entrance opening at one end and a first fluid exit opening
at the opposite end. In this preferred embodiment, the wall projection portions extend
across substantially the full width of the side wall and are oriented with the major
axes of the wall projection portion.load bearing end segments substantially perpendicular
to the longitudinal axis of the channel element.
[0010] Another aspect of the invention relates to a heat exchanger comprising a multiplicity
of channel elements of the above-described type, the channel elements being longitudinally
aligned in parallel spaced relation each with a first fluid entrance opening at one
end and a first fluid exit opening at the opposite end, and common inlet manifold
means and common exit manifold means respectively associated with said first fluid
entrance openings and said first fluid exit openings.
[0011] In a primary surface embodiment of the above-described heat exchanger, the load-bearing
end segments of wall projection portions of the channel elements are shaped and arranged
for mating with and abutting against load-bearing end segments of the projection portions
of an adjacent channel element wall member, with the wall surface portions between
the projection portions thereby forming spaces between adjacent channels through which
a second fluid may be flowed in heat exchange with the first fluid.
[0012] In a preferred primary and secondary surface embodiment of the previously described
heat exchanger, a multiplicity of channel elements are disposed in a stacked array
with secondary surface plate-like members being disposed between adjacent channel
elements with the load-bearing end segments of the wall projection portions of the
channel elements being shaped and arranged for mating with and abutting against the
secondary surface members, whereby the secondary surface members are maintained in
thermal contact with the channel elements along the abutting load-bearing end segments
thereof.
[0013] As used herein, primary surfaces are those which bound the passage walls separating
the two fluids in heat exchange. The flow path between the fluids is merely the thickness
of the passage wall so that heat flows substantially normal to the wall. In contrast,
secondary surfaces are nct in direct contact with the first heat exchange fluid but
rather are substantially surrounded by only the second fluid. Accordingly, the heat
flow path through the secondary surface is substantially parallel to the surface.
Figure 1 is an isometric view of a portion of a heat exchange wall member according
to one embodiment of the present invention.
Figure 2 is an isometric view of a portion of a heat exchange channel element according
to one embodiment of the present invention,
Figure 3 is a sectional, elevational view of a portion of the Figure 2 channel element
along the longitudinal axis L-L thereof.
Figure 4 is a sectional, elevational view of the Figure 2 channel element, taken in
cross section along a wall projection portion thereof.
Figures 5 and 6 show illustrative configurations of wall projection portions such
as may be employed in the Figure 2 channel element.
Figure 7 is a plan view of a portion of the Figure 2 channel element, showing the
geometric and dimensional features of the wall surface of the channel element.
Figure 8 is an isometric view of another heat exchange channel element according to
the invention.
Figure 9 is a plan view of a portion of the Figure 8 channel element, showing the
geometric and dimensional features of the wall surface thereof.
Figure 10 is a plan view of another heat exchange channel element according to the
invention.
Figure 11 is an isometric view of a portion of the Figure 10 channel element, showing
the details of the wall projection portions thereof.
Figure 12 is a sectional elevational view of a portion of a stacked array of channel
elements of the type shown in Figures 10 - 11.
Figure 13 is a sectional elevational view of a portion of another stacked array utilizing
channel elements of the type shown in Figure 10.
Figure 14 is an isometric view of a portion of a heat exchange channel element of
the type shown in Figure 2., provided with a secondary surface fin at one edge thereof.
Figure 15 is an isometric view of a heat exchange channel element of the type shown
in Figure 2 , provided with secondary surface fins at both edges thereof.
Figure 16 is an isometric view of a channel element of the type shown in Figure 2,
provided with multiple fins at both edges thereof,
Figure 17 is an elevational view of a portion of a stacked array of heat exchange
channel elements of the type shown in Figure 2.
Figure 18 is an elevational view of a portion of a stacked array of heat exchange
channel elements of they type shown in Figure 2, with secondary surface plate-like
numbers being disposed between adjacent channel elements.
Figure 19 is an elevational view of a portion of a stacked array of heat exchange
channel elements according to the invention, wherein each channel element is provided
with a sequence of wall projection portions of alternately varying height.
Figure 20 is an elevational view of portions of two distinct channel elements adapted
for mating with one another by means of wall projection portions with non-planar load-bearing
segmencs.
Figure 21 is an isometric view of a portion of a heat exchange channel element according
to the invention showing two types of wall projection portions with non-planar load-bearing
segments.
Figure 22 is an isometric view of a stacked array of heat exchange channel elements
according to another embodiment of the. invention.
Figure 23 is an isometric view of a stacked array of heat exchange channel elements
as shown in Figure 2 but provided with secondary surface fins at each edge thereof
and with a secondary surface plate-like member disposed between adjacent channel elements,
the plate-like member being provided with slatted, slotted louver-type surface distortions.
Figure 24 is a plan view of another secondary surface plate-like member, such as may
alternatively be employed in the Figure 23 stacked array of heat exchange channel
elements.
Figure 25 is a sectional elevational view of the Figure 24 plate-like secondary surface
member taken along line A-A.
Figure 26 is an elevation view of a wind tunnel used to test automobile radiator heat
exchangers.
Figure 27 is an exploded assembly drawing of a portion of a heat exchanger according
to the invention, comprising a stacked array of heat exchange channel elements of
the type shown in Figure 15.
Figure 28 is an isometric view of a portion of the heat exchanger assembly of Figure
27, showing the details of the headering arrangement thereof.
Figure 29 is a sectional plan view of a portion of the headering arrangement of Figure 28.
Figure 30 is an isometric view of a portion of the headering arrangement of Figure
28.
Figure 31 is a graph of convective heat transfer effectiveness factor plotted as a
function of Reynold's number, for various heat exchanger embodiments of the present
invention and for a heat exchanger constructed in accordance with Kun U. S. Patent
No. 3,810,509
Figure 32 is a graph of heat transfer material effectiveness for radiators constructed
in accordance with the present invention and a radiator constructed in accordance
with the aforementioned Kun patent, plotted as a function of gas flow velocity at
the face of the radiator.
Figure 33 is a graph of channel element wall member deflection plotted as a function
of internal vacuum pressure and also as a function of internal buckling pressure,
for a channel element according to the present invention and a channel element according
to Kun U. S. Patent No. 3,810,509.
[0014] Referring now to the drawings, Figure 1 is an isometric view of a portion of a heat
exchange wall member according to the present invention stamped from thin sheet metal.
The wall member 11 is stamped with a surface comprising ridge projections 17 extending
elongately across the top surface of the wall member with flat top surface portions
18 at the extremities of the ridge projections, the flat top surface portions 18 having
an aspect ratio (d
2/d
l) of ar least 10, wherein d
2 is the longitudinal dimension of the ridge projection flat top surface portion and
d
l is the transverse dimension of the ridge projection flat top surface portion. The
flat top surface portions are surrounded by top surface portions 20 having a concave
elevational contour. Edge surface portions 19 are formed between the unstamped margins
16 of the wall member and the aforementioned flat top surface and concave surface
portions of the wall member.
[0015] Figure 2 is an isometric view of a portion of a heat exchange channel element according
to the present invention. The heat exchange channel element 10 includes two spaced-apart
wall members 11 and 12 of thermally conductive material bounding a fluid flow channel
13. A multiplicity of wall projection portions 17 are distributed across the wall
member surface and extend from the wall member surface with load-bearing end segments
18 at their extremities, whereby the channel element may be supported abuttingly against
an adjacent structural member by the load-bearing end segments of the wall projection
portions.
[0016] The two spaced-apart wall members 11 and 12 of the Figure 2 channel element constitute
side walls of the channel element. These side walls are spaced apart by edge walls
comprising edge wall portions 14 and 15. In practice, the edge walls of the channel
element may be formed separately from the side walls and joined to the latter as for
example by braising or welding to form the completed channel element, however, it
is more advantageous in general to form upper and lower halves of the channel element
from unitary sheets of material as shown more 'clearly in Figure 4, so that the upper
half of the channel element comprises (side) wall member 11, edge wall portion 14
and flange-like margins, and with the lower half of the channel element being similarly
formed. With such integral side and edge wall construction, the upper and lower channel
element halves may be joined to one another by welding, braising, adhesive bonding
or other suitable joining method along the mating surfaces of the margins 16.
[0017] The side walls and edge walls of the Figure 2 channel element may suitably have a
thickness of between about 0.003 and 0.25 inch. In the preferred practice of the invention,
wherein the side walls and edge walls are formed of aluminum, as suitably employed
in automobile radiator applications, the walls desirably have a thickness of between
about 0.003 and 0.100 inch.
[0018] As shown in Figure 2, the channel element is formed in such manner that the wall
projection portions 17 are provided in the form of ridges extending across substantially
the full width of the side wall 11, with the wall member surface 20 between adjacent
wall projection portions being concavely curved. In such configuration, the wall projection
portions 17 extend elongately on the wall member surface with the load-bearing segments
18 thereof having major axes which are substantially perpendicular to the longitudinal
axis L-L of the channel element. The load-bearing end segments 18 of the wall projection
portions 17 intersect the edge wall portions 14, 15 of the channel element at edge
wall surfaces 19,_which preferably-are convexly contoured as shown in Figure 3 to
decrease hydrodynamic drag and pressure drop when a second heat exchange medium is
flowed over the external surfaces of the channel element, from left to right as shown
in Figure 4, in heat exchange with a first heat exchange medium flowing through the
channel element interior flow channel 13.
[0019] The illustratively shown channel element in Figure 2 is a portion of a longitudinally
extending element having its unillustrated extremity formed in the same manner as
the extremity shown. Each extremity is provided with an end section 9 having flat
side wall end portions 21. By such configuration, the channel elements may be stacked
in an array of such elements to form a heat exchanger core, with the side wall end
portions 21 of adjacent channel elements mating abuttingly with one another in a manner
as shown more fully hereinafter.
