U.S. patent number 3,866,668 [Application Number 05/307,612] was granted by the patent office on 1975-02-18 for method of heat exchange using rotary heat exchanger.
This patent grant is currently assigned to E. I. du Pont de Nemours and Company. Invention is credited to William A. Doerner.
United States Patent |
3,866,668 |
Doerner |
February 18, 1975 |
METHOD OF HEAT EXCHANGE USING ROTARY HEAT EXCHANGER
Abstract
A rotary heat exchanger comprising an array of closely spaced
parallel annular thermally conductive fins mounted coaxially for
rotation as a unit. A plurality of thermally conductive heat
exchange tubes extends longitudinally through the array of fins
circumferentially about the rotational axis and the fins are
dimensioned and spaced and rotationally driven at a speed operable
to convey a gaseous fluid radially between said fins essentially by
viscosity shear forces and accelerate such fluid substantially to
the velocity providing optimum total heat exchange between said
fluid and another fluid flowing through the heat exchange
tubes.
Inventors: |
Doerner; William A.
(Wilmington, DE) |
Assignee: |
E. I. du Pont de Nemours and
Company (Wilmington, DE)
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Family
ID: |
26808057 |
Appl.
No.: |
05/307,612 |
Filed: |
November 17, 1972 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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110478 |
Jan 28, 1971 |
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25857 |
Apr 4, 1970 |
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Current U.S.
Class: |
165/92; 165/110;
165/125; 415/90; 416/4; 416/95; 416/186A |
Current CPC
Class: |
F28B
1/08 (20130101); F28D 11/04 (20130101); F04D
17/161 (20130101) |
Current International
Class: |
F28D
11/04 (20060101); F04D 17/16 (20060101); F04D
17/00 (20060101); F28B 1/08 (20060101); F28B
1/00 (20060101); F28D 11/00 (20060101); F28d
011/04 (); F28f 005/00 () |
Field of
Search: |
;165/86,88,92,125,110,1
;62/499 ;415/90 ;416/4 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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252,373 |
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Apr 1927 |
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GB |
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381,490 |
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Oct 1932 |
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GB |
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587,149 |
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Apr 1947 |
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GB |
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Primary Examiner: Davis, Jr.; Albert W.
Attorney, Agent or Firm: Howson and Howson
Parent Case Text
This application is a continuation-in-part of my application Ser.
No. 110,478 filed Jan. 28, 1971, which was a continuation-in-part
of my earlier application Ser. No. 25,857, filed Apr. 4, 1970, now
abandoned.
Claims
1. In rotary heat exchange apparatus comprising
an array of a plurality of annular fins disposed coaxially in
predetermined spaced parallel relation for rotation as a unit about
a common axis, each fin having the same inner radius and the same
outer radius and a predetermined inner to outer radii ratio in the
range of 0.70 to 0.85,
a plurality of heat exchange tubes each extending longitudinally
through said fins in spaced relation to the common axis and
arranged circumferentially thereabout,
means for introducing a gaseous first fluid interiorly of said
array of annular fins,
means for introducing and withdrawing a second fluid into and from
said heat exchange tubes,
and means for rotationally driving said plurality of fins about
said common axis,
the improvement which comprises rotationally driving the plurality
of fins at a predetermined speed of rotation correlated to the
axial spacing of said fins and the kinematic viscosity of said
gaseous first fluid to provide a Taylor number in the range of 5.0
to 10.0 and operable at said inner and outer radii ratio of the
fins to convey and accelerate said gaseous first fluid by viscosity
shear forces spirally outward between the fins substantially to the
velocity providing optimum heat exchange between the gaseous first
fluid and the second fluid in said heat exchange tubes.
2. In rotary heat exchange apparatus as claimed in claim 1, wherein
the fin radii ratio is about 0.77, comprising rotationally driving
the plurality of fins at a speed of rotation to provide a Taylor
number of about 6.0.
Description
The present invention relates to rotary heat exchangers, and more
particularly to rotary heat exchangers having an arrangement of
rotating fins through which a gaseous cooling or heating fluid is
entrained and accelerated by viscosity shear forces to the velocity
providing optimum total heat exchange between said fluid and
another fluid in thermal contact with the fins.
