U.S. patent number 3,731,736 [Application Number 05/150,547] was granted by the patent office on 1973-05-08 for plate and fin heat exchanger.
This patent grant is currently assigned to United Aircraft Products, Inc.. Invention is credited to Joseph F. Fernandes.
United States Patent |
3,731,736 |
Fernandes |
May 8, 1973 |
PLATE AND FIN HEAT EXCHANGER
Abstract
A compact heat exchanger of the plate and fin type in which a
manifolded core is constructed for multiple pass flow of at least
one of the involved fluids. Manifold members have ribs achieving
localized crushing engagement with the fin material providing for
separation of adjacent flow passes without the use of dividing
channel and like separable component parts.
Inventors: |
Fernandes; Joseph F.
(Centerville, OH) |
Assignee: |
United Aircraft Products, Inc.
(Dayton, OH)
|
Family
ID: |
22535033 |
Appl.
No.: |
05/150,547 |
Filed: |
June 7, 1971 |
Current U.S.
Class: |
165/166; 165/176;
165/DIG.452; 165/143 |
Current CPC
Class: |
F28D
9/0081 (20130101); F28F 2250/102 (20130101); Y10S
165/452 (20130101) |
Current International
Class: |
F28D
9/00 (20060101); F28f 003/00 () |
Field of
Search: |
;165/143,166 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Streule, Jr.; Theophil W.
Claims
What is claimed is:
1. A heat exchanger wherein corrugated fin material disposes in
continuous strip form between opposing plate-like members to serve
as extended heat transfer surface, and wherein manifold means
applies to at least one end of an assembly comprising opposing
plate-like members and an intermediately disposing fin strip, said
manifold means having rib means to bear against edges of said
plate-like members to define separate manifold chambers on opposite
sides of said rib means; characterized in that said plate-like
members are notched to accommodate said rib means, the insertion of
said rib means crushing portions of the ends of the fin strip
whereby to utilize corrugations of the fin strip to define
separated flow paths through said assembly in individual
approximately sealed communication with said manifold chambers,
said opposing plate-like members forming a tube having a flattened
configuration, opposing walls of the tube at at least one end
thereof being notched to receive said rib means, the fin strip
being longitudinally within the tube and being substantially
coextensive therewith.
2. A heat exchanger according to claim 1, characterized by a header
plate having at least one through opening accommodating the
projection of said one end of said tube therethrough, and means
fixing said header plate to said tube with said one end of said
tube projecting relatively to the plate a distance substantially
equal to the notch depth in said tube end.
3. A multi-pass heat exchanger, comprising spaced apart header
plates each having at least one laterally elongated opening
therein, tube means interposed between said header plates including
a laterally flattened tube having opposite ends projecting through
respective openings in said plates, a strip of corrugated fin
material disposing in said tube with its corrugations extending
lengthwise of the tube substantially coextensively thereof, other
strip fin material superposing above and below said flattened tubes
with its corrugations extending angularly to the corrugations of
the first said fin strip, manifold means for conducting a fluid of
one temperature to flow through said tube in paths defined by the
first said fin strip and for conducting a fluid of a different
temperature to flow over said tube in paths defined by the second
said fin strip material, said manifold means including a manifold
member at each end of said tube and seating to a respective header
plate, each manifold member having a laterally spaced apart series
of vertically extending forwardly projecting ribs to seat to the
header plate, corresponding ribs of the respective manifold members
being laterally offset, inlet and outlet connections for flow of
the said fluid of one temperature to and through said tube by way
of said manifold members, and notches of substantially equal depth
in the projecting ends of said tubes receiving said ribs in an
intersecting relation, said ribs crushing portions of the
projecting ends of the first said fin strip in said tube at said
notches whereby to define a multi-pass heat exchanger where the
ends of adjacent paths are effectively sealed from one another at
the locations of said ribs and where corrugations of the fin strip
define separated flow paths between the manifold members.
4. A multi-pass heat exchanger according to claim 3, wherein said
header plates are fixed to said tubes, each plate being spaced from
a respective end of the tube a distance substantially equal to the
depth of said notches.
5. A multi-pass heat exchanger according to claim 4, wherein said
other strip fin material is confined between said header plates,
characterized by means forming a seal and a bond in the joint
between said tube and said header plates denying intercommunication
of the fluids through said joints.