[0020] Figure 3 shows a sectional, elevational view of a portion of the Figure.2 heat exchange
channel element along the longitudinal axis L-L. The features of the channel element
in Figure 3 are numbered correspondingly with respect to Figure 2. As shown in Figure
3, the upper and lower wall members 11 and 12 of the channel element 10 are similarly
formed with a concavely contoured wall surface between adjacent wall projection portions
and with the upper and lower wall members 11 and 12 oriented with respect to one another
so that the innermost point on the wall surface between adjacent wall projection portions
of one wall member is vertically aligned with a load-bearing end segment of a wall
projection portion of the other wall member. Thus, for example, the innermost point
on the wall surface 20 of upper wall member 11 is vertically aligned with the load-bearing
end segment 18a of lower wall member 12.
[0021] Figure 3 shows the geometric and dimensional characteristics of the channel element.
As indicated above, the wall surface between adjacent wall projection portions in
this embodiment is concavely curved; specifically, the elevational contour of such
wall surface is concavely circular, i.e., the surface in elevation has a uniform radius
of curvature R1between the load-bearing end segments of adjacent wall projection portions.
The relative "depth" of the depression between adjacent wall projection portions is
measured with reference to the base plane P of the wall member, which is a plane containing
the extremities of wall surface projections extending outwardly from the wall member
surface to a uniform extent. In this embodiment of the invention, all wall projection
portions of the channel element extend outwardly from the wall member surface to a
uniform extent, and the load-bearing end segments are flat and horizontally aligned
as shown, so that the load-bearing end segments in this embodiment lie fully in the
base plane P of the wall member.
[0022] The remaining dimensional parameters in Figure 3 are measured by reference to the
above-described base plane of the wall member. The dimension H, which in the Figure
3 embodiment provides a measure of the "depth" of the concavely contoured surface between
adjacent wall projections, is the maximum height measured perpendicularly from the
base plane P of the wall member to the innermost point (i.e., the furthest point from
the base plane) on the wall member surface between adjacent wall surface projections.
The dimension d
l is the length of the minor axis of the wall projection portion load-bearing end segment
measured in the base plane of the wall member. In this embodiment the length of the
load-bearing end segment minor axis is simply the measured lateral dimension of the
load-bearing end segment and this dimension is uniform across the width of the channel
element along which the load-bearing end segment elongately extends. The characteristic
dimension of the load-bearing end segment in the direction of elongation of the associated
wall projection portion (not shown in Figure 3), as shown more fully hereinafter,
is the major axis of the load-bearing end segment. The D dimension is the spacing
between the respective points of intersection of major and minor axes of load-bearing
end segments of adjacent wall projection portions, as measured in the base plane of
the wall member. The minimum channel clearance for the channel element is shown as
dimension C
L.
[0023] Figure 4 is a sectional elevational view of the Figure 1 channel element taken in
cross section at a wall projection portion 17 of the upper wall member 11. As shown,
the channel element has an elongated cross section bound by the two spaced-apart wall
members 11 and 12 as side walls spaced apart by edge walls formed by edge wall portions
14 and 15. The channel element disembodiment is formed from corresponding upper and
lower distinct integral halves which are bonded together along the facing surfaces
of peripheral flange-like margins 16
'. The upper and lower halves of the channel element may suitably be prepared from
sheet metal stock with the illustrated surface configuration by conventional fabricating
techniques such as pressing, stamping, rolling or the like. As indicated hereinabove,
the upper and lower channel element halves may be bonded at their margins by soldering,
braising, welding, adhesive bonding or other suitable joining technique. The surface
19 of edge wall portion 14 adjacent the wall projection 17 has an elevational contour
of convex slope. Alternatively, edge wall surface 19 could be provided with a straight
or concave contour. Nonetheless, the convex contour shown is generally preferred in
practice, inasmuch as it allows the edge walls in the region of the wall projection
portions to accommodate higher internal pressures than can be tolerated with linear
or concave contours of the edge wall surface 19. Furthermore, the convex edge wall
surface 19 greatly reduces the frictional drag that would otherwise be associated
with a blunt edge wall.
[0024] Figures 5 and 6 are sectional, elevational views of wall projection portions having
elevational contours such as have usefully been employed in practice. Figure 5 shows
an elevational contour of the type shown more generally in the Figure
3 drawing, in which the side walls of the projection 17 intersect the flat load-bearing
surface 18 at a sharp corner. Figure 5 shows an alternative elevational contour in
which the side walls of the projection 17 intersect the flat load-bearing surface
18 with a convex contour in the region of intersection. In both the Figure 5 and 6
embodiments, the channel element exterior surface between adjacent wall supporting
projections is a concave surface integral with project curvature having a radius of
curvature R
1 the projection angle θ
1 shown in Figures 5 and 6 is the included angle formed between a tangent to the wall
member surface at the point of intersection of the projection side wall with the load-bearing
end segment of the projection and a plane parallel to the base plane of the channel
element wall member. In the Figure 6 embodiment, wherein the region of intersection
between the projection side wall and the flat load-bearing end segment of the projection
has a convex surface contour, the surface has a radius of curvature R
21 as shown in the drawing.
[0025] With reference to Figures 5 and 6, and by way of example, illustrative dimensional
parameters are set forth below in Table 1 for channel elements having projections
as shown in Figures 5 and 6and otherwise generally constructed in accordance with
the channel element shown in Figures 2 - 4.

[0026] The foregoing dimensional values in Table I have been usefully employed in heat exchange
channel elements utilized to fabricate automotive radiator heat exchangers.
[0027] Figure 7 is a plan view of a portion of a heat, exchange channel element shown in
Figures 2 - 4,showing the dimensional and geometric characteristics of the channel
element in greater detail. The various structural features of Figure 7 are numbered
correspondingly with Those of Figures 2 - 4. As shown in Figure 7, the wall projection
portions 17 extend elongately on the wall member surface with the load-bearing segments
thereof having a major axis cf length d
23 as measured in the base plane of the channel element wall member along the direction
of elongation of the wall projection portion of the channel element. The length of
the major axis of the wall projection load-bearing end segment thus provides a measure
of the extent of the wall support bearing surface provided at the extremity of the
wall projection portion, between the extremities of the load-bearing end segment surface
at opposite edges of the channel element as shown in Figure 7 where the extremities
of the load-bearing end segment surface intersects the edge wall surface portions
19. Likewise, the minor axis d
1 is a measure of the dimensional extent of the wall projection load bearing surface
along a direction transverse to the direction of elongation of the wall projection
(substantially perpendicular to the channel element longitudinal axis in the embodiment
of Figure 7). The major axis and the minor axis of the wall projection load-bearing
end segment are measured in the base plane of the wall member. In embodiments of the
invention such as are shown in Figures 2 - 7, the wall projection load-bearing end
segments of the channel element lie in the base plane of the channel element wall
member, so that the major and minor axes of the load-bearing end segment are merely
the length and width dimensions of the end segment..
[0028] In accordance with the invention, the wall projection portions extend elongately
on the wall member surface of the channel element with the load-bearing segments thereof
having an aspect ratio (d
2/d
l) of at least 10. The reason for such minimum value of the aspect ratio is to provide
a sufficient extent of elongation so that the channel element wall member has sufficient
rigidity to accommodate high internal coolant pressure levels. As a result, channel
elements of the type shown in Figure 2-7 are able to be employed with significantly
higher internal coolant pressures than have been achievable in thin-walled channel
elements of the prior art, including those of Run U. S. Patent No. 3,757,856. Such
characteristic is particularly advantageous in application of the channel element
of the instant invention to fabrication of automobile radiators, since in such application
increased coolant pressures serve to increase the boiling temperature of the coolant,
thereby permitting the radiator to accommodate higher engine temperatures and to function
with the same degree of efficiency in a more compact radiator configuration. In preferred
practice, the aspect ratio d
2/d
l is at least 30.
[0029] As shown in Figures 2 - 7, the wall projection portions of the channel element in
accordance with the present invention are oriented on the wall member surface with
the major axes of the load-bearing end segments of the wall projection portions aligned
substantially parallel to one another. The distribution of wall projection portions
across the wall member surface of the channel element is characterized by dimension
D, which equals the spacing between the major axes of load-bearing end segments of
adjacent wall projection portions, as measured perpendicularly to the major axes in
the base plane of the wall member. As indicated hereinearlier, the base plane of the
wall member is a plane containing the extremities of wall surface projections extending
outwardly from the wall member surface to a uniform extent. In the broad practice
of the invention, the wall projection portions on the wall member surface of the channel
element have a dimensional size and a dimensional relationship therebetween defined
by a D dimension of between about 0.2 and 3.0 inch, a H/D ratio of between about 0.05
and 0.5, and a D/d
l ratio of between about 1.5 and 50. The upper limit on the D dimension of 3.0.inch
is imposed because at spacings above such value the heat exchange area per cubic foot
of heat exchange volume of the channel element or stacked array of channel elements
decreases disproportionately and the ability of the channel element wall member to
accommodate increasing differential pressure across the wall is undesirably reduced.
The lower limit on the D dimension about 0.2 inch dictated by pressure drop considerations
for the external heat exchange medium flowed over the exterior surfaces of the channel
element; at spacing values of less than about 0.2 inch, the pressure drop tends to
become unduly large, so that the advantages of the invention, of maintaining low external
heat exchange medium pressure drop consistent with high heat transfer performance,
are increasingly difficult to achieve. H, the maximum height measured perpendicularly
from the base plane of the wall member to the innermost point on the wall member surface
between adjacent wall surface projections, is related to the aforementioned D dimension
by the constraint that the ratio H/D is between about 0.005 and 0.5. The parametric
range of values permissible for the H/D ratio is associated with maximum and minimum
values which are based on considerations of the maximum and minimum allowable values
for the D dimension, as discussed above, and the maximum and minimum allowable values
for the parameter H. The maximum allowable value for H in a given application is determined
by the requirement of achieving a necessary minimum level of heat exchange area per
cubic foot of heat exchange volume, as necessary for efficient hear transfer. Similarly,
the lower limit on H is imposed by heat exchange surface area considerations, however,
in this case the limit is dictated by the incremental cost required in providing the
contoured surface as compared with the additional area provided by such contoured
surface when compared with an uncontoured planar wall member. All of these various
considerations are effectively accommodated by a H/D ratio of between about 0.05 and
0.5.
