CA1146035A - Phase-change heat transfer system - Google Patents
Phase-change heat transfer systemInfo
- Publication number
- CA1146035A CA1146035A CA000403053A CA403053A CA1146035A CA 1146035 A CA1146035 A CA 1146035A CA 000403053 A CA000403053 A CA 000403053A CA 403053 A CA403053 A CA 403053A CA 1146035 A CA1146035 A CA 1146035A
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- Prior art keywords
- collector
- fluid
- condenser
- heat
- phase
- Prior art date
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Abstract
A phase-change heat transfer system which is selfcontrolled, self-pumping, and uses no moving parts. A heat collector device is connected in series with a condenser and an accumulator. The accumulator includes apparatus for regulating the pressure therein. A fluid capable of phase change within the system travels among the collector, condenser, and accumulator.
Description
~146~:935 , This application is a divisional of co-pending 1 Canadian Patent applicat~on 319,892 fiied January 18, 1979.
The presently available space heating and domestic hot water heating systems have several serious limitations in their performance and reliability. The heat transfer mechanism is inefficient and unreliable. The typical forced-liquid system requires a circulation pump which consumes electricity.
The temperature differential between the collector and the water tank is quite large, e.g., 30~. The coolant is usually corrosive and subject to freezing. Many co~lants are highly toxic (hence hazardous) should there be incursion to the hot water system. The controls are complicated and may not prevent transfer of heat from the condenser to the collector.
The typical installation is neither optimum nor reliable.
The thermal advantage of a phase-change system over a circulating-liquid system is apparent from consideration of latent heat as opposed to sensible heat for energy transport.
The heat absorbed using a circulating liquid is expressed by q = ~ Cp (Tout Tin) where ~ is the flow rate of circulating liquid, Cp is the specific heat of the liquid, and Tout and Tin are the tem-peratures of the liquid leaving and entering the collector.
The comparable expression for the phase-change system in which liquid enters the collector, boils with no change in temperature, and leaves as a vapor, is q = m (hg - hf) where hg and hf are enff~pies of the vapor and liquid respectively, - with their difference being the latent heat of vaporization.
The latent heat of a common refrigerant, Freon 114, is over 40 BTU/lb., compared to the specific heat of water of 1~46~35 1 l.d BTU/lb-F. This means that the circulating rate of the fluid for the phase-change system can be a small fraction of that of a circulating liquid, along with comparable elimination of external pumping power. Reduction of the circulating rate in the circulating liquid system would produce higher collector temperatures, accompanied by higher collector losses.
~ he standard pumped coolant system can neither maintain isothermal conditions within the collector nor provide the automatic maximum heat transfer in the transiently-cooled section of the tank when cold water enters caused by the increased condensing action at that point. Furthermore, the increase in heat transfer, as described above, in connection with a phase-change system, comes only from the collector; no heat is robbed from the upper portion of the tank which was previously heated.
Thus, a beneficial stratification in the water tank is preserved despite the presence of the condenser. These and other difficulties experienced with the prior art devices have been obviated in a novel manner by the present invention.
It is, therefore, an outstanding object of the invention to provide a completely self-regulating heat recovery and transfer system.
Another object of this invention is the provision of a heat collection and transfer system which cannot freeze up.
A further object of the present invention is the provision of a heat collection and transfer system with improved heat transfer capability by using the phase change of the heat transfer fluid.
It is another object of the instant invention to provide a heat collection and transfer system which has no moving parts.
~146~35 1 A still further object of the invention is the provision of a heat collection and transfer system which is more reliable and easily maintained than the prior art.
It is a further object of the invention to provide a heat collection and transfer system for which no outside controls are needed.
It is a still further object of the present invention to provide a heat collection and transfer system which eliminates many expensive and troublesome components.
Another object of the invention is the provision of a heat collection and transfer system which cannot lose heat from the condenser through the heat collector.
