US20110048062A1

US20110048062A1 - Portable Cooling Unit

Info

Publication number: US20110048062A1
Application number: US12/880,940
Authority: US
Inventors: Thomas Gielda; Kristian Debus; Jay Harman
Original assignee: CAITIN Inc F/K/A NEW PAX Inc; Caitin Inc
Current assignee: Pax Scientific Inc
Priority date: 2009-03-25
Filing date: 2010-09-13
Publication date: 2011-03-03

Abstract

A portable cooling unit operates by pumping liquid. Because the portable cooling unit pumps liquid, the compression system that generates the cooling power does not require the use of a condenser. The compression system utilizes a compression wave. An evaporator of the cooling unit operates in the critical flow regime in which the pressure in an evaporator tube will remain almost constant and then ‘jump’ or ‘shock up’ to an increased pressure.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is a continuation-in-part and claims the priority benefit of U.S. patent application Ser. No. 12/732,171, filed Mar. 25, 2010, which is incorporated herein by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention
The present invention generally relates to cooling systems. The present invention more specifically relates to portable cooling units.
2. Description of the Related Art
A vapor compression system as known in the art generally includes a compressor, a condenser, and an evaporator. These systems also include an expansion device. In a prior art vapor compression system, a gas is compressed whereby the temperature of that gas is increased beyond that of the ambient temperature. The compressed gas is then run through a condenser and turned into a liquid. The condensed and liquefied gas is then taken through an expansion device, which drops the pressure and the corresponding temperature. The resulting refrigerant is then boiled in an evaporator. This vapor compression cycle is generally known to those of skill in the art.
FIG. 1 illustrates a vapor compression system 100 as might be found in the prior art. In the prior art vapor compression system 100 of FIG. 1, compressor 110 compresses the gas to (approximately) 238 pounds per square inch (PSI) and a temperature of 190° F. Condenser 120 then liquefies the heated and compressed gas to (approximately) 220 PSI and 117° F. The gas that was liquefied by the condenser 120 is then passed through the expansion valve 130 of FIG. 1. By passing the liquefied gas through expansion valve 130, the pressure is dropped to (approximately) 20 PSI. A corresponding drop in temperature accompanies the drop in pressure, which is reflected as a temperature drop to (approximately) 34° F. in FIG. 1. The refrigerant that results from dropping the pressure and temperature at the expansion valve 130 is boiled at evaporator 140. Through boiling of the refrigerant by evaporator 140, a low temperature vapor results, which is illustrated in FIG. 1 as having (approximately) a temperature of 39° F. and a corresponding pressure of 20 PSI.
The cycle related to the system 100 of FIG. 1 is sometimes referred to as the vapor compression cycle. Such a cycle generally results in a coefficient of performance (COP) between 2.4 and 3.5. The coefficient of performance, as reflected in FIG. 1, is the evaporator cooling power or capacity divided by compressor power. It should be noted that the temperature and pressure references that are reflected in FIG. 1 are exemplary and illustrative.
FIG. 2 illustrates the performance of a vapor compression system like that illustrated in FIG. 1. The COP illustrated in FIG. 2 corresponds to a typical home or automotive vapor compression system—like that of FIG. 1—operating in an ambient temperature of (approximately) 900F. The COP shown in FIG. 2 further corresponds to a vapor compression system utilizing a fixed orifice tube system.
Such a system 100, however, operates at an efficiency rate (i.e., COP) that is far below that of system potential. To compress gas in a conventional vapor compression system 100 like that illustrated in FIG. 1 typically takes 1.75-2.5 kilowatts for every 5 kilowatts of cooling power generated. This exchange rate is less than optimal and directly correlates to the rise in pressure times the volumetric flow rate. Degraded performance is similarly and ultimately related to performance (or lack thereof) by the compressor 110.
Haloalkane refrigerants such as tetrafluoroethane (CH₂FCF₃) are inert gases that are commonly used as high-temperature refrigerants in refrigerators and automobile air conditioners. Haloalkane refrigerants have also been used to cool over-clocked computers. These inert, refrigerant gases are more commonly referred to as R-134 gases. The volume of an R-134 gas can be 600-1000 times greater than the corresponding liquid.
In light of the theoretical efficiencies of systems using haloalkanes or other fluids, there is a need in the art for an improved cooling system that more fully recognizes system potential and overcomes technical barriers related to compressor performance.