[0030] Similarly, D/d
l ratio of between about 1.5 and 50 is based on the various considerations for maximum
and minimum values of D, as discussed above, and maximum and minimum allowable values
of d
1. Depending upon the end use of the channel element, the minor axis dimension on the
load-bearing surface of the wall projection portion, dl is fixed by two competing
considerations. As the value of d
1 increases, the maximum allowable differential pressure across the channel element
wall member will increase, while the available surface area of the channel wall element
for heat exchange will decrease. As a result, in any application of the channel element
of the invention, the relative degree of importance of the heat exchange considerations
as opposed to strength considerations for the channel element will set the upper limit
on the value of dl. The lower limit on the minor axis dimension of the projection
load-bearing segment is determined by manufacturing tolerances, by strength considerations,
i.e., the need to insure that the load which is concentrated at the load-bearing surface
does not produce stresses sufficient to deform or rupture the walls of the channel
element, and by fabrication limitations associated with the material thickness of
the channel element wall member. Tnese various considerations may be effectively accommodated
under D/d
l ratio of between about 1.5 and 50.
[0031] To meet the specific heat exchange requirements for radiators of internal combustion
engines, the channel element is preferably formed with the following geometric and
dimensional characteristics: an H value of between about 0.035 and 0.080 inch; a D
value of between about 0.4 and 1.1 inch; and a d
1 of between about 0.01 and 0.05 inch. For automotive radiators, the H/D ratio is preferably
between about 0.05 and 0.4, on the basis of the previously discussed considerations
applicable to such parameter.
[0032] Referring again to Figures 5 and 6, the elevational contour of the wall member projection
portions should be such as to maintain at acceptable levels in both the projection
portions and the other portions of the channel wall. Preferably, the projection portions
should have an elevational contour such that the ratio 6/R is between about 4° and
2500° per inch, and most preferably between about 4° and 100° per inch for a wall
member wherein the wall surface between adjacent projection portions has an elevational
contour which is concavely circular, i.e., the radius of curvature of the wall member
surface between the load-bearing end segments of adjacent wall projections is constant.
As discussed earlier herein, θ is the included angle between a tangent to the wall
projection side wall at the point of intersection with the load-bearing segment of
the projection and a plane para- lellel to the base plane of the wall member. In terms
of the aforementioned θ/R
1 ratio, and as applicable to the broad practice of the present invention, R
1 is the minimum radius of curvature of the wall projection side walls. The minimum
radius of curvature R
1 may be measured readily conveniently by the well-known optical comparator. In general,
if θ is relatively low, then R
1 (the minimum radius of curvature) can be relatively small. If the wall projection
angle θ is large in value, then R
1 should also be relatively large in magnitude. The upper limit on the θ/R
1 ratio of 2500°/inch is based on wall projection portions having a truncated conical
elevation contour, such as is shown in Figure 10 - 12, described hereinafter in greater
detail. For a wall projection having a truncated conical elevational contour, the
magnitude of the projection angle θ should not exceed 35°. The lower limit. for θ/R
1 of 4°/inch is based on a wall projection having a concavely curved projection side
wall contour and a flat load-bearing end segment, with minimum contour height H and
the largest value of spacing D permitted based on structural stress considerations.
[0033] Figure 8 shows an isometric view of a channel element according to another embodiment
of the invention. The channel element includes two spaced-apart wall members 111 and
112 of thermally conductive material, e.g., aluminum, bounding a fluid flow channel
113 and having a multiplicity of wall projection portions 117 distributed across the
wall member surface 120 and extending therefrom with load-bearing end segment 118
at their extremities.
[0034] The two spaced-apart wall members 111 at 112 constitute side walls of the channel
element which are spaced apart by edge walls made up edge wall portions 114 and 115.
As shown, the channel element is fabricated from upper and lower halves, with the
upper half of the channel element being stamped from a single piece of sheet metal,so
that the upper and lower side walls and their associated edge wall portions are formed
from a unitary sheet of material. The channel element halves so formed are provided
with peripheral margins 116 which are not deformed and thus permit mating and bonding
of the upper and lower channel element halves in the manner previously described in
connection with Figure 2 herein. The channel has a first fluid entrance opening 131
at one end and a first fluid exit opening 130 at the opposite end, with the end sections
121a and 121b of the channel element being characterized by flat side walls which
form mating surfaces for stacking of a series of channel elements on top of one another
in an array to form a heat exchanger core assembly, as descirbed hereinafter in greater
detail.
[0035] Figure 9 is a plan view of a portion of the channel element 110 of Figure 8, showing
the dimensional characteristics thereof. As shown, each of the wall surface projection
portions 117, in contrast to the wall projection portions of the embodiment of Figures
2 - 7, do not extend substantially across the full width of the channel element, but
rather only a portion of the width.
[0036] Nontheless, despite its reduced elongational extent relative to the wall projections
of Figures 2 - 7, the proof the channel element of Figures 8 - 9 are structurally
similar to those previously described herein, having a major axis d
2 which is at least 10, and preferably 30, times the magnitude of the minor axis d
1. As in previous embodiments, the spacing between adjacent channel elements is measured
by dimension D, which equals the distance between the major axes of load-bearing end
segments of adjacent wall projection portions, as measured perpendicularly to the
major axes in the bas plane of the wall member. The wall projection portions 117 in
the Figures 8 - 9 embodiment, as in the preceding embodiments, elongately extend across
the channel element in a direction substantially perpendicular to the channel element
longitudinal axis L - L.
[0037] Figure 10 is a plan view of a portion of another channel element according to the
invention, which differs from the embodiments previously described in that the wall
surface between adjacent wall projection portions 217 is substantially planar. The
channel element 210 is provided with extremities comprising a planar channel element
end section 221 for mating and bonding adjacent channel elements when the channel
elem ints are disposed in a stacked array. A first fluid opening 230 is provided at
the tube end for introduction or egress of a first heat exchange fluid into or out
of the fluid flow channel bounded by the chapel element wall members. The channel
element may be formed from discrete upper and lower halves in the manner previously
described, with mating and bonding of the respective halves to one another along peripheral
margins 216. The surface of the channel element wall member 220 is planar and a multiplicity
of wall projection portions 217 are distributed across the wall member surface, extending
therefrom with load-bearing end segments 218 at their extremities.
[0038] Figure 11 is an isometric view of a portion of the heat channel element of Figure
10, showing the details of the wall member projection portion thereof. The channel
element includes two spaced-apart wall members 220 as side walls spaced apart from
one another by edge 214 and 215 so that the side and edge wall members together bound
and enclose a fluid flow channel 213, whereby a first heat transfer fluid medium may
be flowed through the interior channel 213 in heat exchange with a second heat transfer
medium flowed over the exterior surfaces of the channel element. On the exterior surface
of the channel element wall member 220 is disposed a multiplicity of wall projection
portions 217 having flat load-bearing surface 218 at their extremities. The channel
element shown in Figure 11 differs from those of Figure 2 - 9 in that the former has
a wall surface between adjacent projections which is planar and not continuously curved
as in the preceding described embodiments. The wall projection portions in the Figure
12 embodiment may be formed from the wall members as by stamping, pressing, rolling
and the like, as in the case of the preceding described embodiments, or, alternatively,
the wall projection portions may be provided as separate and distinct structural elements
which are bonded or otherwise affixed to the flat wall member surface of the channel
elements. The provision of the wall member 220 as a separate and distinct structural
part of the channel element from the wall projection portion 217 permits the fabrication
of the channel element to be potentially simplified, inasmuch as no stamping, rolling
or other forming step is necessary for the side wall surface. Thus, for example the
channel element could be fabricated from a flattened tube by soddering, braizing,
or otherwise joining the projection portion 217 to the exterior wall member surface
220, with the wall projection portion being machined, cast or otherwise constructed
by any suitable forming method.
[0039] Figure 12 is an elevational view of a stacked array of two channel elements of the
type shown in Figures 10 and 11,. showing the abutment and mating of the load-bearing
segments of wall projections portions of adjacent channel elements in the array.'
The channel elements 210 and 210a are each provided with a multiplicity of wall projection
portions 217 distributed across their wall surfaces. Each wall projection portion
217 is provided with a flat load-bearing surface 218 at its extremity, so that the
projection portions have a truncated conical elevational contour characterized by
a wall projection angle 8 of preferably less than 35° and a ratio θ/R
1 suitably having a value of between 4° and 2500° per inch, as discussed earlier herein.
In this embodiment, the minimum radius of curvature of the wall projection, R
I, is measured in the region of the intersection of the projection side wall and the
flat surface 220 of the channel element wall member.
[0040] In the Figure 12 stacked array of channel elements, each channel element is structurally
identical with the wall projection portions of the topside and bottomside of the channel
element being vertically aligned. In this array, the load-bearing end segments of
wall projection portions of the channel element are shaped and arranged for mating
with and abutting against load-bearing end.segments of the projection portions of
the adjacent channel element side wall, so that the wall surface portions between
the projection portions thereby form spaces between adjacent channel through which
a second fluid may be flowed in heat exchange with first fluid passed through the
interior channel of the respective channel elements.
[0041] In contrast to the Figure 12 stacked array, Figure 13 shows an array wherein the
channel elements are formed with their upper and lower wall projections staggered
with respect to another. Apart from such difference, the channel elements in Figurel3
are generally similar in construction to the channel elements employed in the array
of Figure 12, the choice alternative Figure 12 and Figure 13 array configurations
being a matter of choice to the heat exchanger designer in a given application.
[0042] Figure 13 is an isometric view of a channel element according to the present invention,
formed in a manner similar to that shown and described in connection with Figures
2 - 7, but with a secondary surface fin at one edge thereof. Corresponding features
of the Figure 14 channel element are numbered correspondingly with rescect to Figures
2 - 7, but with the respective reference n:nbers in Figure 14 being numbered with
respect to the Figureis 2 - 4 drawings by addition of 200 to the corresponding reference
number in Figures 2 - 4. The numbering of Figure 14 is also common to Figures 15 and
16 , as heraim- after described. The secondary surface fins shown in Figures 14'-
16 are of a type as described in Kun U. S. Patent No. 3,810,509 and also disclosed
and claimed in Kun U. S. Patent No. 3,845,814. In all three embodiments of Figures
14 - 16, the secondary surface fin members are joined to the primary surface channel
element at the edge wall margins 316 and, in practice, it may be des able to form
the channel member with the secondary surface fin member integral with one or the
other of the halve; of the channel element.