Description
BACKGROUND OF THE INVENTION
This invention relates to plate and fin heat exchangers,
particularly of the multiple pass type.
The art pertaining to high performance, compact heat exchangers has
become highly developed. The use of strip fin material as an
extended surface means is an important part thereof. In one such
form of device it it known to direct a fluid back and forth across
a heat exchanger, in a single plane or at a single level thereof.
In adjoining planes another fluid is passed. By virtue of
separating, heat conducting plates and through use of inserted fin
material a transfer of heat takes place between the fluids in a
conduction-convection process. A multiple pass flow mode may be
enforced at any or all levels. This has heretofore been achieved by
a use of separable channel-like members which dispose in a side by
side alternating relation to fin strips, between spaced apart
plates, with all parts, after assembly, being united in a brazing
or like operation. A device so constructed is quite satisfactory in
operation. However, the use of separable channels or nose-pieces
adds to the complexity of the article, increasing its cost and
introducing a further reliability factor.
SUMMARY OF THE INVENTION
The instant invention has in view a heat exchanger more simply
constructed than heretofore, with consequent improvement in
fabrication costs and in the reliability factor, and to provide a
device so characterized is an object of the invention.
Another and more particular object is to obviate the use of
separate dividing strips in a heat exchanger providing multiple
passes at a single level.
In accordance with the illustrated embodiment of the invention,
multi-pass performance is achieved using a single fin strip, with
the corrugations of the strip itself serving as a means to separate
adjacent flow passes. Manifold members are applied to ends of the
heat exchanger providing turn-around chambers at the ends of the
flow passes. Between the turn-around chambers projecting ribs on
the manifold members compress against portions of the ends of the
fins substantially to seal adjacent chambers from one another and
enforce longitudinal flow along the corrugations of the fin strip.
Peaks and valleys of the fin corrugations are brazed or otherwise
joined to overlying and underlying plate members. The latter are
notched at their ends to accommodate the projecting ribs on the
manifold members. According to a feature of the illustrated form of
the invention the overlying and underlying plate members are
integrally formed as a flattened tube, thus obviating all need for
separable channel pieces, nose pieces and the like.
Other objects and structural details of the invention will appear
more clearly from the following description, when read in
connection with the accompanying drawings, wherein:
FIG. 1 is a view in front elevation of a heat exchange core in
accordance with the illustrated embodiment of the invention, a
showing of manifold means normally applied to the core being
omitted;
FIG. 2 is a view in transverse section, taken substantially along
the line 2--2 of FIG. 1, the manifold means being in this instance
included;
FIG. 3 is a view in cross section, taken substantially along the
line 3--3 of FIG. 2;
FIG. 4 is a fragmentary view in cross section, taken substantially
along the line 4--4 of FIG. 2; and
FIG. 5 is a fragmentary view in longitudinal section, taken
substantially along the line 5--5 of FIG. 4.
Referring to the drawings, in accordance with the illustrated
embodiment of the invention, a heat exchanger comprises a pair of
spaced apart header plates 10 and 11. The plates 10 and 11 are
identically constructed, having in the present instance a flat
rectangular configuration. Each is formed with a vertical series of
laterally elongated through openings 12. Upper and lower edges of
each opening 12 are parallel to one another. Opposite ends are
curved. The configuration conforms to that of a tube 13 which is
flattened to have the laterally elongated configuration
corresponding to that of the openings 12. The tubes 13 extend
between and interconnect the header plates 10 and 11, opposite ends
of the tubes being accommodated in corresponding openings 12 in the
header plates. The tubes 13 have a closely conforming relation to
the openings 12, and, as will be further described, the parts are
unitarily joined to one another, as by a brazing process. At their
opposite ends, the tubes 13 project through and beyond the
respective header plates 10 and 11. In the projecting end of each
tube is a plurality of cut-outs or notches 14. The notches appear
in both upper and lower end walls of each tube and are comprised in
a laterally spaced apart series of pairs of notches, aligned
notches in the upper and lower end walls constituting each pair. At
opposite ends of the tubes, corresponding pairs of notches are
offset. Each tube 13 forms an enclosure 15 open at its opposite
ends. In the enclosure 15 is a fin strip 16. The member 16 is made
of a thin, ductile heat conductive metallic material gathered or
crimped to the corrugated configuration illustrated.