SUMMARY OF THE CLAIMED INVENTION

The portable cooling unit disclosed herein includes a pump that maintains a circulatory fluid flow through a flow path. The unit also includes an evaporator that operates in the critical flow regime of the circulatory fluid. The evaporator generates a compression wave that shocks the maintained fluid flow, thereby changing the pressure of the maintained fluid flow and exchanging heat introduced into the circulatory fluid flow. No heat is added to the circulatory fluid flow before the circulatory fluid flow passes through the evaporator. The evaporator may use one or more tubes/nozzles, and may generate 20-80 watts of cooling power.
The unit further includes a storage compartment, the storage compartment receiving items to be cooled or maintained at a temperature below ambient. The storage compartment may form a housing for the pump and the evaporator. An external surface of the storage compartment may effectuate convection and further exchange heat introduced into the unit.
The unit may be powered by an adapter such as for a vehicle battery. Moreover, the unit may be powered by a self-contained battery pack. The unit may use a solar cell as a direct power source or as a means of charging a battery pack.
Operating conditions within the unit may include the pump raising the pressure of the circulatory fluid flow from approximately 20 PSI to approximately 100 PSI. In certain embodiments, the pressure may be raised to pressures in excess of 100 PSI, such as 300 or 500 PSI.
A portable cooling system according to the technology disclosed herein may include a storage compartment that receives items to be cooled or maintained at a temperature below ambient. The system may also include a pump that maintains a fluid flow of a compressible fluid through the system, and an evaporator that effects a phase change in the compressible fluid. The system may establish a compression wave in the compressible fluid by passing the compressible fluid from a high pressure region to a low pressure region, the velocity of the fluid being greater than or equal to the speed of sound in the compressible fluid. The compressible fluid is cooled during a phase change so that heat may be transferred from the system by thermally coupling one or more fins between the compressible fluid and the ambient atmosphere.
Operating conditions in the evaporator may include a pressure drop in the cooling liquid to approximately 5.5 PSI. A corresponding phase change results in a lowered temperature of the cooling liquid. The pressure change may occur within a range of approximately 20 PSI to 100 PSI, or the increased pressure may be in excess of 100 PSI, such as 300 or 500 PSI.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 illustrates a vapor compression system as might be found in the prior art.

FIG. 2 illustrates the performance of a vapor compression system like that illustrated in FIG. 1.

FIG. 3 illustrates an exemplary cooling system in accordance with an embodiment of the present invention.

FIG. 4 illustrates an exemplary cooling system in accordance with another embodiment of the present invention.

FIG. 5 illustrates performance of a cooling system like that illustrated in FIGS. 3 and 4.

FIG. 6 illustrates the operation of a single tube cooling system.

FIG. 7 illustrates a method of operation for a portable cooling unit.

FIG. 8 illustrates an exemplary embodiment of the portable cooling unit.