Another object of the invention is the provision of a heat collection and transfer system using a heat transfer medium which is non-corrosive.
Another object of the invention is the proviSion of a heat collection and transfer system using a héat transfer medium which has very low toxicity.
Another object of the invention is the provision of a heat collection and transfer system having a collector which is self-balancing and lsothermal.
~ Another object of the invention is the provision of a heat collection and transfer system in which the stratification of the flui~ to which heat is transferred in the condenser is improved.
Another object of the invention is the provision of a heat collection and transfer system in which heat always flows directly to the coldest point, improving system efficiency.
Another object of the invention is the provision of a heat collection and transfer system which will provide greater heat transfer and provide higher temperatures with ~46~35 1 otherwise unchanged collector and condenser capacities from more standard designs.
With these and other objects in view, as will be apparent to those skilled in the art, the invention resides in the combination of elements set forth in the claims appended hereto.
Another object of the invention is the maintenance of high efficiency, when the system is used as a solar heat collection, for example, even if the collector becomes par-tially shielded from the sun (such as caused by a tree or building) during part of the day.
Another object is the efficient operation of the system even if the installation requires some of the collector system to have difference orientations, i.e., as in the case of a solar heat collector on both the east and west slopes of a roof.
Another object of this invention is to provide a good performance monitor for the system.
Another object for this invention is to provide an effective testfor even very small leaks in the system.
SUMM~RY OE THE INVENTION
The presently preferred embodiment of the invention comprises a solar water heater apparatus which uses phase-change heat transfer, including a condenser immersed in a water tank, a solar collector which evaporates the heat transfer medium, and an accumulator which acts as a regulator for the system. More generally, the invention relates to a heat collection and transfer system which utilizes the phase-change capability of a heat transfer medium and thus avoids the need for a pump for the heat transfer medium. Of course, the heat 1 may be collected from any s.ource, such as solar~ exh~ust gases or heated waste water, and tt may ~e transferred to any medium, such as water or gas, in the condenser.
BRIEF DESCR M TION OF THE DRAWINGS
The character of the ~nvent~on, however, may be best understood by reference to one of its structural forms, as illustrated by the accompanying drawing, in which:
The single figure of drawings represents a somewhat schematic view of an apparatus, embodying the principles of the present invention in a preferred embodiment.
DESC~IPTION OF THE ~REFERRED EM80DIMENT
Referrin~ to the Figure, which.best shows the general features of the ~n~ention in its presently preferred embodiment, a solar water heater, indicated generally by the reference numeral 10, is shown as comprising a condenser 11 which may, for example, comprise a gas-tight conduit having an upper inlet 12, and having a lower outlet 13. This condenser 11 may be immersed in a rela-tively low temperature condensing fluid, such as water 20. The water may be héld in an insulated tank or vessel 14, the tank . 20 having an upper outlet 15 and a lower inlet 16 for water to enter it. Situated below the condenser 11 and connected to the lower outlet 13 through a first conduit 26 is an accumulator 17, which, in the preferred embodiment, is of the bladder type. The ac-cumulator may be located below or even above the collector, so long as it is connected to the system at a location which is below the collector, e.g., at or near the low point of the system so that the collector can be completely drained during shut-down.
The accumulator 17 may have a bladder 18, an accumulator inlet 19, and a means 21 for regulating the pressure about the bladder 18 of the type manufactured under the trade mark "EXTROL" by Amtrol Inc. of West Warwick, R.I. and shown and described in U.S. Patents 119~6~:)35 1 Nos. 2,695,753 and 3,035,614. Located above the accumulator inlet and below the condenser outlet is the solar collector 22 which may be of the type manufactured under the trademark "SOLECTOR" by Sunworks Manufacturing of Somerville, N.J. The solar collector may comprise an upper outlet 23 which communi-cates with the condenser upper inlet 12 through a second conduit 27 and a lower inlet 24 which communicates with the accumulator inlet 19 by an extension of the first conduit 26. Within the solar collector itself may be an inside conduit 25 which connects the collector outlet 23 to the collector inlet 24 and which e~poses a heat transfer medium 28, located at times within the conduit, to solar energy effects. This fluid heat transfer medium is located generally within a closed network formed by the condenser, the first conduit, the bladder, the solar collector conduit, and the second conduit.
