U.S. patent number 3,887,004 [Application Number 05/263,931] was granted by the patent office on 1975-06-03 for heat exchange apparatus.
This patent grant is currently assigned to Hayden Trans-Cooler, Inc.. Invention is credited to Theodore A. Beck.
United States Patent |
3,887,004 |
Beck |
June 3, 1975 |
HEAT EXCHANGE APPARATUS
Abstract
The present invention relates in general to heat exchangers, and
in particular to the type of heat exchanger which includes one or
more tubular heat exchange units as a part thereof. More
particularly, the present disclosure is directed to an improved
tubular heat exchange unit usable in various types of heat exchange
apparatus, and including a fluid flow control core which supports a
plurality of regularly spaced, generally radially oriented heat
exchange fins or splines that are preferably integrally extruded as
a part of the core. In a preferred form the core fins have a novel
cross-sectional configuration with symmetrical concave sides
providing better heat exchange performance by combined improvements
in fluid flow and heat gathering and conducing capacities, such
cross-sectional fin configuration also providing improvements in
assembly and structural integrity. Also disclosed herein are novel
longitudinal configuration of the heat exchange fins including a
step twisted or joggled configuration, a helically or spirally
twisted configuration, and longitudinally segmented fin
constructions provided by either annular grooving of the fins or
helical grooving of the fins, these fin configurations providing
improved heat transfer characteristics by turbulation of fluid
conducted between the fins, and causing a circumferential component
of fluid flow around the tubular heat exchange unit between cold
and hot sides of the overall heat exchange apparatus.
Inventors: |
Beck; Theodore A. (Riverside,
CA) |
Assignee: |
Hayden Trans-Cooler, Inc.
(Corona, CA)
|
Family
ID: |
23003858 |
Appl.
No.: |
05/263,931 |
Filed: |
June 19, 1972 |
Current U.S.
Class: |
165/179;
29/890.049; 165/184; 165/DIG.520; 29/890.047 |
Current CPC
Class: |
F28F
13/12 (20130101); F28F 1/42 (20130101); F28F
1/32 (20130101); Y10T 29/49384 (20150115); F28F
2255/16 (20130101); Y10S 165/52 (20130101); Y10T
29/4938 (20150115); F28F 1/40 (20130101) |
Current International
Class: |
F28F
13/12 (20060101); F28F 1/42 (20060101); F28F
1/10 (20060101); F28F 13/00 (20060101); F28f
001/42 () |
Field of
Search: |
;165/179,183,184 ;138/38
;60/329,337 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
1,290,700 |
|
Mar 1962 |
|
FR |
|
120,867 |
|
Jan 1909 |
|
DD |
|
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Streule; Theophil W.
Attorney, Agent or Firm: Gabriel; Albert L.
Claims
1. A tubular heat exchange conduit which comprises an elongated
central tubular core, a plurality of elongated, generally
longitudinally arranged, circumferentially spaced heat transfer
fins extending generally radially outwardlly from said core, both
sides of each of said fins being concavely curved in the general
radial direction throughout substantially their entire radial
width, with their outer edges being thicker than inner portions
thereof and an elongated, tubular shell peripherally engaged about
and in heat conducting abutting relationship with the outer edges
of said fins, said core, fins and shell defining a plurality of
fluid flow channels between adjacent pairs of the fins.
2. A tubular heat exchange unit as defined in claim 1, wherein said
concave fin sides are of generally parabolic curvature.
3. A tubular heat exchange unit as defined in claim 1, wherein the
rate of curvature of said concave fin sides increases progressively
from the root portions to the toe portions of the fins, so that the
thickness of the fins increases at greater than a linear rate from
said root portions.
4. A tubular heat exchange unit as defined in claim 1, wherein said
tubular core is compsed of a heat conducting metal that is hardest
proximate said tubular core and is progressively softer from said
core radially outwardly through said fins to the outer edges of the
fins.
5. A tubular heat exchange unit as defined in claim 4, wherein said
shell is composed of heat conducting metal that is harder than the
outer edge portions of said fins that are in contact therewith.
6. A tubular heat exchange unit as defined in claim 1, which
includes a series of external fins arranged over said shell with
their planes generally normal to the axis of the tubular unit, said
shell being generally radially outwardly stressed by said extrusion
core and fins against said external fins.
7. A tubular heat exchange unit as defined in claim 1, wherein said
shell has spiral external fin means externally formed thereon.
8. A tubular heat exchange unit as defined in claim 1, which
includes an elongated inner fin structure disposed within said
tubular core.
9. A tubular heat exchange unit as defined in claim 1, wherein said
fins are provided with a twist along at least a portion of the
length thereof, and wherein said twist is stepped.
10. A tubular heat exchange unit as defined in claim 9, wherein
said stepped twist includes a series of alternating, generally
longitudinally oriented fin portions and generally helically
inclined fin portions.
11. A tubular heat exchange unit as defined in claim 10, wherein
the transitions between successive fin portions are discrete angle
bends on the fins.