DETAILED DESCRIPTION

FIG. 3 illustrates an exemplary cooling system 300 in accordance with an embodiment of the present invention. The cooling system 300 does not need to compress a gas as otherwise occurs at compressor 110 in a prior art vapor compression system 100 like that shown in FIG. 1. Cooling system 300 operates by pumping liquid. Because cooling system 300 pumps liquid, the compression cooling system 300 does not require the use of a condenser 120 as does the prior art compression system 100 of FIG. 1. Compression cooling system 300 instead utilizes a compression wave. The evaporator of cooling system 300 operates in the critical flow regime where the pressure in an evaporator tube will remain almost constant and then ‘jump’ or ‘shock up’ to the ambient pressure.
The cooling system 300 of FIG. 3 recognizes a heightened degree of efficiency in that the pump 320 of the system 300 is not required to draw as much power as the compressor 110 in a prior art compression system 100 like that illustrated in FIG. 1. A compression system designed according to an embodiment of the presently disclosed invention may recognize exponential performance efficiencies. For example, a prior art compression system 100 as illustrated in FIG. 1 may require 1.75-2.5 kilowatts to generate 5 kilowatts of cooling power. Prior art compression system 100 therefore may operate at a coefficient of performance (COP) of less than 3. A system 300 like that illustrated in FIG. 3 may pump fluid from approximately 14.7 to approximately 120 PSI with the pump drawing power at approximately 500 W (0.5 kilowatts), with the system 300 also generating 5 kilowatts of cooling power. The system 300 may therefore operate with a COP of 10. As a result of the cycle illustrated in FIG. 3, and the resultant increased efficiencies, system 300 may utilize many working fluids, including but not limited to water.
The cooling system 300 of FIG. 3 may include a housing 310. Housing 310 of FIG. 3 is akin to that of a pumpkin. The particular shape or other design of housing 310 may be a matter of aesthetics with respect to where or how the system 300 is installed. The design of the housing 310 may be influenced by the facility in which the system 300 is installed, or by the equipment or machinery to which the system 300 is coupled. Functionally, housing 310 encloses pump 330, evaporator 350, and the attendant accessory equipment or flow paths (e.g., pump inlet 340 and evaporator tube 360). Housing 310 also contains the cooling fluid to be used by the system 300.
Housing 310, in an alternative embodiment, may also encompass a secondary heat exchanger (illustrated in FIG. 4). A secondary heat exchanger may be excluded from being contained within the housing 310 and system 300. In such an embodiment, the outer surface area of the system 300—that is, the housing 310—may be utilized in a cooling process through forced convection on the external surface of the housing 310.
Pump 330 may be powered by a motor 320, which is external to the system 300 and located outside the housing 310 in FIG. 3. Motor 320 may alternatively be contained within the housing 310 of system 300. Motor 320 may drive the pump 330 of FIG. 3 through a rotor drive shaft with a corresponding bearing and seal or magnetic induction, whereby penetration of the housing 310 is not required. Other motor designs may be utilized with respect to motor 320 and corresponding pump 330 including synchronous, alternating (AC), and direct current (DC) motors. Other electric motors that may be used with system 300 include induction motors; brushed and brushless DC motors; stepper, linear, unipolar, and reluctance motors; and ball bearing, homopolar, piezoelectric, ultrasonic, and electrostatic motors.
Pump 330 establishes circulation of a compressible fluid through the interior fluid flow paths of system 300, the flow paths being contained within housing 310. Pump 330 may circulate fluid throughout system 300 through use of vortex flow rings. Vortex rings operate as energy reservoirs whereby added energy is stored in the vortex ring. The progressive introduction of energy to a vortex ring via pump 330 causes the corresponding ring vortex to function at a level such that energy lost through dissipation corresponds to energy being input.
Pump 330 also operates to raise the pressure of a liquid being used by system 300 from, for example, 20 PSI to 100 PSI or more. Some systems may operate at an increased pressure of approximately 300 PSI. Other systems may operate at an increased pressure of approximately 500 PSI.
Pump inlet 340 introduces a liquid to be used in cooling and otherwise resident in system 300 (and contained within housing 310) into pump 330. Fluid temperature may, at this point in the system 300, be approximately 95 F.
The fluid introduced to pump 330 by inlet 340 traverses a primary flow path to nozzle/evaporator 350. Evaporator 350 induces a pressure drop (e.g., to approximately 5.5 PSI) and phase change that results in a low temperature. The cooling fluid further ‘boils off’ at evaporator 350, whereby the resident liquid may be used as a coolant. For example, the liquid coolant may be water cooled to 35-45° F. (approximately 37° F. as illustrated in FIG. 3).
As noted above, the system 300 (specifically evaporator 350) operates in the critical flow regime, thereby generating a compression wave. The coolant fluid exits the evaporator 350 via evaporator tube 360 where the fluid is ‘shocked up’ to approximately 20 PSI because the flow in the evaporator tube 360 is in the critical regime. In some embodiments of system 300, the nozzle/evaporator 350 and evaporator tube 360 may be integrated and/or collectively referred to as an evaporator.
