US3896635A

US3896635A - Heat transfer device and method of using the same

Info

Publication number: US3896635A
Application number: US336510A
Authority: US
Inventors: Robert C Stewart
Original assignee: Individual
Current assignee: Individual
Priority date: 1973-02-28
Filing date: 1973-02-28
Publication date: 1975-07-29
Anticipated expiration: 1992-07-29

Abstract

A power driven heat transfer device and method of using the same, in which a power driven rotating heat transfer body has first and second portions thereof in physical contact with first and second masses of first and second fluids. The first mass due to physical contact with the rotating body sequentially formed into a first stream of fluid, and the first stream as it is formed concurrently having energy in the form of heat removed therefrom to cool the first stream. The concurrent forming of the first fluid into a first cooled stream thereof is accompanied by transfer of heat from the second portion of the device to the second fluid to heat the latter. The rotation of the device may, if desired, be utilized to sequentially form the second mass of fluid into a second stream thereof, as heat is transferred from the device to the second stream. The heat transfer device is susceptible to numerous uses, such as selectively heating or cooling a confined space, transferring heat from a quantity of circulating fluid to the ambient atmosphere or a desired mass of fluid, and in association with an air foil maintaining a differential in temperature of the air in contact with the upper and lower surfaces thereof to impart a substantial lift to the air foil.

Description

United States Patent 1191 Stew art [451 July 29, 1975 HEAT TRANSFER DEVICE AND METHOD OF USING THE SAME [21] Appl. No.: 336,510

[52] US. Cl. 62/499 [51] Int. Cl. F258 3/00 [58] Field of Search 62/499 [56] References Cited UNITED STATES PATENTS 2,805,558 9/1957 Knight 62/499 3,001,384 9/1961 Hanson et a1. 62/499 3,025,684 3/1962 McLain et al. 62/499 3,139,736 7/1964 Hanson 62/499 X 3,189,262 6/1965 Hanson et al. 62/499 X 3,347,059 10/1967 Laing 62/499 X 3,397,739 8/1968 Miller 62/499 X 3,726,107 4/1973 Hintze 62/499 Primary Examiner-William F. ODea Assistant ExaminerPeter D. Ferguson Attorney, Agent, or Firm-William C. Babcock [57] ABSTRACT A power driven heat transfer device and method of using the same, in which a power driven rotating heat transfer body has first and second portions thereof in physical contact with first and second masses of first and second fluids. The first mass due to physical contact with the rotating body sequentially formed into a first stream of fluid, and the first stream as it is formed concurrentlyiha'ving energy in the form of heat removed therefrom to cool the first stream.

The concurrent forming of the first fluid into a first cooled stream thereof is accompanied by transfer of heat from the second portion of the device to the second fluid to heat the latter. The rotation of the device may, if desired, be utilized to sequentially form the second mass of fluid into a second stream thereof, as heat is transferred from the device to the second stream. The heat transfer device is susceptible to numerous uses, such as selectively heating or cooling a confined space, transferring heat from a quantity of circulating fluid to the ambient atmosphere or a desired mass of fluid, and in association with an air foil maintaining a differential in temperature of the air in contact with the'upper and lower surfaces thereof to impart a substantial lift to the air foil.

2 Claims, 12 Drawing Figures PATENYEI] JUL 2 91975 FIG.5

HEAT TRANSFER DEVICE AND METHOD OF USING THE SAME BACKGROUND OF THE INVENTION l. Field of the Invention Heat transfer device and method of using the same.

2. Description of the Prior Art In the past, the cooling of a confined space has necessitated the use of blowers to circulate air therethrough, as well as a condenser. evaporator. motor driven compressor to liquify the refrigerant. and numerous valves and accessories to control the expansion of the refrigerant in the evaporator. Although the cycle of the above described apparatus may theoretically be reversed to heat the confined space, when such a reversal is effected it can only be accomplished by the use of additional and expensive equipment.

The primary purpose in devising the present invention is to supply a compact, power-driven, rotatable unit that may be selectively used to provide either a heated or cooled stream of air or fluid, a unit that has a simple mechanical structure, is relatively inexpansive, and one that overcomes numerous operational disadvantages inherent to previously available heating and refrigerating assemblies.

SUMMARY OF THE INVENTION A heat transfer device that includes a hollow body in the form of a surface of revolution that is defined by a material having a substantial coefficient of heat transfer. Power means are provided for rotating the body. Heat transfer means are at least partially disposed inside the body and are operatively associated with a first surface portion of the body. The first surface portion of g the body by rotational contact with a mass of a first fluid not only sequentially forms the first fluid into a first stream thereof. but concurrently lowers the temperature of the stream by withdrawing energy in the form of heat therefrom. The heat transfer means as it operates emits heat, and this heat may be used to raise the temperature of a second stream of fluid that contacts a second surface portion of the body.

The power-driven body and associated heat transfer means may be used for such diverse purposes as concurrently forming first and second masses of fluids into a first heated stream and a second cooled stream, with the first and second streams so formed being selectively useable to heat or cool the interior of a confined space. The device when in association with an airfoil may be utilized to establish a differential in temperature of the air above and below the airfoil, with this differential in temperature resulting in a differential in densities of the air situated above and below the airfoil, and this differential in densities of the air imparting a substantial lift to the airfoil.