12. A tubular heat exchange unit as defined in claim 1, having
grooves segmenting said fins throughout substantially their entire
height, said groove means comprising a series of longitudinally
spaced, generally circumferentially arranged grooves in the
fins.
13. A tubular heat exchange unit as defined in claim 12, wherein
said groove means comprises a generally spirally arranged groove in
the fins.
14. A tubular heat exchange unit as defined in claim 12, wherein
said groove means comprises a series of longitudinally spaced,
generally transverse grooves in the fins, the widths of said
grooves being not substantially greater in the longitudinal
direction of the fins than the average fin thickness.
15. A tubular heat exchange unit as defined in claim 14, wherein
the widths of said grooves are substantially the same in the
longitudinal direction of the fins as the average fin thickness.
Description
BACKGROUND OF THE INVENTION
Heat exchangers are currently employed in a wide variety of fields,
and they take a number of different forms. In many fields of heat
exchanger usage, such as oil refining plants and industrial
refrigeration apparatus, neither space nor weight is at a premium,
so the heat exchangers can be large and bulky, and need not be
particularly efficient. However, in certain heat exchanger
environments it is of particular importance to provide a maximum of
heat exchange capacity with a minimum size and weight. An example
of such environment is the use of heat exchange apparatus for
cooling the oils employed in connection with the operation of motor
vehicles, such as transmission fluid used in automatic
transmissions and torque converters, engine oil, power steering
fluid, hydraulic fluids, and the like, such oils hereinafter being
referred to simply as motor vehicle oils. In this motor vehicle
environment, during excessive load conditions large amounts of heat
must be exchanged from the fluid system into the atmosphere.
Nevertheless, there is only minimal space or airflow available in
most motor vehicles for placement of heat exchange apparatus for
such purposes, and only part of the available space is disposed
with good access to the air flow that is necessary for maximum heat
exchanging. Accordingly, it is of vital importance in motor vehicle
heat exchangers of this type to provide a maximum of heat exchange
capacity in heat exchange apparatus of minimum overall
dimension.
Similar considerations of high heat exchange capacity in a minimum
space also prevail in other environments, as for example with other
types of vehicles, in relatively small and compact refrigerations
systems such as those found in the home, in restaurants, in
computers, and the like.
Most heat exchange apparatus of high capacity with minimum size,
such as heat exchange apparatus employed for cooling motor vehicle
oils, is of a type having one or more tubular heat exchange units
having external fins associated therewith, the oil passing through
the tubular units giving up heat to internal fins thereof, the heat
being conducted radially outwardly through the walls of the tubular
units and thence to the external fins and being removed primarily
by radiation and convection from the external fins. Conventional
internal turbulating fin structures in such tubular heat exchange
units are relatively inefficient, tending to permit laminar fluid
flow, and not having particularly good heat gathering capability;
and conventional fin constructions also tend to reduce heat
transfer by obstructing the flow of fluid through the tubular heat
exchange units.
SUMMARY OF THE INVENTION
In view of these and other problems in the art, it is an object of
the present invention to provide a novel tubular heat exchange unit
having a regular annular array of heat transfer fins therein of
improved heat exchange characteristics.
Another object of the invention is to provide a tubular heat
exchange unit of the character described wherein the heat transfer
fins have a novel cross-sectional configuration with symmetrical
concave sides that are preferably, but not necessarily, of
generally parabolic curvature. This concave-sided fin configuration
improves heat transfer performance in a number of ways, including
increasing the fluid flow channel cross section between the
adjacent pairs of fins, reducing pressure drop, adding to the heat
collecting surface areas of the fins, provided improved heat
transfer characteristics between the inner root portions and outer
toe portions of the fins, and adding surface contact area between
the outer ends of the fins and the surrounding tubular shell.
In the presently preferred form of the invention the fins are
integrally extruded with an inner tubular core body, the fins
extending generally radially outwardly from this tubular core body
and having their outer ends seated in metal-to-metal heat-exchange
contact with the tubular outer shell of the tubular heat exchange
unit. In assembling the flow control core consisting of the tubular
core body and its fins to the outer tubular shell, the tubular core
body is expanded radially outwardly to a much greater extent than
the clearance to be taken up between the outer ends of the fins and
the outer shell, and such outward expansion involves a unique
cooperation of varying work hardening from the "as extruded"
condition of the flow control core with the configuration of
tubular core body and fins, wherein the tubular core body becomes a
generally rigid internal supporting structure, the fins are hardest
in their inner root portions where they are thinnest and need
strengthening, and become softer radially outwardly to soft outer
toe portions that are thereby made formable for intimate mating
with the outer tubular shell, the hard internal supporting tube
structure maintaining outward compression of the flow control core
against the outer tubular shell for good structural integrity and
heat conducting interfaces.
