U.S. patent number 3,854,530 [Application Number 05/290,518] was granted by the patent office on 1974-12-17 for heat exchanger.
Invention is credited to Etienne Jouet, Pascal Rebuffe.
United States Patent |
3,854,530 |
Jouet , et al. |
December 17, 1974 |
HEAT EXCHANGER
Abstract
Heat exchangers of generally cylindrical shape, including
structure having at least two chambers being wound on themselves in
self-enclosing spirals, baffles forming passageways through said
chambers to facilitate the flow of heat-exchanging media through
said chambers in alternate centripetal and centrifugal
relationship.
Inventors: |
Jouet; Etienne (95
Montigny-les-Cormeilles, FR), Rebuffe; Pascal
(Boulonge-Billancourt, FR) |
Family
ID: |
26966228 |
Appl.
No.: |
05/290,518 |
Filed: |
September 20, 1972 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
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888591 |
Dec 29, 1969 |
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Current U.S.
Class: |
165/163;
165/DIG.398; 165/165; 165/110; 165/164 |
Current CPC
Class: |
B21D
53/027 (20130101); F28D 9/04 (20130101); F24D
3/082 (20130101); Y10S 165/398 (20130101) |
Current International
Class: |
F24D
3/08 (20060101); F24D 3/00 (20060101); F28D
9/00 (20060101); F28D 9/04 (20060101); B21D
53/02 (20060101); F28f 003/00 () |
Field of
Search: |
;165/166,163,164 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Sukalo; Charles
Attorney, Agent or Firm: Waters, Roditi, Schwartz &
Nissen
Parent Case Text
This application is a divisional application of Ser. No. 888,591;
filed Dec. 29, 1969.
Claims
What we claim is:
1. A heat exchanger of generally cylindrical form acting between
two fluids, comprising:
a. first and second chambers wound in juxtaposed and enclosing
spirals; and a thin metal wall separating said chambers from each
other, said metal wall having gofferings formed thereon and
abutting against the wall of an adjacent chamber;
b. a central cylindrical tube, said chambers spirally encompassing
said tube, fluid inlet and outlet means for said second chamber
being formed by said tube;
c. an external cylindrical hoop concentrically encompassing said
central tube and forming an annular space therebetween, said hoop
and tube forming the supporting framework of said heat exchanger,
said chambers being located in said annular space between said hoop
and said tube, and said external cylindrical hoop axially extending
beyond the level of said spirally coiled chambers;
d. closure caps attached to said cylindrical hoop so as to form two
enclosures, said enclosures being in direct communication with said
first chamber through the open lateral ends thereof and forming
respectively inlets and outlets to said first chamber;
e. obturation means dividing into two portions forming,
respectively, a distribution portion and a collector portion, said
second chamber communicating with the distribution portion at its
central portion and with the collector portion at the other end
thereof;
f. and guide means being positioned within said second spirally
coiled chamber and adapted to guide the fluid in said chamber to
flow therealong in a centrifugal direction from the distribution
portion of the tube substantially to the periphery of said chamber,
and in a centripetal direction from the periphery of said chamber
to the collector portion of said tube.
2. A heat exchanger as claimed in claim 1, said gofferings being
bosses formed in said thin metal wall.
3. A heat exchanger as claimed in claim 1, said guide means being
in the form of partitioning means internally following the
spiralled shape of the second chamber and arranged in a plane
extending perpendicular to the axis of the central tube, said
partitioning means being discontinuous in the region of the outer
periphery of the coiled chamber so as to divide said second chamber
into lower and upper portions and forming a passage between the two
portions of said chamber.
4. A heat exchanger as claimed in claim 1, the walls of said second
chamber being formed of goffered metal sheets having corrugations
impressed thereon, and spaced at a proximity so as to cause the
fluid flowing through said second chamber to be distributed equally
throughout the space of said chamber.
5. A heat exchanger as claimed in claim 1, said first chamber
comprising a spiral partition extending in a plane perpendicular to
the axis of the hoop, said partition having an aperture therein,
and two lateral, spiral shaped sides forming closure means having
an aperture in the radially inner portion thereof, said closure
means and said partition forming guide means causing the fluid to
flow in a path spiralling first in a centrifugal direction and then
in a centripetal direction in countercurrent flow to the fluid
flowing in said second chamber.
6. A heat exchanger as claimed in claim 5 the walls of the second
chamber being made of a goffered metal.
7. A heat exchanger as claimed in claim 1, comprising a jacket made
of a metal foil wound about said spirally coiled chambers, and a
packing of moldable substance poured between said hoop and the
outer wall of the jacket filling the interstitial space between the
outer wall and said hoop, said packing eliminating the spiralled
chambers to be exactly ajusted to the dimensions of the hoop and
facilitating the pressure inside the chambers to be absorbed both
by the hoop and the central tube.
8. A heat exchanger as claimed in claim 1, comprising a first
cylindrical tube, said chambers spirally encompassing said tube, an
internal secondary tube contained in said first tube, the first
chamber being in communication with the annular section of the
first cylindrical tube at one end and with the secondary internal
tube at the other end thereof, said annular section and said
secondary internal tube forming, respectively, an entry and an exit
for a fluid passing through said first chamber, and both concentric
tubes comprising respectively an inlet and outlet disposed on the
same sectional face of the heat exchanger.