[0043] In the Figure 14 embodiment, a single fin member 350 is joined to the channel element
at one edge thereof along margin 316. The fin is, consistent with the teachings of
the above-mentioned Kun patents, suitably provided with slots or louvers 351 along
substantially the entire length of the fin. The channel element shown in Figure 15
represents a modification of the Figure 14 channel element wherein the latter is provided
with an additional fin 352 having louvered surface distortions 353 distributed across
its surface along the length thereof, the additional fin being provided on the opposite
edge wall from the first fin 350. In the Figure 16 embodiment, the channel element
is provided with dual fins 354 and 356 at its opposite edges, the fins having surface
distortions 355 and 357. in the form of "louvered slots of the type described previously
in connection with Figures 14. and
15. In Figures 14 - 16, the end section of each channel element is finless, so that
when the channel elements are stacked in array to form a heat exchanger core assembly,
they can be easily headered in the heat exchanger final assembly by prior art headering
means. The fins in the Figures 14 - 16 embodiments can be separately attached to the
longitudinal edge of the channel element, as for example by welding or braizing, but,
as mentioned, the fins are preferably integral with the edge walls of the channel
elements. Such integral construction greatly improves the heat transfer performance
of the fins.
[0044] Figure 17 is an elevational view of a portion of a stacked array of heat exchange
channel elements of the type shown in Figures 2 - 7. The stacked array 400 is made
up of heat exchange channel elements 110 to form a heat exchanger core assembly. The
channel elements in the Figure 17 array are longitudinally aligned in parallel spaced
relation, i.e., to provide spaces between adjacent channels through which second fluid
may be flowed in heat excha. ge with a first fluid being conducted through the channel
interior passages. Each channel element has a first fluid entrance opening at one
end and a first fluid exit opening at the opposite end, as previously described. The
channel elements 410 in the array have wall projection portions 417 having load-bearing
end segments which are shaped and arranged for mating with and abutting against load-bearing
end segments of the projection portions of an adjacent channel element side wall,
with the abutting load-bearing surfaces of the channel element facing projections
being adhesively bonded to one another by bonding medium 402. Such bonding of the
mating and abutting load-bearing surfaces of the channel element wall projections
is not essential in the practice of the invention, and in some instances it is preferable
to mate an abut the opposed wall projection end-segments against one another without
any interposed bonding medium. The end sections 421 of the channel element in the
stacked array are of enlarged cross section relative to the intermediate sections
of the channel elements and, as previously described, are provided with flat side
wall portions which permit mating of adjacent channel elements in the manner shown.
In practice, it is generally desirable to adhesively bond the channel element . in
section flat side wall portions to one another by adhesive bonding medium 401, so
as to insure leak tightness of the associated inlet or outlet face of the stacked
array at the extremities of the tubes, i.e., so that the first fluid introduced to
or withdrawn from the channel element at its extremity does not leak out of the heat
exchanger between adjacent channel element end section. The bonding media 401 and
402 may suitably comprise an epoxy or other conventional adhesive material.
[0045] Figure 18 is a modification of the form of channel element stacked array shown in
Figure 17. In the Figure 18 array, the multiple channel elements 410 are disposed
in the stacked array 400 with secondary surface plate-like members 403 being disposed
between adjacent channel elements with the load-bearing end segments 418 of the wall
projection portions 417 of the channel elements being shaped and arranged for mating
with and abutting against the secondary surface members, whereby the secondary surface
members are maintained in thermal contact with the channel elements along the abutting
load-bearing end segments thereof. The secondary surface plate-like member 403 may
be anchored in the stacked channel element assembly -by bonding same between the end
section facing side walls of the channel element end sections 421 as shown, with the
extremity of the plate-like member being embedded in the adhesive mass 401 bonding
the adjacent channel elements sections. In this embodiment, the secondary surface
plate-like member is then held in place compressively along the intermediate section
of the channel element by the frictional compressive contact of the channel element
wall projection end segment against the plate-like member. As shown in Figure 18,
the secondary surface members may suitably be substantially planar.
[0046] Figure 19 is an elevational view of a stacked array of channel elements according
to another embodiment of the invention, wherein each channel element is characterized
by an alternating series of projections having different heights. The portion of the
array shown comprises portions of channel elements 50 and 51, the former having alternating
wall projections 52 of greater height and an alternating series of wall projections
54 of lesser height. The taller projections 52 of channel element 50 mate and abut
at their extremities with shorter wall projection portions 53 of channel element 51.
Correspondingly, shorter wall projections 54 of channel element 50 mate and abut at
their load-bearing extremities with taller wall projections 55 of channel element
51. In this manner, the sequential projections of varying height mate abuttingly with
complimentary projections of the adjacent channel element so that the channel elements
are oriented parallelly with respect to one another, i.e., so that their longitudinal
axes are parallel with respect to one another. The load-bearing extremities of all
of the wall projections are flat and parallel to the channel element wall surface
between adjacent wall projections.
[0047] As to characterization of the channel elements in the Figure
19 stacked array, it is seen that each channel elementhas associated therewith two base
planes, base plane P
1 associated with the shorter wall projections of the channel element and base plane
P
2 associated with the taller wall projections of the channel element. As defined hereinearlier
the base plane of the channel element wall member is a plane containing the extremities
of wall surface projections extending outwardly from the wall member surface to a
uniform extent. As a result of the fact that two channel elements are associated with
the channel element, the channel element likewise is characterized by two values of
the H parameter, the maximum height measured perpendicularly from the base plane of
the wall member to the innermost point on the wall member surface between adjacent
wall surface projections. Thus, the H value associated with base plane P
I is H
1 and the H value associated with base plane P
2 is
H2. Despite the fact that each channel element thereby is characterizable by two discrete
values of the H parameter, each value must satisfy the dimensional criteria of the
invention, e.g., the H/D ratio must be between about 0.05 and 0.5. It will be apparent
that the D spacing parameter will have the same numerical value as measured in either
base plane associated with adjacent wall projections of different height, when the
major axes of the wall projections under consideration are projected into the given
base plane.
[0048] Figure 20 is an elevational view of two aligned channel elements 60 and 61 adapted
for mating with one another along the surfaces of their load-bearing end segments.
As shown, chamel element 60 has disposed on its upper wall member surface wall projections
65 having a male load-bearing end segment 72 with a minor axis of length D
1, as measured by the projected length of such minor axis in base plane P
1 containing the extremities of the wall surface projection on the upper wall surface
of the channel element.. On the lower wall member surface of channel element 60 are
disposed wall projection portions 66 having female load-bearing surfaces 71 at their
extremities, with the outermost extremities of the wall projection portions lying
in base plane P . As shown by the Figure 20 embodiment, the H dimension on the upper
surface of the channel element, H
u, may be different from that associated with the lower wall surface, H
1. The channel element 61 in the Figure 20 array is similarly provided with wall projection
portion 67 on its upper surface having male load-bearing end segements 69 and wall
projection portion 68 on its lower wall member with female load-bearing segments at
their extremities. In this manner, the adjacent channel element 60 and 61 may be mated
with one another so that the male and female-load-bearing surfaces 69 and 71 of associated
wall projections . 67 and 66 interfit with an abut against one another.
[0049] Figure 21 is an isometric view of a portion of a heat exchange channel element according
to another embodiment of the invention, having two distinct alternative configurations
disposed on its upper wall member surface. The channel element 74 includes two spaced
apart members 78 and 79 of thermally conductive material bounding a fluid flow channel
77 and having 'the wall section portions 80 and 82 disposed on its wall member surface
75 and extending therefrom with load-bearing end segments 81 and 83 respectively at
their extremities, whereby a channel element may be supported abuttingly against an
adjacent structural member by the load-bearing end segments of the wall projection
portions. The wall members 78 and 79 constitute side walls of the channel element
spaced apart by edge walls 76. Each of the wall projection portions 80 and 82 extend
elongately on the wall member surface 75 across the width of the channel element along
a direct substantially perpendicular to the longitudinal axis L-L of the channel element.
[0050] The-load-bearing end segments of the wall projection portions shown in Figure 21
differ from those previously described in that the load-bearing surface as a continuously
varying elevation along the major axis direction of the wall projection, the first
wall projection 80 having a load-bearing surface 81 which is undulate in elevational
contour along the major axis direction, while the second wall projection 82 has a
load-bearing surface 83 is of saw-tooth form along the major axis direction of the
projection. Where the elevational contour of the wall projection load-bearing end
segment is not flat and wholly within the base plane of the wall member, the length
d of the major axis of the wall projection portion load-bearing end segment is measured
as the projected length of the major axis in the base plane of the wall member, in
the same manner that the non-linear elevational contour of the load-bearing end segment
in the minor axis dimension is measured as the projected length of the minor axis,
or, more simply, as the projected width of the load-bearing surface in the base plane
of the channel element, as shown in Figure 20.
[0051] Figure 22 is an elevational view of a stacked array of heat exchange channel elements
according to another embodiment of the invention. As shown, the stacked array 450
comprises stacked channel elements 456, 457 and 458. Each channel element includes
spaced-apart wall members comprising upper wall member 451 and lower wall member 452,
each formed in accordance with the invention having ridge wall projection portions
453 extending elongately across the channel element substantially from edge to edge
thereof. Each ridge projection has a load-bearing segment 454 at its extremity, with
adjacent ridge projections being spaced apart from one another by interposed concave
surface portions 455. In this manner, the channel elements are "nested" with the ridge
projection load-bearing segments 454 bearing against the crest of the concave surface
portion 455 of an adjacent channel element. Such an arrangement permits very close
stacking of the constituent channel elements and thereby provides a highly compact
heat exchanger assembly.