The coolant fluid of system 300 (having now absorbed heat for dissipation) may be cooled at a heat exchanger to assist in dissipating absorbed heat, the temperature of the fluid being approximately 90-100° F. after having exited evaporator 350. Instead of a heat exchanger, however, the housing 310 of the system 300 (as was noted above) may be used to cool via convection. FIG. 5 illustrates an exemplary performance cycle of a cooling system like that illustrated in FIGS. 3 and 4.
FIG. 6 shows the operation of a single evaporation tube or nozzle cooling system 600. Single tube/nozzle cooling system 600 utilizes the supersonic cooling cycle illustrated in FIGS. 3 and 4, but may typically be implemented in an embodiment requiring a relatively low cooling power, for example 20-100 watts. The system 600 utilizes a small pump 610 and a single nozzle or tube 620. The single tube 620 functions as the evaporator in the system 600. A radiator 630 may be employed to remove heat from the system.
The pump 610 raises the pressure of a fluid in the system 600. Various fluids, including water, may be used in the system. The pressure of the fluid may be raised from 20 PSI to in excess of 100 PSI. The fluid flows through the single tube 620 of the evaporator. Pressure drop and phase change result in a lower temperature of the fluid in the tube 620 and provide the cooling power for the system 600.
Critical flow rate, which is the maximum flow rate that can be attained by a compressible fluid as that fluid passes from a high pressure region to a low pressure region (i.e., the critical flow regime), allows for a compression wave to be established and utilized in the critical flow regime. Critical flow occurs when the velocity of the fluid is greater or equal to the speed of sound in the fluid.
In critical flow, the pressure in the channel will not be influenced by the exit pressure and at the channel exit, the fluid will ‘shock up’ to the ambient condition. In critical flow the fluid will also stay at the low pressure and temperature corresponding to the saturation pressures.
In cooling system 600, the cooled fluid is passed through radiator 630 to effectuate a heat transfer to the atmosphere. The operating steps of the system 600 are described in further detail below with reference to FIG. 8.
FIG. 7 shows an exemplary embodiment of a portable cooling unit 700. Portable cooling unit 700 may be powered by a 12 volt power supply, such as a car battery. An adapter 710 that plugs into a power outlet such as those commonly found in vehicles may be provided with the unit 700. Portable cooling unit 700 may also be powered by self-contained batteries or a solar cell. A solar cell may also be used to charge the self-contained batteries. Those skilled in the art will recognize that many power supply configurations may be utilized in the portable cooling unit 700.
The housing 720 of unit 700 may include one or more fins 730. The fins 730 may be coupled to the cooling fluid in the unit 700, and may be open to the atmosphere. The fins 730 may therefore be used as the radiator to transfer heat from the interior of the unit 700 to the exterior atmosphere.
FIG. 8 illustrates a method of operation 800 for the cooling systems 300, 400. In step 810, a pump raises the pressure of a liquid. The pressure may, for example, be raised from 20 PSI to in excess of 100 PSI. As mentioned above, the increased pressure may be 300 PSI or even 500 PSI. In step 820, fluid flows through the nozzle/evaporator tube(s). Pressure drop and phase change result in a lower temperature as fluid is boiled off in step 830.
Critical flow rate, which is the maximum flow rate that can be attained by a compressible fluid as that fluid passes from a high pressure region to a low pressure region (i.e., the critical flow regime), allows for a compression wave to be established and utilized in the critical flow regime. Critical flow occurs when the velocity of the fluid is greater or equal to the speed of sound in the fluid. In critical flow, the pressure in the channel will not be influenced by the exit pressure and at the channel exit, the fluid will ‘shock up’ to the ambient condition. In critical flow the fluid will also stay at the low pressure and temperature corresponding to the saturation pressures. In step 740, after exiting the evaporator tube, the fluid “shocks” up to 20 PSI. A heat exchanger may be used in optional step 850. Cooling may also occur via convection on the surface of the housings of the systems 300, 400.
While various embodiments have been described above, it should be understood that they have been presented by way of example only, and not limitation. The descriptions are not intended to limit the scope of the invention to the particular forms set forth herein. Thus, the breadth and scope of a preferred embodiment should not be limited by any of the above-described exemplary embodiments. It should be understood that the above description is illustrative and not restrictive. To the contrary, the present descriptions are intended to cover such alternatives, modifications, and equivalents as may be included within the spirit and scope of the invention as defined by the appended claims and otherwise appreciated by one of ordinary skill in the art. The scope of the invention should, therefore, be determined not with reference to the above description, but instead should be determined with reference to the appended claims along with their full scope of equivalents.

