CA1156110A - Integral storage collector solar heat system - Google Patents

Abstract

Abstract In an integral storage collector solar heating system, water heated in a convention hot water heater (12) is first preheated in an integral storage collector (22). The storage collector (22) includes a heat storing medium (46), preferably clean water, in a storage tank (40). Water to be heated is forced by line pressure through heat exchange pipes (44) im-mersed in the heat storing water (46). The heat of fusion of the storing water prevents freezing of the line water. To preclude excessive pressure in the heat storage tank with high temperatures of the heat storing water, a heat pipe (52) is provided to act as a large heat leak at about the vaporiza-tion temperature of the water. Also, a pressure relief valve (48) is provided. The system avoids freezing and contamination of the water and does not require temperature control circuitry or a pump.

Description

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Description Inte~ral Storage Collector Solar Heating System Technical Field This invention relates to the solar heating of water.

Backgxound Art In both domestic and industrial applications, preheating of hot water by solar energy is coming into widespread use.
Generally a solar collector for absorbing light and converting the light to thermal energy is mounted on a roof. Because us~
0 Gf the hot water is periodic, the heat must be transferred to an insulated storage medium which holds the heat energy for subse-quent use.
In early solar water heating systems such as disclosed in U.S. Patents 1,747,826 to Gould and 1,753,227 to Wheeler et al.
hot water pipes in a solar collector were connected to a hot water stor~ge tank. The heated water flowed into the tank by convection and to that end the solar collector was at a level lower than the water storage tank. Because it is generally pre-ferred to have the solar collector at a high point such as on a roof and the water storage at a low point such as in a basement, such convection systems are not usually practical. Further, un-less the solar collector is disconnected at night, cooling of the stored hot water may result. Thus some temperature responsive valve control is required. And once disconnected, if water is then allowed to remain in the collector it is subject to freezing.
A moder~ adaptation of the older water heating systems is found in ~.S. Patent 4,010,734 to Chayet. In that patent a t~ perature controlled pump is used to pump water from a hot wG~-.r stcrage tank to the solar collector. A supplemental elec-trical heating element is also provided in the storage tank. Sucha system requires temperature control circuitry as well as an electrical pump. With periodic turning on and off of the pump~
the pump and circuitry are subject to failure. The system also suffers from the free2ing problem if water is permitted to re-~,ain in the collector on cold nights.

-2 115~110 Most conventional solar water heating systems avoid the freezing problem by using a nonfreezing heat transfer fluid. The transfer fluid is pumped in a closed circuit which passes in heat exchange relationship with the water to be heated. As in the Chayet system, tempera-ture controls and a pump are required for the heat transfer fluid. The systems also suffer from the risk of contamina-tion of the hot water with leakage of the nonfreezing heat transfer fluid. Further, such systems are expensive. Heat trasfer fluid is much more expensive than plain water, and to avoid contamination of the water and to avoid other lea-kage of the expensive heat transfer fluid, a very tight and thus expensive fluid transfer system must be provided.
An object of the present invention is to provide a simplified solar water system which does not require a pump or temperature control circuitry and which thus avoids the expense and unreliability of those elements of the system.
A further object of this invention is to provide such a simplified solar heating system which does not pre-sent the risk of contamination of the heated water while still avoiding freezing of the water.
Yet another object of this invention is to pro-vide a solar water heating system capable of providing a substantial amount of the heat requirement~ in a home, office building or the like.
A solar heating system in accordance with the present invention has an integral storage collector expo-sed to solar illumination. The storage collector includes an absorber for absorbing solar energy, a heat storage me-dium of large heat capacity and high thermal conductivity for storing the absorbed energy, and means defining a wa-ter flow path, said means defining being in heat exchange relationship with the heat age medium. Water is forced ~ through the water flow path by line pressure and is used directly as a hot water supply.

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In accordance with a particular embodiment of the invention there is provided a solar heating system for heating water. The system includes an integral sto-rage collector exposed to solar illumination, the storage collector including absorber means for absorbing solar energy. The storage collector also includes a heat sto-rage medium of large heat capacity and high thermal con-ductivity directly heated by the absorber means. The storage collector also includes means defining a water flow path, the means defining being in heat exchange re-lationship with the heat storage medium. A water outlet from the water flow path is connected as a pressurized heated water supply, a water inlet to the means defining the water flow path is connected to a primary pressurized water supply line such that line pressure forces fresh water through the means defining the water flow path of the integral storage collector as heated water is taken from the water outlet.