[0052] Figure 23 is an isometric view of a portion of a stacked array of heat exchange channel
elements according to the invention, as interleaved with secondary surface plate-like
members to form a heat exchanger core assembly. The heat exchanger core assembly 500
comprises a multiplicity of channel elements 510 of a type similar to that shown in
Figure 15. The structual features of the primary surface of the channel element is
numbered correspondingly with respect to Figure 2 by addition of 500 to the corresponding
reference numerals of Figure 2. The secondary surface fins of the channel elements
are numbered correspondingly with respect to Figure 15 by addition of 200 to the corresponding
reference numerals for the secondary surface fins in Figure 15. In the stacked array,
a multiplicity of channel elements are disposed with secondary surface plate-like
members 503 being disposed between adjacent channel elements with the load-bearing
end segments of the wall projection portions of the channel elements being shaped
and arranged for mating with and abutting against the secondary surface members, whereby
the secondary surface members are maintained in thermal contact with the channel elements
along the abutting load-bearing end segments thereof. The secondary surface plate-like
members in this embodiment have a multiplicity of surface distortions 560 distributed
across portions of their surfaces which are not in abutting contact with channel element
load-bearing segments. More specifically, these plate-like member distortions comprise
parallel slats and slotted apertures arranged in a louvered configuration across the
width of the secondary surface member.
[0053] Figure 24 is a plan view of another secondary surface plate-like member, such as
may alternatively be employed in the Figure 23 stacked array of heat exchange channel
elements. The plate-line member shown in Figure 24 has been found particularly useful
in the practice of the invention wherein the heat exchange channel elements are employed
to form a radiator heat exchanger for automotive vehicles. In this plate-like member
configuration, the surface 606 of the plate member 603 alternatively punched in opposite
directions perpendicular to the plane of the plate so that rectangular strips of metal
are displaced therefrom to form successive depressed portions 604 and raised portions
605.
[0054] Figure 25 is sectional, elevational view of the plate-like member of Figure 24, taken
along line A-A thereof. As shown in Figure 25, the raised portion 605 and depressed
portions 604 are punched in such manner that respective portions are parallelly aligned
in elevational view with the undeformed surface 606 of the plate member 603. This
form of surface distortions of the plate-like secondary surface member permits highly
efficient heat transfer along the gas flow path traversing the plate member in the
direction shown in Figure 23.
[0055] Figure 26 is an elevation view of a wind tunnel for testing performance of heat exchangers,
which was employed to evaluate automobile radiator exchangers constructed according
to the present invention comparatively against radiator heat exchangers of the prior
art, with results as hereinafter described in greater detail.
[0056] The wind tunnel of Figure 2
6 is used to regulate the rate and temperature of an air flow through the passages
formed between adjacent heat exchange channel elements in the radiator heat exchanger
being tested. Air entering the tunnel was first passed through a calibrated orifice
760, whichmeasures the air volume flow into a four cubic foot plenum chamber 761,
and then fed through flow straightening screens 762 into a tapered adapter sections
763. The adapter section 763 was provided to effect a smooth transition in the air
flow between the plenum chamber 762 and a one square foot wind tunnel duct 764 coupled
to a test radiator 765. A blower (not shown) was positioned downstream of the radiator
for controlling the air flow therethrough. The heated air from radiator 765 was either
exhausted via damper 766 or recirculated into the test room via damper 767 so as to
provide a degree of temperature control within the room. To reduce the air flow rate
through the radiator, control damper 768 was coupled downstream of exiting air flow
radiator 765. The tapered adapter section 763 and the flow straightening screens 762
are employed to keep velocity variation through the test radiator 765 at a minimum.
Velocity profiles and pitot tube readings made over the frontal area of different
test radiators 765 indicated that the air velocity variations for all the radiators
tested was insubstantial. One - manometer 770 was positioned as shown in the test
circuit and employed to measure air pressure drop. Two grids, 772 and 773, containing
four thermocouples, each of which was placed in the center of one-quarter of the flow
passage area of the radiator 765, measured the average inlet and exit air temperature
through the test radiators765. A Brown multipoint chart recorder (not shown) and a
Rubicon potentiometer (not shown) were coupled to the grids and recorded the thermocouple
heatings. Thus, an accurate test circuit was provided for measuring the heat transfer
capacity of the test radiators. As indicated above, test results based on evaluation
of heat exchangers constructed in accordance with the present invention and heat exchangers
constructed with the prior art, as derived from evaluation of the various test heat
exchangers in the wind tunnel apparatus of Figure 24 are presented and discussed in
detail hereinafter.
[0057] Figure 27 is an exploded assembly drawing of a portion of a heat exchanger according
to the invention, comprising a stacked array of heat exchange channel elements of
the type shown in Figure 15. As shown, the heat exchanger assembly comprises a stacked
array 850 of heat exchange channel elements 851. Each channel element has a longitudinal
axis and is bounded by thermally conductive pressure withholding walls, with a first
fluid entrance opening at one end, a first fluid exit opening at the opposite end,
and end sections each having a cross-section bounded by flat side walls and by edge
walls comprising edge wall portions extending outwardly from the side walls and convergently
with respect to each other, with the outermost ends of the edge wall portions being
contiguous and coextensive with respect to one another to form a leak-tight edge wall.
Adjacent channel elements in the array are stacked with their end section side walls
in wall to wall contacting relationship and their end section edge walls in alignment
to form a first fluid entrance face at one end of the array and a first fluid exit
face at the opposite end of the array. Each face has a perimeter defined by edge wall
ends 854 of the stacked channel elements and outermost side wall ends 855 of the outermost
channel elements 852 and 853 in the array. The pressure withholding walls of adjacent
channel elements in the interior of the array are disposed in spaced relationship
with respect to each other for flow -of a second fluid through the array in the space
between the channel elements in heat exchange with the first fluid. The heat exchanger
assembly shown in Figure 25 is of the cross-flow type and is constructed and arranged
for flow of the second fluid through the array in a direction normal to the longitudinal
asis of the channel elements. The channel elements are disposed in the stacked array
with their longitudinal axes lying in a common plane. In the preferred practice of
the present invention, in order to achieve a highly compact exchanger configuration
with a high level of heat transfer capability per unit volume of the exchanger, the
stacked array contains at least 40 channel elements per foot width thereof, with the
width of the stacked array being measured in the aforementioned common plane in a
direction perpendicular to the channel element longitudinal axes. Inlet header means
are joined in flow communication with the first fluid entrance face for introduction
of first fluid to the channel elements, and an outlet header is joined in flow commincation
with the first fluid exit face for withdrawal of the first fluid from the channel
elements. The channel elements 853 are provided with secondary surface fins 856 having
louvered surface distortions 857 thereon.
[0058] The headering arrangement in the Figure 27 assembly includes sealing members 858
extending along the end section edge walls of the channel elements at each side of
the stacked array. Each sealing member has a bearing surface with a generally corrugated
contour of grooves 859 and interposed ridges 860 with each of the grooves shaped so
as to surround and abut the edge wall of a single channel element of the array with
the interposed ridges extending inwardly and abutting the facing edge wall portions
of adjacent channel elements. The bearing surface of each sealing member is bonded
to the abutted channel element egge walls associated therewith, and suitably has a
length as measured parallel to the channel element longitudinal axes of at least 0.2
inch which is substantially greater than the thickness of the sealing member as measured
perpendicular to the channel ele-
ment longitudinal axes at a lower extremity of the grooves in the bearing surface thereof.
[0059] In this headering arrangement, clip members 869 are provided having a transversely
extending first segment 870 a leak-tightly abutting the outer end. 857a of the sealing
member 858,a longitudinally extending second segment 870b integrally joined to the
transversely extending first segment and adhesively bonded to an exterior surface
of the sealing member, and a third end segment 871integrally joined to the longitudinally
extending second segment 870b. The header tank means in Figure 27 comprise a header
tank member 874 having enclosure end wall 877 and side wall875, 876 portions and a
transversely outwardly extending flange protion880 at an end of each side wall portion.
The header tank member is provided with conduit 881 for first fluid introduction to
or discharge from the heat exchanger assembly. When header tank member 874 and clip
member869 are disposed in position as assembled, the third end segment 871 of the
clip member is deformed contiguously around the transversely outwardly extending flange
portion 880 of the header tank member to secure the header tank member in position.
[0060] The heat exchanger assembly of Figure 27 features a tie bar structural support member
866 which is disposed against the side wall of the outermost channel element 858 in
the stacked array, to absorb the outwardly directed pressure exerted by the stacked
array in operation. The tie bar 866 is structurally coupled with angle bracemember
861 in the heat exchanger assembly. As shown, angle brace member 861 comprises a longitudinally
extending portion 862 and a transversely extending portion 864. Each of the clip members
869 has a transversely extending tab 872 which is positioned on the top surface of
the transverse portion 864 of angle brace 861. Tie bar 866 is positioned beneath angle
brace member 861, with the flange portion 867 of the tie bar abutting the underside
of the transverse portion 864 of the angle brace member. The header tank member 874
is then positioned so that the flange portion 880 thereof is disposed against the
transverse tabs 872 of the respective clip members 869. In this fashion, the apertures
879 in the flange portion 880 of the header tank member are brought into register
with the apertures 873 in the transverse tabs of the clip members 869, apertures 865
in the transverse portion 864 of the angle brace member 861 and apertures 868 in the
flange portion 867 of tie bar 866, so that bolt or screw means may be inserted through
the aligned apertures so as to secure the assembly together. In this manner, apertures
879 in side wall 876 of the header tank member 874 are brought into alignment with
apertures 863 in the longitudinally extending portion 862 of the angle brace member
861, so that screw or bolt means can be passed through the aligned apertures for additional
securement of the assembly.
[0061] Figure 28 is a sectional plan view of a portion of the Figure 27 heat exchanger assembly,
showing the details of construction thereof. Channel elements 851 in the array 850
are stacked with their end section side walls 890, 891 in wall to wall contacting
relationship adhesively bonded together by adhesive 893 such as epoxy. The channel
element and sections each have a cross-section bonded by flat side walls and by edge
walls 854.comprising edge wall portions 854a, 854b extending outwardly from the side
walls and convergently with respect to each other, with the outermost ends 895 of
the edge wall portions being contiguous and coextensive with respect to one another
to form a leak-tight edge wall. In this manner, a first fluid face is formed at an
end of the array., having a perimeter defined by edge wall ends of the stacked channel
elements and outmost side wall ends 892 of the outermost channel element 853 in the
array. The serpentine-shaped sealing member 858 extends along the end section edge
walls of the channel element at a side of the stacked array. The sealing member 858
has a bearing surface with a generally corrugated contour of grooves 859 and interposted
ridges 860 shaped so that the grooves surround and abut the edge wall of a single
channel element of the array with the interposed ridges extending inwardly and abutting
the facing edge wall portions of adjacent channel elements. The bearing surface of
the sealing member 858 is bonded to the abutted channel element edge walls associated
therewith by means of adhesive medium 897. The exterior surface of the sealing member
858 is adhesively bonded to the longitudinally extending second segment 870b of the
clip member 869 by means of adhesive medium 898. The side wall of the outermost channel
element 853 in the stacked array is adhesively bonded to tie bar 866. As shown, the
third end segment 871 of the clip member 869 is deformed contiguously around the transversely
outwardly extending flange portion 880 of the header tank member to secure the header
tank member in position.