Another important feature of the present invention is the provision
of novel longitudinal configurations of the heat exchange fins. One
such longitudinal configuration is a step-twisted or joggled
configuration wherein the fins are maintained in parallel
relationship to each other, while they are stepped or joggled in a
succession of alternate longitudinal portions which are preferably
generally parallel to the axis of the tubular heat exchange unit
and twisted portions which are inclined at a substantial angle to
the axis and are generally helical; such step twisted or joggled
fin configurations reducing the tendency for laminar flow and
introducing turbulation into the fluid, as well as rotating the
fluid circumferentially about the tubular heat exchange unit
between cold and hot sides thereof.
Another novel longitudinal configuration of the fins is the
segmentation thereof by either a series of annular longitudinally
spaced grooves, or a single spiral or helical groove, such
segmentations being applicable to either straight or joggled or
spirally twisted fins, and adding additional turbulation and in the
case of the spiral groove circumferential movement of the fluid. An
important aspect of such longitudinally interrupted fins is that
the grooves which provide the interruptions, while removing side
surface areas from the fins, add the end surface areas of the fin
segments so that overall surface area is not substantially
reduced.
Other objects, aspects and advantages of the present invention will
be apparent from the following description taken in connection with
the accompanying drawings, wherein:
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is an elevational view illustrating heat exchange apparatus
of one type which is particularly suitable for use with the present
invention.
FIG. 2 is an enlarged cross-sectional view taken on the line 2--2
in FIG. 1 illustrating one form of tubular heat exchange unit
according to the invention.
FIG. 3 is a side elevational view, partly in axial section, showing
a form of the invention wherein the core fins in the tubular heat
exchange unit have a joggled or stepped twist configuration.
FIG. 4 is a view similar to FIG. 3 illustrating a form of the
invention wherein the core fins are longitudinally interrupted by a
series of longitudinally spaced annular grooves.
FIG. 5 is a view similar to FIGS. 3 and 4, but illustrating a flow
control core of the tubular heat exchange unit which has
longitudinaly arranged core fins that are generally parallel to the
axis of the unit.
FIG. 6 is a view similar to FIGS. 3, 4, and 5, but illustrating
longitudinal interruption of the core fins by a helical groove
which provides a series of longitudinally spaced grooves in each of
the fins.
FIG. 7 is a view similar to FIGS. 3 to 6, but illustrating a core
body having helically twisted fins.
FIG. 8 is an end elevational view illustrating a heat exchange unit
similar to that shown in FIG. 2, but with the addition of an inner
fin structure disposed within the tubular core body.
FIG. 9 is an end elevational view illustrating a modified flow
control core having generally flat-sided fins.
FIG. 10 is a view similar to FIG. 9, but illustrating a flow
control core of generally inverted construction wherein the tubular
core body is on the outside and the integral fins extend generally
radially inwardly therefrom.
FIG. 11 illustrates heat exchange apparatus embodying the invention
which has a spiral finned outer shell.
FIG. 12 is a transverse section, with portions shown in elevation,
illustrating heat exchange apparatus wherein a "bundle" of tubular
heat exchange units according to the invention is enclosed within
an outer heat exchanger shell.
FIG. 13 illustrates an expansion method step used in making a
tubular heat exchange unit according to the invention and securing
the same within finned heat exchange apparatus.
DETAILED DESCRIPTION
FIG. 1 illustrates heat exchange apparatus 10 of a general type
that is currently widely employed in heat exchange systems for
cooling motor vehicle oils. Such heat exchange systems employing
heat exchange apparatus of the general type shown in FIG. 1 are
described in U.S. Pat. No. 3,315,464, issued Apr. 25, 1967 to Perez
M. Hayden for "Heat-Exchange System." The heat exchange apparatus
10 represents typical heat exchange apparatus in which the present
invention may be employed, although it is to be understood that the
present invention is adaptable for any type of heat exchange
apparatus which utilizes tubular heat exchange members therein. It
is also to be understood that while the present invention is
particularly useful in heat exchange apparatus that is employed for
cooling motor vehicle oils under circumstances of excessive heat
production, nevertheless the invention is suitable for any heat
exchange purpose involving the transfer of heat from one fluid to
another.
The heat exchange apparatus of FIG. 1 includes a plurality of
tubular heat exchange units 12 according to the present invention,
these heat exchange units 12 being four in number in the apparatus
10, and being arranged in a generally parallel, regularly spaced
planar array. The tubular heat exchange units 12 are maintained in
this array by engagement thereof through spaced apertures in a
series of parallel fins 14 that are disposed normal to the axes of
the tubular heat exchange units 12. The fins 14 serve not only as
supporting structures, but they are in heat exchange relationship
with the outer surfaces of the tubular heat exchange units 12, and
thereby add considerable additional heat exchange area to the outer
surfaces of the tubular heat exchange units 12 so as to increase
the overall heat exchange efficiency of the apparatus 10.
