1. Field of the Invention
The present invention relates generally to air conditioning systems and particularly to air conditioning systems configured to use mechanical leverage in order to save or produce energy.
2. Description of the Related Art
Two-chamber conventional air conditioning systems using an evaporator, a condenser and a compressor to move refrigerant vapors from the evaporator to the condenser are well known. The problem is that these systems are high consumers of electrical energy, and therefore, economically less and less attractive as energy becomes more and more scarce and expensive.
Attempts were also made to design systems that would capture the heat in the attic or other forms of heat energy for the purpose of using it in air conditioning applications, pool heating, refrigeration applications and electrical energy generation. The problem with these systems is that they are difficult and expensive to build and overall inefficient.
Therefore, a new, inexpensive, versatile and more efficient energy saving system is needed to take advantage of the abundantly and freely available ambient heat energy, such as heat from the attic, and/or other forms of heat energy such as the renewable solar energy.
The problems and the associated solutions presented in this section could be or could have been pursued, but they are not necessarily approaches that have been previously conceived or pursued. Therefore, unless otherwise indicated, it should not be assumed that any of the approaches presented in this section qualify as prior art merely by virtue of their presence in this section of the application.
In one embodiment, a mechanical leverage system using refrigerants in conjunction with temperature differences found in the environment is utilized for air conditioning. The mechanical leverage system provides a means for altering boiling point temperatures of refrigerants in which the system is enabled to absorb and expel heat within the temperature differentials found in the environment.
Suitable heat donors and receivers for this process to proceed are essential. This may be economically obtained through heat differences occurring naturally in our environment. Environmental temperature differences are usually ample in supply. For example, temperatures of 120 degrees F. may be readily obtained by utilizing heat from attic spaces and heat collecting devices such as solar panels and parabolic mirrors. Conversely, cooler ambient air temperatures are also readily obtainable. Hence, an advantage of the system is the ability to use ambient heat and/or solar energy collected from the environment to power an air conditioning installation and, thus, to save energy.
In another embodiment, a mechanical leverage system using refrigerants in conjunction with temperature differences found in the environment is used for collecting heat energy from the environment for the purpose of generating electricity. Thus, an advantage of the system is the ability to convert plentifully available ambient heat energy and/or solar energy into electrical energy.
In another embodiment, input of energy may be applied to augment the system, when necessary to supplement the amount of heat energy collected from the environment.
The above embodiments and advantages, as well as other embodiments and advantages, will become apparent from the ensuing description and accompanying drawings.
For exemplification purposes, and not for limitation purposes, embodiments of the invention are illustrated in the figures of the accompanying drawings, in which:
a depicts the bottom-front perspective view of the house roof from
b depicts the house roof from
a depicts the front view of the house roof from
b is a perspective view of the evaporator box from
c depicts the bottom-back perspective view of the house roof from
d depicts the partial side perspective view of the house roof from
e depicts the perspective view of the return conduit 2502a from
What follows is a detailed description of the preferred embodiments of the invention in which the invention may be practiced. Reference will be made to the attached drawings, and the information included in the drawings is part of this detailed description. The specific preferred embodiments of the invention, which will be described herein, are presented for exemplification purposes, and not for limitation purposes. It should be understood that structural and/or logical modifications could be made by someone of ordinary skills in the art without departing from the scope of the present invention. Therefore, the scope of the present invention is defined by the accompanying claims and their equivalents.
The system in
It should be understood that the vertical configuration of the two pistons in
Second sub-chamber 111b communicates with second chamber 112, which contains ammonia vapor 162 at a pressure of 20.33 bars. Next, second chamber 112 communicates with fourth sub-chamber 113b. Finally, third sub-chamber 113a, contains liquid ammonia 133 and ammonia vapors at a pressure of 15.54 bars, and it is configured to communicate controllably with first sub-chamber 111a and second chamber 112, with the aid of counter resistance 141 and pump 142, respectively. The counter resistance 141 may be a release valve, which may be used to release as needed some of the liquid ammonia 133 from third sub-chamber 113a into first sub-chamber 111a. The pump 142 may be used to pump as needed some of the liquid ammonia 133 from third sub-chamber 113a into second chamber 112.
First piston 121 and second piston 122 are communicated by a hydraulic system, comprising hydraulic members 152 and hydraulic hose 151, and are counter balanced against each other. The non-compressible fluid of the hydraulic system transfers pressure from one piston to the other making the actions of the pistons responsive to one another. Thus, it is ensured that, when the equilibrium is disturbed, the distance traveled by first piston 121 is equaled with the distance traveled by second piston 122. The pistons are mechanized by a push/ pull action in that the energy from vaporization will push the first piston 121 and, conversely, the energy from condensation will pull the second piston 122.
The balancing of the two pistons is achieved by using a piston system, where second piston 122 has a larger surface area than first piston 121 in order to compensate for pressure differences. It is well established that:
(Difference in pressure 1)×Area 1=(Difference in pressure 2)×Area 2
From the above formula it may be deducted that in a leverage system, if the difference in vapor pressure acting on the first piston is larger than the difference of pressure acting on the second piston, then the surface area of the first piston is smaller than the surface area of the second piston. Furthermore, since the vapor pressure of refrigerants are proportional to temperature, the temperature differential associated with the first piston having the smaller surface area is greater than the temperature differential associated with the second piston having the larger surface area.
Again, for exemplification purposes, let's assume that first sub-chamber 111a contains liquid ammonia 131 at a pressure of 6.15 bars. The boiling point of ammonia at this pressure is 50 degrees Fahrenheit (F.). Thus, at the temperature of 50 degrees F. or greater, the liquid ammonia 131 will boil filling with ammonia vapors 161 all available space delimited by the walls of first sub-chamber 111a and first piston 121. The second chamber 112 contains liquid ammonia 132 at a pressure of 20.33 bars. The boiling point of ammonia at this pressure is 122 degrees F. Thus, at the temperature of 122 degrees F. or greater, the liquid ammonia 132 will boil filling with ammonia vapors 162 all available space delimited by first piston 121, the walls of second sub-chamber 111b, the walls of second chamber 112, the walls of fourth sub-chamber 113b, and second piston 122. The third sub-chamber 113a contains liquid ammonia 133 and ammonia vapors 163 at a pressure of 15.54 bars. The boiling point of ammonia at this pressure is 104 degrees F. Thus, at the temperature of 104 degrees F. or lower, the ammonia vapors 163 in third sub-chamber 113a will condense joining the liquid ammonia 133.
To summarize, first sub-chamber 111a contains ammonia at a pressure of 6.15 bars and a temperature of 50 degrees F. At these parameters, one kilogram (kg) of ammonia vapor 161 occupies a volume of 0.2056 cubic meters. Second chamber 112 contains ammonia at a pressure of 20.33 bars and a temperature of 122 degrees F. At these parameters, one kilogram of ammonia vapor 162 occupies a volume of 0.0635 cubic meters. Finally, third sub-chamber 113a contains ammonia at a pressure of 15.54 bars and a temperature of 104 degrees F. At these parameters, one kilogram (kg) of ammonia vapor 163 occupies a volume of 0.0833 cubic meters.