The operation and advantages of the invention will now be readily understood in view of the above description. In an initial state the fluid heat transfer medium 28 (which in the preferred embodiment, is Freon 114) would lié substantially within the bladder 18 of the accumulator 17. In this initial state, the fluid level of the Freon 114 lies below the collector inlet 24. Some pressure, e.g., 70 psig, is applied to the bladder 18 through the pressure regulation device 21.
This forces the fluid Freon 28 up into the system, particularly into the solar collector conduit 25. In other words, the pressure applied to the bladder by the device 21 must be great enough to force effectively all of the medium 28 out of the accumulator 17 and up into the system for the system to transfer heat from the collector to the condenser. When the desired temperature of the condensing fluid 20 is reached, dependant upon the pressure exerted by the regulation device 21, the ~1~6~3S
1 pressure in medium 28 will exceed the pressure exerted on the bladder by the device 21. Only at that point does the accumu-lator serve any "useful" purpose (or even "exist") i~sofar as this system is concerned: the heat transfer medium 28 will drain into the accumulator and out of the collector. The bladder will expand against and overcome the force in the pressurizing chamber and the accumulator will thus act as a "thermostatic switch" to shut down the system. Since there is no medium 28 in the collector under these conditions, no effective heat transfer will occur until the temperature of the fluid 20 diminishes to a level at which the bladder again forces all of the medium 28 back into the system.
When the medium 28, e.g., Freon is forced back into the system, it will travel to the collector so that it may be evaporated by energy from the heat source, e.g., the sun 30.
This incxeases the vapor pressure in the closed network and the less dense vapor rises up the conduit of the collector, through the collector outlet 23 to the condenser, by way of the second conduit 27. In this initial instant the condensing fluid 20 is cool. The Freon vapor condenses, thus imparting its energy through the condenser walls to the water. Because of the placement of the water tank above the collector 22 and accumulator 17, gravity 119~6~35 1 forces the condensed liquid Freon back towards the bladder 18.
To use the above example, the vapor pressure of Freon 114 is approximately 70 psig at 140F. It follows, therefore, that this cycle of evaporation and condensation will continue until the temperature of the water 20 becomes slightly greater than 140F. At that time, the vapor pressure within the closed network will slightly exceed 70 psig. Because of this greater pressure being exerted within the bladder, the bladder 18 will expand and thereby lower the liquid level of the Freon within the remainder of the system. Once the Freon level is below the collector inlet 24 and the liquid Freon is no longer exposed to the sun's energy, the evaporation will stop and with it the heat transfer.
At a later time, if the water 20 cools below 140F, the vapor pressure within the system will decrease. This will cause the bladder 18 to contract and the Freon will again be forced into the collector 22 and the cycle will begin again.
The efficiency of the system is further enhanced by the self-balancing feature of the phase-change system which forces the collector 22 to operate isothermally and hence at the greatest efficiency.
Due to the nature of the heat transfer medium, the heat transfer is concentrated at the coldest point within the hot water tank 14 and thus further increases system performance and efficiency. When some cold water enters through the cold water inlet 16, as hot water is removed through the hot water outlet 15, rapid condensation is caused around the lower part of the condenser 11, thus concentrating the heating at that point. This further lowers the vapor pressure and temperature in the Freon system. It also lowers the temperature in the collector 22 and increases further the efficiency of the ~1~6~35 1 collector. Furthermore, no heat is robbed from the upper part of the hot water tank 14 during this transient condition, thus preserving the beneficial stratification within the system.