Rotating heat exchangers comprising an array of heat exchange fins
are known in the art. However, prior to the present invention such
heat exchangers customarily employed conventional lift forces to
convey fluid through the array of heat exchange fins. The use of
lift forces causes cavitation and renders such heat exchange
devices noisy in operation. Also, such heat exchangers are
characteristically inefficient and are necessarily of substantially
bulky and heavy construction so that substantial power is required
to rotationally drive the exchanger at the desired speed. For these
reasons such rotary heat exchangers have not experienced wide usage
or marked commercial success.
With the foregoing in mind, an object of the present invention is
to provide a rotary heat exchange apparatus of the type described
having high-performance characteristics affording optimum total
heat exchange between two selected fluids.
Another object of the invention is to provide a rotary heat
exchange apparatus as set forth which is of relatively small
compact size and lightweight construction requiring low power
consumption to rotationally drive the apparatus at the desired
speed.
Another object of the invention is to provide a rotary heat
exchange apparatus of the type described which is substantially
devoid of cavitation and relatively noiseless in operation.
More particularly, an object of the invention is to provide a
high-performance rotary heat exchange apparatus comprising an array
of closely spaced parallel annular fins operable by viscosity shear
forces to entrain a gaseous heat exchange fluid radially outward
between the fins and accelerate said fluid to the velocity
affording optimum total heat exchange between said fluid and
another fluid having thermally conductive relation therewith.
A further object of the invention is to provide a rotary heat
exchange apparatus which is suitable for use as a condenser and is
particularly adapted for use as a condenser for the exhaust vapors
from the expander in high-performance closed Rankine cycle power
systems having a rotary boiler to which the condenser can be
directly mounted coaxially for rotation with the boiler as a
unit.
These and other objects of the invention and the various features
and details of the construction and operation thereof in accordance
with the invention are hereinafter set forth and described with
reference to the accompanying drawings, in which:
FIG. 1 is a sectional view diametrically of a rotary heat exchange
condenser made according to and embodying the present
invention;
FIG. 2 is a view, partially in section, taken on line 2--2, FIG.
1;
FIG. 3 is a detached fragmentary view, in expanded or exaggerated
form, of a continuous spiral or helicoidal fin arrangement;
FIG. 4 is an end elevational view of the fin arrangement shown in
FIG. 3;
FIG. 5 is a sectional view similar to FIG. 1 showing a modified
form or arrangement of apparatus embodying the present
invention;
FIG. 6 is a sectional view taken on line 6--6, FIG. 5;
FIG. 7 is a detached view showing one of the U-shaped heat exchange
tubes embodied in the condenser shown in FIG. 5;
FIG. 8 is a fragmentary sectional view diametrically of a rotary
heat exchanger showing another modification of the invention,
and
FIG. 9 is a fragmentary sectional view on line 9--9, FIG. 8.
Referring now more particularly to FIG. 1 of the drawings, the
illustrated embodiment of a rotary condenser made according to the
present invention comprises a cylindrical body or casing 1 of
selected diameter and relatively short axial length having a
continuous circumferentially extending wall 2 and axially spaced
side walls 3 and 4, respectively. Fixedly secured to and extending
coaxially outward from the casing side wall 3 is a tubular shaft
member 5 that is in communication with the interior of the casing 1
through an axial opening in said side wall 3. The shaft 5 is
rotatably mounted in bearings 6 and 7 and said shaft 5 and casing 1
are rotationally driven at the desired speed by means of an
electric motor M driving a gear 8 which in turn drives a gear 9
secured on the shaft 5.
Mounted outwardly adjacent the opposite side wall 4 of the casing 1
for rotation therewith, is an array of annular fins 10 arranged
coaxially of the casing 1 in predetermined equally spaced parallel
relation and defining internally thereof a coaxial inlet chamber C
for gaseous heat exchange fluid to be discharged outwardly between
the fins 10 as hereinafter described. The fins 10 consist of
separate or independent annual disk elements supported and secured
in the desired closely spaced parallel relationship with respect to
one another and the casing 1 by means of a plurality of heat
exchange tubes or pipes 11 that extends longitudinally through the
array of fins 10 circumferentially about the rotational axis
thereof. The fins 10 and tubes 11 are fabricated of metal having
high thermal conductivity such as, for example, copper or aluminum,
and said fins preferably are bonded to said heat exchange tubes 11
by brazing, soldering or the like, to provide maximum thermal
conductivity therebetween.
