|Publication number||US3828573 A|
|Publication date||Aug 13, 1974|
|Filing date||Jun 20, 1973|
|Priority date||Jan 11, 1972|
|Publication number||US 3828573 A, US 3828573A, US-A-3828573, US3828573 A, US3828573A|
|Original Assignee||M Eskeli|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (7), Referenced by (28), Classifications (32)|
|External Links: USPTO, USPTO Assignment, Espacenet|
United States Patent n91v Eskeli 1451 Aug. 13, 1974 [541 TREATING AND COOLING WHEEL  Inventor: MichaelEskeli, 6220 Orchid Ln.,
Dallas, Tex. 75230 221 Filed: June 20, 1973 21 App1.No.: 371,939
Related US. Application Data  Continuation-impart of Ser. No. 216,938, Jan. 11,
 11.8. C1 62/401, 62/87, 122/11, 165/88, 415/88, 415/114, 415/178, 416/96 [.51] Int. Cl. F25b 3/00  Field of Search 415/114, 177, 178, 179,
 References Cited UNlTED STATES PATENTS 2,367,223 l/l945 Larrecq 165/166 X 2,451,873 10/1948 Roebuck 62/401 X 2,490,064 12/1949 Kollsman 62/401 X 2,511,691 6/1950 Bramley 62/93 X 3,306,574 2/1967 Bachl 415/199 A X FOREIGN PATENTS OR APPLICATIQNS 409,942 3/1945 Italy .f62/401 26,184 1 H1907 Great Britain Primary Examiner-Albert W. Davis, Jr. Assistant ExaminerS. .1. Richter  ABSTRACT from said first fluid to said secondfluid, so that when said fluids aredischarged 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.
9 Claims, 4 Drawing Figures i g C 1 HEATING AND COOLING WHEEL Cross References to Related Applications: This application is a continuation-in-part application of Heating and Cooling Wheel," filed Jan. 1 l, 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.
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 it 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. is casing, 41 is rotor, 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. 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, 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'6l 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 ,saidsecond fluid, with heat then being transferred from said first fluid to said second fluid. Referring to FIG. 3, said first fluid enters said rotor viaopening 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 increasein pressure that is greater for a predetermined rotor speed than would be for an isentropic compres- 'sion for said first fluid. On the exit side of the rotor, in-
,lows 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 thatdescribed 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.
What is claimed is:
l. 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 ef- 0 fecting 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 radiand 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; ll. 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.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2367223 *||Apr 7, 1942||Jan 16, 1945||Gen Electric||Combined centrifugal compressor and cooler|
|US2451873 *||Apr 30, 1946||Oct 19, 1948||Roebuck John R||Process and apparatus for heating by centrifugal compression|
|US2490064 *||Jan 12, 1945||Dec 6, 1949||Paul Kollsman||Thermodynamic machine|
|US2511691 *||Dec 5, 1945||Jun 13, 1950||Arthur Bramley||Centrifugal dehydrating and cooling system|
|US3306574 *||Apr 15, 1965||Feb 28, 1967||Herbert Bachl||Rotary fluid flow machine|
|GB190726184A *||Title not available|
|IT409942A *||Title not available|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US3874190 *||Jan 31, 1974||Apr 1, 1975||Eskeli Michael||Sealed single rotor turbine|