At equilibrium the force exerted on piston 121 equals the force exerted on piston 122:
Force 1=Force 2
(P2−P1)×A1=(P2−P3)×A2; (Eq. 1);
Since both pistons are interconnected, if first piston 121 travels 1 meter then second piston 122 also travels 1 meter. This means that:
Work 1=Work 2, or
P1×V1=P2×V2
P1×A1×Si=P2×A2×S2; (Eq. 3);
The ammonia in first sub-chamber 111a will boil and absorb heat from the room where it is placed. At 6.15 bars of vapor pressure, the temperature of the ammonia in first sub-chamber 111a is 50 degrees F. The ammonia at this temperature will adequately remove heat from a room where the temperature is greater than 50 degrees F. (for example, 75 degrees F.). As heat is removed from the room into first sub-chamber 111a, the ammonia within it will boil and will tend to equilibrate to the point of saturation. The resulting increase in ammonia vapor pressure (P1) in first sub-chamber 111a will translate into a pushing force exerted on first piston 121.
The second chamber 112 contains ammonia at a pressure of 20.33 bars (P2). Ammonia at this pressure requires a temperature of 122 degrees F. to boil. Heat may be acquired from ambient temperature of the attic, where second chamber 112 may be placed, and/or, from other sources, such as solar panels or reflectors, if needed. The boiling of the ammonia in second chamber 112 will result in an increase of the vapor pressure (P2), which will translate into a pushing force exerted on the first piston 121 and the second piston 122. The force exerted on second piston 122 is greater than the force exerted on first piston 121 due to the surface area of second piston 122 being greater than that of first piston 121. Hence, when, in second chamber 112, the pressure P2, which at system equilibrium is 20.33 bars, increases, the two pistons 121, 122 move clockwise (when looking at the exemplary system depicted in
Third sub-chamber 113a contains ammonia at a pressure of 15.54 bars (P3) and a temperature of 104 degrees F. The ammonia vapor will condense by loosing heat to the cooler outside ambient air having a temperature of, for example, 95 degrees F. The condensation of the ammonia vapor in third sub-chamber 113a results in a decrease of vapor pressure, and thus, will have a pulling force effect exerted on second piston 122.
As explained later, the pressure/temperature difference between chamber 2 and third sub-chamber chamber 113a may be narrower with the use of the leverage system. The narrowing of this pressure/temperature difference makes it possible for the system to absorb heat and expel heat within the temperature ranges found in the environment. Thus, enabling the refrigerant in second chamber 112 to boil, and subsequently condense in sub-chamber 113a, at narrower pressure/temperature differences between attic and outside ambient air. This is an important advantage as the environmental temperatures are invariably uncontrollable. Hence, it becomes necessary to configure the leverage system to work within these parameters.
First sub-chamber 111a acts as an evaporator and third sub-chamber 113a acts as a condenser. Again, the three interconnected chambers may be placed at different locations. First chamber 111 may be placed inside the space to be cooled, second chamber 112 may be placed in the attic, and third chamber 113 may be place outside. The forces exerted by the actions of the ammonia vapors on piston 121 and piston 122 are transferred between the two pistons by hydraulic pressure hose(s) 151 and the ammonia is transferred among the various chambers by tubing 191.
Each of the three chambers will tend to reach equilibrium with one another, as changes in temperature occur. Either by the process of boiling or condensing, each chamber will strive to maintain vapor pressures corresponding to their respective temperatures and saturation levels. The boiling and condensing of the refrigerant creates a pushing and pulling force on the pistons and drives the system forward.
The specific volume of the ammonia vapors in first sub-chamber 111a is 0.2056 cubic meter/kg and the specific volume of vapor in second chamber 112 is 0.0635 cubic meter/kg. The specific volume of vapor from sub-chamber 111-a to second chamber 112 is decreased by a factor of (0.2056/0.0635) or 3.227. This is equivalent to saying that the density of the ammonia vapors in second chamber 112 is 3.227 times greater than the density of the ammonia vapors in first sub-chamber 111a. The area of second piston 122 is 2.96 greater than the area of first piston 121. Therefore, second piston 122 displaces (3.227×2.96) or 9.5 times more vapor than first piston 121. The production of the required additional vapor takes place in second chamber 112. As discussed, most of the vapor production and heat absorption takes place in second chamber 112. This makes up the greatest portion of the required energy to power the system.
Fortunately, this additional energy, in the form of heat, may be derived from unwanted heat from spaces such as the attic. Higher temperatures may also be readily obtained by utilizing heating devices such as solar panels and parabolic mirrors. Solar heat collectors such as venting canal systems may also be used. Venting canals are made up of insulated panels affixed to the bottom portion of the rafters of a pitched roof. This results in a longitudinal compartment bounded by the adjacent rafters on each side and by the sheathing of the roof on the top and the insulated panels on the bottom. The longitudinal compartment or canal confines the air space below the roofline and concentrates the heat to higher temperatures. The heated air rises, within the canals, to the apex of the roof where the heat is absorbed by the boiling of the refrigerant in second chamber 112.
Second chamber 112 may be in the form of a long tube, containing refrigerant, and may be placed along the apex or ridgeline of the roof, thus, absorbing heat from the attic and/or, for example, venting canals. Hence, the boiling of the refrigerant in the tube is caused by the heat from the attic and/or the venting canals. Thus, this unwanted and abundantly available heat becomes the fuel that powers the cooling system.
There is a two-fold advantage to this process. First, the more heat is absorbed by the refrigerant in second chamber 112, the more heat is also absorbed in first chamber 111, namely its 111a first sub-chamber, and hence, more cooling occurs in the living area. This is because, the higher the temperature in second chamber 112, the greater is the pushing and “pulling” (because of the hydraulic link) effect on second piston 122 and first piston 121, respectively, exercised by the refrigerant gases from second chamber 112. This translates in expanded volume, and thus, lower pressure and lower temperature in first sub-chamber 111a, which means that more heat will be absorbed from the living area. Secondly, the heat that would normally accumulate in the attic and ultimately penetrate the living spaces of a house is diverted and absorbed by second chamber 112 of the cooling system. Consequently, this absorbed heat never has the opportunity to penetrate and heat the inside of the house.
When the system is at equilibrium the parameters of temperature and pressure in the three chambers are maintained and stabilized as earlier described (first chamber 211 contains liquid ammonia 231 and ammonia vapor 271 at a pressure of 6.15 bars (P1) and a temperature of 50 degrees F.; second chamber 212 contains liquid ammonia 232 and ammonia vapor 272 at a pressure of 20.33 bars (P2) and a temperature of 122 degrees F.; third chamber 213 contains liquid ammonia 233 and ammonia vapor 273 at a pressure of 15.54 bars (P3) and a temperature of 104 degrees F.). However, the equilibrium state of the chambers become disturbed as the refrigerant boils in chambers 211 and 212 and condenses in chamber 213. The resultant change of vapor pressure in the chambers pumps the vapor through the system.
Pistons 221 and 222 are adjoined and move together as a unit, pushing the vapor through the system. The connector 251 between the two pistons 221, 222 may be a hydraulic system or link, which may comprise hydraulic member(s), such as a hydraulic piston, and hydraulic hose(s). When the four valves 260a are open and the four valves 260b are closed, as shown in
When the two pistons 221, 222 reach their end point to the right in the respective cylinders 214, 215, an electronic or a mechanical switch for example, close the four valves 260a and open the four valves 260b (as illustrated in
The cycle repeats when the polarity of pressure reverses again, when the pistons 321, 322 reach the end point to the left. The vapor flows continuously through the system as pistons 321 and 322 oscillate back and forth.