The power-driven rotating body and heat transfer means may also be employed to provide cooling for an operating unit such as an internal combustion engine, or the like. Also. the power-driven rotating body and associated heat transfer means may in certain forms be employed to utilize and store solar energy, as well as to employ the solar energy for cooling and refrigerating purposes. The heat transfer means used in association with the rotating body may be a circulating fluid. a volatile, liquifyable refrigerant, adsorbing means. or ab sorbent means.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of the first form of the device for concurrently producing a first stream of a cooled fluid, and a second stream of a heated fluid;

FIG. 2 is a vertical, cross-sectional view of the device shown in FIG. 1, taken on the line 2-2 thereof;

FIG. 3 is a transverse cross-sectional view of the device shown in FIG. 2, taken on the line 33 thereof;

FIG. 4 is a fragmentary longitudinal cross-sectional view of the device shown in FIG. 2, taken on the line 4-4 thereof;

FIG. 5 is a fragmentary transverse cross-sectional view of the device shown in FIG. 2, taken on the line 55 thereof; A

FIG. 6 is a fragmentary vertical cross-sectional view of the device shown in FIG. 5, taken on the line 66 thereof;

FIG. 7 is a longitudinal cross-sectional view of the device shown in FIG. 1, taken on the line 7-7 thereof;

FIG. 8 is a cross-sectional view of an airfoil. with a heat transfer device operatively associated therewith in such a manner as to impart a lifting force to the airfoil;

FIG. 9 is a longitudinal cross-sectional view of a second form of the heat transfer device that employs adsorbent means for heat transfer purposes;

FIG. 10 is a fragmentary transverse cross-sectional view of the second form of the device shown in FIG. 9, taken on the line l010 thereof;

FIG. 11 is a longitudinal cross-sectional view of a third form of the device in which adsorbent means are employed for heat transfer purposes;

FIG. 12 is a combined cross-sectional and side elevational view of a power-driven unit for transferring heat from a first fluid that circulates therethrough to a first stream of fluid that is generated by the device as the latter rotates.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The first form A of the invention as illustrated in FIG. l7 inclusive, includes a housing B that is partially defined by a cylindrical shell 10 and a vertically extending V-shaped wall l2. The V-shaped wall 12 hs two vertically spaced arcuate bands 12a and 12b extending forwardly therefrom that define a space 13 therebetween that is occupied by a section of shell 10. The shell 10 may be manually rotated relative to housing B for reasons that will later be explained in detail.

The shell 10 and wall 12, as may best be seen in FIGS. 2 and 3, cooperatively define a confined space 14 therebetween. The housing B also includes a top 16 and bottom 18 that are secured to the ends of the wall 12, upper edge of band and lower edge of band 121). An evaporator coil C and a condenser coil D are provided, both of which are in the form ofa surface of revolution, and are coaxially aligned with one another as illustrated in FIG. 2. The evaporator coil C and condenser coil D. as may be seen in FIGS. 2 and 3, are held in the coaxially aligned relationship previously mentioned by a number of circumferentially spaced. longitudinally extending rigid members 20 that are secured to the evaporator and condensing coils by conventional fastening means.

The coils C and D are each formed from a material such as copper, or the like, that has a substantial coefficient of heat transfer. To further facilitate transfer of heat through the material defining the coils C and D, each of the coils preferably has a number of longitudinally spaced transversely positioned fins 22 extending outwardly therefrom. The upper and lower ends of the members 20, as best seen in FIG. 2 have first and second circular plates 24 and 26 secured thereto. A third plate 28 is intermediately positioned between the adjoining ends of the evaporator coil C and condenser coil D. as also may be seen in FIG. 28. and the third plate secured to members 20 by conventional means. The peripheral edges of the first. second and

third plates

24, 26 and 28, respectively, are in rotatable, slidable contact with circular ribs 24a. 26a and 2811 that extend inwardly from the interior surface of the cylindrical shell 10.

The top 16, first plate 24, and portion of shell as shown in FIG. 2, cooperatively define a first confined space 30 therebetween. First plate 24, third plate 28 and shell 10 also cooperate to define a second confined space 32 therebetween. Shell 10 has a mesh-covered first opening 34 therein that is in communication with the first confined space 30. The shell 10 also includes a second mesh-covered opening 36 that is in communication with second confined space 32. A horizontal base plate 38 is secured by conventional means to the interior surface of the housing B above the bottom 18 and cooperates with the bottom and side wall to define a space 40. Shell 10 has a circular flange 10a on the lower extremity thereof that rests on the base plate 38. Flange 10a slidably and rotatably engages a number of circumferentially spaced clips 38a secured to base plate 38. The base plate 38, second plate 26, and portion of shell 10 as may best be seen in FIGS. 7, cooperate to define a third confined space 42 therebetween. Second plate 26, third plate 28 and portion of shell 10 also cooperate to define a fourth confined space 44 therebetween. Second plate 26, third plate 28 and portion of shell 10 also cooperate to define a fourth confined space 44 therebetween. Third and fourth meshcovered openings 46 and 48 respectively. are formed in the cylindrical shell 10 and communicate with the third and fourth confined

spaces

42 and 44 respectively. A number of circumferentially spaced first ports 50 are formed in the first plate 24 as shown in FIG. 7, and at all times maintain communication between the first and second confined

spaces

30 and 32. A second group of circumferentially spaced ports 52 are formed in the second plate 26 and serve to at all times maintain communication between the third confined space 42 and fourth confined space 44. A stub shaft 54 extends upwardly from the center of first plate 24. The upper end of shaft 54 is journaled in a bearing 56 secured to the under side of the top 16.