[0062] Figure 29 is a sectional elevational view of. a portion of the heat exchanger assembly
of Figure
27. In the portion of the assembly as shown, the channel element 900 has an end section
901 and edge wall portions 902 having outer ends 903 which form a leak-tight edge
wall. The channel element features a secondary surface fin 904 with slatted, louver-type
surface distortions 905 thereon. The header tank member 874 has a transversely outwardly
extending flange portion 680 at an end of the side wall portion 875. The sealing member
858 has bearing surface with a generally corrugated contour of grooves 859 and interposed
ridges 860, with each of the grooves shaped so as to surround and abut the edge wall
of a single channel element of the array with the interposed ridges extending inwardly
and abutting the facing edge wall portions of adjacent channel elements. The bearing
surface of the sealing member 858 is bonded to the abutted channel element edge walls
associated therewith by adhesive bonding medium 910. Sealing element 858 suitably
has a length as measured parallel to the channel element longitudinal axis of at least
0.2 inch which is substantially greater than the thickness t of the sealing member
as measured perpendicular to the channel element longitudinal axis at a lower extremity
of the grooves in the bearing surface thereof. The headering arrangement comprises
clip member 869 having a transversely extending first segment 870 leak-tightly abutting
the outer end 858a of the sealing member 858, a longitudinally extending second segment
906 integrally joined to the transversely extending first segment 870 and adhesively
bonded. to an exterior surface of the sealing member by adhesive bonding medium 909,
and a third end segment 871 integrally joined to the longitudinally extending second
segment 906 and deformed contiguously arround the transversely outwardly extending
flange portion 880 of the header tank member 874 to secure the header tank member
in position. As shown, the clip member second segment 906 is also adhesively bonded
to the header tank member enclosure side wall portion 875 by adhesive 908 to further
secure the header tank member in position.
[0063] Figure 30 is an isometric view of a portion of a heat exchanger assembly employing
another type of headering arrangement which may suitably be employed in a heat exchanger
according to the present invention. In the portion of the assembly as shown, the heat
exchanger core 799 comprises a stacked array of channel elements 800 each having edge
wall portions 802 which form a leak-tight edge wall. The header tank member 874 has
a transversely outwardly extending flange portion 880 at an end of the side wall portion
875. The sealing member 858 has a bearing surface with a generally corrugated contour
of grooves 859 and interposed ridges 860, with each of the grooves shaped so as to
surround and abut the edge wall of a single channel element of the array with the
interposed ridges extending inwardly and abutting the facing edge wall portions of
adjacent channel elements. The bearing surface of the sealing member 858 is suitably
bonded to the abutted channel element edge walls associated therewith by an adhesive
bonding medium as described hereinabove in connection with Figure 29. Sealing element
858 preferably has a length as measured parallel to the channel element longitudinal
axisof at least 0.2 inch which is substantially greater than the thickness of the
sealing member as measured perpendicular to the channel element longitudinal axis
at a lower extremity of the grooves in the hearing surface thereof. The headering
arrangement comprises clip member 869 having a transversely extending first segment
870 leak-tightly abutting the outer end 858a of the sealing member 858, a longitudinally
extending second segment 806 integrally joined to the transversely extending first
segment 870 which may be adhesively bonded to an exterior surface of the sealing member
858 by any suitable adhesive bonding medium, and a third end segment 871 integrally
joined to the longitudinally extending second segment 806 and deformed contiguously
around the transversely outwardly extending flange portion 880 of the header tank
member 874 to secure the header tank member in position. As shown, a gasket 890 is
positioned in a groove in the side wall 875 of the header tank member 874 such that
the gasket bears compressively against the upper surface of the clip member first
segment 870 to form a leak-tight seal between the heat exchanger core assembly and
the header tank member 874. In practice, the gasket may be formed of any suitable
material as for example Buna-N or neoprene having a durometer value of 60 to 80.
[0064] The heat exchange channel element of this invention as incorporated in automobile
radiator exchangers has been extensively tested relative to the prior art stacked
channel element heat exchangers disclosed in Kun U. S. Patent No. 3,757,856; Kun U.
S. Patent No. 3,810,509; and Kun U. S. Patent No. 3,845,814. Such testing has amply
proven the superiority of the channel element and heat exchanger fabricated therefrom
according to the present invention relative to the channel elements and heat exchangers
of the aforementioned Kun patents, as shown in the ensuing discussion.
[0065] Figure 31 is a graph of convective heat transfer effectiveness factor plotted as
a function of Reynold's number, for various heat exchanger embodiments of the present
invention and for a heat exchanger constructed in accordance with Kun U. S. Patent
No. 3,810,509. The data from which the curve shown in Figure 31 were plotted were
generated with radiator heat exchanger test samples, as hereinafter described, in
the wind tunnel test apparatus shown in Figure 26 and described hereinabove. In a
typical test in the wind tunnel apparatus, the inlet air velocity was maintained at
90°F with a 100°F temperature difference between the inlet air and the temperature
of the coolant fluid introduced into the radiator at the inlet face of the heat exchanger
core assembly. The coolant fluid circulated through the interior passages of channel
elements in the radiator samples during the tests was a mixture of 45% ethylene glycol.,in
water; this coolant was circulated through the radiator samples at the rate of 14.5
gallons per minute per foot width of the radiator, the width of the radiator being
measured in a plane containing the longitudinal axes of the stacked channel elements,
in a direction perpendicular to the channel element longitudinal axes.
[0066] Curve A of Figure 31 is based on data for a radiator sample constructed in accordance
with the prior art. Each channel element in the radiator sample was fabricated from
0.008 inch thick aluminum in the manner taught in Kun U. S. Patent No. 3,810,509.
Each channel element was 1.112 inches wide and the primary surface wall member was
provided with eliptical shaped wall-supporting projection portions having an effective
diameter, d as defined in the Kun patent of 0.137 inch. The wall-supporting projection
portions were provided in a triangular array with an effective spacing D of 0.48 inch
between adjacent projections. Each wall-supporting projection portion of the channel
element wall member had a height H of 0.043 inch. Secondary surface fins were provided
fore and aft on the edge walls of the channel elements, each fin having a fin angle
Y of 30°, a slot angle α of 90° and a slat angle of 45°, all as defined in the Kun
patent. Each secondary surface fin was 0.389 inch wide with an individual slat dimension
for the louvered surface distortions on the fin of 0.035 inch by 0.327 inch. The radiator
heat exchanger constructed from the above-described channel elements had a density
of 100
` channel elements per foot width of the heat exchanger, with the width of the stacked
array being measured in a common plane containing the channel element longitudinal
axes, in a direction perpendicular to the channel element longitudinal axes.
[0067] The ordinant of the Figure 31 draft is the dimensionless ratio of the Colburn factor
j to the Fanning friction factor f. This ratio is a convective heat transfer effectiveness
factor, with a value of 0.5 being the theoretical maximum value. The abscissa of the
draft is the Reynold's number, with the Reynold's number being based on the flow of
air through the radiator heat exchanger interchannel spaces in a direction normal
to the aforementioned common plane containing the longitudinal axes of the stacked
channel elements in the radiator's core assembly. As shown by curve A in Figure 29,
a radiator fabricated from primary surface heat exchange channel elements, as described
hereinabove, which is typical of the teachings of the aforementioned Kun patent, has
a j/f value of about 0.225 at a Reynold's number of 600 which decreases to a j/f value
of about 0.156 at a Reynold's number of about 4,000.
[0068] The heat transfer performance of the prior art radiator constructed in accordance'with
the teachings of the Kun patent, as reflected in curve A, is to be contrasted with
curves B, C, D and E, which represent the heat transfer performance of various radiator
heat exchangers constructed in accordance with the present invention.
[0069] In the radiators which were tested to yield curve B - E, the heat exchange channel
elements in the radiators were fabricated from 0.008 inch thick aluminum. Each channel
element was 0.94 inch in width. The channel elements at a configuration generally
similar to that shown in Figure 2 - 4. herein, with the following dimensions: H =
0.055 inch, d
l = 0.020 inch and D = 0.6 inch. The wall surface between adjacent ridge projections
at a circular concave contour with a constant radius of curvature, R
1 of 0.792 inch, and the edge wall of the channel element at a convex contour as shown
in Figure 4. Each radiator had88 channel elements per foot width thereof, with the
width of the raidator being measured in a common plane containing the longitudinal
axes of the channel elements, as measured in a direction perpendicular to the channel
element longitudinal axes.
[0070] Curve B of Figure 31 is a plot of heat transfer data for a radiator with a core of
the type shown in Figure 18, wherein planar secondary surface plate-like members are
disposed between adjacent channel elements. Each plate-like member had smooth surfaces
no surface distortions thereon. Each plate-like member was fabricated from aluminum
of 0.006 inch thickness and had a width of 0.0625 inch. The secondary surface member
was secured between the adjacent channel element solely by the compressive forces
between the abutting opposed wall projection portions of the respective channel elements.
As shown by the graph of Figure 31, this radiator had a j/f value of 0.275 at a Reynold's
number of 600 and a value of about 0.220 at a Reynold's number of 4,000. These values
represent a 22% increase in heat transfer effectiveness at the Reynold's number value
of 600 and a 41% increase in heat transfer effectiveness at the upper value of Reynold's
number of 4,000 relative to the performance of the prior art radiator of curve A.
[0071] Curve C is a plot of the heat transfer data for a radiator having a core as shown
in Figure 16 herein. The plotted data show that this radiator at a j/f value of 0.320
at a Reynold's number of 600 and a value of about 0.232 at a Reynold's number of 4,000.
