U.S. patent number 3,828,573 [Application Number 05/371,939] was granted by the patent office on 1974-08-13 for heating and cooling wheel.
Invention is credited to Michael Eskeli.
United States Patent |
3,828,573 |
Eskeli |
August 13, 1974 |
HEATING AND COOLING WHEEL
Abstract
A method and apparatus for producing heating or cooling by
passing two fluids in heat exchange relationship with each other
within a rotating rotor wherein said fluids are compressed to a
higher pressure. The first fluid is a compressible fluid, such as
air, which when compressed will also have a temperature increase;
the second fluid may be either a compressible fluid or may be a
non-compressible fluid, which when compressed may not have a
temperature raise or the temperature raise for said second fluid
will be less than for said first fluid. Heat then will be
transferred from said first fluid to said second fluid, so that
when said fluids are discharged from said rotor, said first fluid
will be at lower temperature at exit than it was at entry; also,
said second fluid will leave said rotor at higher temperature than
said fluid entered. For the first fluid, air or other compressible
gases may be used; said air may be at ambient temperature. For said
second fluid, air, water or other fluids may be used; said water or
air may be at ambient or natural temperature. Said apparatus may be
used for air conditioning where both fluid streams are air; also,
it may be used to heat water.
Inventors: |
Eskeli; Michael (Dallas,
TX) |
Family
ID: |
26911464 |
Appl.
No.: |
05/371,939 |
Filed: |
June 20, 1973 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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216938 |
Jan 11, 1972 |
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Current U.S.
Class: |
62/401; 62/87;
165/88; 415/88; 415/178; 122/11; 415/1; 415/114; 416/96R |
Current CPC
Class: |
F24F
5/00 (20130101); F25B 9/06 (20130101); F24H
1/00 (20130101); F25B 3/00 (20130101); F28D
21/0007 (20130101); F28D 21/0008 (20130101); F28D
11/02 (20130101); F25B 1/00 (20130101) |
Current International
Class: |
F25B
9/06 (20060101); F24F 5/00 (20060101); F25B
3/00 (20060101); F24H 1/00 (20060101); F25B
1/00 (20060101); F28D 21/00 (20060101); F28D
11/00 (20060101); F28D 11/02 (20060101); F25b
003/00 () |
Field of
Search: |
;415/114,177,178,179,199A ;416/95,96 ;126/247 ;62/401,402,403
;122/26 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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409,942 |
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Mar 1945 |
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IT |
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26,184 |
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Nov 1907 |
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GB |
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Primary Examiner: Davis, Jr.; Albert W.
Assistant Examiner: Richter; S. J.
Parent Case Text
Cross References to Related Applications: This application is a
continuation-in-part application of "Heating and Cooling Wheel,"
filed Jan. 11, 1972, Ser. No. 216,938, the descriptive matter of
which is incorporated herein by reference
Some of the material used with the device of this invention was
also used in "Gas Compressor," filed Nov. 27, 1972, Ser. No.
309,909, the descriptive matter of which is incorporated herein by
reference.
Claims
What is claimed is:
1. A rotary heat exchanger comprising:
a. structural support for supporting rotating shafts;
b. a power input shaft journalled in bearings in said structure for
rotation;
c. a rotating rotor mounted on said power input shaft so as to
rotate in unison therewith, said rotor having an axis of rotation,
structural walls, a radial center, and a periphery said rotor
having:
i. first fluid passageway comprising:
I. first entry port having a first area of opening and disposed
near the center of said rotor so as to have a small first diameter
and a first radius with respect to a central longitudinal axis of
said power input shaft and said rotor;
Ii. at least one first radially extending passageway having first
means for ensuring that a first fluid therewithin rotates at
substantially the same rotational speed as said rotor for effecting
centrifugal compression and effecting a high pressure, compressed
fluid at elevated temperature at the outermost periphery of said
rotor; said first means serving as cooling means and being heat
conductive for cooling said first fluid during centrifugal
compression thereof; said first means being disposed adjacent a
second fluid passageway for conducting heat to a second fluid in
said second fluid passageway;
Iii. a first peripheral portion communicating with said first
radially extending passageway and peripherally disposed in said
rotor for collecting said high pressure compressed fluid;
Iv. at least one second radially extending passageway communicating
with said first peripheral portion and extending inwardly toward
the center of said rotor; said second radially extending passageway
having second means for recovering the work associated with
deceleration of a compressed first fluid; and
V. a first discharge port having a second area of opening that is
operably sufficient for automatic flow of a first fluid and having
a second diameter and a second radius with respect to said central
longitudinal axis that are greater, respectively, than said first
diameter and said first radius for effecting automatic flow of said
first fluid and less than the respective diameter and radius of
said peripheral portion for consuming less power and for effecting
greater efficiency in operation; said first discharge port