The tubes or pipes 11 are arranged in equally spaced radially
staggered relation circumferentially of the fins 10 and casing 1 as
shown in FIG. 2 of the drawings. The inner ends of the tubes 11 are
mounted and secured in corresponding openings 12 provided through
the casing side wall 4 so that the interiors of the tubes 11 are in
communication with the interior of the casing 1. The outer ends of
the tubes 11 are mounted and secured in recesses 13 provided in an
annular end ring 14 that is disposed coaxially of the apparatus
adjacent the outermost of the fins 10. The end ring 14 effectively
closes the outer ends of the tubes 11 and also supports them in the
desired relationship.
As shown in FIG. 1, the outer radius of all of the fins 10 is the
same and conforms substantially to the radius of the casing 1. The
inner radius of all the fins is also the same. More particularly,
the inner and outer radii of the fins 10 are predetermined and
interrelated to provide an inner to outer radii ratio within a
predetermined relatively narrow range of limits hereinafter
described.
The array of annular fins 10 does not extend axially inward
entirely to the casing wall 4 and the innermost of the fins 10 is
spaced from the adjacent surface of said wall to provide between
the wall 4 and fins 10 an annular passage P for the radial
discharge of dirt, dust and other solid particles that become
entrained and carried into the chamber C by the gaseous heat
exchange fluid. Such particles have greater density and momentum
than the gaseous fluid and tend to travel to the inner end of the
chamber C. Thus, the particles are discharged outwardly through the
discharge passage P and do not accumulate in the heat
exchanger.
Extending coaxially into the chamber C from the casing wall 4 is a
tapered guide member G having a curvilinear concave lateral
circumferential surface that functions to guide the foreign solid
particles outwardly through the discharge passage P and also to
guide and distribute the gaseous heat exchange fluid outwardly
between the fins. The guide member G may be formed as an integral
part of the casing wall 4 as shown, or separately and secured
thereto, as desired.
The outer diameter of the end ring 14 is substantially the same as
the outer diameter of the fins 10 and the inner diameter of said
ring is substantially the same as the inner diameter of the
adjacent group of fins so as not to restrict the flow of fluid into
the chamber C. An outwardly flared or bell shaped fluid intake
member 15 is fixedly mounted on a stationary base or support 16 and
disposed coaxially adjacent the outer face of the end ring 14. The
smaller end of the intake member 15 adjacent the ring 14 has a
diameter substantially the same as the inner diameter of said ring
14 to provide smooth uninterrupted flow of fluid inwardly through
the member 15 and ring 14 to the chamber C.
In the condenser embodiment of the invention shown in FIG. 1 the
vapor to be condensed enters the casing 1 through the tubular shaft
5 and then passes into the tubes 11 where the vapor is condensed by
heat exchange with a gaseous cooling fluid, such as ambient air,
discharged outwardly between the spaced fins 10 as herein
described. The condensate thus formed in the tubes 11 flows back
into the casing 1 from which it is discharged radially by
centrifugal force generated by rotation of the condenser. In the
arrangement shown, the condensate discharged from the casing 1
through a plurality of U-shaped tubes 19 that form liquid traps
which prevent discharge of the vapor directly from the casing and
cause the vapor to be diverted into the heat exchange tubes 11.
Upon leaving the U-shaped tubes 19 the vapor condensate is
discharged radially outward against the inner surface of the
cylindrical peripheral wall 20 of a stationary annular housing 2l
that circumscribes the rotating casing 1 and has spaced apart side
wall portions 22 and 23 which lie closely adjacent the peripheral
portions of the casing side walls 3 and 4, respectively. Condensate
collecting in the housing 21 discharges therefrom through a drain
24.