The corrugations or individual fins of the strip 16 are of uniform
height. This is by design approximately the same as or slightly
greater than the internal dimension between the upper and lower
walls of the tube. Upon insertion of the fin strip into the
enclosure 15, therefore, the fin corrugations are in lightly
compressive, substantially continuous contact with the internal
tube walls. As will be later noted, in a brazing or like process,
the fin peaks and valleys may be unitarily joined to overlying and
underlying tube walls by means forming a seal and a bond. The strip
16 is oriented in each tube to have its fin corrugations extend
lengthwise of the tube or from end to end thereof. In length, it is
substantially coextensive with the tube, portions of the fin strip
tending to occupy and fill the locations of notches 14.
Disposing between the header plates 10 and 11, in an alternating
relation to the tubes 13, are other fin strips 17. These are or may
be constructed similarly to the strips 16, and, where positioned
between adjacent tubes 13, have individual fin corrugations in
contacting relation to overlying and underlying walls as defined by
wall surfaces of the tubes 13. Fin strips 17 are oriented to lie
perpendicularly of or at right angles to the fin strip 16. The
header plates 10 and 11 and adjacent tubes 13 form flow paths 18
occupied by the fin strips 17. At upper and lower ends of the
assembly comprised of alternating fin strips 17 and tubes 13, core
sheets 19 and 21 may be installed to complete a heat exchanger
core. In fabricating the defined core, the header plates 10 and 11,
the tubes 13, fin strips 16 and 17 and core sheets 19 and 21 are
assembled to occupy the relative positions illustrated. The
assembled core is then subjected to a brazing or like operation in
which contacting parts are connected to one another by means
constituting a seal and a bond. A unitary one-piece assembly
accordingly is defined constructed for flow of fluids of different
temperature through the tubes 13 and through the flow paths 18. A
transfer of heat between the fluids takes place, utilizing a
conduction-convection process. All four sides of the heat exchanger
core may be manifolded for a controlled fluid flow. In the
illustrated instance flow of the fluid through the tubes 13 is
manifolded, while flow of a fluid through passages 18 is shown as
occuring in relative unrestricted manner, as if the core were
interposed in a duct wherein a flowing fluid is constrained freely
to have access to and to move longitudinally through the passages
18 in a single pass.
A manifold member 22, which may be a cast metallic structure, is
applied to one face of the heat exchanger core, in enclosing
relation to projecting ends of tubes 13. Turned over marginal edges
on an inner face of the manifold member 22 are turned over and make
an abutting contact with header plate 11. A welding or like
operation may be used positively to unite the cast manifold with
the header plate. Also on the inwardly facing side of the manifold
member 22 is a laterally disposing series of recesses 23 of
vertical extent. At opposite ends of the series of recesses 23 are
somewhat smaller recesses 23a and 23b which for convenience of
terminology will be identified as inlet and outlet recesses
respectively. The several recesses or chambers in the inwardly
facing side of the manifold member 23 are separated by projecting
ribs 24 of vertical extent. On its outwardly facing side, the
manifold member 22 is formed with lower and upper projecting bosses
25 and 26 which are internally threaded to connect in fluid flowing
lines and which serve respectively as the fluid inlet and the fluid
outlet for the heat exchanger. Boss 25 communicates with a cored
passageway 27 leading by way of an opening 28 to inlet recess 23a.
Boss 26 communicates with a passageway 29 leading through an
opening 31 to outlet recess 23b.
On the opposite face of the heat exchanger core is another manifold
member 32 constructed similarly to the member 22 but without the
inlet and outlet bosses and without the cored passageways 27 and
29. Marginal edges of the member 32 are turned over and welded to
the header plate 12. A lateral series of recesses 33 of
longitudinal extent face the core and are separated by projecting
ribs 34. The manifold members 22 and 32 are in an opposing relation
with, however, the respective corresponding recesses 23 and 33
being laterally offset relatively to one another. Ribs 24 and 34
are accordingly correspondingly offset and it will be understood
that the spacing and locations of these ribs are such as to
correspond with the notches 14 in the ends of tubes 13.