Description
The invention relates to the exchange of heat between at least two
fluids. More precisely, the invention relates to heat exchangers
comprising at least two chambers, these chambers being wound on
themselves in self-enclosing spirals, the exchanger being of
generally cylindrical shape.
In the present state of the known art, exchangers of this kind have
already been proposed, in which at least one of the fluids passes
into (or out of) its chamber through the intermediary of a capacity
located at the centre of the spirals, and passes out (or comes in)
at the periphery into another capacity placed at the exterior of
the spirals. In order to withstand the pressures of the fluids, it
is necessary to employ either an outer shell which supports the
spiral nest, it being observed that the passage of the fluid
through the shell causes a considerable loss of pressure, or
alternatively to build the chambers with sheet metal of fairly
large thickness in order that the last turn, suitably bent back and
welded to itself, achieves the same result with external
reinforcements.
The first solution results in costly and almost inextricable
difficulties of practical construction of fluid-tight coupling
between the exchange surface and the external capacity through the
shell, these members having substantially different thicknesses and
being subjected to dissimilar thermal variations which create large
stresses at the most awkward points. The second solution is heavy
and not very economical. Neither of the two solutions can be
adapted for high pressures. Thus, it is found that the production
cost of exchangers of the spiral type does not in any way enable
them to replace other types of exchangers, for example the
multi-tubular type.
At the same time as reducing the production cost to half or
one-third that of conventional exchangers, the object of the
invention is to dispense with their capacity or volume located
outside the shell, which has been referred to above, either by
winding the exchange walls round the inlet and outlet capacity of
the same fluid, or by providing for the passage of the fluids
through lateral openings formed in the sides of the spiral body
(for high flow-rates). By this means, all the disadvantages
indicated above are eliminated in the two cases.
There is thus obtained a spiral nest independent of the outer shell
intended to contain the pressures, and in which the invention
provides simple guiding means yo be produced so as to cause at
least one fluid to follow a complicated path. The fact of having
separated the nest from the shell constitutes an essential
advantage which makes it possible to use very thin exchange walls,
even with high pressures, by making use of the two central
capacities as a frame intended to withstand the thrust of the
internal pressures directed towards the centre and an external
shell intended to contain the thrust of the internal pressures
directed towards the periphery.
It is advantageous to make use of spacing means for the walls so as
to assist in the guiding of the fluids. Thus, in accordance with a
preferred form of construction, the exchange walls are held apart
from each other by bosses intended to assist in the guiding of the
fluid, either directly or in order to position partitions, at the
same time having four other functions: to keep the sheets at a
distance, to increase the exchange surface (by elongation of the
metal) to reinforce the rigidity of the sheet metal, which makes it
possible further to reduce its thickness, to induce turbulence
intended to increase the coefficient of thermal exchange.
Finally, another object of the invention is to be capable of
treating, with these exchangers, fluids in which the inlet
temperatures are very different, which is possible with a
concentric arrangement of the central capacities, completely
eliminating all stress due to thermal expansion, and rendering the
apparatus easy to dismantle.
In another alternative form of the invention, a supplementary sheet
is employed as a spacing means, this sheet serving at the same time
to considerably increase the exchange surface in contact with the
said fluid. Boilers and air-coolers are constructed in this
way.
From the advantages listed above, it follows that the exchangers
according to the invention have an exceptional thermal efficiency,
are very compact, are constructed with only half or one-third the
amount of material and can be readily manufactured by mass
production, being well adapted to all heat-exchange problems. Their
production costs is one-third to one-half that of known exchangers,
while at the same time their performance is better.
Forms of embodiment of the present invention will now be described
with reference to the accompanying drawings, given by way of
examples and not in any limitative sense; in these drawings:
FIGS. 1 to 6 relate to a heat exchanger between two fluids, in
which:
FIG. 1 is a perspective view of the path represented as thread-like
in heavy lines for one of the fluids, the path of the other fluid
being shown in fine lines;
FIG. 2 shows part of the thin metal wall;
FIG. 3 is a perspective view showing the manufacture of the
exchanger;
FIG. 4 is a cross-section taken along the line IV--IV of FIG.
3;
FIG. 5 is a transverse section of the exchanger;
FIG. 6 is a perspective view of the extremity of the exchanger;
FIG. 7, similar to FIG. 4, relates to an alternative form of the
previous exchanger;
FIG. 8 is a transverse section of a heat exchanger between three
fluids, a central heating boiler, for example, of which FIG. 9 is
an explanatory detail;
FIG. 10, similar to FIG. 2, shows a portion of another thin metal
wall;
FIGS. 11 and 12 relate to another heat exchanger between two
fluids, for which:
FIG. 11, similar to FIG. 1, is a perspective view of the paths of
the two fluids;
FIG. 12, similar to FIG. 5, is a transverse section of the
exchanger;
FIGS. 13 to 16 relate to another heat exchanger between two fluids,
for which:
FIG. 13 is a perspective view of the path of one of the fluids;
FIG. 14 is an axial section of the exchanger;
FIG. 15 is a transverse section taken along the line XV--XV of FIG.