The condensed ammonia liquid in third chamber 213 must be recycled to first chamber 211 and second chamber 212 in proportion to their original amounts. Input of work is required at turbine 242 to pump ammonia liquid from third chamber 213 into second chamber 212, against a pressure difference of 4.79 bars (P2−P3). However, work is gained at turbine 241 as 9.39 bars (P3−P1) of ammonia liquid pressure is released from third chamber 213 into first chamber 211. A counter resistance of 9.39 bars at turbine 241 is necessary to keep the system in equilibrium.
It should be noted that the volume of chambers 211, 212 and 213 are substantially larger than the volume of cylinders 214, 215 so as to create minimal change in pressure in chambers 211, 212 and 213 as the ammonia vapor ingresses and egresses via the opening of valves 260a and 260b.
If the volume displaced by each stroke of piston 221 equals 1 cubic meter then the volume of each stroke displaced by piston 222 is 2.97 cubic meters. This is because, as it was explained earlier when describing
As stated earlier, the specific volume of the ammonia in chamber 211 is 0.2056 cubic meter/kg, which means that its density is 4.86 kg/cubic meter. In chamber 212 the specific volume of the ammonia is 0.0635 cubic meter/kg, which means that its density is 15.74 kg/cubic meter.
From the above, it can be deducted that, with each stroke of 1 cubic meter, the amount of ammonia vapor displaced by first piston 221 is 4.86 kg. In the same time, the amount of ammonia vapor displaced by piston 222 is 46.59 Kg (15.74 kg/cubic meter×2.96 cubic meters). Thus, the ratio of ammonia to be recycled back into chamber 211 and chamber 212 is 4.86/46.59 or 1:9.5, respectively.
The work required to return the liquid ammonia to the respective chambers is a function of its density or volume and the pressure difference of the respective chambers (the specific volume of liquid ammonia is 0.0015 cubic meter/kg):
Work=V(P1−P2)
Work Gain (4.86 kg moved from chamber 213 to chamber 211):
Since one part of liquid ammonia (i.e., 4.96 kg) is returned to chamber 211, the difference of 41.73 kg (i.e., 46.59 kg−4.86 kg) is returned to chamber 212.
Work Expended (41.73 kg moved from chamber 213 to chamber 212)
The conventional method of air conditioning does not utilize second chamber 212 but does require the equivalence of pumping ammonia in the form of vapor from first chamber 211 to third chamber 213. The conventional method does not use a mechanical leverage advantage system. The work required in pumping 1 cubic meter or 4.86 kg of ammonia vapor from chamber 211 to chamber 213 may be determined as follows:
Work=V(P2−P1)
Volume of 4.86 Kg of ammonia vapor in chamber 211=1 cubic meter
Pressure of ammonia vapor in chamber 211=6.15 bars
Pressure of ammonia vapor in chamber 213=15.54 bars
W=1 cubic meter×(15.54−6.15) bars=1 cubic meter×9.39 bars=9.39 cubic meter×bar
The work required for pumping a given quantity of ammonia (NH3) from one pressure to another is directly related to its specific volume as described earlier. Therefore, comparatively speaking, the work required for pumping a certain quantity of NH3 in the form of a gas is significantly greater than pumping the same quantity of NH3 in the form of a liquid.
The work required for pumping 1 Cubic Meter of NH3 vapor from chamber 211 to chamber 213 using the conventional method is 9.39 Cubic Meter×bar as determined above. The conventional method requires pumping NH3 in the form of a vapor. The NH3 vapor, having a much higher specific volume than that of NH3 liquid, requires significantly much more energy.
In the mechanical advantage system, the work of pumping the vapor from chamber 211 to chamber 212, and ultimately condensing it in chamber 213, is achieved by the boiling of liquid NH3 in chambers 211 and 212 and the condensing of NH3 vapor in chamber 213. Although work is necessary to return NH3 in the form of a liquid back into chamber 211 and 212, the advantage is that liquid NH3, having a much lower specific volume, requires less work than pumping NH3 vapor. As determined earlier, the conventional method of pumping ammonia vapor requires 9.39 Cubic Meter×Bar of work per one kilogram of ammonia, while the mechanical leverage advantage method requires only 0.231 Cubic Meter×Bar for the return of the liquid ammonia to its original state. It follows that, the mechanical advantage system requires 40.64 times (9.39/0.231=40.64) less energy than the conventional method. That's a very significant energy saving advantage.
By increasing the area of second piston 422 relative to first piston 421, the pressure difference between second chamber 412 and third chamber 413 may be decreased. Consequently, there is a decreased temperature difference between the points at which the NH3 refrigerant boils in chamber 412 and condenses in chamber 413. This is a valuable concept, in that it also lowers the temperature at which the NH3 refrigerant will boil in chamber 412. This is especially valuable on days with diminished sunlight and when the temperature of the attic is not sufficient to power the system.
For exemplification purposes, let's assume that the area of second piston 422 is increased to be 6 times greater than the area of first piston 421. This means that the area of second piston 422 in
(P2−P1)×A1=(P2−P3)×A2
(P2−6.15) bar=(P2−15.54)bar×6;
At a pressure of 17.41 bars, the boiling point of NH3 in second chamber 412 is approximately 112 degrees F. Thus, the increased (i.e., double) area of piston 422 lowered the required temperature of second chamber 412 from 122 degrees F. to 112 degrees F. This means that at this considerably lower attic temperature, the system still remains functional.
During hot and sunny days, the temperature of the attic of a house would normally reach 122 degrees F. However, second chamber 412, at this temperature level, absorbs heat from the attic at a more rapid rate and will maintain the attic cooler, closer to the range of 112 degrees F., and cooler attic spaces translate to cooler living spaces. Additionally, the excess heat in the attic may be converted into energy as discussed in the following section.
The parameters of the system can be changed to make the system run without any input of energy or even to create a surplus of energy. The change in parameters that would produce a surplus of energy is that which makes F2, the force acting on second piston 422, larger than F1, the force acting on first piston 421. This may be achieved by, for example, increasing the pressure/temperature of chamber 412 or increasing the surface area of piston 422 with respect to piston 421. This conclusion may be deducted from the following formulas:
Force 1<Force 2, or
(P2−P1)×A1<(P2−P3)×A2
For example, if starting with the same parameters for the system in
If, for example, A1 is 1 square inch and the area A2 is increased to 6 times A1, it follows that:
(20.33−6.15) Bar×1 sq. inches<(20.33−15.54) Bar (6 sq. inches), or
14.18 Bar (sq. inches)<4.79 Bar (6 sq. inches), or
14.18 Bar (sq. inches)<28.74 Bar (sq. inches);
Because with each stroke both pistons 421 and 422 travel the same distance (e.g., 1 foot or 12 inches), then:
Work 1=14.18 Bar (12 inches) and Work 2=28.74 Bar (12 inches), or
Work 1=170.16 Bar×Cubic inches, and Work 2=344.88 Bar×Cubic inches
From the above, it may be deducted that, for example, by increasing the surface area of piston 422 from 2.97 square inches to 6 square inches, a work surplus of 174.72 (344.88−170.16) Bar×Cubic inches is obtained. This work surplus may be used to generate electricity by coupling the system to a generator.
One of ordinary skills in the art would recognize that the system may be configured to have a fixed (i.e., unchangeable) ratio or a flexible (i.e., changeable) ratio between the areas of second piston 422 and first piston 421 or between the work they perform. When the system is configured with a fixed ratio, it may be preferred to use from the start an “oversized” system having a relatively larger ratio than the ratio determined as needed for the system to be functional, given the estimated ambient temperature for second chamber 412 (e.g., attic temperature). By doing so, it may be ensured that the system will still function should the ambient temperature drop below the estimated level. Furthermore, as explained earlier, during hot days, an “oversized” system may convert any work surplus in electricity.