An alternative fin construction is shown in FIGS. 3 and 4 of the
drawings wherein the fins 10a are formed by adjacent turns or coils
of a continuous spiral or helical arrangement of a flat strip of
high thermally conductive material. As in the case of the fins 10
in the first embodiment, the adjacent fins 10a are disposed
coaxially of the casing 1 in predetermined equally spaced parallel
relation and are supported and secured in the desired relationship
with respect to one another and the casing 1, for rotation with the
latter as a unit, by means of heat exchange tubes or pipes 11a
extending therethrough and arranged and secured in the casing wall
4 and end ring 14 as previously described for the tubes 11 in FIG.
1.
The axial spacing or distance between the adjacent fins 10 or 10a
is determined with relation to the rotational speed at which the
fins are driven, the inner and outer radii of the said fins and the
kinematic viscosity of the gaseous fluid so as to utilize the
viscous properties of the fluid and the shear forces exerted
thereon by the rotating fins 10 and 10a to pump the fluid radially
outward between said fins. Thus, upon rotation of the fins 10 or
10a at the predetermined speed related to the spacing of the fins
10 or 10a, their inner and outer radii and the fluid kinematic
viscosity, gaseous fluid is caused to flow inwardly through the
intake member 15 and ring 14 to the chamber C and enter radially
into the spaces between the fins 10 or 10a where it is accelerated
by the shear forces generated by the difference or slip between the
speed of the fins and the velocity of the fluid. As the fluid is
accelerated and forced outwardly between the fins the fluid follows
a spiral trajectory and is pressurized and ultimately discharged at
the outer edges of said fins.
For optimum results the axial spacing of the fins, their speed of
rotation and their inner and outer radii are correlated so that the
gaseous fluid passing between the fins is accelerated to a velocity
substantially less than the outer peripheral speed of the fins in
order to retain the fluid between the fins 10 or 10a the longer
time required to provide the optimum total heat flux or total heat
exchange between the fluid passing between the fins and another
fluid in the tubes or pipes 11 or 11a.
The axial spacing between the fins 10 and 10a or the relationship
of the inner radius of the fins to their outer radius may vary
within predetermined ranges or limits for any given range of speeds
of rotation (r.p.m.) of the condenser. The nature of the flow for
rotational shear force devices is completely described by the
Taylor number, N.sub.Ta, where:
N.sub.ta = d.sup.2 w/v
d = distance between fins
w = angular velocity (radians per sec.)
v = kinematic viscosity
We have found that most efficient pumping occurs when N.sub.Ta =
3.25. However, efficient fluid pumping does not lead to an
efficient heat exchanger. Efficient pumping occurs when the energy
transfer to the fluid is maximized. Efficient heat exhange depends
upon both the fin area and the difference between the speed of the
fins and the velocity of the fluid flowing between them. Thus, for
heat transfer, the Taylor number is not adequate by itself to
completely describe an optimum configuration. We have found that
for various combinations of inner radius (Ri) and outer radius (Ro)
of the fins the Taylor number for an efficient heat exchanger will
always be greater than 4.5. The precise values of Taylor number and
the ratio of the inner to outer radii of the fins depend upon the
thermodynamic and transport properties of the fluids exchanging
heat and whether the heat transfer mechanism for the fluid in the
heat exchange tubes is boiling, condensing or convective. For heat
transfer to or from air on the fin side to or from a boiling or
condensing fluid within the tubes, it has been determined that the
Taylor number for an efficient heat exchanger is within the range
of from 5.0 to 10.0 and the inner to outer radii ratio of the fins
is within the range of from 0.70 to 0.85. For optimum results the
Taylor number will be in the neighborhood of 6.0 and the fin radii
ratio in the neighborhood of 0.77, and these values constitute good
starting points for the design of an efficient heat exchanger
according to the present invention. The particular optimum design
and operating conditions for any given heat exchanger installation
can be determined by a person skilled in the art. It has been
determined that the values of Taylor number and fin radii ratio for
other gaseous fluids are essentially the same as the values stated
for air.