A compressor E is provided, and is preferably supported from the under side of the third plate 28 by bolts 58 or other suitable fastening means. The compressor E, as may best be seen in FIG. 5, includes a generally elliptical rotor 60 that is driven by a shaft 62 that extends downwardly therefrom as shown in FIGS. 2 and 4. The lower end of shaft 62 is secured to a circular drive plate 64 by a key 66 or other suitable fastening means. The drive plate 64 is rotatably supported on a ball bearing assembly 68, which in turn is mounted on the upper surface of a first block 70. The first block 70 defines a first cam surface 72 that slidably and rotatably engages a second cam surface 74 formed on a second block 76 that is supported on the bottom 18, as illustrated in FIG. 2.

A steel arm 78 extends outwardly from first block and is so operatively associated with a solenoid 80, that the first block 70 is rotated relative to the second block 76 when the solenoid is energized. The second plate 26 has a hollow drive shaft 82 extending downwardly therefrom that is of tubular structure. Shaft 82 is secured to the second plate 26 by welding beads 84. or the like. The shaft 82 has two vertically spaced sets of

ball bearing assemblies

86 and 88 situated within the confines thereof that rotatably engage the shaft 62.

A first driven pulley 90 is secured to the exterior surface of the shaft 82 by a key 92, or other suitable fastening means. A first endless belt 94 extends from the first driven pulley 90 to a first driving pulley 96 that is mounted on a shaft 98 of a motor 100. The lower end of the hollow shaft 82, as may be seen in FIG. 4, rotatably supports a second pulley 102 by a ball bearing assembly 104. When first block 70 is rotated relative to second block 76, the drive plate 64 is moved upwardly into frictional pressure Contact with the second drive pulley 102, and as a result the shaft 62 is rotated. The second pulley 102 engages a resilient endless belt 106 that extends to a second driving pulley 108 mounted on the shaft 98, as best seen in FIG. 2. Driving

pulleys

76 and 108 are of the same diameter. However. pulley 90 has a substantially greater diameter than pulley 102. As a result. shaft 62 rotates faster than do coils C and D and compressor E. A thrust bearing F is provided. as may best be seen in FIG. 4. The thrust bearing F is situated in an opening 108 formed in the base plate 38. The thrust bearing F includes an outer race 110 that is secured to the base plate 38, and an inner race 112 that rotatably engages the exterior surface of the hollow shaft 82. The thrust bearing F includes a number of tapered rollers 114, as is conventional with such devices. The second plate 26 has a roller bearing assembly 114 in abutting contact with the under surface thereof, and the roller bearing assembly by means of a sleeve 116 that slidably and rotatably engages the exterior surface of the second shaft 82, transmitting the weight of the coils C and D and compressor E to the inner race 112, as shown in FIG. 4. A cylindrical guide 118 extends upwardly from the base plate 38 and serves to maintain the bearing assembly 114 and thrust bearing F in vertical alignment.

The compressor E. as may best be seen in FIGS. 5 and 6, includes a housing that is defined by a cylindrical shell 124 and first and second end plates 126 and 128. A ring 130 is supported in a fixed position relative to the shell 124, with the ring defining a circular interior surface 132. The ring 130 has first. second. third and fourth radially extending

slots

134, 136. 138 and 140 respectively. formed therein in which first. second. third and fourth vanes 134a. 136a I381: I400 are slidably supported. First. seeond. third and

fourth levers

142, 144. 146 and 148. respectively. are pivotally supported by pins within the confines of the shell 124. First. second. third and fourth levers 142, I44, 146 and 148 have first. second. third and fourth weights 142a. 144a. 146a and 148a affixed to first ends thereof. with the weight when the compressor F is rotating as a whole. causing the levers to pivot to exert inwardly directed forces on the exterior ends of the vanes 134a. 136a. 138a and 140 a to maintain the vanes in slidable sealing contact with the rotors 60.

When the electric motor 100 is energized, and the first and

second belts

96 and 106 driven, the rotor 60 will rotate relative to the rotating ring 130, due to the difference in diameters of the first and

second pulleys

90 and 102, respectively. The rotor 60, as may best be seen in H6. 6, has a transverse partition 152 therein that cooperates with the first and second end plates 126 and 128 to define first and

second compartments

154 and 156.

Evaporator coil C has a first end 155 and second end 157. The second end 157 is by conduit or other means 158 at all times maintained in communication with the first compartment 154, as shown in FIG. 6. Condenser coil D, as may be seen in FIG. 7, has third and fourth ends 159 and 160. The second compartment 156 of the compressor E is by a conduit 162 at all times maintained in communication with the third end 159 of condenser coil D. The exterior surface of the rotor 60 is defined by a general elliptical side wall 164 that cooperates with the circular side wall 132 to define two oppositely disposed crescent-shaped spaces 165, which crescent-shaped spaces rotate as the rotor 60 rotates relative to the ring 130.