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1 15~ ~0 The heat storage medium is pre~Eerably water so that the heat of fusion of the storage medium prevents freezing of the line water.
To avoid high pressures in the heat storage medium with high temperatures, a pressure relief is provided. Preferably, the pressure relief includes a heat pipe which acts as a large heat leak at about the vaporization temperature of the heat storage medium.

Brief description of the drawings The foregoing and other objects, features, and advantages of the invention will be apparent from the following more parti-cular description of a preferred embodiment of the invention, as illustrated in the accompanying drawings in which like reference characters refer to the same parts throughout the different views.
The drawings are not necessarily to scale, emphasis instead being placed upon illustrating the principles of the invention.
Fig. 1 is an illustration of a solar heating system em-bodying the present invention;
Fig. 2 is a perspective view of the solar collector of Fig. l;
Fig. 3 is a cross sectional view of the collector of Fig. 2 taken along line 3-3;
Fig. 4 is a longitudinal sectional view of the collector of Fig. 2 takenalong line 4-4 and showing the heat pipe tempera-ture control component.

Best mode of carrying out the invention As shown in Fig. 1, hot water is stored in a conventional hot water tank 12 which is generally located in the basement or on the first floor of a building. The tank is wrapped in a heat insulating material 14.
Water supplied to the tank 12 through inlet port 16 is heated by an electrical resistance heating ccil 18. The heating 1 1 5 ~ 0 coil is temperature controlled to maintain a predetermined range of water temperature. As an alternative, some other heating element such as a gas flame may be provided. From the outlet 20 hot water is provided on demand at any number of taps and the like thro~ghout the building.
In accordance with the present invention the water supplied to the conventional hot water tank 12 is first preheated in an integral storage collector 22. Water at line pressure is pro-vided from a primary water supply line 23 through a valve 24 to a collector water inlet pipe 26. The supply line 23 is generally connected to a town water supply, and it supplies water at a pressure which obviates pumps at individual buildings.
After preheating in the integral storage collector 22 the water, still at line pressure, flows through the collector outlet pipe 28 and a valve 30 to the hot water tank inlet port 16. The valves 24 and 30 are conventional hand operated valves which are left open in normal operation of the system.
The entire length of pipe 28 is wrapped in thermal insula-tion 29 to reduce heat loss from the pipe. Only the length of pipe 26 exposed to a cold environment is insulated at 27. With that insulation, sufficient heat is conducted from the building and from the collector through the pipe 26 to prevent freezing of water in the pipe.
The integral storage collector 22 of Fig. 1 is shown in de-tail in Figs. 2, 3 and 4. The collector includes a box casing 32.
The open side of the casing 32 faces the sun and is covered by an outer glass or plastic transparent plate 34. Spaced below the plate 34 is a transparent plate 36 of Teflon (a trademark for polytetrafluoroethylene). The sheets 34 and 36 are transparent to light but reflect heat.
The bottom and sides of the casing 32 are packed with a thermal insulating material 38. A flat tank 40 is seated in the insulation and has an energy absorbing surface 42 facing the transparent sheets 34 and 36. The absorbing surface 42 is ~ 1 5 ~ 0 is coated with a flat black paint or with a selective black coating wh~ch i9 a good absor~er of radiation in the solar spectrum but a poor emitter of infrared energy.
The heat absorbing arrangement of the collector 22 in-cluding the transparent plates 34 and 36 and the black absorbing surface 42 are conventional. Other arrangements may include any number of transparent plates as well as a convection suppression arrangement.
Tank 40 is filled with water as a heat storage medium 46.
A serpentine water conduit 44 connecting the water inlet 26 and water outlet 28 is enclosed in the tank 40 and carries line water to be preheated. The water conduit 44 is copper tubing.
Copper does not react with water and has a high thermal condu~-tivity to provide good heat exchange between the heat storage medium 46 and the line water in the tubing.
~ eat storage mediums other than water such as heat transfer oils may also be used; however, for several reasons water is the preferred medium. For one, water is very inexpensive and is readily available. Further, where fresh water without antifreeze is used, there is no danger of contamination of the line water.
Finally~ by use of water as the storage medium, freezing of the line water in the collector is avoided. At night, where the am-bient temperature drops below freezing, the temperature of the water in the collector, including the storage medium, can be ex-pected to drop to 0C, the freezing temperature of water. But the heat of fusion which must be removed from the large mass of water at the freezing temperature before the water will freeze is substantial. Given the high thermal insulating characteristics of the storage collector, there is insufficient heat transfer from the heat storage water to freeze that wa~er. Total freezing would only occur after days of subfreezing weather with no light, an unlikely occurence in most regions.
Thus, because the substantial heat of fusion required to freeze the tank of water prevents the line water from freezing, the storage medium must have a fusion temperature of 0C or -115~1~0 .