This performance represents a 42% increase at the lower Reynold's number value of
600 and a 49% increase at the upper value of 4,000 relative to the prior art.radiator
of curve A. Furthermore, based on these data, the radiator of curve C represents a
16% improvement in heat-transfer effectiveness factor at the lower Reynold's number
value of 600 and a 6% increase at the upper value of 4,000, relative to the radiator
of curve B. Apart from such comparison of convective heat transfer efficiency, the
radiator of curve B is superior to the radiator of curve C in other respects, as will
be shown more fully hereinafter.
[0072] Curve D is a plot of the heat transfer data for a radiator comprising channel elements
formed similarly to the channel element of Figure 14 herein, with each channel element
being provided with a single front longitudinal secondary surface fin and a single
rear longitudinal fin. The secondary surface fins each had slatted, slotted louvered
surfac distortions in the manner taught by Kun U. S. Patent No. 3,845,814. The front
fin had an angle of orientation .; of 30°, while the rear fin had an angle of orientation
of 0°. Each fin had a slot angle a of 90° with a slat angle 9 of 45°. The fins were
each 0.324 inch in width with the individual slats having a dimension of 0.25 inch
by 0.35 inch. The fin angles γ, α and β referred to above are as defined in the aforementioned
Kun patent. These finned channel elements were stacked in the heat exchanger core
as shown in Figure 17, with a smooth secondary surface plate-like member being disposed
between the adjacent channel elements. This radiator had a j/f value of 0.382 at a
Reynold's number of 600 and a j/f value of 0.287 at a Reynold's number of 4,000. This
performance represents a 70% increase in the convective heat transfer efficiency factor
at the lower Reynold's number value of 600 and an increase of 84% at the upper Reynold's
number value of 4,000 relative to the prior art radiator of curve A.
[0073] Curve E plots the heat transfer data for radiator constructed in the same manner
as the radiator of curve D, but without secondary surface plate-like members disposed
between adjacent channel elements in the radiator core. Otherwise, tne radiator for
curve E was identical in all dimensional respects to the radiator of curve D. as shown,
the radiator of curve E had a j/f value of 0.422 at a Reynold's number of 600, and
a value of 0.318 at a Reynold's number of 4,000. These end-point values for the particular
Reynold's number range considered represent convective heat transfer performance improvement
of 88% and 104%, respectively, relative to the prior art radiator of curve A. As shown
by the graph of Figure 31, the radiators constructed in accordance with the present
invention all provided substantial improvement in convective heat transfer efficiency
over the full Reynold's number range considered relative to the prior art radiator
(curve A) constructed in accordance with the teachings of Kun U. S. Patent No. 3,810,509.
[0074] Based on the respective curves B - E of Figure 31, representing various embodiments
of the present invention, it might appear that the use of a secondary surface plate-like
member between adjacent channel elements in the radiator core, in the manner shown
in Figure 18 herein, would be disadvantageous relative to the provision of a heat
exchanger core lacking such form of secondary surface, as for example, in a core of
the type shown in Figure 17 herein. In Figure 31, the position of the curves C and
E, representing radiators with such secondary surface plate-like members, are seen
to be positioned vertically above the corresponding curves B and D, respectively,
the latter pair of curves representing radiators provided with such secondary surface
plate-like members between the adjacent elements in the heat exchanger core. Despite
such fact i.e., that the provision of secondary surface plate-like members between
adjacent channel elements in the core of the radiator decreases the convective heat
transfer effectiveness of the radiator, it is shown in Figure 32 that the heat transfer
material effectiveness of the radiators with secondary surface plate-like members
is in fact higher than the heat transfer material effectiveness values for radiators
lacking such secondary surface members.
[0075] Figures 32 is a graph of heat transfer material effectiveness for the radiators previously
described in connection with Figure 31, plotted as-a function of gas flow velocity
at the face of the radiator. The curve designations B - D in Figure 32 refer to the
same radiators described in connection with the correspondingly labeled curves in
Figure 31. The ordinate of Figure 32 is the material effectiveness of the radiator,
expressed in units BTU/lb. of metal in the radiator core, representing the amount
of heat transferred, in BTUs, from the coolant flowing through the interior passages
of the channel elements to the external heat transfer medium (air) flowing over the
exterior surfaces of the channel elements and secondary surface members, if " present.
The abscissa of Figure 32 is the face velocity of the air flow through the radiator,
measured in units of feet per minute; the face velocity is the gas velocity measured
at the forward base of the radiator in the test assembly, as measured in a direction
perpendicular to the plane containing the longitudinal axes of the stacked channel
elements in the radiator core. As illustrated in Figure 32, the use of secondary surface
plate-like members between adjacent channel elements in the radiator, represented
by curves B and D, provided significant improvement in the heat transfer capacity
per unit weight of metal employed in the radiator as compared to the material effectiveness
values for the corresponding heat exchanger lacking such secondary surface plate-like
members, represented by curves C and E, respectively. Inasmuch as weight considerations
are an important factor in general radiator design, the use of secondary surface plate-like
members between adjacent channel elements in the manner previously described imparts
a valuable design flexibility in radiators according to the present invention, since
the same total heat transfer capacity can be realized in a correspondingly smaller
sized radiator than if such secondary surface members are not employed. It will be
apparent that the choice of whether or not to employ secondary surface plate-like
members between adjacent channel elements in heat exchangers constructed according
to the present invention will depend on various considerations including those reflected
in Figures 31 and 32 of convective heat transfer effectiveness (pressure drop) and
material effectiveness of the heat exchanger in terms of the heat exchange capacity
per unit weight of heat transfer surface in the exchanger.
[0076] The channel elements of the present invention also afford a substantial advantage
relative to the. channel elements of the previously mentioned Kun patents with respect
to the pressure loadings and differentials which the channel elements can accommodate.
This is shown by Figure 33, which is a graph of channel element wall member deflection
plotted as a function of internal vacuum pressure and also as a function of internal
buckling pressure for a channel element according to the present invention (represented
by the curves labeled "M") and a channel element according to Kun U. S. Patent No.
3,810,509 (represented by curves labeled "
N').
[0077] In both the buckling and vacuum pressure tests, from which the data plotted in the
graphs of Figure 31 were generated, a single channel element was restrained by two
blocks each disposed along a side wall of the channel element against the load-bearing
end segments of the wall projection portions thereof. The end blocks were formed of
rigid plastic and, when positioned against the side wall projections of the channel
element, were retained in position by suitable clamping means. Small holes were provided
in the blocks through which deflection probes were inserted to measure deflection
of the channel element side wall member at the innermost point on the exterior wall
surface. In these tests, the deflection of the blocks was also measured and the values
measured were subtracted from the indicated values of deflection of the channel element
wall member. Both initially open ends of the channel element were sealed with an epoxy
sealant, and a tube was provided at one end section of the channel element in closed
gas flow communication with the interior passage of the channel element for feeding
of gas into the channel element interior passage or exhaustion gas therefrom. The
curves in Figure 33 each represent averaged values for multiple runs of the test procedure.
[0078] The curves labeled "N" in the graphs of Figure 31 were based on tests involving channel
elements fabricated from aluminum of 0.008 inch thickness in the manner taught Kun
U. S. Patent No.3, 810,509. The surface of such channel element was provided with
a multiplicity of wall projection portions distributed across-the wall member surface,
each projection having a circular load-bearing end segment with a diameter of 0.045
inch. The wall surface projections were provided in a triangular array with an effective
spacing between projections of 0.48 inch and the height of each wall supporting projection
was 0.043 inch. The channel element according to the present invention, which was
tested to yield the curves labeled "M" in the graph of Figure 33, was fabricated from
aluminum of 0.008 inch thickness and had the dimensional parameters set forth in Table
I herein under the heading "Figure 5 Elevational Contour".
[0079] In the vacuum pressure deflection test, reflected in the plots on the left-hand side
of Figure 33, gas was evacuated from the channel element through the aforementioned
conduit in gas flow communication with the interior passage of the channel element
and the deflection of the wall member surface between adjacent wall projections was
measured at various values of vacuum pressure, measured in units of inches of Hg.
As shown by the plot of vacuum pressure deflection, the prior art channel element
of curve N relatively large and rapidly increasing levels of deflection with increasing
vacuum pressure, while the channel element according to the present invention, by
comparison, showed relatively little wall deflection even at high negative pressure
level. For example, at a vacuum pressure of -20 inches Hg, the deflection measured
for the prior art channel element curve N was about 0.43 mm while the wall deflection
of the channel element according to the present invention at the same vacuum pressure
level was - only 0.04 mm. The deflection of the channel element according to the present
invention was thus over 90% lower than the wall deflection of the channel element
according to the prior art, at the vacuum pressure level of -20 in. Hg. f
[0080] The right hand plot in Figure 33 shows deflection of the channel element wall member
as a function of positive internal pressure in the channel element interior passage.
As shown, the deflection values characteristic of the prior art channel element (curve
N) are substantially and increasingly greater than the deflection values for the channel
element according to the present invention (curve M). For example, at an internal
pressure level of 50 psi, the prior art channel element of curve N exhibited a wall
deflection of approximately .37 mm, while the channel element according to the present
invention exhibited a deflection of only 0.097 mm, a value 74% lower than deflection
level of the prior art channel element. As also shown by the plot, the channel - element
of the present invention can accommodate increasing internal pressure levels of up
to 60 psi without undue or rapidly increasing deflection. At an internal pressure
level of 60 psi, the deflection of the wall member according to the present invention
is only about .12 mm, a deflection value which is already exceeded by the prior art
channel element at an internal pressure of only 20 psi. The various curves in Figure
33 thus clearly show the striking, substantial and unexpected improvement in channel
element structural strength and integrity which is achieved by the channel element
of the present invention -over prior art channel elements.
[0081] Although preferred embodiments of the present invention have been described in detail,
it will be appreciated that other embodiments are contemplated only with modification
of the disclosed features, as being within the scope of the invention. For example,
although the disclosure herein has been directed primarily to cross flow heat exchangers
employing open-ended channel elements, it will be appreciated that the heat exchange
wall member of this invention may suitably be employed in other heat exchanger configurations,
such as the plots and fin variety, in various flow modes including cross flow, concurrent
flow and counter flow of the heat exchanging fluids.