Two oppositely disposed ports 168 are formed in the rotor 60 that at all times are in communication with the first compartment 154. Two second ports 170 are also formed in the rotor 60, and are at all times in communication with the second compartment 156. The second ports 170 are spaced substantially 90 relative to the first ports 168. The rotor 60 as illustrated in FIG. 5, rotates in a clockwise direction relative to the ring 130. After the first ports 168 rotate past the first and third vanes 134a and 138a the crescent-shaped spaces 166 start to form between the first and second vanes 134a and 136a and the third and fourth vanes 138a and 140a. The evaporator coil C contains gaseous refrigerant (not shown), which refrigerant will liquify when compressed to a first predetermined pressure, and the temperature thereof will have lowered to a first prede termined temperature. As the first ports 168 move towards the second and fourth vanes 136a and 14011, the eliptical side wall 164 cooperates with the circular side wall 132 to start forming the spaces 165 between the third and fourth vanes 138a and 140a and the first and second vanes 134a and 136a, and with gaseous refrigerant being drawn into these spaces from first compartment 154 through the first ports 168. Gaseous refrigerant will continue to be drawn into the spaces 165 until the first ports 168 move past the second and fourth vanes 136a and 140a, respectively. As the rotor 60 continues to rotate, the first ports 168 move into sealing contact the circular side wall 132, and the part of the spaces 165 defined by the second and third vanes 136a, l40a, the ring-shaped surface 132 and elliptical-shaped surface 164 decreasing in volume to increase the pressure on the gaseous refrigerant therein, with this increase in pressure forcing the gaseous refrigerant through the second ports. 170 into the second compartment 156. As this increase in pressure on the gaseous refrigerant takes place, the second ports 170 move into sealing contact with the ring-shaped surface 132, and the compressed gaseous refrigerant flowing as a result thereof through the conduit 162 into the third end 158 of the condenser coil D. During the time the rotor 60 rotates relative to the ring 130, the above described cycle is repeated. with gaseous refrigerant being withdrawn from the evaporator coil C and compressed by the compressor E to be discharged into the condenser coil D. a

A conduit 172 that includes an orifice-defining member 174 extends between the fourth end 160 of compressor coil D and first end 154 of evaporator coil C. Two electrical conductors 176 extend from the solenoid to a source of electric power 178, with the circuit from the source of power to the solenoid being opened or closed by manipulation of a switch 180. When the switch 180 is closed, the solenoid 80 is actuated to pivot the block 70 relative to the second block 76, and in so doing, force the circular drive plate 64 into frictional contact with the first driven pulley 102. The shaft 62 then rotates to drive the rotor 60 relative to the ring in the compressor E.

As the rotor 60 is rotating relative to the ring 130, the evaporator coil C and condenser coil D are concurrently rotating as a unit. Rotation of the evaporator coil C due to the fan action thereof causes air to flow inwardly through the first opening 34 and first ports 50 into the second confined space 32, and through the evaporator coil C to discharge through the second opening 36. Rotation of the evaporator coil C not only results in a current of air being discharged through the second opening 36, but concurrently this current of air is cooled by contact with the cooled evaporator coil.

When the evaporator coil C and the condenser coil D rotate concurrently as above described, the compressor E discharges gaseous refrigerant through the conduit 162 into the third end of the condenser coil. Rotation of the condenser coil D causes a current of air to be drawn inwardly through the third opening 46 into the fourth confined space 44 where the air contacts the evaporator coil D and is discharged through the fourth opening 48. As the gaseous refrigerant is compressed in the compressor E the refrigerant is heated, but with this heat being transferred to air in fourth confined space 44 that is subsequently discharged outwardly through the fourth opening 48. Heat is transferred from the condenser coil D to the outgoing current of air at a sufficiently rapid rate that the temperature of the pressurized refrigerant in condenser coil D is lowered to the extent that it liquifies, due to the compressor exerting greater than a predetermined pressure thereon. The liquid refrigerant as it accumulates in the coil D is forced due to the vapor pressure thereof through the orifice-defining member 174 to expand in the evaporator coil C, with the heat required for this expansion being extracted from the current of air that is generated by rotation of the evaporator coil, and with this current of air discharging outwardly through the second opening 36 to be used for any desired purpose. The air discharging from the fourth opening 48, which has been heated by contact with the condenser coil D, may likewise be used for any desired purpose. Should it be desired to increase the volume of the current of air generated as the evaporator coil C and compressor coil D are concurrently rotated. the members 20 may be formed to define fan blades as shown in FIG. 3. The shell 10 is rotatably adjustable to housing B, and as a result a confined space adjacent to the first form A may be heated or cooled, depending on whether the first or second stream of air from opening 36 or opening 48 is discharged thereinto.

A circular airfoil G is shown in FIG. 8 that is preferably defined by a convex shaped upper skin 182 and concave shaped lower skin 184. Airfoil G has a centrally disposed opening 186 formed therein that is defined by a cylindrical shell 188 that extends between the upper and

lower skins

182 and 184. The center portion 184a of the skin 184 is substantially flat and has a number of ports 190 formed therein. The skin portion 184a serves as a support for a compressor E.

An evaporator coil C in the form of a surface of resolution is disposed within the space'186 and is held in a fixed position therein by suitable supporting means 192. A cup-shaped shell 194 extends downwardly from the center portion of the airfoil G and is secured to the lower skin 184 by conventional means (not shown). The shell 194 has a number of air discharge openings 196 defined in the side portions thereof. as shown in FIG. 8. The evaporator coil D that is in the form of a surface of revolution is disposed within the confines of the shell 196 and held in a fixed position therein by bracket means 198 that are secured to the lower skin 184. The shell 194 serves as a support for a motor 100 that by a shaft 198 drives the compressor E and the compressor having a driven shaft 200 extending therefrom that may be used to support a fan or propeller 202 on the upper free end thereof, as shown in FIG. 8. The motor 100 may be any type of prime mover. such as an electric motor. internal combustion engine. or the like. The evaporator coil C. condenser coil D are connected to one another and to the compressor E in the same manner as previously described in connection with the evaporator coil C, condenser coil D and compressor E. as shown in FIG. 7. The connection of the evaporator C, condenser coil D and compressor E are not shown in Figure as they have been previously described.