14;
FIG. 16 is another axial section taken along the line XVI--XVI of
FIG. 15;
FIG. 17 represents a transverse section similar to that of FIG. 15;
and relates to an alternative form of the above exchanger;
FIG. 18 is an axial section similar to that of FIG. 14, and relates
to a further alternative form of the said exchanger;
FIG. 19 is a detail in axial cross-section, showing a construction
of the top and bottom partitions of the above exchangers;
FIG. 20 is a transverse section similar to that of FIG. 15, and
shows a construction of the peripheral turns of the above
exchangers;
FIG. 21 is an axial section similar to that of FIG. 14, and
concerns a further heat exchanger suitable for use as a condenser,
evaporator, or boiler;
FIGS. 22 and 23 show, in axial and transverse section respectively,
a further arrangement of the collectors of the above
exchangers;
FIG. 24 is a plan view showing still another arrangement of the
collectors of the above exchangers;
FIG. 25 is an axial section showing a further arrangement of the
collectors of the above exchangers;
FIGS. 26 to 31 are concerned with a preferred construction of a
heat exchanger according to the invention:
FIG. 26 is a perspective view with numerous parts broken away, of
the diagram of circulation of a fluid in this exchanger;
FIG. 27 is a general view in elevation;
FIG. 28 is a transverse section taken along the line XXVIII--XXVIII
of FIG. 27;
FIG. 29 is a half-radial section of the lower portion;
FIG. 30 is a detail showing the closure of the spiral sheets;
FIG. 31 is a detail showing a ribbed metal sheet suitable for the
said exchanger;
FIGS. 32 to 37 relate to another preferred form of construction of
a heat exchanger according to the invention:
FIG. 32 is a perspective view with numerous parts broken away, of
the circulation diagram of a fluid in this exchanger;
FIG. 33 is a general view in elevation;
FIG. 34 is a transverse section taken along the line XXXIV--XXXIV
of FIG. 33;
FIG. 35 is a half-radial section of the lower portion;
FIG. 36 is a detail showing the closure of the spiral sheet;
FIG. 37 shows another stamped metal sheet suitable for the said
exchanger;
FIG. 38 is an axial section of a dismantlable exchanger fairly
similar to that previously described.
With reference to FIG. 1, this heat exchanger according to the
invention provides for the circulation of two fluids, each
following four identical spirals which are successively traversed
in opposite directions, the spirals for the two fluids being
inserted one in the other in pairs and traversed in opposite
directions by the two fluids.
In more detail, the path of one of the fluids, shown in heavy
lines, causes it to pass at 1 into the upper part of a collector or
header 2 (shown in broken lines) passing then in the centrifugal
direction through a spiral 3, after which it moves down at 4 into a
part of another header 5, passes through a spiral 6 in the
centripetal direction, moves down at 7 into another part of the
header 2, passes in the centrifugal direction into a spiral 8,
flows-down at 9 into another part of the header 5, passes through a
spiral 10 in the centripetal direction, and finally passes out at
11 at the lower portion of the header 8.
Symmetrically, the path of the other fluid, shown in fine lines,
causes it to pass at 21 into the lower portion of a header 22
(shown in broken lines), to traverse in the centrifugal direction,
a spiral 23 identical with the spiral 10, but displaced by half a
revolution, each turn of one being placed between two turns of the
other, to move upwards at 24 into another header 25, to traverse in
the centripetal direction a spiral 26 placed in the same manner in
the said spiral 8, to rise at 27 into another part of the header
22, to traverse in the centrifugal direction a spiral 28 housed in
the said spiral 6 in the same manner, to rise at 29 into another
part of the header 25, to pass in the centripetal direction through
a spiral 30 housed in the same manner in the said spiral 3, and to
pass out at 31 at the upper portion of the header 22.
It will be observed that the path of each fluid is at every point
in the opposite direction to the path of the other fluid at the two
points of each side of the said point, and that this is obtained by
a structure of identical spirals having the same direction, and
therefore of a practical construction which will now be described
with reference to FIGS. 2 to 6.
In this form of a structure which provides for the two fluids, the
paths which have been described above with reference to FIGS. 1,
these two fluids circulate on each side of a thin metal wall 41.
Generally speaking, this thin wall is a sheet on which has been
impressed, by stamping or goffering, impressions, for example the
elongated bosses 42 arranged in line, as shown in FIG. 2. These
impressions have a three-fold purpose, on the one hand the
mechanical function of spacing apart from each other the turns of
the wall 41 (as will be seen later), on the other hand the thermal
function of increasing the heat exchanges through the wall 41, at
the same time by increasing the surface area and by creating local
turbulence in the fluids, and finally the function of positioning
the partitions intended to guide the circulation of the fluid.
With reference to FIG. 3, which is a perspective view of the
structure in course of manufacture, and to FIG. 4 which is a
half-section just above the plane of the wall 41 (plane IV--IV of
FIG. 3): the sheet 41 with the bosses 42 in relief on the straight
portion (the edge of which has been shown as a heavy continuous
line, and underneath the left hand-side (the edge of which has been
shown as a heavy broken line) with margins without bosses,
reveives, for example by welding, the four headers 2, 5, 22, 25
already referred to; they are of semi-circular section, each with a
longitudinal lateral slot and transverse internal partitions, which
are mounted facing the lines of bosses 42. For example, the header
2 is provided with a slot 43 and with two internal partitions 44
(see FIG. 4); the same thing applies to the header 5, which ensures
for one of the two fluids the path of oppositely-directed spirals
described with reference to FIG. 1 and which are again shown,
unwound flat, in FIG. 4.