The system may also be configured to have the flexibility to adjust the ratio as needed in order to make the system still functional during a drop in the ambient temperature or to make the system generate electricity. In one example, this may be achieved by using a variable gear link between first piston 421 and second piston 422 in order to change the distance traveled by, for example, second piston 422, and therefore, the volume of vapor displaced per stroke by pistons 421, 422, and hence, the ratio between the work performed by the two pistons. In another example, a cluster of a plurality (i.e., two or more) of first pistons and/or second (i.e., larger) pistons may be used, with the system being capable to engage and disengage pistons as necessary, to achieve the desired ratio at given temperature/pressure levels.
If the temperature in the living area is adequate, the cooling portion of the system may be disengaged by bypassing first chamber (e.g., 211 or 411), thus making the system work solely to generate electricity.
Let's assume that the surface area of the piston 522 is 6 square inches and each stroke of the piston 522 travels 12 inches. Then, from
Work=Difference in Pressure×Volume, it results that,
Work Gained is: (20.33−15.54) bars×6 sq. inches×12 inches, or
4.79 bars (72 cubic inches), or
344.88 bar×cubic inches
From the formula, Force=(P1−P2)×A, the force exerted on piston 522 may be calculated as follows:
F=(20.33−15.54) bars×6 sq. inches, or
F=4.79 bars×6 sq. inches, or
F=14.6 psi/bar×4.79 bars×(6 sq. inches), or
F=419.6 lbs.
An electrical generator apparatus 570 may be connected to the shaft 580 of the piston 522 to captures the mechanical energy produced by the system and convert it in electrical energy. The generator apparatus 570 may be in the form of a coil encasing the shaft 580 of the piston 522 while the encased portion of the shaft 580 may be compared to a magnet for inducing magnetic flux as the shaft oscillates back and forth (i.e., left and right in
As shown in
One of ordinary skills in the art would recognize that a system may be built to completely miss first chamber and first piston, to be used, as described above, solely for the purpose of generating useful work and/or electricity. Such a system would not depart from the scope of the present invention.
To compensate for the lower than adequate ambient heat available to second chamber 712, in addition to increasing the surface area ratio of second piston 722 relative to first piston 721, as earlier described, external augmenting energy may be used, as described below. The two solutions may be used separately or in combination.
In
Let's assume that, while all other parameters are the same as in
One of ordinary skills in the art would recognize that forth chamber 714 may be eliminated from the system's configuration without departing from the scope of the invention. The compressor 743 may be configured to alternately pump ammonia vapor from second chamber 712 directly into left side 715a (i.e., third sub-chamber) and right side 715b (i.e., fourth sub-chamber) of second cylinder 715 until the desired pressure level is achieved directly in those spaces.
It should be noted that at 111 degrees F. the pressure (P2) of the ammonia vapor in second chamber 712 is 17.34 bars. The following is the calculation for the pressure (P4) of fourth chamber 714 required to maintain the system in equilibrium and third chamber 713 unchanged at 104 degrees F. and a pressure (P3) of 15.54 bars:
The use of a compressor requires the input of external energy. However, the energy required is much less than that required by conventional air conditioning systems. In the mechanical leverage system, with the exception of the relatively insignificant amount of energy required to pump liquid ammonia from third chamber 713 to second chamber 712, as described earlier under
To illustrate, let's assume that the stroke for each piston for both the conventional and mechanical leverage system travels 1 meter. A rough estimate of work and comparison is as follows:
Conventional System: W=(6.14−15.54) bar×CubicMeter=9.4 bar×CubicMeter
Mechanical Leverage: W=(19.32−17.34) bar×A2×1 meter;
If, for example, the temperature of chamber 712 reaches 114.8 degrees F., at this temperature the pressure of NH3 vapor is 18.30 bars. Using the same calculations as above, it can be determined that the mechanical advantage system is using 52% less energy than the conventional system.
As previously described the polarity of pressure is reversed by the action of the valves. By alternating the opening and closing of valves 760a and 760b, the pistons will oscillate back and forth (i.e., left and right). Again, as earlier described under FIG. 2., when the four valves 760b are closed and the four valves 760a are open, the two pistons 721, 722 move to the right. It should be noted that during this time the pressure levels of the ammonia vapor are identical in first chamber 711 and left side 714a (i.e., first sub-chamber) of cylinder 714 (6.15 bars), in the right side 714b (i.e., second sub-chamber) of cylinder 714 and second chamber 712 (17.34 bars), in fourth chamber 714 and left side 715a (i.e., third sub-chamber) of cylinder 715 (19.32 bars), and, in the right side 715b (i.e., fourth sub-chamber) of cylinder 715 and third chamber 713 (15.54 bars).
As earlier described, when the two pistons 721, 722 reach the right end of their respective cylinders 714, 715, through, for example, an electronic or mechanical switch, the process is reversed by opening valves 760b and closing valves 760a, thus, causing the two pistons 721, 722 to move to the left. When the two pistons 721, 722 reach the left end of their respective cylinders 714, 715, valves 760b are closed and valves 760a are opened again, and the process repeats itself.
The system from
The mechanical advantage system is not limited to the use of ammonia (NH3) as the refrigerant. Other refrigerants may prove to be more effective and less expensive. Water may also be used as a refrigerant. The use of water as a refrigerant may be desirable because it has a high latent heat of vaporization and is environmentally safe. It is also inexpensive.
The pressure and the temperature levels of the refrigerant, as well as the values of other measurable characteristics of the system, such as the surface area of the pistons, are given for exemplification purposes only. One of ordinary skills in the art would recognize that alteration of these levels and values may be made without departing from the scope of the invention.
The mechanical leverage system may be reversed in the winter for use as heat pump for space heating applications. It may also be adapted for pool heating, hot water applications and/or refrigeration applications.
Some of the disadvantages of the use of a reciprocal piston mechanism as described above may be that it utilizes numerous valves with switching mechanisms for opening and closing valves at specific and synchronized times for each set of valves. Thus, in another embodiment, it may be advantageous to replace the reciprocal piston mechanism with rotary turbines, rotary pumps or scroll pumps. Rotary turbines do not require valves, hence, are simpler in design and are more reliable than reciprocal pumps. A two-cycle piston and cylinder may also be used since it also works without the use of valves. It should be noted that many other types of mechanical leverage systems may be used for this application and it is not the intent of this invention to be limited to the methods discussed here or elsewhere.
The same principles described above when referring to the reciprocal piston mechanisms (see description above referring to
Besides rotary turbines, rotary pumps, scroll pumps and the like may also be used for this application. For the purpose of this disclosure, the term turbine will be adopted, rather than pump, since pump pertains to compression and turbine may pertain to both compression and expansion.
It is well known that, at equilibrium:
Work 1=Work 2 (Eq. 1)
or,
(Difference in pressure 1)×Volume 1=(Difference in pressure 2)×Volume 2
Thus, in a mechanical advantage system, if the difference in vapor pressure acting on the first turbine is greater than the difference of pressure acting on the second turbine, then, at equilibrium, the volume of the first turbine is smaller than the volume of the second turbine. Since the vapor pressure of refrigerants are proportional to their temperature, the temperature differential associated with the first turbine having the lesser volume is greater than the temperature differential associated with the second turbine having the larger volume.