When the motor 100 is actuated the propeller 202 is driven to discharge a current of air downwardly over the evaporator coil C to pass therethrough and be cooled. with the cooled air flowing through the port 190 to thereafter flow through the condenser coil D. as shown by arrows in FIG. 8 to discharge from the openings 196 as a heated current of air. The heated current of air flows over the lower skin 184, and due to the differential in density of this heated air relative to the air immediately adjacent the upper skin 182, a substantial lift is imparted to the airfoil G. This lift imparted to the airfoil G may be utilized in moving a load 204 that is secured to the shell 194 by a cable 206 or other supporting means.

The heat transfer apparatus H shown in FIG. 12 is power-driven and is not only adapted to create a current of air or gas. but to transfer heat to the current or stream of gas so created from a heated fluid. The apparatus H includes a hollow cylindrical shaft 208 that is rotatably supported in a bearing 210 that is secured to a rigid member 212. A conduit 214 is provided that by a longitudinally extending portion 216 is divided into a first passage 218 and second passage 220. A seal 222 is mounted on the conduit 214 and is in rotatable sealing contact with a first end 208a of the hollow shaft 208. The partition 216 has a seal 224 in rotatable contact therewith, with the seal being connected to a tubular member 226 that extends longitudinally through the hollow shaft 208 to terminate in a tubular leg 230. A tube 232 formed from a material having a high coefficient of heat transfer is wound into the form of a surface of revolution, as may best be seen in FIG. 12. with a first end 232a thereof being connected to the leg 230 and a second end 232!) of the tube 232 being in communication with the interior of the hollow shaft 208.

In using the form H of the apparatus the liquid or fluid J to be cooled is discharged through the passage 218 to enter the space defined between the tube 226 and the hollow shaft 208 and thereafter enter the tube 232 through the second end 232b thereof. A driving pulley 234 is rigidly secured to the hollow shaft 208 as shown in FIG. 12, and is engaged by a power driven belt (not shown). As the pulley 234 is driven. the tube 232 in the form ofa surface of revolution is rotated and sequentially transforms the body of air or gas (not shown) that it is in contact it into a stream of air or gas. Due to the motion of this stream of air or gas over the tube 232 as it rotates. the heat is transferred from the liquid J to this current of air or gas by flowing through the tubing 232. The fluid .I after traversing the rotating tube 232 in the form of a surface of revolution exits therefrom through the tube 226 to flow into the second passage 220 where it is again heated, with the above described cycle being repeated. The apparatus H above described is ideally adapted for use on an internal combustion engine. and when so used may replace the conventional radiator. fan and accessory equipment required in conjunction with the last mentioned pieces of equipment. Due to the centrifugal force to which the fluid J is subjected when traversing the tubing 232 as the latter is rotated. there will be a minimum tendency for solid partical material carried with the fluid to settle out by gravity.

The second form L of heat transfer device is illustrated in FIGS. 9 and 10, and includes a generally cylindrical shell 300 having closed ends. The shell 300 includes a side wall 302. bottom. 304, and top 306. Top 306 is illustrated as having a tube 308 extending upwardly therefrom. Tube 308 has a closed upper end 310. Tube 308 has a driving pulley 312 secured thereto, which pulley is engaged by an endless belt 314 that extends to a motor (not shown) or other prime mover. A thrust bearing assembly M is provided that has an inner and outer race 316 and 318 with rollers 320 situated therebetween. The outer race 318 is supported by a frame N that is operatively associated with the second form L of the device.

The inner race 316 is rigidly secured to the exterior of the tube 308 as shown in FIG. 9. The top 306 includes an upwardly and inwardly tapering ring-shaped member 322 that on its inner end develops into a vertical wall 324, and the wall on the lower end thereof being connected to a ring shaped plate 326 that is connected on the inner periphery thereof to the lower extremity of the tube 308. Wall 324, plate 326 cooperate with tube 308 to define a reservior 328 into which cooling water 329 is discharged through a pipe or conduit 330, with the cooling water being withdrawn from the reservior 328 through the conduit 332 by a pump or other suitable means (not shown).

End 310 has a sealing member 334 mounted thereon that rotatably engages a shaft 336 that extends downwardly through tube 308. The upper end of the shaft 336 supports a magnetically attractable body 338 that holds the shaft in a stationary position when a solenoid 340 that forms a part of a housing 342 is electrically energized. The solenoid 340 has one terminal thereof connected by a conductor 344 to one terminal of a source of electric power 346. with the other terminal of the source of power being connected by a conductor 348 to a manually operated switch 350 which in turn is connected to the second solenoid 340. When the switch 350 is placed in the closed position. the solenoid 340 is electrically energized, and holds the body 338 and shaft 336 in a stationary position as the shell 300 is driven by the pulley 312.

Thelower end of the shaft 336 develops into a number of downwardly and outwardly extending legs 352 that support a first generally circular tray 354 that includes an upwardly extending side wall 356 that is of circular shape. The legs 352 also support a downwardly extending second tube 358 that has an upper open end. The tube 358 on the lower end thereof supports a second tray 360 that includes an upwardly and outwardly extending circular side wall 362.