higher in subfreezing ~limate.
To avoid freezing of the heat storage medium, and thus freezing of the line water, two critical parameters must be considered; the amount of heat which must be transferred from the water to cause complete freezing and the rate of heat loss from the storage medium.
The rate o~ heat loss can be determined from the heat trans-fer coefficient U of the collector calculated with respect to the absorber surface area. Although heat is lost from other than the face of the collector, heat loss through the absorber and transparent plates is dominant. A collector having two inches of insulation behind the heat medium storage tank and two glass plates over the tank has an overall heat transfer coefficient of about 2.5 Cal m 2 C l hr 1. Thus, with the storage medium at 0C and the ambient temperature at -12C, the rate of heat loss from the absorber is only about 30 Cal-m 2-hr 1.
For very cold climates, the transfer coefficient U can be lowered to about 1.5 by using an additional glass or plastic plate over the collector absorber. In warm climates a single-plate collector having a heat transfer coefficient of about 5might be sufficient.
The amount of heat which must be transferred to freeze the stored water is dependent on the mass of the water. Specifically, to cool the water in the storage tank to the freezing temperature, a heat loss of 1 Cal. per kilogram of water per C is required.
Then, the water remains at 0C until the heat of fusion of 79.7 Cal. kg 1 of water is transferred from the storage medium.
If; for example, the storage collector contains 43 kilograms of water per square meter of surface area, the heat loss from the storage collector required to freeze water at 0C i ~~t 3430 Cal m 1 of collector area.
~ As~uming that no water flows through the collector and that the solar flux to the collector is zero, the time required to freeze 0C water in the collector at any ambient air temperature can be determined from the equation 115~1~0 .

U x ( ~ ~a~ x t = 79.7 x M
where U is the overall heat transfer coefficient in Cal-m 2-oC l-hr 1, Ta is the ambient air temperature in C, M is the weight of water in kg/m2 and t is the time to freeze in hours.
Thus, assuming a U factor of 2.5 and ambient temperature of -12C, about 115 hours is required to totally freeze the heat storage medium after the temperature of the medi~m has been reduced to 0C. Note that even this lengthy period of time is based on an assumption of no solar flux. However, even a small amount of solar energy in the range of about 55 to about 135 Cal-m 2-hr 1 is available even on cloudy days. And partic-ularly cold weather is generally accompanied by relatively clear sky conditions resulting in even higher solar flux. Thus, nor-mally any partial freezing which occurs at night will be counter-ed during the day by the solar energy absorbed. As a practical matter, water contained in the integral storage collector will not totally freeze.
From the above equation for determining the length of time required to totally freeze the storage medium, one can define a freezing time ratio as M/U~ From that ratio it can be seen that one can increase the tLme for freezing, and thus decrease the likelihood of total freezing, by either making the mass of water per unit area large or the heat transfer coefficient low. To prevent freezing in those warmer climates where the water may be subject to freezing, a freezing time ratio of about 28 kg-hr l-oC l~Cal is sufficient. In substantially colder cli-mates a freezing time ratio of at least about 55 is required.
When one intends to use water as the storage medium a use-ful design parameter is a volumetric freezing time ratio V~Uwhere ~ is the storage tank volume per collector surface area.
Because one liter of water is one kilogram, the ratios M/U and V/U are directly related. ~he minimum volumetric freezing time ratio for the warmer climates is thus about 28 liters-hr l-oC 1 Cal 1 and that for the colder climates is ~ 15~ l ~ O