In this manner the size differential of the turbines or the mechanical advantage ratio of the turbines may be adjusted to fit the specific temperature parameters that are available in the environment and favorable to run, for example, an air conditioning system. In this example, the refrigerant used may be, for example, R-410A.
The schematic view and an exemplary set of parameters of a mechanical advantage system using turbines and R-410A as refrigerant are depicted and illustrated in
Chart 1
At equilibrium, Force 1=Force 2 (Eq. 2); F=P×A, thus, at equilibrium, the difference of pressure acting upon the internal surface area or vanes of the two turbines may be expressed as follows:
(P2−P1)×A1=(P2−P3)×A2
If A1=1 Unit (e.g., 1 square foot), then:
(364.1−170.7) psi×1=(364.1−339.9) psi×A2; or
193.4=24.2×A2; thus, A2=7.99
Hence, in this scenario, the surface area of the vanes (A2) of turbine D (see
It is well known that Work may be expressed as P1×V1=P2×V2, and that the ratio of the surface area of the vanes of the turbines, A2/A1, is proportional to the ratio of volume displacements of the turbines (A2/A1 is proportional to V2/V1). Hence, the greater the ratio of the surface areas of the vanes in the turbines (A2/A1), the greater the ratio of volume of displacement between turbine D and turbine C. Thus, the greater the mechanical advantage produced by the turbines, and thus, the system.
Referring now to
Chamber 2 (i.e., second chamber) 1012 may contain R410-A refrigerant at a pressure of 364.1 psi. The refrigerant at this pressure will require a temperature of 110 degrees F. to boil. The resultant increase in vapor pressure due to boiling of the refrigerant has a pushing force on both turbine C and turbine D. However, since turbine D displaces a greater volume of vapor than turbine C, the pushing force exerted on turbine D is greater than that of turbine C. Heat may be acquired from the ambient space of, for example, the attic of a house or other spaces where chamber 1012 is installed. Additionally, heat may be received from other sources such as solar panels or reflectors, if needed. It should be apparent that the heat source (e.g., the attic of a house) has to have a temperature higher than 110 F (e.g., 120 F as shown in
Chamber 3 (i.e., third chamber) 1013 acts as a condenser and may contain R410-A refrigerant at a pressure of 339.9 psi and a temperature of 105 degrees F. Because of the temperature difference, the R410-A vapor will condense, releasing heat into the cooler (e.g., 95 F as shown in
It should be noted that the pressure/temperature difference between chamber 1012 and chamber 1013 may be narrower if the mechanical advantage ratio between turbines D and C is increased. The mechanical advantage ratio between turbines D and C may be increased by designing the system from the start so that it has a higher mechanical advantage ratio, or, by configuring the system so that the ratio is adjustable, by, for example, changing (i.e., increase or decrease) the gear ratio between the two turbines to compensate for the change (i.e., decrease or increase, respectively) in the pressure/temperature difference between chamber 1012 and chamber 1013. The narrowing of the necessary pressure/temperature difference makes it possible for the system to absorb heat and expel heat within the temperature ranges found in the environment. Thus, enabling the refrigerant in chamber 1012 to boil and subsequently condense in chamber 1013. Environmental temperatures are invariably uncontrollable and it becomes necessary to adjust the mechanical advantage ratio between turbine D and turbine C to adapt the leverage/advantage system to work within these parameters.
Thus, chamber 1011 acts in the system as an evaporator, chamber 1012 also acts as an evaporator and a heat collector and chamber 1013 acts as a condenser. The three interconnected chambers may be placed at different locations or may be within close proximity of each other, depending on the application. For example, chamber 1011 (the evaporator) may be placed inside the living area of a house. Chamber 1012 (the heat collector) may placed in the attic of a house. Chamber 1013 (the condenser) may be placed outside of a house. The forces exerted by the actions of turbine C and turbine D are interconnected. In this example the turbines are interconnected by means of an axle 1071. However the interconnection may be accomplished by other means such as belts, gears, pulleys, and the like.
It should be apparent that the fluid refrigerant, whether in gas-phase or liquid-phase, is transferred to the various chambers by tubing.
It will be understood by one of ordinate skills in the art that each of the three chambers will tend to reach equilibrium with one another, as changes in temperature occur. Either by the process of boiling or condensing, each chamber will strive to maintain vapor pressures corresponding to their respective temperatures and saturation levels. The boiling and condensing of the refrigerant creates a pushing and pulling force on the turbines and drives the system forward. The chief driving force of the system is the increase pressure derived from the refrigerant boiling in chamber 1012 and the decrease in pressure derived from the refrigerant condensing in chamber 1013. The difference in the two pressures acts upon turbine D.
The processes that have been described herein are similar to that of a Rankine cycle process, in that the force exerted on turbine D is that of a typical Rankine cycle, and that the force exerted on turbine C is that of a Rankine cycle in reverse powered by the leveraged energy generated by turbine D.
Typically there are four processes in the Rankine cycle, each changing the state of the working fluid:
The condensed liquid refrigerator in chamber 1013 must be recycled back into chamber 1011 and chamber 1012 in proportion to their original amounts given off as vapor. Input of work is required at turbine B to pump the liquid refrigerator from chamber 1013 back into chamber 1012, against a pressure of 24.2 psi (i.e., the difference between 364.1 psi in chamber 1012 and 339.9 psi in chamber 1013). However, work is gained at turbine A as 169.2 psi of liquid refrigerant pressure (i.e., the difference between 339.9 psi in chamber 1013 and 170.7 psi in chamber 1011) is released into chamber 1011.
The analysis of the net work expended and the comparison with a conventional air conditioning system is similar as described above when referring to the piston-based mechanical advantage system. Thus, as shown there, for the return of the refrigerant, the mechanical advantage system consumes several times less work than a conventional air conditioning system, and that's a significant increase in energy consumption efficiency offered by the mechanical advantage system described herein.
It should be apparent that a counter resistance of 169.2 psi at turbine A is necessary to keep the system in equilibrium.
In the following discussion referring to
In the event that heat from the sun, collected for example from the attic of a house, is insufficient to raise the temperature level of the refrigerant in the second chamber (1112 in
Assuming that the outside temperature is 95 F (i.e., around chamber 1113) and the temperature of chamber 1112 only reaches 103 F. At this level, the temperature differential would not be sufficient to allow the system to work properly. To overcome the deficiency, external energy provided by motor E is applied to the system in order for the system to remain in function.
The following is the calculation for the work deficiency when the pressure of the refrigerant in chamber 1112 (
At 103 F the vapor pressure of R410A is 355 psi.
It is known that: Work 1=Work 2, or P1V1=P2V2, or, (P2−P1)×V1=(P2−P3)×V2.
We will assume that turbine D displaces 8 times more volume than turbine C per each revolution of each turbine as described earlier. Then, if V1=1 cubic inch (in), V2=8 cubic in. Thus, (355−170.7) psi (V1)=(355−339.9) psi (V2), or 184.3≢15.1(8), or 184.3>120.8.
Subtracting the expansion side from the compression side of the equation the result is 63.5 psi cubic in., or 34.4% deficiency of work ((184.3−120.8) psi. cubic in.=63.5 psi. cubic in.; 63.5/184=0.344=34.4%).
Thus, the net work needed to supplement the system is 63.5 psi cubic in. or 34.4%. This is a superior advantage offered by the mechanical leverage system. In the mechanical leverage system, external energy is only required to boost the system by 63.5 psi cubic in. as opposed to the conventional air conditioning method that would require 184.3 psi cubic in. of work, pumping vapor from 170.7 psi cubic in. to 355 psi cubic in.