The bottom 304 has a third tube 364 extending upwardly therefrom through the second tube 358 to terminate on the upper end thereof in a flared upper end 366. A spiral wound ribbon 368 is rigidly secured to the exterior surface of the third tube 364, and with the outer edges of the spiral ribbon being in movable sealing contact with the interior surface of the second tube 358. The side wall 302 supports a horizontal partition 370 as may best be seen in FIG. 9, that divides the interior of the shell 300 into an upper compartment 372 and a lower compartment 374.

Second tube 358 has a number of circumferentially spaced first ports 376 formed therein that are located above the partition 370. The partition 370 has a centrally disposed opening 378 therein that sealingly and rotatably engages the external surface of the second tube 358. Third tube 364 has a number of second circumferentially spaced ports 379 formed in the lower extremity thereof directly above the bottom 304, as best seen in FIG. 9.

The interior of the shell 300 is at all times maintained at a pressure that is negative relative to the ambient atmosphere. A ring-shaped flange 380 extends outwardly from the side wall 302, as shown in FIG. 9, with the outer end of the flange developing into an upwardly extending cylindrical wall 382. The flange 380 wall 382 and portion of side wall 302 cooperatively define a second annulus-shaped reservior 384 into which hot water 385 may be discharged through a conduit 386, with hot water as it cools being withdrawn from the reservior 384 by a conduit 388. The lower surface of the flange 380 slidably engages a ring-shaped guide 390 as shown in FIG. 9. that is secured to the frame N. The guide 390 and flange 380 cooperatively maintain the shell 300 in the fixed position as it is rotated by the driven pulley 312. The bottom 304 preferably has a number of radially spaced. circumferentially extending blades 392 depending therefrom. the purpose of which will later be explained.

The partition 370 has a number of circumferentially spaced. downwardly extending tubular bosses 394 depending therefrom, as shown in FIG. 9. The second form L of the invention is charged with an absorbate 396 which for the purposes of illustration is an aqueous solution of lithium bromide and water upwardly through the second tube 358 to discharge the same into the first compartment 372. The absorbate 396 due to centrifugal action. is thrown outwardly against the upper interior portion of the side wall 302 that is heated. with a portion of the water from the absorbate 396 vaporizing and passing upwardly as shown by arrows in FIG. 9 to enter the opening 398 defined between the wall 324. and wall 356. The plate 326 due to cooling water, is maintained below thedew point ofthe water vapor in first compartment 372, with the vapor condensing to water that flows downwardly between the legs 352 into the flared end 366 and thereafter flow downwardly through the third tube 364 to discharge through the second ports 379.

After discharging from the second ports 379. water tends to move outwardly from the third tube 364 due to the centrifugal force imparted thereto by the rotating shell 300, and as the water moves outwardly it evaporates and is transformed into water vapor that flows through an opening 400 defined between the interior surface of the side wall 300 and the upper extremity of the wall 362. The water vapor. due to the affinity of the adsorbate 396 therefor, mixes with the adsorbate and thereafter flows through third ports 381 into the confines of the second tube 358. The absorbate and water mixed therewith is thereafter moved upwardly by rotation of the spiral blade 368 to discharge through the first ports 376 onto the upper surface of the partition 370. Due to centrifugal action. the adsorbate thereafter 396 tends to move outwardly towards the shell 302, with a portion of the adsorbate having water vapor evaporated therefrom to move upwardly through the opening 398 and condense to water due to contact with the cold plate 326. The water that so condenses flows downwardly between the legs 352 to discharge from the second ports 378 onto the bottom 304 where it again evaporates, and in so evaporating cools the exterior surface of the bottom. Due to rotation of the shell 300, the blades 392 serve to not only transform fluid that they contact into a stream thereof, but to cool the stream by removing heat therefrom. The removed heat is used to evaporate water from the interior surface of the bottom 304. The cylindrical shell 306 may be formed from any rigid material having a substantial coefficient of heat transfer.

The member 322 of top 306. as may best be been in FIG. 9, preferably includes a ring-shaped inwardly projecting extension 322a. to prevent cooling water from being inadvertently discharged from the reservior 328, when the second form L of the device is rotating. As the second form L of the heat transfer device operates. cooling water 329 is withdrawn from the reservior 328 through the tube or conduit 332 which is connected to the suction side of a pump 400. The pump 400 is driven by a sheave 402 that is rotated by the belt 314. Water is discharged from the pump 400 through a conduit 404 to a conventional cooling tower 406 that is exposed to the atmosphere, with the water after traversing the cooling tower being returned to the reservior 328 through the conduit 330. When the fluid being cooled is a gas or air. it is preferable that suitable ducting 408 be extended around the lower portion of the second form M of heat transfer device, in order that the air or gas after being cooled may be directed along a desired path.

The hot water 385 is preferably circulated into and out of the reservior 384. To effect such circulation a second pump 410 is provided that is driven by a sheave 412 which if desired. may be rotated by engagement with the endless belt 314. The suction pump 410 is connected to the conduit 388. The discharge of pump 410 is connected to a conduit 414 that extends to a heater 416 that is preferably actuated by solar energy. Water after being heated in the heater 416 is discharged through the conduit 386 into the reservior 384.

The second form L of the device is particularly adapted for large sized installations, and may be used to transform solar energy into the cooling of fluids either air or liquid. with the fluid when air being used to temperature condition in the interior of a building. and when liquid being used for cooling purposes in numerous installations. It will be apparent that when the liquid being cooled is water. the temperature thereof may be lowered to the extent that it freezes. with the ice resulting from this freezing operation serving to store solar energy for future use. It will also be apparent that by proper location of the second form L of the heat transfer device. that solar energy may be directed onto the top 306, and in such an installation, the hot water circulating system above described may be eliminated.