After the said welding, the assembly is wound and there is obtained
the structure of spirals shown in cross-section in FIG. 5 (in which
the two right-hand and left-hand portions of the wall 41 before
winding are again shown respectively in heavy continuous lines and
in heavy broken lines for the sake of clearness of the drawing).
Extremity welds 45 stop the turns and fix the whole in a casing 46.
This latter is not essential and may be replaced by additional
turns of the wall 41. FIG. 6 shows a perspective view of one
extremity of this exchanger; it may comprise a welded end-plate 47
as shown, or it may be closed by welds of the edges of the wall 41
or by filler metal, brazing or welding, or by a polymerized
material which has set into a block.
It is clear that in the description which has been given above, the
number of spirals, the number of the rows of bosses and internal
partitions of the headers may be modified according to
considerations of choice or opportunity, without departing from the
scope of the invention.
For example, when the pressures contemplated are not too high, for
example when the difference of the pressures between the two fluids
does not exceed 20 bars, it is not only possible to simplify the
casing as already explained, but also to eliminate the headers as
shown in FIG. 8.
Certain lines 48 of the bosses 42 of the sheet 41 (those which have
to vary the path of the fluid) are then extended so as to be
substituted for these headers in their function of guiding of the
fluid, and only the inlet and outlet orifices 49 are required.
There will now be described another embodiment of the invention
relating to a boiler for a flat or a building, that is to say for
heating by means of combustion gases, on the one hand water for
heating by radiators and on the other hand water for domestic
purposes. With reference to FIG. 8, which is a transverse section
in the upper portion, and to FIG. 9 which is an explanatory detail
in transverse section towards the central portion, this boiler
comprises an axial header 51 in the form of a volute with a single
turn closed by a radial partition 52. On this volute there are
wound simultaneously: a first goffered metal wall 53, a second
goffered metal wall 54, the gofferings of which are displaced with
respect to those of the first wall 53, a third goffered metal wall
55, the gofferings of which are displaced with respect to those of
the second wall 54, a flat metal wall 56 and a sheet with
rectangular ribs 57.
Preferably, but not necessarily, as very clearly shown in FIG. 8,
the walls 54 and 55 form part of the same metal sheet folded back
on itself along the wall 52, and similarly, the walls 53 and 56
form part of another single metal sheet folded back on itself
around the previous sheet along the partition 52. As shown in FIG.
9, the bosses of the walls 53, 54 and 55 and the partitions which
direct the flow of the fluids along the transverse spirals, are
interrupted at a certain distance from the partition 52, leaving
vertical passages 61, 62 and 63 along this partition. Towards the
middle of the winding (FIG. 8), a longitudinal partition 64
reinforces or extends, at its two extremities, one of the ribs of
the sheet 57, which defines a first chamber 71 containing half the
sheet 57 with rectangular ribs, between the partitions 52 and 64.
At the periphery, the last turn of the wall 53 is welded at 65 on
the last turn but one of the wall 56, which defines a second
chamber 72 containing the other half of the sheet 57 with
rectangular ribs, between the partitions 64 and the weld 65. A
little farther on at the periphery, the ends of the walls 54 and 55
are welded together at 66, which defines a third chamber 73 open at
its upper portion on an orifice 74 and at its lower portion on an
identical orifice (not shown on the drawing). A little further
still on the periphery, the last turn of the wall 56 is welded at
67 on its last turn but one, which defines a fourth chamber 75 and
a fifth chamber 76 which open together at their upper portion on an
orifice 77 and at their lower portion on an identical orifice (not
shown on the drawing).
The hot combustion gases coming from a furnace below the plane of
FIG. 8 pass up through the interior of the header 51, are sent back
by a partition (above the plane of the drawing) and pass down again
through the chamber 71, in contact with the rectangular ribs of the
sheet 57, are again sent back by a partition (below the plane of
the drawing) and rise again through the chamber 72 passing over the
rectangular ribs of the other half of the sheet 57, and are then
evacuated to the chimney. The water for heating by radiators enters
the upper portion through the orifice 77 (arrows F1), and divides
between two spiral centripetal paths in the chambers 75 and 76.
It will be observed that each turn of the chamber 71 or 72 for the
hot gases is housed between a turn of the chamber 75 and a turn of
the chamber 76. This water, coming in towards the centre (FIG. 9)
moves down, for the chamber 75, through the passage 63 (arrow F2)
and for the chamber 76 by the passage 61 (arrow F3). At the lower
portion, the water than follows the same chambers 75 and 76 but in
the opposite direction (the direction opposite to that of the
arrows F1 for the upper portion, as in FIG. 8) and in this case
also, each turn of the chamber 71 or 72 is housed between one turn
of the chamber 75 and a turn of the chamber 76, and passes out
downwards through the orifice corresponding to the orifice 77.
Finally, the water for domestic use passes in at the bottom through
the orifice corresponding to the orifice 74, circulates in the
lower part of the chamber 73 (in the opposite direction to the
arrows F5 of FIG. 8), moves upwards (FIG. 9) through the passage 62
(arrow F4), circulates in the opposite direction (arrows F5 of FIG.
8), in the upper portion of the chamber 73 and passes out at the
top through the orifice 74. It will be noted that for the bathroom
water also, each turn of the chamber 73 is housed between a turn of
the chamber 75 and a turn of the chamber 76 in which the central
heating water circulates in the opposite direction.