The tubular heat exchange units 12 are interconnected by means of a
series of U-shaped end fittings 16 so that the tubular heat
exchange units 12 are arranged for serial flow of fluid
therethrough between open ends 18 and 20 which are adapted to be
connected into the heat exchange system.
FIG. 2 illustrates a presently preferred cross-sectional
arrangement for a tubular heat exchange unit 12 according to the
present invention. The heat exchange unit 12 includes two principal
structural components, a tubular flow control core 22 and a tubular
outer shell 38. Both of these components 22 are preferably
extrusions, and they may be extruded from any material having good
heat transfer characteristics, as for example aluminum, copper or
other heat conducting metal.
The flow control core 22 includes a tubular core body 24 which
serves as an inner tube member for the heat exchange unit 12.
Integrally extruded with the core body 24 are a plurality of
regularly spaced, generally radially outwardly extending core fins
or splines 26. For illustrative purposes 18 of these regularly
spaced core fins 26 have been shown in FIG. 2. However, any desired
number of these core fins 26 may be provided without departing from
the present invention. Thus, for example, flow control cores 22 may
be provided with 12 fins, 18 fins, 22 fins, or other desired number
of fins. Since most of the useful heat transfer area of heat
exchange unit 12 exposed to the fluid that flows therethrough is in
the side surfaces of the core fins 26, what is desired is a maximum
of such core fin side surface heat transfer area, while at the same
time maintaining a maximum flow conduit cross section between
adjacent fins 26. In other words, what is desired is the best
possible combination of heat transfer area and minimum pressure
drop in the tubular heat exchange unit 12. With present extrusion
techniques, the presently preferred number of core fins 26 is about
22, which allows the fins to be relatively long in the radial
direction, while at the same time being relatively narrow in the
circumferential direction, so as to provide an excellent
combination of large heat transfer area and low pressure drop.
However, if extrusion die manufacturing techniques materially
improve over those currently available, then the "tongue ratio"
(area/width.sup.2) of the fins could be increased to allow an
increase in the number of fins without the fins being shortened to
the point of losing performance.
Nevertheless, the optimum number of fins will depend upon the
viscosity, specific heat and conductivity of the heat exchange
fluid, as these factors will determine the frictional losses and
the heat transfer characteristics in relation to any particular
number of the fins 26.
Still referring to FIG. 2 of the drawings, each of core fins 26
commences at a root portion 28 proximate the core body 24 and
terminates in a toe portion 30 having a free end surface 32 that is
preferably arcuately complementary to the curvature of the inside
of the tubular shell 38 within which the flow control core 22 is
engaged. Each core fin 26 is symmetrical about its radial axis, and
in the preferred cross-sectional form of the invention as shown in
FIG. 2, each core fin 26 has symmetrical side surfaces 34 which are
concave in the general radial direction, the core fin being
relatively thin at its root portion 28, and thickening at a
non-uniform, progressively increasing rate from the root portion 28
to the free end surface 32. The preferred form of this concave
curvature of the side surfaces 34 is parabolic.
The symmetrical concave side surface configuration for the core
fins 26 provides a number of advantages over core fins that have
parallel straight sides or radially outwardly flaring straight
sides. One advantage is that the concave side surfaces 34 provide a
substantial increase in the cross sections of the fluid flow
channels 36 between adjacent fins 26, without losing any heat
collecting or transferring capacity of the fins. In fact, a second
advantage of the concave side surfaces 34 of the fins 26 is that
the increased surface area provided thereby and the flaring at the
toe portion 30 actually provide increased efficiency in heat
collection and transfer to the free end surfaces 32 of the fins 26.
Another advantage of the concave side configuration for the core
fins 26 is that when the flow control core 22 is expanded outwardly
against the tubular outer shell 38 as hereinafter described in
detail, the concavities in the sides of the core fins 26
accommodate some bulging in the fins. Another factor of improvement
caused by the concave sides is that the resulting circumferential
widths of the free end surfaces 32 of the fins 26 are greater,
providing increased heat flow contact surface areas between the
outer surfaces of the fins 26 and the inner surface of the tubular
shell 38. Not only does this added circumferential width at the fin
ends 32 increase the heat transfer, but it also tends to stabilize
the generally radial orientation of the fins against buckling or
distortion as the flow control core 22 is expanded outwardly
against the tubular shell 38.
FIG. 13 illustrates a presently preferred method of making heat
exchange apparatus embodying the present invention. FIG. 13
illustrates a fragmentary section of heat exchange apparatus like
the apparatus 10 shown in FIG. 1, taken axially of one of the
tubular heat exchange units 12 of the invention. Prior to the
method step that is in progress in FIG. 13, the parallel fins 14
were assembled over the tubular shell 38 of heat exchange unit 12,
and the tubular shell 38 was expanded outwardly against the fins 14
to provide secure mechanical interconnection between the shell 38
and fins 14. Such outward expansion of the tubular shell 38 against
the fins 14 is by conventional means, as for example by passing an
expander mandrel axially through the tubular shell 38. Such outward
expansion of the tubular shell 38 causes work hardening in the
shell 38 so that shell 38 is illustrated in FIG. 13 is
substantially harder than in the "as received" condition
thereof.