The above-mentioned features further allow cascading of hot water flow in two or more tanks while operating the Freon coils in parallel. The sel~ regulation of the final temperature and the concentration of heating at the coldest point in the tanks enhance the operation. This also provides a lower profile for the tanks and hence will ~it within a greater number of home designs.
A novel feature of this system is that no heat energy can be transferred from the hot water tank 14 to the collector 22. This occurs because, if the collector 22 is cooler than the hot water 20, the liquid remains entirely within the collector and the vapor pressure is lower than that required to cause condensation within the condenser 11: hence no heat trans~er can take place. I~ the water 20 surrounding the condensing coil 11 is cooler than the collector 22, condensing of the vapor will -commence and efficient heat transfer will take place between the collector 22 and the water 20. Typical differential tem-peratures are less than 5F.
From the above description it can be seen that the system provides its own thermostat, as well as providing a "thermodiode", so that heat can only flow in the proper direction. Further, the bladder accumulator prevents the release of Freon to the atmosphere and protects the system.
An alternate configuration where the hot water storage tank cannot be placed above the collector utilizes a condenser located above the collector rather than within or attached to the storage tank. The heat is transferred from this condenser _ g 1~46~35 1 to the storage tank by means of a circulating pump for forcing circulation of the storage tank water through the condenser.
This then provides many of the benefits of the above system even though the optimum location of the storage tank is precluded.
A good performance monitor of the system is pro~ided, since the pressure gage within the pressure regulating device 21 indicates the actual operating temperature of the collector until the regulated pressure is reached. It also indicates proper operation of the system. It is possible to provide an effective test for very small leaks in the system when Freon is used in the system, since a conventional commercial halogen-type leak detector functions very well. By its use, the integrity of the system is tested easily and effectively.
It is obvious that minor changes may be made in the form and construction of the invention without departing from the material spirit ther~of. It is not, however, desired to confine the invention to the exact form herein shown and described, but it is desired to include all such as properly come within the scope claimed.
For example, the collector may be employed to collect heat from any suitable source, such as laundry waste water, furnace smoke stack gasses, etc. Similarly, the condenser may transfer the useful heat to any desired gas or liquid.
Further, in the preferred or any alternate embodiment, the pressure regulating device 21 may be used to control the heat transfer medium pressure, and thus the temperature at the system output. Those skilled in the art will realize that the only limitation here will be based upon the size of the system, the volume of the heat transfer medium in the system, and the particular characteristics of the medium.
The presently available space heating and domestic hot water heating systems have several serious limitations in their performance and reliability. The heat transfer mechanism is inefficient and unreliable. The typical forced-liquid system requires a circulation pump which consumes electricity.
The temperature differential between the collector and the water tank is quite large, e.g., 30~. The coolant is usually corrosive and subject to freezing. Many co~lants are highly toxic (hence hazardous) should there be incursion to the hot water system. The controls are complicated and may not prevent transfer of heat from the condenser to the collector.
The typical installation is neither optimum nor reliable.
The thermal advantage of a phase-change system over a circulating-liquid system is apparent from consideration of latent heat as opposed to sensible heat for energy transport.
The heat absorbed using a circulating liquid is expressed by q = ~ Cp (Tout Tin) where ~ is the flow rate of circulating liquid, Cp is the specific heat of the liquid, and Tout and Tin are the tem-peratures of the liquid leaving and entering the collector.
The comparable expression for the phase-change system in which liquid enters the collector, boils with no change in temperature, and leaves as a vapor, is q = m (hg - hf) where hg and hf are enff~pies of the vapor and liquid respectively, - with their difference being the latent heat of vaporization.
The latent heat of a common refrigerant, Freon 114, is over 40 BTU/lb., compared to the specific heat of water of 1~46~35 1 l.d BTU/lb-F. This means that the circulating rate of the fluid for the phase-change system can be a small fraction of that of a circulating liquid, along with comparable elimination of external pumping power. Reduction of the circulating rate in the circulating liquid system would produce higher collector temperatures, accompanied by higher collector losses.