According to the invention, the bosses 42 of the goffered metal
sheet 41 may also be of the elongated shape shown for example in
FIGS. 2, 4 and 7, as well as other forms. For example, in the case
of the bosses in line of the ribs shown in FIG. 10, and for the
other bosses with hemispherical impressions, the whole in relief
for one-half of the sheet 41 and recessed as regards the other
half, preferably and as shown in FIG. 10, with a transverse
displacement 78 between the two halves. For the purpose of winding,
it is then only necessary to utilize two mandrels each comprising a
flat strip applied one above and the other below the central area
79 of the sheet 41 so as to obtain, after winding and removal of
the mandrels, a heat exchanger of the above-mentioned type.
Naturally, it remains within the scope of the invention to
eliminate the chamber 73. In this case there may be contemplated
the use of the exchanger as an air cooler, the gases passing for
example directly in one direction only through the whole chamber 71
and 72. The ribbed sheet 57 plays the part of a secondary surface,
and there is an advantage in improving its connection to the
exchange walls 53 and 56, by dipping the apparatus into a bath of
metal with a low melting point, for example zinc. Without departing
from the scope of the invention, it is also possible to arrange the
inlet and the outlet of fluid passing spirally through its chamber,
at the centre.
Another embodiment of the invention will now be described with
reference to FIGS. 11 and 12, which relate to a heat exchanger
between two fluids, with a central tube divided into two parts by a
central horizontal separation, thus forming the inlet capacity and
the outlet capacity of the first fluid.
FIG. 11 is a perspective view of the path shown as being of
thread-like form in heavy lines of this fluid, the path of the
other fluid being shown in fine lines. The first fluid enters at 81
into the inlet capacity, at the upper portion of the central tube
83, passes out at 84, describes a spiral 85 in the centrifugal
direction, flows down at 86, describes a spiral 87 in the
centripetal direction, returns into the tube at 88 and passes out
at 89 through the lower part of the central tube 83, that is to say
through the outlet capacity. The second fluid enters peripherally
at the top at 91, describes a spiral 92 in the centripetal
direction, identical with the spiral 85, each turn of one being
placed between two turns of the other, flows down along a vertical
wall 93, describes a spiral 94 in the centrifugal direction,
identical with the spiral 87, each turn of one being placed between
two turns of the other, and passes out peripherally at the bottom
at 95.
It will be observed in this case also that the path of each fluid
is, at each point of each spiral, of opposite direction to the path
of the other fluid on both sides of the said point, and that this
is obtained by a structure of identical spirals having the same
direction, and therefore of practical construction, which will now
be described with reference to FIG. 12. It is furthermore
advantageously possible to cause the two fluids to follow the same
path, but in opposite directions, the inlet being made at 95 and
the outlet at 91, thus producing a counterflow exchanger.
With reference to FIG. 12, which shows a transverse section of this
heat exchanger, the winding can be carried out round the header 83,
after having arranged this latter on a goffered sheet 41,
approximately at its centre, and after having fixed the extremities
of the header 83, which extend slightly beyond the sheet 41, to a
flat strip 93. This flat strip is slightly curved so as to follow
the radius of curvature of the header 83, and the goffered sheet 41
can be provided with additional impressions 96 which give it a
spiral form at the outset. At the midheight of each chamber (not
shown in FIG. 12) a blade or a joint forming a partition separates
each chamber into two superimposed zones which give the paths of
the two fluids the form of double spirals, described in connection
with FIG. 11.
When the winding is completed, the two extremities of the sheet 41
are cut and welded at 97 along a generator line. A goffered sheet
98 can then be wound with several turns, the bosses 99 of this
sheet having a height which decreases from the generator line 97 ot
the generator line 101 so as to give the whole a generally
cylindrical form. The goffered sheet 98 is welded at 102 on the
sheet 41 and at 103 on itself. The assembly is then inserted into a
casing 104 and the edges of the sheet 41 are welded to each other
except for the outer portion between the generator lines 97 and 101
which leaves open, at the top, the said inlet 91 for one of the two
fluids, and at the bottom, the said outlet 85 (not shown in FIG.
12) of this fluid. The other fluid passes in at the top at 84 and
passes out at the bottom, at 88 (not shown in FIG. 12).
There will now be described the embodiments of the invention which
are particularly suitable for high flow-rates of fluid. With
reference to FIG. 13, this drawing shows a perspective view of the
sheets in the form of spiral cylinders followed by one of the
fluids, and in fine lines at the upper portion, the inlet and
outlet headers for this fluid. The other fluid follows identical
sheets, each of two sheets of the first fluid and its headers are
at the lower portion, but FIG. 13 does not show these for the sake
of clearness of the drawing (they are shown on the figures which
follow). The first fluid passes at 111 into the header 112, in the
form of a half-cylinder opening at its lower portion on a plurality
(in this case 4) of spiral cylindrical sheets 113, passes through
each of these sheets on both sides in a double spiral, passing
under staggered central baffles 114 (arrows 115) and passes out
through the header 116 and the outlet 117.
With reference to FIGS. 14, 15 and 16, which are cross-sections of
the construction of the heat exchanger ensuring the conditions
which have been specified in connection with FIG. 13, these
sections being respectively axial in passing through the inlet 111
and outlet 117, transverse along the line XV--XV of FIG. 14 and
axial passing through the baffles 114 along the line XVI--XVI of
FIG. 15.