In making heat exchange apparatus like the apparatus 10 shown in
FIG. 1, normally all of the tubular shells 38 will be assembled
with the fins 14 by the aforesaid expansion of the shells 38, and
at least one end of each of the shells 38 (i.e., each of the four
in the apparatus 10 of FIG. 1) will be left open for insertion of a
respective flow control core section 22 therein. Thus, for example,
in the apparatus 10 of FIG. 1, the U-shaped end fittings 16 may all
be absent when the cores 22 are inserted in the respective tubular
shells 38, or if desired the two end fittings 16 at the left-hand
side of the apparatus 10 as shown may be installed, and the single
central fitting 16 may still be unconnected, so that all of the
four flow control cores 22 can be inserted from the right-hand ends
of the tubular shells 38. For ease of assembly, it is preferred to
provide some clearance between the free end surfaces 32 of the core
fins 26 and the inner surface of the tubular shell 38. For example,
for a typical flow control core 22 having an O.D. of approximately
11/16 inch, it is desirable to have a clearance of approximately
0.005 inch between the thin ends 32 and the inner surface of shell
38. With present extrusion techniques it is difficult to establish
such clearance with the desired uniformity, so that it is preferred
to either roll or draw the flow control cores 22 to the desired
size. Such rolling or drawing provides a configuration of the free
end surfaces 32 of the core fins 26 which is more nearly accurately
complementary to the inner surface of tubular shell 38, for better
mating therebetween and hence better heat transfer
characteristics.
Referring to FIG. 13, after the flow control core 22 is slidably
inserted into tubular shell 38, the core 22 is then expanded
radially outwardly into compressive engagement with the shell 38 by
any conventional means, as for example by one or more passes of a
mandrel 40 axially through the tubular core body 24 of the flow
control core 22, the mandrel 40 having a bead or "bug" 42 thereon
which causes the expansion. It is preferred to expand the core body
24 outwardly much more than the amount of the clearance between the
end surfaces 32 of the fins and the shells 38 in order to provide a
preferred combination of work hardening in strategic portions of
the core 22 and intimate mating between the free end surfaces 32 of
the core fins and the shell 38. For example, with an initial
clearance of about 5/1000 inch between the fin end surfaces 32 and
the shell 38, it is desirable to apply approximately three times
this amount or about 15/1000 inch of radial expansion to the
tubular core body 24. This expansion step is illustrated in FIG.
13, the flow control core 22 being expanded from left to right by
the mandrel bead 42.
This relatively large amount of radial expansion of the core body
24 relative to the initial clearance causes a considerable amount
of work hardening of the tubular core body 24 from its initially
soft "as extruded" condition, so that the internal supporting
tubular core body 24 becomes quite hard, and serves as a stable
internal supporting structure for the core fins 26. This expansion
also causes a considerable amount of work hardening in the actual
fins 26, but such work hardening is greatest proximate the root
portions 28 of the fins, and decreases outwardly through the fins
to a minimum of work hardening proximate the toe portions 30 of the
fins, and particularly at the free end surfaces 32 of the fins.
Thus, the relatively thin root portions 28 of the fins are
substantially strengthened by work hardening, while the thicker toe
portions 30 which inherently have greater structural strength
remain softer, and the soft free end surface portions 32 of the
fins are formable against the tubular shell 38 for excellent mating
contact therewith and consequent good thermal flow characteristics
therebetween. Generally the tubular shell 38 will be harder from
its aforesaid work hardening than the free end surfaces 32 of the
fins 26, and with the relatively hard inner core body 24 and the
relatively hard outer tubular shell 38, there will be good
permanent radial loading on the fins 26 under all operative
conditions of the heat exchange apparatus.
For the example given, with an initial clearance between the O.D.
of the flow control core 22 and the I.D. of tubular shell 38 of
about 0.005 inch, and with an expansion of the tubular core body 24
of about 0.015 inch, it is found in practice that the outer tubular
shell 38 will be further expanded outwardly approximately another
0.001 inch, which serves to further secure the structural
connection between the shell 38 and the fins 14 and thereby provide
a stronger overall heat exchange apparatus.
After a flow control core 22 is thus inserted and expanded into
each of the tubular shells 38 of the heat exchange apparatus 10,
then the end fitting connections of the apparatus 10 may be
completed.
While the flow control cores 22 will normally only be used in
straight sections of the outer tubular shells 38, it is to be
understood that an assembled tubular heat exchange unit 12,
including both the flow control core 22 and the tubular outer shell
38, may be bent as desired for a particular heat exchange
installation, provided the arc of the bend is sufficiently large to
avoid crimping or collapsing of the assembly.