~ he standard pumped coolant system can neither maintain isothermal conditions within the collector nor provide the automatic maximum heat transfer in the transiently-cooled section of the tank when cold water enters caused by the increased condensing action at that point. Furthermore, the increase in heat transfer, as described above, in connection with a phase-change system, comes only from the collector; no heat is robbed from the upper portion of the tank which was previously heated.
Thus, a beneficial stratification in the water tank is preserved despite the presence of the condenser. These and other difficulties experienced with the prior art devices have been obviated in a novel manner by the present invention.
It is, therefore, an outstanding object of the invention to provide a completely self-regulating heat recovery and transfer system.
Another object of this invention is the provision of a heat collection and transfer system which cannot freeze up.
A further object of the present invention is the provision of a heat collection and transfer system with improved heat transfer capability by using the phase change of the heat transfer fluid.
It is another object of the instant invention to provide a heat collection and transfer system which has no moving parts.
~146~35 1 A still further object of the invention is the provision of a heat collection and transfer system which is more reliable and easily maintained than the prior art.
It is a further object of the invention to provide a heat collection and transfer system for which no outside controls are needed.
It is a still further object of the present invention to provide a heat collection and transfer system which eliminates many expensive and troublesome components.
Another object of the invention is the provision of a heat collection and transfer system which cannot lose heat from the condenser through the heat collector.
Another object of the invention is the provision of a heat collection and transfer system using a heat transfer medium which is non-corrosive.
Another object of the invention is the proviSion of a heat collection and transfer system using a héat transfer medium which has very low toxicity.
Another object of the invention is the provision of a heat collection and transfer system having a collector which is self-balancing and lsothermal.
~ Another object of the invention is the provision of a heat collection and transfer system in which the stratification of the flui~ to which heat is transferred in the condenser is improved.
Another object of the invention is the provision of a heat collection and transfer system in which heat always flows directly to the coldest point, improving system efficiency.
Another object of the invention is the provision of a heat collection and transfer system which will provide greater heat transfer and provide higher temperatures with ~46~35 1 otherwise unchanged collector and condenser capacities from more standard designs.
With these and other objects in view, as will be apparent to those skilled in the art, the invention resides in the combination of elements set forth in the claims appended hereto.
Another object of the invention is the maintenance of high efficiency, when the system is used as a solar heat collection, for example, even if the collector becomes par-tially shielded from the sun (such as caused by a tree or building) during part of the day.
Another object is the efficient operation of the system even if the installation requires some of the collector system to have difference orientations, i.e., as in the case of a solar heat collector on both the east and west slopes of a roof.
Another object of this invention is to provide a good performance monitor for the system.
Another object for this invention is to provide an effective testfor even very small leaks in the system.
SUMM~RY OE THE INVENTION
The presently preferred embodiment of the invention comprises a solar water heater apparatus which uses phase-change heat transfer, including a condenser immersed in a water tank, a solar collector which evaporates the heat transfer medium, and an accumulator which acts as a regulator for the system. More generally, the invention relates to a heat collection and transfer system which utilizes the phase-change capability of a heat transfer medium and thus avoids the need for a pump for the heat transfer medium. Of course, the heat 1 may be collected from any s.ource, such as solar~ exh~ust gases or heated waste water, and tt may ~e transferred to any medium, such as water or gas, in the condenser.
BRIEF DESCR M TION OF THE DRAWINGS
The character of the ~nvent~on, however, may be best understood by reference to one of its structural forms, as illustrated by the accompanying drawing, in which:
The single figure of drawings represents a somewhat schematic view of an apparatus, embodying the principles of the present invention in a preferred embodiment.