Claims

1. A portable cooling unit comprising:

a pump that maintains a circulatory fluid flow through a flow path;

an evaporator that operates in the critical flow regime of a circulatory fluid and generates a compression wave that shocks the maintained fluid flow, thereby changing the pressure of the maintained fluid flow with no heat being added to the circulatory fluid flow before the circulatory fluid flow passes through the evaporator;

a heat exchanging mechanism thermally coupled to the circulatory fluid flow; and

a storage compartment, the storage compartment receiving items to be cooled or maintained at a temperature below ambient, wherein the cooling unit is readily transportable.

2. The portable cooling unit of claim 1, wherein the storage compartment forms a housing for the pump and the evaporator.

3. The portable cooling unit of claim 2, wherein at least a portion of an external surface of the storage compartment serves as the heat exchanging mechanism by effectuating convection from the interior of the unit to the atmosphere.

4. The portable cooling unit of claim 1, wherein the heat exchanging mechanism is a radiator.

5. The portable cooling unit of claim 1, wherein a single tube is utilized in the evaporator.

6. The portable cooling unit of claim 5, wherein the cooling unit generates approximately 80 watts of cooling power.

7. The portable cooling unit of claim 1, wherein the unit is battery powered.

8. The portable cooling unit of claim 7, wherein the battery is charged by a solar cell.

9. The portable cooling unit of claim 1, wherein the unit is powered by a solar cell.

10. The portable cooling unit of claim 1, wherein the pump raises the pressure of the circulatory fluid flow from approximately 20 PSI to approximately 100 PSI.

11. The portable cooling unit of claim 1, wherein the pump raises the pressure of the circulatory fluid flow to more than 100 PSI.

12. A portable cooling system comprising:

a storage compartment, the storage compartment receiving items to be cooled or maintained at a temperature below ambient;

a pump that maintains a fluid flow of a compressible fluid through the system; and

an evaporator that effects a phase change in the compressible fluid, wherein the system establishes a compression wave in the compressible fluid by passing the compressible fluid from a high pressure region to a low pressure region, the velocity of the fluid being greater than or equal to the speed of sound in the compressible fluid, the compressible fluid being cooled during a phase change so that heat is transferred from the system by thermally coupling one or more fins between the compressible fluid and the ambient atmosphere, and wherein the cooling unit is readily transportable.

13. The system of claim 11, further comprising a pump inlet that introduces a cooling liquid maintained within the housing to the pump, and wherein the cooling liquid is a part of the circulatory fluid flow.

14. The system of claim 12, wherein the evaporator induces a pressure drop in the cooling liquid to approximately 5.5 PSI, a corresponding phase change resulting in a lowered temperature of the cooling liquid.

15. The system of claim 13, wherein the cooling liquid is water.

16. The system of claim 13, wherein a pressure change within a fluid flow of the compressible fluid occurs within a range of approximately 20 PSI to 100 PSI.

17. The system of claim 13, wherein a pressure change within a fluid flow of the compressible fluid involves a change to an excess of 100 PSI.

18. The system of claim 13, wherein a pressure change within a fluid flow of the compressible fluid involves a change to less than 20 PSI.

19. The system of claim 11, wherein the pump raises the pressure of the circulatory fluid flow from approximately 20 PSI to approximately 100 PSI.

20. The system of claim 11, wherein the pump raises the pressure of the circulatory fluid flow to more than 100 PSI.