The exchanger comprises a central tube 121 of cylindrical shape,
closed at its extremities, on which is wound double, as already
described for other exchangers, a thin goffered metal wall 41. This
double wound wall can be replaced by two walls 122 and 123, each
stamped for example with impressions of small spherical caps of
increasing height on the first turn and then of constant height,
their goffering being displaced from one wall to the other and the
two walls being welded at their starting point close to the central
tube 121, together and to this tube.
The baffles 114 may be constituted by lines of bosses such as those
already described with reference to FIGS. 7 and 10.
Along the length of the last turn of each wall, the gofferings are
of decreasing height so as to restore the circular form. The walls
are welded into an outer tube 124 of generally cylindrical shape
and substantially higher so as to form the headers 112 and 116
which are separated by a partition 118 (FIG. 14). The chamber 113
is closed at the bottom by a weld which may be made automatically
after having brought the edges of the walls 122 and 123 together by
means of a knurling tool, following a spiral passing from one tube
to the other.
Symmetrically, the other fluid enters at 131 into the header 132,
circulates in the chamber 133 (closed at the top in FIG. 14),
passing above the baffles 134 (FIG. 15) and passes out through the
header 136 at 137. The baffles 114 and 134 are of progressively
variable heights and leave a passage for the fluid, the size of
which varies with the opening section of the sheet considered on
its header.
If for one of the two fluids it is desired to reduce the section of
passage while increasing the length of the path travelled in the
exchanger, additional baffles and partitions may be utilized as
shown in FIG. 17 (similar to FIG. 15). The fluid coming into the
upper right-hand quadrant between the partitions 141 and 142 flows
down into the sheets, passes into the lower right-hand quadrant
underneath the partition 142 by passing round the baffles 144, and
then into the lower left-hand quadrant, avoiding the baffles 147 by
the chamber defined in the header by the partitions 142, 148 and
149, passes into the upper left-hand quadrant, underneath the
partition 149 while passing round the baffles 150, and passes out
through the header. It is clear that the length of the path can be
increased by multiplying the number of baffles and partitions, by
providing in succession a partition which completely closes the
section of the turn and baffles which only leave a section of
passage for the fluid which is lower or higher; this arrangement
can be applied to a different extent for each chamber, and this
makes it possible to provide, for each fluid, a path having a
section and length appropriate to the thermal problem
considered.
With reference to FIG. 18, this other exchanger according to the
invention is, for reasons of choice or opportunity, of larger
diameter with respect to its axial length. For the path of one or
both fluids, there are then provided several turns traversed
successively, quite simply by closing these turns on the side which
was open to the header. Thus, the spiral sheet 113 which is
outermost in FIG. 18, comprises a turn open at the top to the inlet
header 112, and then several turns, for example two as shown,
closed at the top at 152, for example by a partition or by welding,
these turns being successively traversed by the fluid while passing
round the baffles which they comprise (not shown in FIG. 18), and
finally a turn open at the top to the outlet header 116. The other
spiral sheets 113 comprise the same closures 152 at the top, which
may, as shown, be common to several of them. Similar closures may
be provided, but at the bottom as shown, for the other fluid.
It has been stated that these closures may be effected by bringing
the edges together with a knurling tool, followed by welding, or by
a partition. A closure of this kind by a partition will be
described with reference to FIG. 19, which is an axial section of a
detail. The consecutive turns of the thin metal wall 41 (bent back
in a double spiral on itself), or alternatively the consecutive
turns of the two sheets 122 and 123 with their bosses 42, are
closed by metal strips 153 inserted between the edges of the
spirals and secured by insetting at 154 in the winding, and/or by
welding. These strips 153 are of course interrupted at the desired
places so as to permit the fluid to pass into or out of the
corresponding chamber 113 or 123. In this construction of the
closures 152, in order to avoid difficulties towards the outer end
of the spirals, these interstitial spaces 155 and 156 (FIG. 20) are
filled with a mouldable material such as concrete, fusible metal or
plastic.
This lateral closure of the chambers, like the fixing of the
nozzles, can advantageously be carried out by the solidification
into a mass of a polymerized material or of an alloy with a lower
melting point, this setting into a mass forming an end-plate
imprisoning the lateral extremities of the exchange walls, the
edges of the nozzles in contact with the said extremities, and the
extremities of the internal and external cylindrical tubes.
The heat exchangers according to the invention can be employed to
effect the change of state of one of the fluids when this change of
state takes place from the gaseous state to the liquid state
(condensers). It may take place at the points of condensation of
the local depressions, and similarly, when this change of state
takes place from the liquid state to the gaseous state (evaporators
and boilers) it could take place at the points of vaporization of
the local excess pressures. In order to prevent this, the invention
gives to the two-phase fluid (to be condensed or vaporized) a large
direct access to the spiral sheets.
With reference to FIG. 21, which is an axial section similar to
that of FIG. 14, there can again be seen the spirals of goffered
walls 122 and 123, de-limiting the spiral sheets 113 for one fluid
and 123 for the other fluid, and the internal tubes 121 and
external tubes 124. In this case, the chamber 113 provided for the
two-phase fluid, is opened directly at the top of all the spiral
sheets 113 on the header 112 of the inlet of gas to be condensed in
the case of a condenser; the condensates are collected by spouts or
by lines of bosses 161, preferably as shown, aligned in descending
spirals and preferably, as shown, having a greater length for the
lower spouts. At the bottom points of these spouts, the
condensation liquid is evacuated into the internal tube 121 through
the orifices 162, and from there to the exterior through a conduit
163.