DESC~IPTION OF THE ~REFERRED EM80DIMENT
Referrin~ to the Figure, which.best shows the general features of the ~n~ention in its presently preferred embodiment, a solar water heater, indicated generally by the reference numeral 10, is shown as comprising a condenser 11 which may, for example, comprise a gas-tight conduit having an upper inlet 12, and having a lower outlet 13. This condenser 11 may be immersed in a rela-tively low temperature condensing fluid, such as water 20. The water may be héld in an insulated tank or vessel 14, the tank . 20 having an upper outlet 15 and a lower inlet 16 for water to enter it. Situated below the condenser 11 and connected to the lower outlet 13 through a first conduit 26 is an accumulator 17, which, in the preferred embodiment, is of the bladder type. The ac-cumulator may be located below or even above the collector, so long as it is connected to the system at a location which is below the collector, e.g., at or near the low point of the system so that the collector can be completely drained during shut-down.
The accumulator 17 may have a bladder 18, an accumulator inlet 19, and a means 21 for regulating the pressure about the bladder 18 of the type manufactured under the trade mark "EXTROL" by Amtrol Inc. of West Warwick, R.I. and shown and described in U.S. Patents 119~6~:)35 1 Nos. 2,695,753 and 3,035,614. Located above the accumulator inlet and below the condenser outlet is the solar collector 22 which may be of the type manufactured under the trademark "SOLECTOR" by Sunworks Manufacturing of Somerville, N.J. The solar collector may comprise an upper outlet 23 which communi-cates with the condenser upper inlet 12 through a second conduit 27 and a lower inlet 24 which communicates with the accumulator inlet 19 by an extension of the first conduit 26. Within the solar collector itself may be an inside conduit 25 which connects the collector outlet 23 to the collector inlet 24 and which e~poses a heat transfer medium 28, located at times within the conduit, to solar energy effects. This fluid heat transfer medium is located generally within a closed network formed by the condenser, the first conduit, the bladder, the solar collector conduit, and the second conduit.
The operation and advantages of the invention will now be readily understood in view of the above description. In an initial state the fluid heat transfer medium 28 (which in the preferred embodiment, is Freon 114) would lié substantially within the bladder 18 of the accumulator 17. In this initial state, the fluid level of the Freon 114 lies below the collector inlet 24. Some pressure, e.g., 70 psig, is applied to the bladder 18 through the pressure regulation device 21.
This forces the fluid Freon 28 up into the system, particularly into the solar collector conduit 25. In other words, the pressure applied to the bladder by the device 21 must be great enough to force effectively all of the medium 28 out of the accumulator 17 and up into the system for the system to transfer heat from the collector to the condenser. When the desired temperature of the condensing fluid 20 is reached, dependant upon the pressure exerted by the regulation device 21, the ~1~6~3S
1 pressure in medium 28 will exceed the pressure exerted on the bladder by the device 21. Only at that point does the accumu-lator serve any "useful" purpose (or even "exist") i~sofar as this system is concerned: the heat transfer medium 28 will drain into the accumulator and out of the collector. The bladder will expand against and overcome the force in the pressurizing chamber and the accumulator will thus act as a "thermostatic switch" to shut down the system. Since there is no medium 28 in the collector under these conditions, no effective heat transfer will occur until the temperature of the fluid 20 diminishes to a level at which the bladder again forces all of the medium 28 back into the system.
When the medium 28, e.g., Freon is forced back into the system, it will travel to the collector so that it may be evaporated by energy from the heat source, e.g., the sun 30.
This incxeases the vapor pressure in the closed network and the less dense vapor rises up the conduit of the collector, through the collector outlet 23 to the condenser, by way of the second conduit 27. In this initial instant the condensing fluid 20 is cool. The Freon vapor condenses, thus imparting its energy through the condenser walls to the water. Because of the placement of the water tank above the collector 22 and accumulator 17, gravity 119~6~35 1 forces the condensed liquid Freon back towards the bladder 18.