communicating with said second radially extending passageway for
discharge of a first fluid therefrom;
ii. second fluid passageway comprising:
I. a second entry port having a third area of opening and disposed
near the center of said rotor so as to have a small third diameter
and third radius with respect to a central longitudinal axis of
said power input shaft and said rotor;
Ii. at least one third radially extending passageway having third
means for ensuring that a second fluid therewithin rotates at
substantially the same rotational speed as said rotor; said third
means serving as heating means and being heat conductive for
heating said second fluid by heat conducted from said first fluid
both during compression of said first fluid and at said first
peripheral portion;
Iii. a second peripheral portion communicating with said third
radially extending passageway and peripherally disposed in said
rotor for collecting said second fluid;
Iv. at least one fourth radially extending passageway communicating
with said second peripheral portion and extending radially inwardly
toward the center of said rotor; said fourth radially extending
passageway having fourth means for recovering the work associated
with deceleration of a second fluid; and
V. a second discharge port having a fourth area of opening and
having a fourth diameter and a fourth radius with respect to said
central longitudinal axis that are less than the respective
diameter and radius of said second peripheral portion for consuming
less power and effecting greater efficiency of operation; said
second discharge port communicating with said fourth radially
extending passageway for discharge of said second fluid therefrom;
and
iii. heat conductive walls intermediate said first and second
peripheral portions of, respectively, said first and second fluid
passageways and said first and third means for conducting heat from
said high pressure, compressed fluid at elevated temperature to
said second fluid;
d. a compressible first fluid being automatically passed through
said first fluid passageway in said rotor without requiring energy
exteriorly of said rotor; said first fluid being heated by
centrifugal compression and transferring heat to said second fluid
through at least said heat conductive wall intermediate said first
and second peripheral portions and said first and third means such
that said compressible first fluid is at a lower temperature at its
outlet from said rotary heat exchanger than it was at its inlet
thereto; and
e. a second fluid being flowed through said second fluid passageway
and being heated in at least its said peripheral portion by heat
transferred from said first fluid such that said second fluid is at
a higher temperature at its outlet from said rotary heat exchanger
than it was at its inlet thereto.
2. The rotary heat exchanger of claim 1 wherein said second
peripheral portion has a radius that is less than is the radius of
said first peripheral portion; and said heat conductive wall
extends intermediate said first and third radially extending
passageways for transferring heat from said first fluid during
centrifugal compression thereof and into said second fluid.
3. The rotary heat exchanger of claim 2 wherein said first fluid is
flowed through the outermost first peripheral portion such that it
is subjected to a greater centrifugal force field than is said
second fluid which flows through the interiorly disposed second
peripheral portion of the second fluid passageway and heat is
transferred from said first fluid to said second fluid.
4. The rotary heat exchanger of claim 1 wherein said first fluid is
a gas and said second fluid is a gas and said fourth diameter and
said fourth radius of said second discharge port are greater,
respectively, than said third diameter and said third radius of
said second entry port for effecting automatic flow of said second
fluid also.
5. The rotary heat exchanger of claim 1 wherein said second fluid
is a liquid when entering said rotary heat exchanger and wherein
said second fluid passageway includes sufficient restriction that
said second fluid is heated sufficiently within said rotary heat
exchanger to at least partially vaporize it.
6. The rotary heat exchanger of claim 1 wherein said structure
includes a casing that encloses said rotor.
7. The rotary heat exchanger of claim 1 wherein said second entry
port and said second discharge port have substantially the same
third and fourth diameters and the same third and fourth radii; and
said first and second fluids are flowed countercurrently to each
other; and wherein a heat conductive wall is provided intermediate
the heated said second fluid and said first fluid downstream of
said second peripheral portion with respect to said second fluid
such that said second fluid is heated downstream of said second
peripheral portion for effecting automatic flow of said second
fluid.
8. The rotary heat exchanger of claim 1 wherein said second fluid
passageway comprises a finned tube heat exchanger disposed within
said first fluid passageway; said finned tube heat exchanger being
connected in fluid communication with said second entry port and
said second discharge port.
9. The rotary heat exchanger of claim 1 wherein said first and
second fluid passageways include restrictive passages to regulate
the respective radial velocities of said fluids when passing
through said rotor and said rotating rotor is of circular
configuration in cross section taken transversely to said axis of
rotation with its structural walls being thicker near the center
than at the periphery and decreasing monotonically toward the
periphery.