For example, in the case of an air cooled condenser comprising fins
having an outer radius of 7.00 inches and driven at a speed of 2400
r.p.m., optimum results are obtained where the Taylor number is 6.3
and the inner radius of the fins 10 and 10a is 5.25 inches, giving
a fin radii ratio of 0.75, and the axial spacing between the
adjacent fins 10 or 10a is 0.027. The total number of fins 10 or
10a employed is directly proportional to the heat load of any given
installation. Increasing the number and/or diameter of the heat
exchange tubes which pass through the fins will provide more heat
exchange surface for the fluid inside the tubes but this increased
area is obtained at the expense of reduced fluid flow between the
fins. That is, the presence of the tubes tends to impede slightly
the air flow between the fins. Tube shapes other than round are
possible. For example, heat exchange tubes having air foil
cross-section shape with the chord of the air foil disposed
substantially parallel to or in the direction of the flow
streamline between the fins tend to reduce fluid flow resistance
between the fins and may be desirable in certain installations.
A rotary condenser made according to the present invention is
characterized by its comparatively small compact size and
lightweight construction and the minimum power that is required to
rotationally drive the heat exchanger at the desired speed. Also,
the use of viscosity shear forces to convey the fluid between the
spaced fins 10 or 10a with the inherent absence of flow separation,
produces a very low operating noise level free of cavitation such
as frequently occurs when conventional lift forces are employed to
accelerate a fluid.
By reason of these characteristics and advantages, a rotary
condenser embodying the present invention is particularly suited
for use in high-performance closed Rankine cycle power systems
having a rotary boiler to which the condenser can be directly
mounted or coupled coaxially for rotation with the boiler as a
unit. In such a power system incorporating a rotary condenser
according to the present invention, the vapor from a power
generator, for example, a turbine, enters the condenser through
shaft 5 where it is condensed in the tubes 11 or 11a by heat
exchange with cooling air moving outwardly between the fins 10 or
10a and then is discharged into the housing 21 from which it is
returned directly to the rotary boiler for regeneration into vapor
and the cycle is repeated continuously. A rotary boiler
construction and power system suitable for use with a condenser of
the present invention is disclosed in my U.S. Pat. No. 3,590,786
issued July 6, 1971.
The use of a rotary heat exchanger embodying the present invention
is not limited to use as a condenser for boiler vapors as
previously described. For example, another embodiment of the
invention is shown in FIGS. 5, 6 and 7 of the drawings which may be
used to provide high-performance heat exchange between a cooling or
heating fluid and another fluid. Referring to FIG. 5, the heat
exchanger illustrated is essentially similar in construction and
operation to the first embodiment of the invention previously
described. Accordingly, it is not necessary to repeat a detail
description of the heat exchanger, and the parts thereof which are
similar to the parts shown and described with reference to the
embodiment in FIGS. 1 and 2 have been correspondingly referenced
with the addition thereto of the letter b.
The principal difference between the two embodiments of the
invention shown in the drawings resides in the casing structure 1b
and the heat exchange tubes 11b. Thus, referring to FIG. 5, the
casing 1b is subdivided by a partition 28 into inlet and outlet
chambers I and O, respectively, and the heat exchange tubes 11b are
of elongated U-shape provided with longer and shorter leg portions
11c and 11d, respectively. The ends of the shorter leg portions 11d
of the U-shaped tubes 11b are mounted and secured in openings 12b
provided through the casing side wall 4b so that said tubes are in
communication with the interior of the inlet chamber I of the
casing 1b. Similarly, the ends of the longer leg portions 11c are
mounted and secured in openings 28b provided through the casing
partition 28 so that said tubes are in communication with the
interior of the outlet chamber O in the casing 1b. The tubes 11b
extend through an end ring 14b with their U-shaped ends projecting
outwardly beyond said ring as shown.
The tubular shaft 5b is journaled in bearings 6b and 7b and
communicates with the interior of the outlet chamber O of the
casing 1b to constitute the outlet passage for vapors or liquids
from the heat exchange tubes 11b. The inlet passage for vapors or
liquids is provided by a smaller tubular shaft 29 disposed
coaxially within the shaft 5b and the inner end of said shaft 29
communicates with the interior of the inlet chamber I of the casing
1b from which the incoming vapor or liquid enters the shorter leg
portions 11d of the tubes 11b. In the embodiment shown in FIG. 9
the heat exchanger is driven at the desired speed of rotation by a
motor M' through a conventional multiple belt drive including
pulley 30, belts 31 and pulley 32 secured on the shaft 5b.