To use the above example, the vapor pressure of Freon 114 is approximately 70 psig at 140F. It follows, therefore, that this cycle of evaporation and condensation will continue until the temperature of the water 20 becomes slightly greater than 140F. At that time, the vapor pressure within the closed network will slightly exceed 70 psig. Because of this greater pressure being exerted within the bladder, the bladder 18 will expand and thereby lower the liquid level of the Freon within the remainder of the system. Once the Freon level is below the collector inlet 24 and the liquid Freon is no longer exposed to the sun's energy, the evaporation will stop and with it the heat transfer.
At a later time, if the water 20 cools below 140F, the vapor pressure within the system will decrease. This will cause the bladder 18 to contract and the Freon will again be forced into the collector 22 and the cycle will begin again.
The efficiency of the system is further enhanced by the self-balancing feature of the phase-change system which forces the collector 22 to operate isothermally and hence at the greatest efficiency.
Due to the nature of the heat transfer medium, the heat transfer is concentrated at the coldest point within the hot water tank 14 and thus further increases system performance and efficiency. When some cold water enters through the cold water inlet 16, as hot water is removed through the hot water outlet 15, rapid condensation is caused around the lower part of the condenser 11, thus concentrating the heating at that point. This further lowers the vapor pressure and temperature in the Freon system. It also lowers the temperature in the collector 22 and increases further the efficiency of the ~1~6~35 1 collector. Furthermore, no heat is robbed from the upper part of the hot water tank 14 during this transient condition, thus preserving the beneficial stratification within the system.
The above-mentioned features further allow cascading of hot water flow in two or more tanks while operating the Freon coils in parallel. The sel~ regulation of the final temperature and the concentration of heating at the coldest point in the tanks enhance the operation. This also provides a lower profile for the tanks and hence will ~it within a greater number of home designs.
A novel feature of this system is that no heat energy can be transferred from the hot water tank 14 to the collector 22. This occurs because, if the collector 22 is cooler than the hot water 20, the liquid remains entirely within the collector and the vapor pressure is lower than that required to cause condensation within the condenser 11: hence no heat trans~er can take place. I~ the water 20 surrounding the condensing coil 11 is cooler than the collector 22, condensing of the vapor will -commence and efficient heat transfer will take place between the collector 22 and the water 20. Typical differential tem-peratures are less than 5F.
From the above description it can be seen that the system provides its own thermostat, as well as providing a "thermodiode", so that heat can only flow in the proper direction. Further, the bladder accumulator prevents the release of Freon to the atmosphere and protects the system.
An alternate configuration where the hot water storage tank cannot be placed above the collector utilizes a condenser located above the collector rather than within or attached to the storage tank. The heat is transferred from this condenser _ g 1~46~35 1 to the storage tank by means of a circulating pump for forcing circulation of the storage tank water through the condenser.
This then provides many of the benefits of the above system even though the optimum location of the storage tank is precluded.
A good performance monitor of the system is pro~ided, since the pressure gage within the pressure regulating device 21 indicates the actual operating temperature of the collector until the regulated pressure is reached. It also indicates proper operation of the system. It is possible to provide an effective test for very small leaks in the system when Freon is used in the system, since a conventional commercial halogen-type leak detector functions very well. By its use, the integrity of the system is tested easily and effectively.
It is obvious that minor changes may be made in the form and construction of the invention without departing from the material spirit ther~of. It is not, however, desired to confine the invention to the exact form herein shown and described, but it is desired to include all such as properly come within the scope claimed.
For example, the collector may be employed to collect heat from any suitable source, such as laundry waste water, furnace smoke stack gasses, etc. Similarly, the condenser may transfer the useful heat to any desired gas or liquid.
Further, in the preferred or any alternate embodiment, the pressure regulating device 21 may be used to control the heat transfer medium pressure, and thus the temperature at the system output. Those skilled in the art will realize that the only limitation here will be based upon the size of the system, the volume of the heat transfer medium in the system, and the particular characteristics of the medium.