A third form P of the invention is shown in FIG. 11 and includes a generally cylindrical shell 418 that has closed ends. The shell 418 includes a cylindrical side wall 420, a bottom 422, and an upwardly and inwardly extending top 424 that at the center develops into an upwardly extending tube 308'. A transverse partition 426 divides the interior of the shell 418 into an upper compartment 428 and a lower compartment 430.

The upper central portion of the partition 426 supports the exterior body of a compressor E. which compressor may be identical in construction to the com pressor E described in connection with the first form A of the heat transfer device. However. other forms of compressors may be used if desired. The compressor E has an intake 157' thereon that is in communication with the lower compartment 430 and a discharge 162 thereon that isin communication with the upper compartment 428. The shaft 62' of the compressor is by a coupling 432 connected to a shaft 336' that is of the same construction as the shaft 336 shown in the second form L of the heat transfer device.

The portions of the third form P of the invention that are common to the second form L thereof are indicated in FIG. 11 by the same numerals previously used in describing the second form L, but to which primes have been added. When the shell 418 is rotated by the belt 314 driving the sheave 312', the exterior portion of the compressor E rotates, and the interior portion of the compressor remains stationary due to the shaft 62 being connected to the stationary shaft 336.

An inverted concave block Q of a porous adsorbent material is supported between the partition 426 and the top 424 as best seen in FIG. 11. The block Q includes an upwardly and inwardly tapering top 432 and a cylindrical side wall 434. The interior surface of the top 432 and side wall 434, together with the exterior surface of the compressor E and the upper surface of the partition 426 serve to define the upper compartment 428. The exterior surface of the top 424 has a cylindrical side wall 436 secured thereto. and the side wall on the upper end develops into an upwardly and inwardly extending ring-shaped member 438. The side wall 436 and top 424. together with the extention 438, serve to define a reservior 440 into which cooling water 329 is continuously circulated by use of the conduit 330 and 332 in the same manner as described in the second form L of the heat transfer device. The cooling water 329' serves to maintain the top 424 and the top 332 of block Q at a temperature less than that of the ambient temperature.

The lower compartment 430 is charged with a quantity of an adsorbate R. which may be water. ammonia, or the like. The pressure in the first compartment 430 is reduced to a pressure P-l at which the adsorbate R will boil. preferably at ambient temperature. and be transformed into vapor. As the third form 0 of the invention is driven by the belt 314', the compressor E' is actuated to draw the adsorbate vapor from the lower compartment 430 and discharge it into the upper compartment 428 at a pressure P-2.

The exterior surface 442 of the side wall 434 cooperate with the upper surface of the side wall 420, a portion of the top 424, and partition 426 to define a second annulus shaped compartment 444, as may best be seen in FIG. 11. A number of circumferentially spaced ports 446 are formed in the outer part of the partition 426 and at all times maintain communication between the second compartment 444 and the lower compartment 430.

The vapor of the adsorbate R when disposed in the upper compartment 428 flows into minute spaces defined in the porous block Q. and in the top thereof the temperature is lowered by the cooling water 329. The vapor condenses and by centrifugal action tends to migrate outwardly in the direction shown by arrows. Also. vapor tends to flow from the compartment 428 through the side wall 434. and in so doing. contact condensed vapor flowing downwardly from the top 432 due to the centrifugal force to which the rotating block Q is sub jected. The flow of vapor and liquid adsorbate R through the top 434 and side wall 436, takes an appreciable time. as the flow of fluid therethrough is restricted due to the porous nature of the block. As a result. a differential in vapor pressure is at all times maintained between the second outer compartment 444 and the upper compartment 428. This differential in pressure, as well as the centrifugal force to which the condensed vapor of the adsorbate R is subjected maintains a constant flow of the condensed vapor through the second form 0 of the device. with the flow of the vapor and the condensed liquid being illustrated by arrows in FIG. 11. Inasmuch as the shell 418 is rotating at a substantial rate. the flow of condensed adsorbate after flowing downwardly through the ports 446 will be along the interior surface of the lower portion of the side wall 420, and this side wall will be subjected to maximum cooling as the condensed adsorbate again evaporates. The lower exterior surface of the side wall 420 has a number of circumferentially spaced blades 448 projecting outwardly therefrom, which blades rotate within the confines of suitable ducting 449 to create a current of fluid as the second form 0 of the device is actuated. This current of fluid as it flows through the ducting 449 is cooled. due to heat being removed therefrom to effect evaporation of the adsorbate from the interior surface of the side wall 420. and to a lesser degree, from the bottom 422.

The side wall 420 of the shell 418 has a circular flange 450 extending outwardly therefrom that slidably engages a lug or member 452 supported from the frame N. to stabilize the rotary motion of the second form 0 of the device and to assure that it will rotate on a fixed vertically extending axis 454. The ducting 448 is supported from the frame N by a suitable bracket 456 as shown in FIG. 11.

The vapor of the adsorbate R must be raised to a pressure P-2 in compartment 428. and this pressure being such that the adsorbate will condense to the liquid state when the block Q is cooled by the cooling water 440, with the temperature of the water 440 being such as that may be attained by the use of a conventional cooling tower 406 such as used with the second form L of the heat transfer device.

The use and operation of third form of the heat transfer device has previously been explained in detail and need not again be repeated.