about 55.
The amount of water stored in the collector is also de-pendent on the heat storage capacity required for significant preheating of the line water. For household use, from about 20 liters-m 2 to 55 liters-m 2 i5 su~ficient. One can select the volume of water stored in the collec~or from that range.
This sets the values of M and V. Then, to attain the necessary freezing time ratio, one need only set the heat tran~fer co-efficient. To reduce collector cost, that coefficielt should be set at the lowest value possible while still avoiding freezing for a particular climate.
Other practical design considerations also aEfect the choice of M and V. Increasing those parameters requires a de2per absorb-er panel and that increases collector costs. Also, increa~ing those parameters tends to decrease the high temperature attainea by the storage medium during sunny periods.
A 32.6 liters m integral storage collector having a stor-age tank of about 0.91m by 83 m by 2.54 cm and having a thermal transfer coefficient of 2.5 Cal-m 2 oC l hr~l has been tested for a year in the Boston, Massachusetts, area. During that pe-riod only partial freezing along the tank walls has occurred despite temeratures below -18C; and there has been no resultant damage to the collector.
Isolation of the line water from the storage medium by means of the serpentine tubing 44 in the collector is required for several reasons. For one, the line pressure is as much as 7.66 kg-cm . Tank construction necessary to withstand such high pressures would be exceptionally costly. Another advan-tage is that it provides a closed volume of heat storage medium.
This is particularly advantageous where water is used as the storage medium because the continued introduction of impurities t`o the tank is avoided. Thus, the tank may be of steel ana need not be lined with plas~ic, ceramic or the like. Such a liner is generally required in a water storage tank in which water is ~ ~ 5 ~

continuously introduced because the fresh impurities react with the tank. A final reason for the use of tubing 44 is that partial freezing is likely in the storage medium during extreme weather conditions. However, that freezing occurs first along the side walls of the tank. With the line water, carried by tubes 44, set in from the side walls that water is the last to freeze in the tank. Thus, there is no danger of ice breaking loose to form an ice dam in the line.
During periods when heat is not extracted from the heat storage medium, that is when tap water is not being drawn through the syst~m, the daytime temperature of the water could reach 150C to 200~C. The tank construction which would be required to withstand such high temperatures and the resultant high pressure is expensive. Thus pressure relief means are provided.
In regions where such high temperatures are not likely, a simple pressure release valve 48 may be used. The valve is in fluid communication with the heat storage medium through a port 50. If the pressure in the tank 40 were to build up to some predetermined level, for example in the order of two atmos-pheres, the valve 48 would open and pressurized fluid would beexpelled. Unless an overflow tank were used in conjunction with the valve 48, the tank 40 would then have to be refilled.
Where over-temperature conditions are likely, some other means for controlling the temperature and thus the pressure of the heat storage water is preferred. For that purpose, a heat pipe 52 shown in Figs. 2 and 4 is provided at the upper end of the heat storage tank. Although shown as a U-shaped tube con-nected at each end to the tank 40, the heat pipe may be a straight or bent tube closed at one end. Beat conducting fins 54 are spaced along the tube 52.
At the usual operating temperatures of the storage collec-t~r, that is at about 55C to 65C , there is little vapor in the space 56 over the heat stor~ge water 46. Thus, heat losses through the pipe 52 result only from heat conduction through the dry air and the sides of the tube. Those heat losses are insig-115 ~ o nificant. However, when the temperature of the water in tank40 approaches the vaporization temperature, or boiling tempera~
ture, of water at 100C, the tube 52 is converted into a sim-plified heat pipe. Water vapor fills the pipe 52, is cooled by heat transfer into the environment, and condenses. The cooled, condensed liquid 58 then flows back int~ the tank 40 as return condensate. Thus, as in a conventional heat pipe, there is a natural convection of hot vapor toward the cold end of the pipe with the flow of condensate back to the hot end of the pipe.
The substantial heat of vaporization is extracted from the vapor and passed to the cool environment.
The tube 52 acts as a heat pipe only at about the vapori-zation temperature of the water. Thus, substantial heat leakage is provided at about that temperature to prevent continued rise in the temperature of the water, but there are only insignificant heat losses in the normal operating range of the storage collec-tor.
In order to avoid the occurrence of a poc~et of dry air remaining in the heat pipe even when the water vaporizes, a plug of gas permeable, moisture impermeable material may be positioned at the upper end of the heat pipe. With increased pressure the wet air forces dry air through the plug and fills the heat pipe.
The heat pipe 52 need not be opened to the vapor space 56 if a quantity of water or other vaporizable fluid were contained in the heat pipe. That alternative would allow for adjustment of the heat leakage temperature. By choosing a heat pipe fluid having a vaporization temperature other than 100C or by pres-surizing or drawing a vacuum in the pipe, the leakage tempera-ture could be set at any desired level.
As noted above, some heat storage and transfer fluid o~herthan water may be used in the tank 40. If the vaporization ~em-perature of such a medium were higher than any temperature pos-sibly encountered in the storage collector, the pressure relief ~15~1i0 valve 48 and the heat pipP 52 may not be required. Such a heat storage and transfer fluid would be more expensive and would present the possibility of contamination of the line water. However, contamination is less likely than in conven-tional systems in which the heat tran6fer fluid is pumped into heat exchange relationship with the water. In the present case the water is under pressure, and the heat transfer fluid is preferably held at near one atmosphere pressure. Thus, leak-age would be from the line water into the heat transfer fluid rather than vice versa.
In operation, the water 46 in the tank 40 is heated by the solar energy absorbing surface 42. The water is usually heated to a temperature within the range of 55C to 65C. When hot water is not drawn from the system, line water sits in the tubing 44 and is heated to the temperature of the storage medium.
On demand from taps on line 20, hot water is drawn from the hot water tank 14. With that, preheated water from the storage collector 22 is forced by line pressure into the tank 14 where it may be further heated if necessary. The initial volume of water drawn from the collector 22 may be within the range of 55C to 65C and require no further heating. Addi~ional water forced through the collector from the line 23 is preheated by heat exchange with the storage medium 46. The large heat ex-change area provided by the serpentine, high conductivity tubing 44 provides sufficient preheating of the flowing water to sub-stantially reduce the amount of heating required by the resis-tance coil 18. The demand for water is normally in brief in~
tervals of no more than three minutes and the heat stored re-builds sufficiently between intervals for subsequent preheating of the line water.
It is recognized that on cold nights the heat storage water in tank 40 may cool below the temperature of ~he line water and result in negative preheating. However, the period during which the temperature in the tank 40 is low corresponds to the normal ~ 1 5 ~ 0 . .
, . .