Conversely, in the case of an evaporator or boiler, the liquid
comes in through the conduit 163 in the direction opposite to the
arrows, passes through the internal tube 121 and the orifices 162,
passes over the spouts 161, and then passes out in the gaseous
state through the header 112.
The circulation of the cooling (or heating) fluid in the spiral
sheets 133, remains the same as that already described. The
temperatures of operation are regulated by adjusting the path of
the cooling (or heating) fluid by the arrangement of the spiral
spouts in particular; in certain sections, it is only necessary to
arrange shorter paths for the fluid in order to produce a more
powerful cooling (or heating).
The headers of the exchangers described above may be given other
arrangements according to the invention. With reference to FIGS. 22
and 23, which are respectively an axial section taken along the
line XXII--XXII of FIG. 23 and a transverse section taken along the
line XXIII--XXIII of FIG. 22, the inlet headers 112 and outlet
header 116 of one of the two fluids only occupy part of the upper
end-plate of the exchanger. In a common nozzle 165, they are placed
on each side of the partition 118, below which partitions 166 such
as lines of bosses 42 separate the turns. Thus the fluid which has
entered at 112 passes through the assembly of the turns and passes
out at 116. The same arrangement can be adopted at the lower
portion for the other fluid.
With reference to FIG. 24 which is a plan view, one of the fluids
passes into the exchanger at 111 through a nozzle 168, passes into
the spiral sheets (not shown) while being divided between the
right-hand and left-hand halves, and passes out at 117 through a
nozzle 169. The two nozzles are rigidly fixed to an end-plate 170
in the form of a ring which assembles together the tubes 121 and
124. The same arrangement can be provided at the lower portion for
the other fluid.
With reference to FIG. 25 which is an axial section, the inlet 111
and outlet 117 of a fluid are also in this case diametrically
opposite, but are placed on the outer tube 124 itself. The headers
112 and 116 are of semi-annular shape on each side of the partition
118.
There will now be described a preferred embodiment of the
invention. With reference to FIG. 26, which represents a
perspective view with a number of parts broken away in order to
simplify and clarify the drawing, of the diagram of circulation of
one of the fluids, in principle the cold fluid. This cold fluid
passes in at 181 to the bottom portion of an axial tube 182, closed
at its middle 183 and open laterally by two diametrically-opposite
slots 184 and 185 which each open into a spiral sheet 186 and 187,
these two sheets being identical and displaced by a half-turn so as
to be housed spaced apart from each other. These sheets are closed
at the top, at the bottom and at their extremities. In the
interior, in a central horizontal plane passing through 183, they
are provided with a partition starting from the central tube and
stopping at a certain distance from the peripheral extremity of the
sheet, so as to leave between the said extremity and the partition
a section of passage 188 or 189 substantially equal to the slots
184 and 185.
Thus, each half of the cold fluid describes a spiral sheet in the
centrifugal direction. On arrival at the periphery, each half of
the fluid rises into the top portion of the exchanger at 188 or
189, by a wide communication formed between the lower portion and
the upper portion of the spiral sheets 186 and 187, and describes
these sheets in the reverse direction, that is to say in the
centripetal direction. On arrival at the centre, each half of the
fluid passes through the upper portion of the slots 184 or 185 into
the upper half of the tube 182 and passes out of the exchanger at
190.
Thus the cold fluid has described two spiral sheets successively in
opposite directions. The other fluid, in principle the cold fluid,
passes from the top to the bottom, parallel to the general axis
X--X, passing through the spaces between the spiral sheets 186 and
187.
The construction of this heat exchanger will now be described with
reference to FIG. 27, which is a general elevation drawing, FIG.
28, which is a transverse section taken along the line
XXVIII--XXVIII of FIG. 27, FIG. 29 which is a radial half-section
of the lower portion, and FIG. 30, which is a detail of the closure
of the sheets.
The start of the spiral windings of the goffered sheets 192 and 193
is effected from a part 194 fixed on the axial tube 182 (FIG. 28),
and similarly, the start of the goffered sheets 196 and 197 is made
from a part 195. The axial tube 182 is divided into lower and upper
portions by a closure device 183 (FIG. 27); the spiral sheets 186
(between the goffered sheets 193 and 196, and 187 (between the
goffered sheets 192 and 197) are similarly divided into upper and
lower portions by a horizontal separation 198 and 199, which stops
before the end of the spirals (FIG. 28) so as to leave the
abovementioned communications 188 and 189.
The said goffered sheets may be those already described. In
particular, they may comprise hemispherical impressions as shown in
FIG. 30. At the top and the bottom of the exchanger, the spiral
sheets are closed, as already described, by bringing together and
welding, or by the insertion of metal strips 201 (FIGS. 29 and 30).
At the central portion, the separations 198 and 199 are
advantageously formed by a joint of rubberized asbestos, for
example of round or better still rectangular shape, held in
position by the bosses.