Description
BACKGROUND OF THE INVENTION
This invention relates generally to heating and cooling apparatus,
wherein cooling or heating is produced when a fluid is circulated
within a system.
The art of providing cooling, refrigeration or heating has seen a
variety of devices. In some of these devices, such as heat pumps, a
fluid is expanded in an expansion device, allowed to evaporate
producing cooling, and is then compressed and condensed thereby
completing the cycle. In air conditioning, by circulating the air
through the evaporator coil, cooling is produced, and by
circulating the air over the condenser, heating is produced.
The main disadvantage of these conventional systems is that they
require relatively large amounts of power for their operation.
Also, a separate fluid, such as a halogenated hydrocarbon, is
required within said device as the heat exchange fluid which is
sometimes a vapor and sometimes a liquid within the said system;
use of such fluid requires sealing against leakage and adds to
cost.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a cross section of one form of the device, and FIG. 2 is
an end view of the unit shown in FIG. 1 with a section removed to
show interior.
FIG. 3 is a cross section of another form of the device, and FIG. 4
is an end view of the device shown in FIG. 3, with a portion
removed to show interior details.
DESCRIPTION OF PREFERRED EMBODIMENTS
It is an object of this invention to provide a method and apparatus
for providing heating or cooling as normally required for air
conditioning, heating or for refrigeration.
It is also an object of this invention to provide a method and a
device wherein, for air conditioning systems, the air being
circulated within a space to be air conditioned, is also being
circulated within the device, without intermediate fluids such as
Freon or other similar fluids.
It is also an object of this invention to provide a method and
apparatus wherein either one, or both of the fluid streams passing
through the device, are self propelled within the device; the
transport of the fluids being provided by suitable arrangement of
the heat transfer surfaces relative to the fluid streams thus
providing density differences within the device to provide said
self propelling feature.
Referring to FIG. 1, therein is illustrated a cross section of one
form of the device. First fluid, which is the compressible fluid,
is passed in heat exchange relationship with a second fluid, which
may be either compressible or non-compressible fluid. The device
shown in FIG. 1 is especially arranged to employ fluids that are
both compressible, with said first fluid in outer rotor passage,
and said second fluid in inner rotor passage. 40 is casing, 41 is
rotor, 50 is rotor shaft, 47 and 58 are rotor bearings and seals,
52 is a hole that communicates with the space between rotor and
casing. The fluid stream to be heated enters said rotor 41 via
opening 49, and passes through passage 43 to outlet opening 57;
said fluid stream is being compressed by the centrifugal action of
said rotor on said fluid when passing outward within said rotor;
vanes 46 are placed in said passage to assure that said fluid will
rotate with said rotor and also to serve as heat exchange members.
Another stream of fluid enters said rotor 41 via openings 56,
passes outward within said rotating rotor 41 via passages 42; said
fluid stream being compressed by centrifugal action on said fluid
by said rotor; said fluid passage being provided with vanes 45 to
assure that said fluid will rotate with said rotor and also to
serve as heat exchange members. The fluid entering said rotor via
opening 56, being in the outer fluid passage, will have a higher
tangential velocity and therefore experience a higher centrifugal
force, than the fluid entering via opening 49. 55 and 54 are
dividing walls, and 53 is rotor outer wall. 51 indicates a layer of
thermal insulation that is applied to rotor dividing wall to
prevent heat transfer in the area indicated by 51. Heat transfer
will take place through wall 54 in the area indicated by 54, and
this heat transfer will remove heat from said first fluid, and add
heat to said second fluid, 60 and 61 are openings in fluid passages
42 and 43 to restrict fluid flow to maintain a predetermined radial
velocity for the said fluids.
In FIG. 2, an end view of the unit shown in FIG. 1, is illustrated,
with a section removed to show interior details. 40 is casing, 45
is a vane in outer fluid passage 42, 43 is inner fluid passage, 55
is dividing wall, 41 is rotor, 60 and 61 are fluid openings, 57 and
56 are fluid openings to rotor, and 59 is unit base.
In FIG. 3, another form of the device is shown, this unit being
specially arranged to employ a gaseous first fluid and a liquid
second fluid, and intented to heat said second fluid, and to remove
heat from said first fluid. Said first fluid is self propelling
within the rotor, and the second fluid, being a liquid, is normally
pumped through the heat exchanger coils. 65 is casing, 66 is rotor,
67 is rotor dividing wall, 68 is thermal insulation, 69 is vane
within rotor passage, 70 is a rotor seal, 71 is shutter for the
first fluid passage and is adjustable, 72 is rotor shaft bearing,
73 is rotor shaft, 74 is first fluid exit, 85 is casing vent, 83,
is bearing support, 82 is bearing, 80 and 81 are second fluid entry
and exit, 78 is first fluid entry, 77 is rotor seal, 76 is second
fluid distribution conduit, 75 is heat exchanger.