In addition to the forming of the free end surfaces 32 of the core
fins 26 against the inner surface of tubular shell 38, the outward
pressurization of the fins against the shell 38 described in detail
hereinabove results in the outer ends of the fins actually slightly
sinking into the material of tubular shell 38, which is a factor in
the excellent heat flow characteristics of the interface between
the fins 26 and the tubular shell 38.
If desired the core 22 may be secured within the tubular shell 38
by furnace brazing as an alternative to the aforesaid preferred
expansion technique.
The central passage within tubular core body 24 may either be
blocked off against the flow of fluid therethrough so as to force
all of the fluid to flow through the flow channels 36, or left open
so that fluid will flow both through the flow channels 36 and
through the center of core body 24. If there is an unlimited flow
of fluid available, then the maximum heat exchange capacity of a
tubular heat exchange unit 12 will be achieved by having the center
of core body 24 open and passing fluid through both the flow
channels 36 and the center of core body 24. However, without a
large fluid flow availability the tubular heat exchange unit 12
will be more efficient if the center of core body 24 is blocked off
and the fluid is thereby required to flow through the channels 36.
An alternative arrangement is to provide valve means within core
body 24 which permits the flow of fluid through core body 24
according to the temperature and/or viscosity of the fluid, such
alternative being the subject matter of another patent application
concurrently filed by the present applicant and entitled "Heat
Exchange Valve System."
FIG. 3 illustrates a tubular heat exchange unit 12a having a flow
control core 22a which includes a tubular body 24a and core fins
26a. This flow control core 22a preferably, but not necessarily,
has a cross-sectional configuration like that illustrated in FIG. 2
and described in detail in connection therewith. In the heat
exchange unit 12a the core fins 26a are provided with a stepped
twist or joggle, while nevertheless being maintained parallel to
each other. Thus, each of the core fins 26a is formed to a series
of alternating longitudinal portions 44 which are generally
parallel to the axis of the core 22a and twisted portions 46 which
are inclined at a substantial angle relative to the axis of core
22a so as to be generally helically disposed. The transitions from
longitudinal portions 44 to twisted portions 46 and from twisted
portions 46 back to longitudinal portions 44 are preferably sharply
defined direct angle bends 48 in the core fins 26a. The step
twisted or joggled core fins 26a provide step twisted or joggled
flow channels 50 therebetween, and each of these channels as it
extends longitudinally along the flow control core 22a progresses
circumferentially around the flow control core 22a, preferably at
least 180.degree..
The step twisted or joggled flow channels 50 have several important
advantages. One advantage is that each direction change imposed
upon the fluid flowing through the channels 50 causes a reduced
film thickness of the fluid proximate the fin surfaces, thereby
improving the heat transfer characteristics. Additionally, each
direction change causes a turbulence in the fluid, which further
increases the heat transfer characteristics. The sharper and more
direct the change in direction of the fluid flow at the angle bends
48, the more effective the film thickness reduction and
turbulation, and accordingly the better the heat transfer
characteristics. Also, the channels between the twisted fin
portions 46 are narrower than those between the straight fin
portions 44, whereby the fluid flow in the twisted channels will
have increased velocity and reduced pressure (according to
Bernouli's principle), which causes a further turbulation, tending
to create fluid vortices when the fluid is suddenly subjected to
speed reduction, pressure increase and direction change as it
enters the straight channels from the twisted channels.
Another important advantage of the step twisted or joggled fin
construction as shown in FIG. 3 is that it conducts the fluid
peripherally around the tubular heat exchange unit 12a from one
side to the other in a heat exchange apparatus such as the
apparatus 10 that embodies a heat exchange unit 12a. Heat exchange
apparatus such as apparatus 10 is typically disposed in an
airstream which enters through one flat side of the apparatus 10
and leaves through the other, so that the side through which the
airstream enters becomes colder than the side from which the
air-stream leaves. The stepped twist or joggled arrangement of the
core fins 26a thus causes the fluid in the tubular heat exchange
unit 12a to rotate around the unit 12a between the cold and hot
sides of the overall heat exchange apparatus, producing maximum
heat transfer efficiency.
FIG. 4 illustrates a tubular heat exchange unit 12b that is similar
to the heat exchange unit 12a shown in FIG. 3, but which has
annular grooves cut in the core fins thereof by saw or knife
cutting or the like for further turbulation of the fluid passing
generally axially through the heat exchange unit 12b. Thus, the
unit 12b includes flow control core 22b having step twisted or
joggled core fins 26b which are parallel and which each include a
series of alternate longitudinal portions 44b and twisted portions
46b. The core fins 26b are longitudinally interrupted by a series
of longitudinally spaced annular grooves 52 which may extend into
the core fins 26b to any desired depth. Preferably, the annular
grooves 52 are cut approximately through the entire depth of the
core fins 26b to the tubular core body 24b, but if desired the
depth of the cut may be either less or more. Some or all of the
grooves 52 may be unequally cut, if desired, to an extent providing
some communicating passages between the flow control channels
defined between adjacent core fins 26b and the bore within the
tubular body 24b.