In the assembly of the heat exchanger, the core unit is fabricated
as before described, a brazing or like process terminating the
fabrication process and uniting the parts into an integrated
structure. In the brazing process, the peaks and valleys of the fin
corrugations of strip 18 are joined to overlying and underlying
walls of the tube 13, forming continuous seals along the length of
each fin corrugation. Also in the brazing process, tubes 13 are
joined to header plates 10 and 11 in a manner to preclude an escape
of fluid around the tubes and core sheets 19 and 21 are attached to
header plates 10 and 11 to confine fin strips 17 and to close upper
and lower ends of the core. In a subsequent assembly step, the
manifold castings 22 and 32 are welded to the outer faces of header
plates 11 and 10. In carrying out such method step, the manifold
members are applied to a respective core face in a manner to align
the ribs 24 or 34 with corresponding notches 14 in the projecting
ends of tubes 13. Then, as the manifold members are pressed to a
seat on the respective header plates, the ribs 24 and 34 enter
notches 14, being received therein with a relatively close fit. In
entering the notches, the projecting ribs compress against and
crush the material of fin strip 16 disposing within the notches. An
inwardly thrusting rib accordingly deforms a portion of the rib
corrugations and forms therewith a substantial barrier to
by-passing flow from one recess 23 or 33 around an intermediate rib
24 or 34. The ribs 24 and 34 are projected substantially to the
same extent as marginal edges of the manifold members are turned
over. Accordingly, in the process of applying the manifold members
to the header plates the ribs 24 and 34 seat to the header plate at
the same time that marginal portions of the manifold members seat
thereto. The notches 14 are predetermined to have a depth adequate
to permit such simultaneous seating.
In the operation of the heat exchanger, a first fluid is directed
through the passages 18, a preferred direction of flow being as
indicated by the arrows 35 in FIG. 2. A second fluid, at a
temperature different from the first, is brought to the inlet boss
25. There it enters passageway 27 and is conducted through opening
28 to inlet recess 23a. Here the fluid is denied by-passing flow
around the adjacent rib 24 by virtue of this rib seating to header
plate 11 and being at the locations of notches 14 in crushing
engagement with the material of fin strip 16. The fluid accordingly
is compelled to enter the communicating portion of tube 13 and
flows along the fin corrugations in such portion until reaching
recess 33 in the opposite manifold member 32. In the course of such
flow, the fluid is restricted to paths defined by those
corrugations communicating with the inlet recess 23a since the fin
corrugations are joined to the tube walls and define continuous
barriers to lateral flow from one side of the heat exchanger to the
other. Upon reaching the opposing recess 33 in member 32, the fluid
turns around or reverses therein and comes back across the heat
exchanger core, using as flow path defining means the fin
corrugations which are in communication with this recess 33 and
with the recess 23 immediately adjacent the inlet recess 23a . In a
manner believed to be obvious, and as indicated by arrows 36, flow
of the second fluid continues in this manner, making multiple
reverse travels across successive portions of the tubes 13 until it
finally reaches outlet recess 23b and is directed from there to
outlet boss 26. It will be understood that the recesses 23 and 33
are in simultaneous communication with all of the tubes 13 and that
flow through corresponding portions of the tubes occurs in
unison.
It will be evident that structural modifications are possible in
the invention as disclosed, without departing from the intent and
spirit thereof. For example, while three tubes 13 have been
illustrated a heat exchanger with a lesser or greater number of
flow paths could be constructed and made to perform in accordance
with disclosed inventive concepts. Also, the tubes 13 serve a
useful purpose in helping to avoid a use of separator strips within
the heat exchanger core. Thus, not only is it unnecessary to lay in
strips of material to act as internal extensions of the ribs 24 and
34 but it is also unnecessary to provide end strip means
constituting side closures for the passageways 15. In both
instances fabrication of the heat exchanger is simplified and is
therefore less costly and reliability is increased since the
reduction in number of parts and in the number of brazed joints
reduces opportunity for failure. However, if desired, a more
conventional manner of construction could be used in which the
upper and lower walls of the tube 13 were made as separate core
sheets, resembling members 19 and 21, with side margins of such
core sheets joined together by solid spacer elements. Also, fin
strip material 17 has been shown placed in flow passages 18, since
this will conventionally be done in the making of a high
performance, compact heat exchanger. It could be omitted if not
needed to meet heat transfer requirements. Similarly, should it be
desired to make the passages 18 of a multi pass form, manifold
members could be applied to the ends of the heat exchange core and
cooperate with plate and fin portions substantially in the same
manner that manifold members 22 and 32 are applied to sides of the
heat exchanger.
* * * * *