The operation of the embodiment of the invention shown in FIGS. 5,
6 and 7 is essentially the same as previously described with
reference to the first embodiment. Thus, the vapor or liquid to be
cooled or heated enters the heat exchanger through shaft 29 to
inlet chamber I from which the fluid enters the tubes 11b, passing
first through the shorter leg portions 11d and then through the
longer leg portions 11c, during which the fluid is cooled or
heated, as the case may be, by heat exchange with a gaseous cooling
or heating fluid discharged from the chamber C' outwardly between
the spaced fins 10b and 17b in the manner previously described. The
fluid, cooled or heated in the tubes 11b, enters the outlet chamber
O of the casing 1b from which it is discharged through the tubular
shaft 5b.
In some installations guide members such as G are not completely
effective in distributing the gaseous first fluid outwardly between
the fins 10 uniformly throughout the entire axial length of the fin
array, and there is a tendency for less fluid to flow outwardly
between the several fins adjacent to the inlet to the chamber C
than between the more inward fins of the array. Also, the amount of
fluid discharged between the fins at the inlet end of the chamber C
becomes less as the axial length of the array of fins is
increased.
I have discovered that in installations where there is less fluid
flow between the fins at the inlet end of the chamber C, as
described, this can be corrected and the flow of fluid outwardly
between all of the fins in the array made substantially uniform by
providing at the inlet end portion of the array of fins, an axially
spaced pair of continuous annular radially projecting flanges or
flange portions F and F' that extend a predetermined distance
outwardly beyond the outer peripheral edges of the fins 10 and
rotate as a unit with the array of fins.
As shown in FIG. 8 of the drawings, the flange F is disposed at the
extreme outer or fluid inlet end of the array of fins 10 and can be
provided simply by increasing the radial dimension of the end ring
14 previously described. The flange F' is provided by an annular
ring member 31 having openings therethrough for the heat exchange
tubes 11 and mounted in spaced relation inwardly from the flange F
a distance to include or bracket between the flanges F and F' a
predetermined relatively small number of the fins 10 depending upon
the requirements of the particular heat exchange installation.
As in the case of the end ring 14 the inner diameter of the ring 31
is the same as the inner diameter of the fins 10 and the ratio of
the outer radius of the flanges F and F' to the outer radius of the
fins will vary according to the dimensional specifications for a
particular heat exchanger and usually will be of the order of about
1.3.
The volume of fluid flow outwardly through the several fins
bracketed by the flanges F and F' can be further increased as
desired or required by providing circumferentially about the fins
between the flanges F and F' a plurality of axially extending
radially disposed blades 32 that rotate with the array of fins as a
unit. The inner edges of the blades 32 are spaced outwardly from
the outer edges of the fins, and the number of blades 32 employed
in a particular installation will vary according to the design and
operation specifications of the heat exchanger.
The invention may be employed for heat exchange purposes generally,
including other condenser applications as well as the cooling or
heating of liquids, gases, and vapors where high-performance
optimum total heat exchange is desired along with the accompanying
advantages of compact lightweight construction, minimum power
requirement and substantially noise-free operation. Rotary heat
exchangers of the present invention can be used as condensers for
closed Rankine cycle engines in vehicles for land use, such as the
automobile, in which case air would be the preferred exterior
fluid. Also, air-cooled engines using the present invention are
useful in total energy systems wherein the heat rejected by the
condenser in the form of hot air could be used to heat homes,
shops, and other buildings, and the shaft energy can be
simultaneously converted to electric power by means of a generator.
In the case of a total energy system in which hot water is the
preferred means of rejecting heat, the rotary heat exchanger of
this invention can be optimized for silence, high efficiency, and
low power consumption and thus could be used for total energy on
land and in boats. Other applications of the present invention
include its use for assisting in the cooling of other types of
engines, such as the internal combustion engines, for refrigeration
cycle condensers and evaporators, and for chemical process
cooling.
While certain embodiments of the present invention have been
illustrated and described, it is not intended to limit the
invention to such disclosures and changes and modifications may be
made and incorporated as desired within the scope of the
claims.
* * * * *