In FIG. 4, an end view of unit shown in FIG. 3, is illustrated with
a section removed to show internal details. 65 is casing, 66 is
rotor, 75 is heat exchanger, 76 is second fluid distribution
conduit, 80 is second fluid entry, 83 is shaft bearing support.
In operation, one of the fluid streams will be the compressible
fluid, supplying heat to said second fluid. The second fluid may be
either a compressible fluid, or be a non-compressible fluid, as
desired. Within the rotor, said first fluid, being more
compressible, will have a higher temperature gain, than said second
fluid; both fluids being compressed by centrifugal action on said
fluids by said rotor. Alternately, said first fluid will be
arranged to be in a rotor passage that is further outward from the
center of rotation and thus will have greater compression than said
second fluid, with heat then being transferred from said first
fluid to said second fluid. Referring to FIG. 3, said first fluid
enters said rotor via opening 78, and is then passed outward within
said rotating rotor, and is compressed by said rotor. Due to
compression, the temperature of said first fluid tends to increase,
and heat is then transferred to said second fluid within heat
exchanger placed within said rotor at the inlet side of said rotor,
item 75 in FIG. 3. During said compression of said first fluid,
heat is removed continuously from said first fluid with an increase
in pressure that is greater for a predetermined rotor speed than
would be for an isentropic compression for said first fluid. On the
exit side of the rotor, indicated by item 69 in FIG. 3, the
expansion of said first fluid is isentropic, with no heat transfer,
and thus the pressure differential between periphery and exit 74
follows laws pertaining to isentropic compression:
To control radial velocity, shutter 71 has been provided; this is
adjustable, so that the first fluid velocity may be set to suit.
Also, this shutter may be used to control air flow, if said device
is connected directly to duct system in a building.
The flow of the fluids in the unit shown in FIG. 1, is similar to
that described hereinbefore. The passage of heat from said first
fluid to said second fluid is arranged to occur so that said first
fluid will release heat during compression, while said second fluid
will receive heat during expansion. Thus, both fluids will be self
propelling. Openings 60 and 61 are located at periphery, to allow
control of radial velocity of said fluids; the size of said
openings 60 and 61 can be made to suit the amount of fluid being
flown through said rotor. Alternately, a shutter may be used for
one or both of these fluid streams similar to item 71, in FIG. 3.
Also, the shutter and the openings at periphery may be both used,
if desired, to control said radial fluid velocities.
The unit shown in FIG. 1, may be directly connected to building
duct system, to provide both heating and cooling. One of the fluid
streams in such arrangement will be building air from ducts, and
the other fluid stream will be outside air. These two streams may
be swithed from one rotor passage to another, and also be mixed, if
desired, to obtain a precise degree of heating and cooling. The
duct arrangements and damper arrangements with associated controls,
are not further being described herein, since they are assumed to
be within existing art. The self propelling feature, wherein said
air will pass from rotor entry to rotor exit, will usually be
sufficient to provide for passing said outside air through said
rotor; for the building air, a fan to circulate said building air
through the duct work may be required. Alternately, the exit
opening from the rotor, may be made larger in diameter, as shown by
item 74 in FIG. 3, to provide additional pressure differential for
the building air.
Work input to the device is low, since both fluids enter and leave
the rotor near the center of rotation. Work is required to
accelerate the fluids when passing from center toward rotor
periphery, and work is recovered by the rotor when the fluids
travel from the periphery toward rotor center. Referring to FIG. 1,
the fluid streams when both gaseous, will be self propelling
through the rotor, so that thus the work input will consist of
friction losses in seals and bearings, some work required if a
vacuum pump is used, to evacuate the space around rotor, and losses
due to residual fluid velocities leaving the rotor at center; all
these work quantities are very low resulting in a unit that is very
economical to operate. In the unit shown in FIG. 3, work is
required to pump the liquid through the resistance of the rotor
coil, and also for a vacuum pump, seal and bearing losses and
losses due to first fluid residual velocity leaving the rotor;
since the first fluid is self propelling, the total work input to
obtain heating or cooling is very low, and is almost negligible
when expressed per amount of cooling or heating generated.
As noted, the casing space between rotor and casing may be
evacuated to eliminate fluid friction on rotor external walls.
Alternately, the rotor walls may be closely fitted to casing as
shown in FIG. 1, item 53, thus allowing the rotating rotor to
partially evacuate the said space and thus reduce fluid friction on
said rotor.
* * * * *