Claims (5)
1. A heat collection apparatus using phase-change heat transfer comprising:
an housing having an inlet and an outlet for the passage of a condensing fluid to be heated therethrough;
a condenser operatively related to said housing for transfer of heat from said condenser to a condensing fluid in said housing, said condenser having a heat transfer fluid inlet and outlet;
a heat collector means having a heat transfer fluid inlet and an outlet, said outlet being below said condenser fluid inlet;
means for locating said collector in a position for the exposure thereof to a relatively high temperature;
conduit means connecting said condenser outlet to said collector inlet and said collector outlet to said condenser inlet, all in fluid-tight relationship;
a phase-change fluid heat transfer medium in a system formed by said collector, condenser, and conduit means; and means for controlling the pressure of said phase-change fluid within said system in order to thereby select a temperature of the fluid within said housing at which the transfer of heat from said collector to said condenser is effectively stopped.
an housing having an inlet and an outlet for the passage of a condensing fluid to be heated therethrough;
a condenser operatively related to said housing for transfer of heat from said condenser to a condensing fluid in said housing, said condenser having a heat transfer fluid inlet and outlet;
a heat collector means having a heat transfer fluid inlet and an outlet, said outlet being below said condenser fluid inlet;
means for locating said collector in a position for the exposure thereof to a relatively high temperature;
conduit means connecting said condenser outlet to said collector inlet and said collector outlet to said condenser inlet, all in fluid-tight relationship;
a phase-change fluid heat transfer medium in a system formed by said collector, condenser, and conduit means; and means for controlling the pressure of said phase-change fluid within said system in order to thereby select a temperature of the fluid within said housing at which the transfer of heat from said collector to said condenser is effectively stopped.
2. The apparatus of claim 1 wherein said heat collector means comprises solar energy collection means suitably oriented relative to the sun for collection of such energy.
3. The apparatus of claim 1 wherein said predetermined temperature selection means comprises;
means for accumulatng a sufficient volume of said phase-change fluid as a liquid at a low point in the system, when the condensing fluid in said housing reaches a predetermined temperature, in a volume sufficient to effectively prevent further heating of the condensing fluid.
means for accumulatng a sufficient volume of said phase-change fluid as a liquid at a low point in the system, when the condensing fluid in said housing reaches a predetermined temperature, in a volume sufficient to effectively prevent further heating of the condensing fluid.
4. The apparatus of claim 3 wherein said predetermined temperature selection means for further comprises means for forcing all of the said phase-change fluid out of said accumulating means and into said collector, condenser, and conduit means when the temperature of the condensing fluid is less than the predetermined temperature.
5. The apparatus of claim 3 wherein said accumulating means comprises;
a variable volume fluid-containment means and means for exerting a selected pressure on said containment means for thus controlling and selecting said predetermined temperature of said condensing fluid.
a variable volume fluid-containment means and means for exerting a selected pressure on said containment means for thus controlling and selecting said predetermined temperature of said condensing fluid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000403053A CA1146035A (en) | 1978-01-19 | 1982-05-14 | Phase-change heat transfer system |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US87062478A | 1978-01-19 | 1978-01-19 | |
| CA319,892A CA1126115A (en) | 1978-01-19 | 1979-01-18 | Phase-change heat transfer system |
| CA000403053A CA1146035A (en) | 1978-01-19 | 1982-05-14 | Phase-change heat transfer system |
| US870,624 | 1992-04-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1146035A true CA1146035A (en) | 1983-05-10 |
Family
ID=27166048
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000403053A Expired CA1146035A (en) | 1978-01-19 | 1982-05-14 | Phase-change heat transfer system |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1146035A (en) |
-
1982
- 1982-05-14 CA CA000403053A patent/CA1146035A/en not_active Expired
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| Date | Code | Title | Description |
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