period of lowest hot water demand. Tests show that substan-tial preheating of hot water is provided from the late morning to several hours after dusk even during winter months, and any heat losses encountered at night and early morning are countered by high system efficiency during the daytime. Heating of the heat storage medium is direct and heat exchange losses associated with conventional systems are thereby reduced.
Tests indicate that the system can provide 40 to 60% of the heating requirements for a home hot water system at about half of the installation cost of prior comparable systems.
Further, reliability is increased and maintenance costs are re-duced because of the absence of a pump and control circuitry.
While the invention has been particularly shown and de-scribed with reference to a preferred embodiment thereof, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as described by the ap-pended claims.
The invention is applicable in any solar heating system for heating water. It has its prime utility as a preheating unit to a conventional water heating system.

Claims (8)

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

1. A solar heating system for heating water compri-sing:
an integral storage collector exposed to solar illumination, the storage collector including absorber means for absorbing solar energy, a heat storage medium of large heat capacity and high thermal conductivity direc-tly heated by said absorber means, and means defining a water flow path, said means defining being in heat exchange relationship with said heat storage medium a water outlet from said water flow path connec-ted as a pressurized, heated water supply and a water inlet to said means defining the water flow path connected to a primary pressurized water supply line such that line pressure forces fresh water through the means defining the water flow path of the integral storage collector as heated water is taken from the water outlet.

2. A solar heating system as claimed in Claim 1 wherein the heat storage medium is water.

3. A solar heating system as claimed in Claim 1 further comprising a pressure relief means for preventing excessive pressure buildup of the heat storage medium, said pressure relief means being in fluid communication with said heat storage medium.

4. A solar heating system as claimed in Claim 3 wherein the pressure relief means is a heat pipe which may be opened at one end to said heat storage liquid.

5. A solar heating system as claimed in Claim 3 wherein the pressure relief means is a pressure responsive valve.

6. A solar heating system as claimed in Claim 3 wherein the collector has a freezing time ratio M/U of at least about 28kg.hr-l.°C-l.Cal-1 where M is the weight of water in kg/m2 of absorber surface area and U is the heat transfer coefficient of the collector in Cal.m-2.°C-l.hr-1.

7. A solar heating system as claimed in Claim 4 wherein the freezing time ratio M/U is at least about 55kg .hr-l-.°C-l.Cal-1.

8. A solar heating system as claimed in Claim 1 wherein said water outlet from said means defining the water flow path is connected to the inlet port of a hot water heater.