By way of another example of bosses, FIG. 31 shows ribs 203 formed
obliquely so as to still further increase the local turbulence and
to facilitate mechanical cleaning. After winding, the assembly is
inserted (FIGS. 27 and 28) in an external tube 204, with flanges
for the two fluids. Without departing from the scope of the
invention, the number of sheets may be increased or the slots of
the central tube may be replaced by any other orifices which
provide an equivalent section of passage.
There will now be described still another preferred embodiment of
the invention. With reference to FIG. 32, which shows in
perspective, with numerous parts broken away in order to simplify
and clarify the drawing, the diagram of circulation of one of the
fluids, in principle the cold fluid. The cold fluid passes at 211
into the lower portion of an axial tube 212 closed at its middle
213 and open along a generator line by a slot 214 which opens into
a spiral sheet 216. This sheet is closed at the bottom and the top
and contains a separation in a central horizontal plane similar to
198 and 199, towards the centre of the exchanger. The fluid
describes the spiral sheet in the centrifugal direction. When it
reaches the periphery, the fluid passes upwards into the upper
portion of the exchanger through a wide communication 218 formed
between the lower portion and the upper portion of the spiral sheet
216, and describes this sheet in the reverse direction, that is to
say in the centripetal direction. When it reaches the centre, the
fluid passes through the upper half of the slot 214, into the tube
212 and passes out of the exchanger at 220.
Thus the cold fluid has described successively, in opposite
directions, two spiral sheets. The other fluid, in principle the
hot fluid, passes from the top to the bottom through the spaces
between the turns of the spiral sheets 216, either directly as
explained in the construction comprising two sheets, as in FIG. 26,
or by passing by means of a central separation along a similar path
in counter-flow, as explained for the construction of FIG. 11, or
again by dividing the chamber into several sections, as explained
for the construction of FIG. 18.
The construction of this heat exchanger will now be described with
reference to FIG. 33 which is a general elevation, to FIG. 34 which
is a transverse section taken along the line XXXIV--XXXIV of FIG.
33, to FIG. 35 which is a radial half-section of the lower portion,
and to FIG. 36 which is a detail of the closure of the sheets. The
goffered sheet 222 is provided with bosses 223, for example
hemispherical, as shown in FIG. 36, and in relief alternately on
one side of the sheet and on the other. This goffered sheet 222 and
a flat sheet 224 are wound together, their edges welded together
along a generator line 225 (FIG. 34) placed just in front of the
slot 214 of the axial tube 212. The axial tube 212 is divided into
upper and lower portions by a closure device 213 (FIG. 33). The
spiral sheet 216 is similarly divided into upper and lower portions
by a horizontal separation 226 which stops before the end of the
spiral (FIG. 35) so as to leave the above-mentioned communication
218.
At the top and the bottom of the exchanger, the spiral sheet is
closed at 227 by bringing the edges together with a knurling tool
and welding as shown; this closure could be effected by inserting a
metal strip as already described in connection with FIG. 30. The
end of the spiral winding is fixed by a flat strip 228 (FIG. 34)
and the assembly is inserted into an outer tube 229 with flanges
for the two fluids.
The goffered sheet 222 and its horizontal separation 226 may be
produced in one of the ways already described, but with bosses on
both faces of the sheet. It may also be produced by the method
indicated in FIG. 37 which shows it by the side of the axial tube
212 and not yet wound. The bosses 223 are distributed in a variable
manner; they are relatively close together in the central region
near to the closure device 213 of the tube 212, and they are
relatively spaced apart towards the top and the bottom of the
peripheral edge (to the right of FIG. 37).
This arrangement which effects in a simple manner the horizontal
separation 226 obtains, at the same time as local turbulence, the
correct proportion of the times of transit for the various fluid
streams passing from the lower part of the slot 214 to its upper
portion.
The heat exchangers which have been described above, and in
particular the two preferred constructions shown in FIGS. 24 and
33, lend themselves well to a diamantlable construction, with the
advantage not only of being able to be cleaned, but also of being
unaffected by the different thermal expansions of different metals
with its constructional and economic advantages.
With reference to FIG. 38, which is an axial section of an
exchanger fairly similar to that shown in FIG. 33, the external
tube is in this case in two parts, on each side of a flange 231
with a joint. The body 232 contains, without being fixed thereto,
the spirals 216, and it is provided with an inlet flange 233 and an
outlet flange 234 for the hot fluid, preferably with a standard
domed bottom 235. The head 237, preferably also with a standard
domed end 238, is fixed to an axial tube 241 in which is secured
another coaxial tube 242. The assembly of these two tubes is
rigidly fixed to the spiral sheet 216 into the bottom of which the
tube 242 delivers, through a slot 243 along a generator line, and
which opens at the top into the tube 241 through a similar slot
244. The cold fluid enters through the flange 246 into the central
tube 242, passes through the slot 243 into the lower portion of the
spiral sheet 216 through which it passes in the centrifugal
direction, flows upwards at 218 into the upper portion of the
spiral sheet 216 through which it passes in the centripetal
direction, passing out through the slot 244 into the outer tube
241, and passes out of the exchanger through the flange 247.
A similar construction but having two jointed flanges, the outer
tube being in three parts, is quite obvious and will not therefore
be described.
It will be clear to those skilled in the art that, without
departing from the scope of the invention which has just been
described, various modifications may be made thereto, and in
particular there may be provided other associations of the various
arrangements which have been described.
* * * * *