When the augmenting work/energy is applied, for example, by an electric motor E, to either the compressor C or pneumatic motor D, the pressure in chamber 1113 is increased favoring condensing of the refrigerant and causing heat to be expelled to the outside ambient air. The pressure in chamber 1111 is decreased favoring evaporation of the refrigerant causing heat to be absorbed from the inside of the living space. The pressure of chamber 1112 is increased by chamber 1111 and simultaneously decreased by chamber 1113. However, chamber 1111 increases the pressure of chamber 1112 by a 1 part portion by volume, while chamber 1113 decreases the pressure of chamber 1112 by a portion of 8 parts by volume. This ratio is determined by the mechanical advantage factor between the displacement of the volume of vapor between the compressor C and the pneumatic motor D as described earlier. Thus, the overall pressure of chamber 1112 is decreased. Consequently, the temperature at which the refrigerant in chamber 1112 boils is also decreased, favoring increased absorption of heat from the attic. Thus, the system remains functional and efficient even at a lower temperature level in chamber 1112 (103 F in this example).
Energy from the Attic Harnessed and Mechanically Leveraged
In another embodiment, when there is a surplus of energy from the system, the first chamber (not shown in
The energy potential between the pressure difference of chamber 1212 and chamber 1213 is harnessed to the pneumatic motor D and is leveraged to actuate an electrical generator G. Thus, the system may convert the excess heat from the attic of a house into electrical energy. The energy produced may be stored in batteries.
In another embodiment, as shown in
A dispensary of compressed air may be placed within the house or garage, or the like, and may be used to refill portable canisters. The canisters filled with compressed air may be fitted to run air tools. Pneumatic equipment have less movable parts, and thus, are more reliable. They are also more convenient to use and less expensive to manufacture. These devices may include chain saws, lawn mowers, vacuum cleaners, garbage disposals, scooters, mopeds, and so on.
Work 1=Work 2, or
(P4−P0)V1=(P2−P3)V2
As in the previous applications described above, V1 equals one unit and V2 equals 8 units for the mechanical advantage system described herein for illustration purposes. Thus, the mechanical advantage is 1:8. Using similar parameters as in the previous air conditioning application described above, we have:
(P4−1 Atm.) V1=(P2−P3) V2, where P4 is the pressure in tank 1314; this means that:
(P4−14.7) psi cubic in.=(364.1−339.9) psi cubic in. (V2), or
(P4−14.7) psi cubic in.=24.2 psi (8 cubic in.); thus,
P4=193.4 psi+14.7 psi; or
P4=208.1 psi, where P0 is the outside atmospheric pressure, P2 is the pressure in chamber 1312, P3 is the pressure in chamber 1313 and P4 is the pressure in tank 1314.
It should be noted that the energy derived from the pneumatic motor D may also be directly leveraged to run the compressor of a conventional air conditioner. Alternatively, a conventional air conditioner may be run by the compressed air or electricity generated from the system obtained as described above.
Similarly as described earlier, the condensed liquid refrigerant in chamber 1313 must be recycled back to chamber 1312 in proportion to its original amount given off as vapor. Again, input of work is required at turbine B to pump liquid refrigerant from chamber 1313 into chamber 1312, against a pressure of 24.2 psi.
In still another embodiment, the work generated from the pneumatic motor D may be leveraged to run a heat pump as shown in
In this embodiment, chambers 1411 and 1413 act as condensers and chamber 1412 as evaporator. The vapor generated in chamber 1412 is preferably leveraged to a higher pressure, and thus, a higher temperature in chamber 1411. Heat is conducted and transferred, from the condensing vapor in chamber 1411 to the water to be heated.
Referring now to
Using a 4.5:1 mechanical advantage, the leveraged pressure is 474 psi and the temperature is 130 F as it will be shown and derived below. The incoming cool water 1445 is then piped through the 130 F vapor chamber 1411. As the high pressure heated vapor comes into contact with the piping containing the cool water, heat is transferred by the condensing vapor and is conducted through the piping and heats the water. Thus, hot water 1446 is obtained. The longer the incoming water travels through the conducting tube and absorbing heat from the condensing vapor, such as by passing the water through a spiral, or coils, its temperature becomes closer to that of the vapor in chamber 1411 (i.e., 130 F).
Thus, chamber 1411 acts as a condenser.
The 4.5:1 mechanical advantage ratio is derived as follows:
Work 1=Work 2, or, P1V1=P2V2; or, (P1−P2)×V1=(P2−P3)×V2, wherein P1 is the pressure in tank 1411, P2 is the pressure in tank 1412, P3 is the pressure in tank 1413.
If V1 equals 1 unit, then: (474−364.1) psi cubic in.=(364.1−339.9) V2, or, 109.9 psi cubic in.=24.2 psi V2. Thus, V2=4.5 cubic in.
As described earlier, also in this embodiment, the condensed liquid refrigerant in chamber 1413 and chamber 1411 must be recycled to chamber 1412 in proportion to its original amount given off as vapor. Input of work is required at turbine B to pump R-140A liquid from chamber 1413 into chamber 1412, against a pressure of 24.2 psi. However, here also, work is gained at turbine A as approximately 110 psi of liquid-phase refrigerant pressure (i.e., 474 psi in chamber 1411 minus 364.1 psi from chamber 1412) is released from chamber 1411 into chamber 1412. A counter resistance of 110 psi at turbine A is necessary to keep the system in equilibrium and release as needed.
If the same pneumatic motor D is being used for the water heating system, that is being used for the air conditioning system, having a mechanical advantage of 1:8, then the compressor C of the water heating system in
Mechanical advantage=V2/V1
If v2=8 cubic in.; then we have 4.5=8V1; thus, V1=1.77 cubic in.
It should be noted that the heat pump application described above would similarly work with the piston-based mechanical advantage system described earlier in this disclosure. It should also be noted that whether turbines, pistons or the like are used by the system, the heat pump aspect as described above may be used for other heating applications such as the heating of a house.
Referring now to
Additionally, alternative methods of implementing energy augmentation in mechanical advantage systems used in air conditioning will be described when referring particularly to
As previously discussed, heat may be obtained from the attic space, or other sources, and converted into useful energy. A mechanical advantage/leverage system used in conjunction with a refrigerant may derive energy from the temperature differences between the attic space and the outside ambient air. This energy may then be leveraged by the mechanical advantage system to run an air conditioning system for example.
Again, in the reciprocal piston system, two pistons may be interconnected to one other and actuated by the push/ pull action of the refrigerant as it vaporizes and condenses. For the system to create mechanical leverage, the surface area of the first piston (1521;
As stated before, it is well established that: (Difference in pressure 1)×Area 1=(Difference in pressure 2)×Area 2. This equation is central to the mechanical leverage system. From this equation it may be deducted that, if the difference in vapor pressure acting on the first piston is larger than the difference of pressure acting on the second piston, then the surface area of the first piston is smaller than the surface area of the second piston. Since the vapor pressure of refrigerants is proportional to their temperature, the temperature differential associated with the first piston, having the smaller surface area, is greater than the temperature differential associated with the second piston, having the larger surface area. Furthermore, increasing the surface area of the second piston in relation to the first piston decreases the pressure/temperature difference necessary to act on the second piston, thus, making it possible for the system to work within the temperature ranges found within the environment (e.g., attic temperature and outside temperature).