1 claim:

1. An apparatus for concurrently forming a mass of air into a first cooled stream and a second heated stream thereof that includes:

a. an elongated housing that includes a top, bottom and continuous side wall extending therebetween, said housing having first, second, third and fourth longitudinally spaced openings therein;

b. a rotatable assembly disposed in said housing, said assembly including a first upper circular plate, a second lower circular plate, a third circular plate intermediately positioned between said first and second plates, a plurality of elongate, circumferentially spaced, rigid members connected to the peripheries of said first, second and third plates; a tubular evaporator coil supported from said members above said third plate; a tubular condenser coil supported from said members below said third plate; a compressor that includes a housing having an inlet and an outlet, a rotor, and shaft for driving said rotor, said housing secured to said third plate; said evaporator coil having first and fourth ends and said condenser coil second and third ends, said first end connected to said inlet, said second end connected to said outlet; a length of tubing within said evaporator and condenser coils that connects said third and fourth ends; an expansion valve in said length of tubing; and a quantity of refrigerant in said evaporator and condenser coils that liquifies when subjected to a predetermined pressure;

c. first means for rotatably supporting said assembly in a fixed position in said housing; said top, first plate and a portion of said housing defining a first confined space in communication with said first opening; said first plate, third plate, and said evaporator coil defining a second confined space, with said first and second confined spaces at all times being in communication by at least one first port formed in said first plate; said second plate and the portion of said housing therebelow defining a third confined space in communication with said fourth opening; said second and third plates and said evaporator coil defining a fourth confined space that is in communication with said third confined space due to at least one second port formed in said second plate; said second and fourth confined spaces at all times in communication with said second and third openings;

d. first, second and third sealing means that extend inwardly from said housing and slidably engage said first, second and third plates as said assembly rotates;

e. power means for concurrently rotating said assembly and said shaft of said compressor at different rates of rotation, with said refrigerant being subjected to said predetermined pressure by said compressor as said refrigerant discharges into said condenser coil to liquify therein and to subsequently expand back to the gaseous state as it flows through said expansion valve back to said evaporator coil to absorb heat as it expands in said evaporator coi; and air in said second and third confined spaces being concurrently discharged therefrom through openings in said evaporator and condenser coils due to the centrifugal action imposed on said air as said assembly rotates, said air so discharged constituting said first and second streams that flows outwardly from said housing through said second and third openings therein, said first and second streams prior to flowing from said second and third openings being cooled and heated respectively due to heat exchange contact with said evaporator and condenser coils, and said air as it discharges from said second and third confined spaces being replaced by air that flows thereinto from said mass of air through said first openings and said first port and said fourth opening and second port respec tively.

2. An apparatus as defined in claim 1 that further includes:

f. second means for selectively discharging said first and second streams through said second or third openings to cool or heat said mass of air exteriorly of said housing.

Claims

1. An apparatus for concurrently forming a mass of air into a first cooled stream and a second heated stream thereof that includes: a. an elongated housing that includes a top, bottom and continuous side wall extending therebetween, said housing having first, second, third and fourth longitudinally spaced openings therein; b. a rotatable assembly disposed in said housing, said assembly including a first upper circular plate, a second lower circular plate, a third circular plate intermediately positioned between said first and second plates, a plurality of elongate, circumferentially spaced, rigid members connected to the peripheries of said first, second and third plates; a tubular evaporator coil supported from said members above said third plate; a tubular condenser coil supported from said members below said third plate; a compressor that includes a housing having an inlet and an outlet, a rotor, and shaft for driving said rotor, said housing secured to said third plate; said evaporator coil having first and fourth ends and said condenser coil second and third ends, said first end connected to said inlet, said second end connected to said outlet; a length of tubing within said evaporator and condenser coils that connects said third and fourth ends; an expansion valve in said length of tubing; and a quantity of refrigerant in said evaporator and condenser coils that liquifies when subjected to a predetermined pressure; c. first means for rotatably supporting said assembly in a fixed position in said housing; said top, first plate and a portion of said housing defining a first confined space in communication with said first opening; said first plate, third plate, and said evaporator coil defining a second confined space, with said first and second confined spaces at all times being in communication by at least one first port formed in said first plate; said second plate and the portion of said housing therebelow defining a third confined space in communication with said fourth opening; said second and third plates and said evaporator coil defining a fourth confined space that is in communication with said third confined space due to at least one second port formed in said second plate; said second and fourth confined spaces at all times in communication with said second and third openings; d. first, second and third sealing means that extend inwardly from said housing and slidably engage said first, second and third plates as said assembly rotates; e. power means for concurrently rotating said assembly and said shaft of said compressor at different rates of rotation, with said refrigerant being subjected to said predetermined pressure by said compressor as said refrigerant discharges into said condenser coil to liquify therein and to subsequently expand back to the gaseous state as it flows through said expansion valve back to said evaporator coil to absorb heat as it expands in said evaporator coi; and air in said second and third confined spaces being concurrently discharged therefrom through openings in said evaporator and condenser coils due to the centrifugal action imposed on said air as said assembly rotates, said air so discharged constituting said first and second streams that flows outwardly from said housing through said secoNd and third openings therein, said first and second streams prior to flowing from said second and third openings being cooled and heated respectively due to heat exchange contact with said evaporator and condenser coils, and said air as it discharges from said second and third confined spaces being replaced by air that flows thereinto from said mass of air through said first openings and said first port and said fourth opening and second port respectively.

2. An apparatus as defined in claim 1 that further includes: f. second means for selectively discharging said first and second streams through said second or third openings to cool or heat said mass of air exteriorly of said housing.