As the fluid passes through a channel defined between either a pair
of longitudinal fin portions 44b or a pair of twisted fin portions
46b, the velocity and viscosity of the fluid tend to make its flow
become laminar; but before substantial laminar characteristics of
flow can be established, the fluid reaches a groove 52 and becomes
turbulated to disturb such laminar flow. In this manner, the fluid
flow is repeatedly disturbed as the fluid progresses both axially
and circumferentially through the heat exchange unit 12b, and
optimized heat exchange characteristics are obtained by maintaining
a balance of turbulent and laminar flow.
It will be noted that in FIG. 4 the grooves 52 are shown as being
cut proximate the angle bends of the step twisted or joggled fins.
This provides opposite end faces 54 and 56 on the discrete core fin
segments which are proximate the change of direction of flow of the
fluid for good turbulating effect of both upstream and downstream
faces. The sharp, knife-like corners of the fin segments which face
upstream scavenge some of the central fluid flow from each channel
and divert it into the next channel and against the fin sides,
thereby assuring repeated fin surface contact of all portions of
the fluid.
However, if desired the grooves 52 may alternatively be cut through
the longitudinal centers of the longitudinal portions 44b and the
twisted portions 46b of the core fins 26b; or the grooves 52 may be
longitudinally spaced at other intervals.
Satisfactory turbulating results have been achieved with the
grooves 52 cut from about 0.020 inch to about 1/4 inch in axial
width, with their centers axially spaced from about 1/4 inch to
about 1 inch. However, it is preferred to have the axial width of
each groove 52 approximately equal to the average core fin
thickness, which provides a substantial turbulating gap, without
any substantial loss in heat transfer surface area of the fins
since the surface area of the added faces 54 and 56 substantially
completely compensates for the loss in side surface area of the
fins. If the grooves 52 were made substantially wider in the axial
direction of the unit 12b, then heat transfer surface of the fins
would be sacrificed; while on the other hand, if the grooves 52
were made substantially narrower in the axial direction of the unit
12b, then turbulation would be decreased. Because of the importance
of having a maximum amount of heat transfer surface area in the
fins, and since the heat transfer area is actually increased by the
grooves 52 if they are narrower than the average fin thickness, and
heat transfer surface area is not reduced until the width of the
grooves 52 becomes greater than the average thickness of the fins,
it is preferred according to the invention to provide grooves 52
which are not substantially wider in the axial direction than the
average fin thickness.
The stepped type of twist is shown in FIGS. 3 and 4 can be provided
by taking an untwisted flow control core 22 such as that shown in
FIG. 5 and, before insertion thereof in the outer shell 38,
gripping the core 22 at spaced axial locations corresponding to the
longitudinal portions 44 of the fins as shown in FIG. 3 and
applying the required twisting forces to twist the core 22 until
the fins acquire the desired amount of twist, such as the twist of
the fin portions 46 as shown in FIG. 3. Gripping force for such
twisting action, and definition of discrete angle bends 48, may be
achieved by engaging a series of gripping lugs between adjacent
core fins proximate the longitudinal portions 44 thereof as shown
in FIG. 3, such lugs having substantially the same axial length of
the longitudinal fin portions 44 as shown in FIG. 3.
Nevertheless, a tubular heat exchange unit 12 as shown in FIG. 5,
including a flow control core 22 having generally straight core
fins 26 and intermediate flow channels 36 which are generally
parallel to the axis of the heat exchange unit 12, will have good
heat exchange characteristics with a cross-sectional configuration
generally as shown in FIG. 2.
Referring now to FIG. 6 of the drawings, a tubular heat exchange
unit 12c is illustrated which embodies a generally untwisted or
straight flow control core 22c having tubular core body 24c and
core fins 26c. In this form of the invention a helical groove 58 is
provided in the core fins 26c, as by saw or knife cutting or the
like, such helical groove 58 separating each of the core fins 26c
into a series of discrete core fins sections having end faces 60
and 62. The angular inclines and sharp leading corners of the faces
62 resulting from the helical type groove 58 tend to deflect and
swirl the fluid streams in vortexlike movements proximate the
groove for good turbulation. The angular faces also tend to
circulate the fluid circumferentially as it progresses axially
through the heat exchange unit 12c, shifting the centers of the
fluid streams into contact with fin surfaces and moving the fluid
between cold and hot sides of heat exchange apparatus embodying
this type of heat exchange unit 12c.
The spiral frequency or number of spirals per inch of the groove 58
is important to the heat transfer capability, and is preferably
about the same as the spacing between adjacent grooves 52 in the
form shown in FIG. 4. Accordingly, a suitable "lead" for the groove
58 is about 3/8 inch between groove centers for a particular fin,
with leads between 1/4 inch and 1 inch operating satisfactorily,
for a flow control core 22c that is roughly 3/4 inch in diameter.