As stated before, the second chamber (1512 in
Hence, the driving force acting on the second piston is the pressure difference between second chamber 1512 and third chamber 1513. The energy acting on the second, larger piston 1522 is communicated to a first, smaller piston 1521. In this example, the energy exerted on the second piston is leveraged and stepped up to a mechanical advantage of 1/3.7, as it will shown/derived below. The stepped up force in turn drives the smaller, first piston 1521, which acts as a compressor. The compressor draws refrigerant gas from first chamber 1511, resulting in a lower pressure therein and causing the refrigerant to boil and absorb heat from the surrounding area (e.g., the living area of a home). As shown in
It should be noted that the mechanical leverage system depicted in
The following chart (Chart 2) relates to the parameters used in
The following are the calculations derived to determine the ratio of the surface areas between first piston 1521/1621 versus second piston 1522/1622, and thus, the mechanical advantage ratio for the system:
It is known that Force (F)=Pressure (P)×Area (A); at equilibrium, the force acting on first piston is equal with the force acting on second piston, or (P3−P1)×A1=(P2−P3)×A2, where A1 and A2 are the surface areas of first and second piston, respectively. It follows that:
(364.1−170.7) psi−1=(416.4−364.1) psi×A2
193.4 psi=52.3 psi×A2
Thus, the ratio of the surface area of the first piston versus the second piston is: 1/3.7. Hence, if A1=1 square inches then A2=3.7 square inches.
For the system to be in equilibrium, work performed by first piston (W1) should equal work performed by second piston (W2), or W1=W2. Specifically, W1 represents the amount of work necessary to compress a given amount of refrigerant vapor from first chamber 1511 to third chamber 1513, while W2 represents the amount of work gained from the expansion of refrigerant gas from second chamber 1512 to third chamber 1513.
The following example illustrates the use of the aforementioned parameters of second piston 1522 (
(P3−P1)×V1=(P2−P3)×V2
(364.1−170.7) psi (V1)=(416.4−364.1) psi (V2)
193.4=52.3(3.7)
As previously stated, work is required to compress the refrigerant gas from first chamber 1511 (1611 in
Thus, using the common condenser (second chamber) system and method depicted in
It should be noted that the other details regarding the operation of the system depicted in
Again, the refrigerant in first chamber 1511 (1611 in
Second chamber 1512 (1612 in
The third chamber 1513 (1613 in
As previously stated, when referring to the earlier described systems, the necessary pressure/temperature difference between second chamber 1512 and third chamber 1513, may be narrower if the mechanical leverage/advantage ratio of the system is increased. The mechanical advantage ratio between second piston 1522 and first piston 1521 may be increased by designing the system from the start so that it has a higher mechanical advantage ratio, or, by configuring the system so that the ratio is adjustable, by, for example, changing (i.e., increase or decrease) the gear ratio between the two pistons to compensate for the change (i.e., decrease or increase, respectively) in the pressure/temperature difference between chamber 1512 and chamber 1513. The narrowing of the necessary pressure/temperature difference makes it possible for the system to absorb heat and expel heat within the temperature ranges found in the environment. Thus, enabling the refrigerant in chamber 1512 to boil and subsequently condense in chamber 1513. Environmental temperatures are invariably uncontrollable and it becomes necessary to adjust the mechanical advantage ratio between piston 1522 and piston 1521 to adapt the leverage/advantage system to work within these parameters.
Again, chamber 1511 and chamber 1512 act as evaporators and chamber 1513 acts as a condenser. The three interconnected chambers may be placed at different locations or may be within close proximity of each other, depending on the application. The force exerted by the second piston 1522 (the expander), drives the first piston 1521, (the compressor). The refrigerant vapor is transferred to the various chambers by tubing. Chamber 1511 (the evaporator) may be placed, for example, inside the living area of a house. Chamber 1512 (the heat collector and evaporator) may be placed in the attic. Chamber 1513 (the condenser) may be placed, for example, outside of a house such that it may expel heat to the outside.
It should be noted again that each of the three chambers will tend to reach equilibrium with one another, as changes in temperature occur. Either by the process of boiling or condensing, each chamber will strive to maintain vapor pressures corresponding to their respective temperatures and saturation levels. The boiling and condensing of the refrigerant in each chamber changes the pressure in the chambers of the system and creates a pushing and pulling force on the expander (1522) and compressor (1521) pistons and drives the system forward.
The condensed liquid refrigerant in chamber 1513 must be recycled back into chamber 1511 and chamber 1512 in proportion to their original amounts given off as vapor. Input of work is required at turbine 1542 to pump liquid refrigerant from chamber 1513 into chamber 1512, against a pressure of 52.3 psi. However, work is gained at turbine 1541 as 193.4 psi (i.e., (364.1−170.7) psi) of liquid refrigerant pressure is released from chamber 1513 into chamber 1511. A counter resistance of 193.4 psi cubic inch at turbine 1541 is necessary to keep the system in equilibrium.
It should be noted that the preceding discussion referring to
In another embodiment, referring to
Additionally, as previously described when referring to
Furthermore, the embodiments of
Again, the system may be designed with a mechanical advantage ratio that is selected based on, among other factors (e.g., the type of refrigerant used), the expected temperature differentials available in the environment where the system will be used. For example, systems with greater mechanical ratio will generally be needed in cooler climates. Moreover, as explained earlier, the system may be designed such that it is capable of adjusting its mechanical ratio (e.g., by changing the gear ratio between the two pistons) so that the same system may be used in different climates, and/or, that the system operates properly in a given climate even though, as naturally expected, the temperature differentials will vary, for example from day to day. In addition to the mechanical ratio adjustability feature, the system may be equipped with augmentation feature(s) as earlier described and as specifically exemplified and described below when referring to
Referring now to
For exemplification purposes, let's assume that the outside temperature is 95 F and the temperature of chamber 1712 only reaches 115 F. At this level, the temperature differential would not be sufficient to allow the system to work properly. To overcome the deficiency, external energy is applied to the system. In this first example, a compressor 1743 (
The following chart (Chart 3) relates to the parameters used in
What follows is the calculation for the work deficiency when the pressure in chamber 1712 only reaches 389.6 psi, (designated as P4), at 115 F, rather than 416.4 at 120 F, and thus, the additional, external work needed to maintain the system in equilibrium.
Thus, there is a 99.1/193.4=51.2% pressure deficiency, which will need to be compensated by compressor 1743.
In a second example, a compressor 1844 (see
(P5−P3)V1=(P4−P3)V2
(364.1−P5) psi=(389.6−364.1)psi×3.7
364.1−P5=25.5×3.7 psi
364.1−P5=94.3
Thus, if the pressure in chamber 1 is 170.7 psi, then an augmentation of 99.05 psi, using compressor 1844 will be necessary to run the system ((269.75−170.7) psi=99.05 psi). Using the conventional method of air conditioning, as shown in the above derivation (when referring to
In a third example of augmentation depicted in
(P6−P3)V1=(P4−P3)V2
(P6−170.7) psi=(389.6−364.1) psi×3.7
P6−170.7 psi=25.5×3.7 psi
P6−170.7=94.3
Thus, if the pressure in chamber 1913 is 364.1 psi, then an augmentation of 99.1 psi, using compressor 1945, will be necessary to maintain the system in equilibrium ((364.1−265) psi=99.1 psi). Again, to compress the same amount of vapor, using the conventional method of air conditioning, work of 193.4 psi. cubic inches is required to compress vapor from chamber 1911 to chamber 1913. In the mechanical leverage system, external energy is only required to boost the work by a quantity of 99.1 psi cubic in. or 51.2% of the work normally needed by conventional air conditioning (99.1/193.4=51.2%).