1. A heat exchange wall member of thermally conductive material having a multiplicity
of wall projection portions distributed across the wall member surface and outwardly
extending/therefrom with load-bearing end segments at their extremities, whereby said
wall member may be supported abuttingly against an adjacent structural member by said
load-bearing end segments of said wall projection portions, characterized in that:
said wall projection portions extend elongately on said wall member surface with the
load- hearing segments thereof having an aspect ratio (d2/d1) of at least 10, wherein d2= length of the major axis of said wall projection portion load-bearing end segment
measured in the base plane of the wall member and d1 = length of the minor axis of said wall projection portion load-bearing end segment
measured in the base plane of the. wall member,
said wall projection portions -are oriented on said wall member surface with the major
axes of said load-bearing end segments of said wall projection portions aligned substantially
parallel to one another; and
said wall projection portions have a dimensional size and a dimensional relationship
therebetween defined by a D dimension of between about 0.2 and 3.0 inch, a H/D ratio
of between about 0.05 and 0.5, and a D/dl ratio of between about 1.5 and 50, wherein:H equals the maximum height measured perpendicularly
from the base plane of the wall member to the innermost point on the wall member surface
between adjacent wall surface projections; D equals the spacing between the major
axes of load-bearing end segments of adjacent wall projection portions as measured
perpendicularly to said major axes in the base plane of the wall member; and the
base plane of the wall member is a plane containing the extremities of wall surface
projections extending outwardly from the wall member surface to a uniform extent.
2. A heat exchange channel element including two spaced-apart wall members of thermally
conductive material bounding a fluid flow channel and having a multiplicity of wall
projection portions distributed outwardly across the wall member surface and extending/therefrom
with load-bearing end segments at their extremeties, whereby said channel element
may be supported abuttingly against an adjacent structural member by said load-bearing
end segments of said wall projection portions, characterized in that:
said wall projection portions extend elongately on said wall member surface with the
load-bearing segments thereof having an aspect ratio (d2/dl) of at least 10, wherein d2= length of the major axis of said wall projection portion load-bearing end segment
measured in the base plane of the wall member and d1 = length of the minor axis of said wall projection portion load-bearing end segment
measured in the base plane of the wall member;
said wall projection portions are oriented on said wall member surface with the major
axes of said load-bearing end segments of said wall projection portions aligned substantially
parallel to one another; and
said wall projection portions have a dimensional size and a dimensional relationship
therebetween defined by a D dimension of between about 0.2 and '3.0 inch, a H/D ratio
of between about 0.05 and 0.5, and a D/d1 ratio of between about 1.5 and 50, wherein:H equals the maximum height measured perpendicularly
from the base plane of the wall member to the innermost point on the wall member surface
between adjacent wall surface projections; D equals the spacing between the major
axes of load-bearing end segments of adjacent wall projection portions as measured
perpendicularly to said major axes in the base plane of the wall member; and the base
plane of the wall member is a plane containing the extremities of wall surface projections
extending outwardly from the wall member surface to a uniform extent.
3. A heat exchange channel element according to claim 2 wherein said two spaced-apart
wall members constitite side walls of the channel element and are spaced apart by
edge walls, with said side walls and edge walls each having a thickness of between
about 0.003 and 0.25 inch.
4. A heat exchange channel element according to claim 3 wherein said side walls and
edge walls are formed of aluminum and have a thickness of between about 0.003 and
0.10 inch.
5. A heat exchange channel element according to claim Z which extends longitudinally
and has an elongated cross section bound by said two spaced-apart wall members as
side walls spaced apart by edge walls, said channel element having a first fluid entrance
opening at one end and a first fluid exit opening at the opposite end.
6. A heat exchange channel element according to'claim 5 wherein said wall projection
portions extend across substantially the full width of the side wall and are oriented
with the major axes of said wall projection portion load bearing end segments substantially
perpendicular to the longitudinal axis of the channel element.
7. Apparatus according to claim 1 or 2 wherein the wall surface between adjacent wall
projection portions is substantially planar.
8. Apparatus according to claim 1 or 2 wherein the wall member surface between adjacent
wall projection portions is concavely curved.
9. Apparatus according to claim 1 or 2 wherein the wall surface between adjacent wall
projection portions has an elevational contour which is concavely circular.
10. A heat exchanger comprising at least one heat exchange channel element according
to claim 2.
11. A heat exchanger comprising a multiplicity of channel elements according to claim
2 each having an elongated cross section bound by said wall members as side walls
spaced apart by edge walls, said channel elements being longitudinally aligned in
parallel spaced relation each with a first fluid entrance opening at one end and a
first fluid exit opening at the opposite end, and common inlet manifold means and
common exit manifold means respectively associated with said first fluid entrance
openings and said first fluid exit openings.
12. A heat exchanger according to claim 11 wherein the load-bearing end segments of
wall projection portions of said channel elements are shaped and arranged for mating
with and abutting against load-bearing end segments of the projection portions of
an adjacent channel element side wall, with the wall surface portions between said
projection portions thereby forming spaces between adjacent channels through which
a second fluid may be flowed in heat exchange with the first fluid.
13. A heat exchanger according to claim 12 comprising secondary surface fins associated with said channel elements.
14. A heat exchanger according to claim 11 wherein said multiplicity of channel elements
are disposed in a stacked array with secondary surface plate-like members being disposed
between adjacent channel elements with the load bearing end segments of the wall projection
portions of the channel elements being shaped and arranged for mating with and abutting
against said secondary surface members, whereby said secondary surface members are
maintained in thermal contact with said channel elements along the abutting load-bearing
end segments thereof.
15. A heat exchanger according to claim 14 wherein said secondary surface members
are substantially planar.
16. A heat exchanger according to claim 14 wherein said secondary surface members
have a multiplicity of surface distortions distributed across portions of their surfaces
which are not in abutting contact with channel element load-bearing segments.
17. A heat exchanger according to claim 16 wherein said surface distortions of said
secondary surface members comprise parallel slats and slotted apertures arranged in
a louvered configuration across the width of the secondary surface member.
18. Apparatus according to claim 1 or 2 wherein said aspect ratio (d2/dl) is at least 30.
19. Apparatus according - to claim 1 or 2 wherein said wall projection protions extend
outwardly to a uniform extent and have flat load-bearing end segments at their extremities.
20. Apparatus according to claim 1 or 2 wherein: H is between about 0.035 and 0.080
inch; D is between about 0.4 and 1.1 inch: and d1 is between about 0.01 and 0.05 inch.
21. A heat exchanger including a stacked array of longitudinally extending channel
elements each having two spaced-apart wall members of thermally conductive material
bounding a fluid flow channel and a multiplicity of wall projection portions formed
from each wall member being distributed across the wall member surface and extending
outwardly therefrom to a uniform extent with flat load-bearing end segments at their
extremities, whereby said channel elements may be supported abuttingly against adjacent
structural members said load-bearing end segments of said wall projection portions,
characterized in that:
said channel element wall projection portions extend elongately across substantially
the full width of said wall member surfaces of said channel elements with the load-bearing
segments thereof having an aspect ratio (d2/d1) of at least 30, wherein d = length of the major axis of said wall projection portion
load-bearing end segment measured in the base plane of the wa..l member and d1 = length of the minor axis of said wall projection portion load-bearing end segment
measured in the base plane of the wall member;
said channel element wall projection portions are oriented on said wall member surfaces
of said channel elements with the major axes of said load-bearing end segants of said
wall projection portions aligned sub- stantia by parallel to one another and substantially
per- pendicuar to the longitudinal axes of said channel elements and said channel
element wall projection portions having a dimensional size and a dimensional re- lationshi
therebetween defined by a D dimension of between about 0.2 and 3.0 inch, a H/D ratio
of between about 0.05 and 0.5, a D/d1 ratio of between about 1.5 and 50, wherein: H equals th maximum height measured perpendicularly
from the bas plane of the channel element wall member to the innermost point on the
wall member surface between adjacent wall surface projections of the channel element;
D equals the sacing between the major axes of load-bearing end segments otadjacent
wall projection portions of the channel element, measured perpendicularly to said
major axes in tl base plane of the channel element member; d the base plane of the
channel element wall memb is a plane containing the load-bearing segments c he wall
surface projections of said wall member.
22. Apparatus according to claim 1 or 2 wherein said wall projection portions are
formed from said wall member.
23. Apparatus according to claim 1 or 2 wherein the H/D ratio is between about 0.05
and 0.4.
24. A heat exchanger according to claim 11 wherein said channel elements are disposed
in a stacked array with their longitudinal axes lying in a common plane and said stacked
array contains at least 40 channel elements per foot width thereof, with the width
of said stacked array being measured in said common plane in a direction perpendicular
to the channel element longitudinal axes.
25. A heat exchange wall member according to claim 1 wherein said wall projection
portions extend uninterruptedly across substantially the full extent of said wall
member in the direction of elongation of said wall projection portions.
26. A heat exchanger comprising at least one heat exchange wall member according to
claim 1.
27. A heat exchanger according to claim 26 wherein the load-bearing end segments of
wall projection portions of said wall member are shaped and arranged for mating with
and abutting against load-bearing end segments of the projection portions of an adjacent
wall member, with the wall surface portions between said projection portions thereby
forming spaces between adjacent wall members through which a second fluid may be flowed
in heat exchange with a first fluid on the other side of said wall member.
28. A heat exchanger according to claim 27 wherein a multiplicity of wall members
are disposed in a stacked array with secondary surface plate-like members being disposed
between adjacent wall members with the load bearing end segments of the wall projection
portions of the wall members being shaped and arranged for mating with and abutting
against said secondary surface members, whereby said secondary surface members are
maintained in thermal contact with said wall members along the abutting load-bearing
end segments thereof.
29. A heat exchanger according to claim 28 wherein said secondary surface members
are substantially planar.
30. A heat exchanger according to claim 28 wherein said secondary surface members
have a multiplicity of surface distortions distributed across portions of their surfaces
which are not in abutting'contact with channel element load-bearing segments.
31. A heat exchanger according to claim 30 wherein said surface distortions of said
secondary surface members comprise parallel slats and slotted apertures arranged in
a louvered configuration across the width of the secondary surface member.