However, an increase in the spiral frequency will generally be
desirable to accommodate an increase in the number of fins. As with
the grooves 52 of FIG. 4, groove widths for the helical or spiral
grooves 58 may be a width from about 0.020 inch to about 1/4 inch,
but it is preferred that the width be approximately the same as the
average thickness of the fins 26c, and not be substantially greater
than the average thickness of the fins 26c. The helical groove 58
preferably extends radially inwardly through the entire radial
depth of the core fins 26c.
While the helical groove form a flow control core has been shown in
FIG. 6 with generally straight fins 26c, it is to be understood
that the helical groove may be applied to a flow control core
according to the invention which has step twisted or joggled core
fins like those shown in FIG. 3, or which has helically twisted
fins like the fins 26d illlustrated in FIG. 7 which figure
illustrates a tubular heat exchange unit 12d having flow control
core 24d comprising tubular core body 24d and the helically twisted
fins 26d extending generally radially therefrom. Similarly, the
annular type grooves like those shown in FIG. 4 in connection with
the step twisted or joggled core fins may alternatively be applied
to straight core fins like those shown in FIG. 5 or to helically
twisted core fins like those shown in FIG. 7.
If desired, further heat exchange capacity can be provided in
tubular heat exchange units according to the present invention by
incorporating within the tubular core body a small inner fin
structure 64 as shown in FIG. 8, and allowing the fluid to pass
through the core body. Such fluid flow may, if desired, be
controlled by valve means in the core body 24 which regulates the
flow according to the temperature and/or viscosity of the fluid, as
shown and described in said concurrently filed application for
"Heat Exchange Valve System." The inner fin structure 64 shown in
FIG. 8 may be formed of a multifolded strip of metal, and fin
constructions similar to this are disclosed in the aforesaid Hayden
U.S. Pat. No. 3,315,464, and also in U.S. Pat. No. 2,797,554,
issued July 2, 1957 to W. J. Donovan for "Heat Exchanger in
Refrigeration System" and U.S. Pat. No. 3,197,975, issued Aug. 3,
1965 to C. Boling for "Refrigeration System and Heat Exchangers."
If desired, the inner fin structure 64 may be supported in its
operative position by a central core 65 which is shown as a rod,
but may be a small tube.
FIG. 9 illustrates a tubular heat exchange unit according to the
present invention wherein the flow control core 66 has a tubular
core body 68 with integral core fins 70 which expand radially
outwardly from the core body 68 to the outer shell 38 with
generally flat, radially oriented sides 72.
FIG. 10 illustrates a tubular heat exchange unit which is generally
inverted or "inside out" from the other forms of the invention
disclosed herein, having a flow control core 74 that consists of an
outer tubular core body 76 having integral inwardly extending fins
78 therein, the core body 76 and fins 78 preferably being formed
together by extrusion. The inner tubular shell 80 may be a
separately extruded tube that is inserted inside the inner ends of
the fins 78 and then expanded outwardly against the fins 78. If
desired, such outward expansion of the inner shell 80 may be
sufficient to cause an overall outward expansion of the outer
tubular core body 76 for securing the latter in a series of fins
such as the fins 14 shown in FIGS. 1 and 13.
FIG. 11 illustrates heat exchange apparatus generally designated 82
comprising a spiral finned outer shell 84 commonly referred to as
"wolverine tubing," with a flow control core 22 of the present
invention fitted therein. The core 22 is preferably expanded
outwardly into intimate heat transfer engagement with the inner
tubular surface of the shell 84 generally in the manner illustrated
in FIG. 13. Heat exchange apparatus 82 of this type is particularly
useful for small heat exchange requirements wherein a plurality of
tubular heat exchange units such as the arrangement in FIG. 1 is
not required.
FIG. 12 illustrates a further type of heat exchange apparatus 86
within which tubular heat exchange units 12 according to the
present invention may be employed. The apparatus 86 includes a
tubular outer shell 88 within which a bundle of the heat exchange
units 12 is contained, the outer shell 88 having inlet and outlet
conduits 90 and 92 for circulation of one fluid about the outsides
of the tubular heat exchange units 12 through the interstitial flow
channels 94; while the ends of the heat exchange units 12
communicate with respective headers (not shown) for passage of
another fluid through the heat exchange units 12. Heat exchange
apparatus of this general type is illustrated in the aforesaid
Donovan U.S. Pat. No. 2,797,554.
In general, tubular heat exchange units 12 according to the present
invention will provide improved heat exchange performance in any
type of heat exchange apparatus which employs tubular heat exchange
members therein, such as the apparatus 10 shown in FIG. 1,
apparatus similar to that of FIG. 1 but with a plurality of the
tubular heat exchange units arranged for parallel flow between end
headers, the apparatus 82 shown in FIG. 11, the apparatus 86 shown
in FIG. 12, or other heat exchange apparatus.
While the instant invention has been shown and described herein in
what are conceived to be the most practical and preferred
embodiments, it is recognized that departures may be made therefrom
within the scope of the invention. I claim:
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