In a fourth example of augmentation (see
The following is a calculation of the pressure and work deficiency when the temperature in chamber 2012 only reaches 115 F for this system (all other parameters being the same as above).
By subtracting the expansion side of the equation from the compression side of the equation, we have 99.05 psi. cubic in. This is the work required to compensate for the pressure (P7) deficiency, and thus, to augment the system to maintain it at equilibrium. Thus, P7=(193.4−94.35) psi=99.05 psi.
Hence, approximately 51.2% deficiency of work (99.05/193.4=0.512) has to be compensated by the device 2046. Again, using the conventional method of air conditioning, work of 193.4 psi. cubic inches is required to compress 1 cubic inch of vapor from chamber 2011 to chamber 2013. In the mechanical leverage system, external work is only required to boost the work applied to the shaft by an equivalence of work of 95.35 psi cubic in.
It should be noted that any of the preceding examples of augmentation may be utilized by itself or may be implemented in any other combination with one or more of the other examples described here. Also, these are merely examples of augmenting the system and are not intended to limit the general principle of augmentation for mechanical advantage systems.
In a mechanical advantage system that is in equilibrium, the area of the rectangle representing the compressive side 21c of the equation is equal to the rectangle representing the expansive side 21e of the equation, or 193.4 psi. cubic in=193.4 psi. cubic in, as derived earlier when referring to
It should be apparent that the mechanical advantage/leverage system described herein is a power source that may be employed for different applications such as air conditioning, power generation, compressed air generation, heating applications, and so on.
It should be noted that the terms “expander” and “pneumatic motor” are synonymous for the purpose of this disclosure. Also, the terms “fluid,” “working fluid” and “working medium” are synonymous for the purpose of this disclosure.
Again, the pressure and the temperature levels of the refrigerant, as well as the values of other measurable characteristics of the system, such as the surface area of the vanes of the turbines, were given herein for exemplification purposes only. One of ordinary skills in the art would recognize that alteration of these levels and values may be made without departing from the scope of the invention.
A great portion of the heat entering the living space of a house results from the direct rays of the sun. Due to the large surface areas of roofs, a great quantity of heat is absorbed from the direct exposure to the sun. Consequently, attic temperatures can reach substantially higher temperatures than the outside ambient air. Presently, the attic space serves as a buffer between the heat absorbed by the roof and the heat that ultimately penetrates the living area of a house.
What follows is the description of a solar heat colleting system that captures and concentrates heat from the roof. The collected heat, in conjunction with a refrigerant, is then used to fuel a mechanical leverage system.
The captured heat may be absorbed by a refrigerant, in a heat exchange coil system, located in second chamber (e.g., 1512 in
In general, the greater the temperature differential between the heat capturing system and the outside ambient air, the greater the power generated by the mechanical leverage system. In this respect, it is advantageous to maximize the quantity of heat captured from the sun and concentrate its intensity. This may be achieved, for example, by confining and limiting the volume of air, to the space between the rafters of a roof, such that the quantity of air to be heated becomes less, thus, greater temperatures can be reached. This smaller volume of air, when heated, reaches greater temperatures that are normally reached in attic spaces where the entire attic space is heated.
A principal embodiment of the invention is to enclose the space between the rafters 2301 (see
Thus, when the rays from the sun heat the roof 2304, the heat from the roof then transfers into the canal system 2302 and warms the air between the rafters 2301. The heated air, within the canals 2302, rises by convection and is thus swept upward along the pitch of the roof towards the apex and ridge board 2305.
Again, the isolative panels 2403 are affixed and cover the lower portion of the rafters 2401. However, a space/opening 2406 of about 3 to 4 inches is left open before reaching the ridge board 2405 (See
As the main stream duct collects heated air from the tributary canals, it transports it to one end of the ridge line and the heated/warm air is passed through an evaporator box 2509 (see
Again, the warm air that has passed through the evaporator 2510 (see
The return conduit 2502a (see
Alternatively, the air may be rerouted back into the far/distal end 2507a (see
For purposes of illustration the roof sheathing has been removed in
Again, the enclosing bottom sections of the tributary canals system are comprised of panels 2403 (see
Again, the panels may be pre-manufactured at manageable lengths and widths to allow them to be cut and refitted end-to-end with the use of inserts. Cutting and rejoining the segments may achieve the desired lengths of the panels. As stated earlier, the panels are composed of a thermally insulative material, and preferably also of a fire retardant material.
It should be noted that the heat that would normally accumulate in the attic and ultimately penetrate the living space of a house is diverted into the evaporator box 2509 (
If the goal was solely to cool the attic space, vents may be opened to allow warm air to escape and the compressor portion or any other load of the system may be disengaged or made nonexistent. In this instance, the second chamber (1512 in
The greater the mechanical advantage ratio of the system, the greater the volume of refrigerant gas that is displaced from second chamber 1512, and the cooler the air in the heat collecting system becomes. Consequently, the lower temperatures of the tributary canals increases the rate of heat absorption from the sun and ultimately a greater quantity of total heat is absorbed (hence energy) into the system. The roofing material preferably should have the properties that readily absorbs and conducts heat. Materials of dark colors or materials composed of metal or glass are quite suitable.
The heat collecting system is especially useful with vaulted ceilings where attic space is limited. The principle of heat collecting canals may also be integrated in roofing tiles. The tiles may be configured to interlock with one another and the canals within each tile may be aligned as to allow the flow of heated air from one tile to the other and ultimately to a mainstream duct placed close to the ridge board as described above.
Another application of the heat collecting system is its utilization with sun-exposed walls. In this application portholes or tubing are placed in the fire stops between the outside wall and the interior wall of the building. Heated air is drawn from between the walls and fed into the mainstream duct. Furthermore, the same principle may be applied to extract heat from within double paned windows or any other heat source.
Although specific embodiments have been illustrated and described herein for the purpose of disclosing the preferred embodiments, someone of ordinary skills in the art will easily detect alternate embodiments and /or equivalent variations, which may be capable of achieving the same results, and which may be substituted for the specific embodiments illustrated and described herein without departing from the scope of the present invention. Therefore, the scope of this application is intended to cover alternate embodiments and /or equivalent variations of the specific embodiments illustrated and/or described herein. Hence, the scope of the present invention is defined by the accompanying claims and their equivalents. Furthermore, each and every claim is incorporated as further disclosure into the specification and the claims are embodiment(s) of the present invention.
This application is a continuation-in-part and claims the benefit of the now pending U.S. Non-provisional application Ser. No. 13/530,097 filed Jun. 21, 2012, which is a continuation in part of U.S. Non-provisional application Ser. No. 13/011,729 filed Jan. 21, 2011, which in turn claims the benefit of U.S. Provisional Application No. 61/336,465, filed Jan. 25, 2010. This application also claims the benefit of U.S. Provisional Application No. 61/572,435, filed Jul. 18, 2011 and U.S. Provisional Application No. 61/630,122, filed Dec. 6, 2011. All prior filed applications mentioned above are hereby incorporated by reference to the extent that they are not conflicting with the present application.
Number | Date | Country | |
---|---|---|---|
61336465 | Jan 2010 | US | |
61572435 | Jul 2011 | US | |
61630122 | Dec 2011 | US |
Number | Date | Country | |
---|---|---|---|
Parent | 13530097 | Jun 2012 | US |
Child | 13552599 | US | |
Parent | 13011729 | Jan 2011 | US |
Child | 13530097 | US |