|US3962888 *||Apr 3, 1975||Jun 15, 1976||Michael Eskeli||Heat exchanger|
|US3970408 *||Feb 3, 1975||Jul 20, 1976||Bio-Medicus, Inc.||Apparatus for use with delicate fluids|
|US4124993 *||Aug 26, 1977||Nov 14, 1978||Michael Eskeli||Refrigeration machine|
|US4727722 *||Feb 11, 1987||Mar 1, 1988||The United States Of America As Represented By The United States Department Of Energy||Rotary magnetic heat pump|
|US5117655 *||Aug 12, 1991||Jun 2, 1992||Anderson Raymond L||Heat exchanger|
|US5765387 *||Feb 5, 1996||Jun 16, 1998||Entropy Systems, Inc.||Device and method for thermal transfer using air as the working medium|
|US6138471 *||Sep 21, 1998||Oct 31, 2000||Phoenix Environmental Asset Corp.||Device for air conditioning|
|US6196020||Jan 14, 1998||Mar 6, 2001||Jan-Erik Nowacki||Motor, refrigeration machine or heat pump|
|US6431828 *||Apr 5, 2000||Aug 13, 2002||Envirotech Pumpsystems, Inc.||Non-planar rotor cover for a centrifugal pump|
|US7555891||Nov 11, 2005||Jul 7, 2009||Board Of Trustees Of Michigan State University||Wave rotor apparatus|
|US7938627||Nov 11, 2005||May 10, 2011||Board Of Trustees Of Michigan State University||Woven turbomachine impeller|
|US8449258||May 28, 2013||Board Of Trustees Of Michigan State University||Turbomachine impeller|
|US8506254||Apr 18, 2011||Aug 13, 2013||Board Of Trustees Of Michigan State University||Electromagnetic machine with a fiber rotor|
|US20060130478 *||Nov 11, 2005||Jun 22, 2006||Norbert Muller||Wave rotor apparatus|
|US20100089550 *||Feb 13, 2008||Apr 15, 2010||Heleos Technology Gmbh||Process And Apparatus For Transferring Heat From A First Medium To A Second Medium|
|US20100108295 *||Feb 13, 2008||May 6, 2010||Heleos Technology Gmbh||Process And Apparatus For Transferring Heat From A First Medium to a Second Medium|
|US20110067847 *||Apr 14, 2009||Mar 24, 2011||Rotoboost As||Device and Method for Transporting Heat|
|US20110146951 *||Jul 3, 2009||Jun 23, 2011||Frank Hoos||Process and apparatus for transferring heat from a first medium to a second medium|
|US20110200447 *||Aug 18, 2011||Board Of Trustees Of Michigan State University||Turbomachine impeller|
|USRE45396||Mar 1, 2011||Mar 3, 2015||Board Of Trustees Of Michigan State University||Wave rotor apparatus|
|EP2300769A1 *||Apr 14, 2009||Mar 30, 2011||Rotoboost AS||A device and method for transport heat|
|EP2489839A1||Feb 18, 2011||Aug 22, 2012||Heleos Technology Gmbh||Process and apparatus for generating work|
|WO1998030846A1 *||Jan 14, 1998||Jul 16, 1998||Nowacki Jan Erik||Motor, refrigeration machine or heat pump|
|WO2008098964A1 *||Feb 13, 2008||Aug 21, 2008||Heleos Technology Gmbh||Process and apparatus for transferring heat from a first medium to a second medium|
|WO2010000840A1||Jul 3, 2009||Jan 7, 2010||Heleos Technology Gmbh||Process and apparatus for transferring heat from a first medium to a second medium|
|WO2011137476A1||May 9, 2011||Nov 10, 2011||Bernhard Adler||Device and method for converting thermal energy|
|WO2012110546A2||Feb 15, 2012||Aug 23, 2012||Heleos Technology Gmbh||Process and apparatus for generating work|
|U.S. Classification||62/401, 416/96.00R, 415/1, 415/178, 165/88, 122/11, 415/114, 62/87, 415/88|
|International Classification||F28D21/00, F25B9/06, F24F5/00, F28D11/02, F25B3/00, F25B1/00, F24H1/00|
|Cooperative Classification||F28D21/0008, F28D21/0007, F24F5/00, F25B3/00, F25B1/00, F28D11/02, F25B9/06, F24H1/00|
|European Classification||F24F5/00, F25B1/00, F28D21/00A4B4, F28D21/00A4B6, F25B9/06, F24H1/00, F28D11/02, F25B3/00|