EP2129977A1

EP2129977A1 - Method and apparatus for combining a heat pump cycle with a power cycle

Info

Publication number: EP2129977A1
Application number: EP07759002A
Authority: EP
Inventors: George Mahl, Iii
Original assignee: Individual
Current assignee: Individual
Priority date: 2007-03-21
Filing date: 2007-03-21
Publication date: 2009-12-09
Also published as: EP2129977A4; WO2008115236A1

Abstract

Method and apparatus for combining a heat pump cycle with a power cycle. The working fluid for the heat pump cycle will be different than that for the power cycle.

Description

TITLE

METHOD AND APPARATUS FOR COMBINING A HEAT PUMP CYCLE WITH A POWER CYCLE

INVENTOR: MAHL, George, III, a US citizen, of 7217 Westminster Drive, Harahan,

Louisiana 70123 CROSS-REFERENCE TO RELATED APPLICATIONS

The following applications are incorporated herein by reference: US Patent Application Serial No. 1 1/203,783, filed 15 August 2005: US Provisional Patent Application Serial No. 60/602,270, filed 16 August 2004; and US provisional Patent Application Serial No. 60/604,663, filed 26 August 2004.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT Not applicable

REFERENCE TO A "MICROFICHE APPENDIX

Not applicable BACKGROUND

1. Field The present invention relates to cycles. More particularly, the present invention relates to a method and apparatus for combining a power cycle with a refrigeration cycle or heat pump.

2. General Background

A general vapor power cycle can include a boiler, turbine, condenser and a pump. Figure 1 shows a general power cycle. From "a" to "b" subcooled fluid can be heated to the saturated fluid temperature in the boiler. From "b" to "c" saturated fluid can be vaporized in the boiler, producing saturated gas. From "c" to "d" a superheater option can be used to increase the fluid temperature while maintaining pressure. From

"d" to "e" vapor expands through a turbine and does work as it decreases in temperature, pressure, and quality. From "e" to "P vapor is liquified in the condenser.

From f to a liquid is brought up to the boiler pressure. The expansion process between states d and c is essentially adiabatic. Ideal turbine expansion also is isentropic.

The Carπot cycle is an ideal power cycle which is stated to set the maximum attainable work output from a power cycle or heat engine. Various property diagrams for a Carnot cycle are provided in Figures 2A through 2C. Figure 2 A shows a pressure- volume diagram. Figure 2B shows a temperature-entropy diagram. Figure 2C shows an enthalpy-entropy diagram. From "a" to "b" occurs isothermal expansion of a saturated fluid to a saturated gas. From "b" to "c" occurs isentropic expansion. From

"c" to "d" occurs isothermal condensation. From "d" to "a" occurs isentropic compression. The thermal efficiency of the entire cycle is calculated by the following formula:

Refrigeration cycles are essentially power cycles in reverse. Figure 3 is a schematic diagram of a refrigeration cycle. It is necessary to do work on the refrigerant in order to have it discharge energy, Q_n, to a high temperature sink. After discharging energy to the high temperature heat sink the refrigerant is expanded through an expansion valve to drop its temperature allowing it to absorb energy, Q₁ , from a low temperature heat source . A heat pump also operates on a refrigeration cycle. One difference between a refrigerator and a heat pump is the purpose of each. The refrigerator's main purpose is to cool a low temperature area and to reject the absorbed heat to a high temperature area. The heat pump's main puipose is to reject the absorbed heat to a high temperature area, having picked up that heat from a low temperature area. Heat pumps use energy more efficiently than resistance heaters. For each kilowatt of energy used by the compressor of a heat pump, one kilowatt of compression heat is produced plus heat picked up through a refrigeration effect. The refrigeration effect of the heat pump can vary from ten to as high as five hundred percent or higher of the energy input into the compressor. This refrigeration effect is dependent on the temperatures involved and fluid used. Up to this point it was believed that the Carnot cycle was the most efficient power cycle that could be used. However, this belief did not consider a refrigeration/heat pump cycle being combined with a power cycle. No one has used a refrigeration cycle or heat pump as a heat source in a power cycle.

While certain novel features of this invention shown and described below are pointed out in the annexed claims, the invention is not intended to be limited to the details specified, since a person of ordinary skill in the relevant art will understand that various omissions, modifications, substitutions and changes in the forms and details of the device illustrated and in its operation may be made without departing in any way from the spirit of the present invention. No feature of the invention is critical or essential unless it is expressly stated as being "critical" or "essential."

BRIEF SUMMARY

The apparatus of the present invention solves the problems confronted in the art in a simple and straightforward manner. What is provided is an original process for the removal and use of energy from the ambient environment, including air, water, or earth. This energy is removed in the form of mechanical motion such as work, which maybe used either directly or to drive electrical generators, or supply other energy needs.

In one embodiment the process can consist of a combined refrigeration/power cycle. A first media (Media No. 1) can be vaporized at ambient temperatures, compressed, and condensed at a higher temperature, T₁₁ in a first heat exchanger. This portion of the method and apparatus can be a cycle similar to conventional heat pumps. The refrigeration/heat pump cycle can be combined with a second cycle in which a second media (Media No.2) is vaporized at the higher temperature, T_(I. Energy can then be extracted from Media No. 2 by flowing it through a mechanical drive turbine or other engine, then condensing Media No. 2 at ambient temperature in the condenser. The heat pump cycle using Media No. 1 produces a quantity of available energy at T₅₁ equal to the energy of evaporation of Media No. 1 at ambient temperature plus the energy of compression of Media No. 1. Thus, the energy available at T_n compared to the input of mechanical energy is:

E @ T₁₁ = E Evap. + E Mech. Input The ratio of E @ T₁₁ to E Mechanical Input depends upon the thermodynamic properties of Media No. 1, the ambient temperature and condensation temperature, T_n at which the cycie is operating.

The second portion of this process is the cycle of Media No. 2. Media No. 2 is evaporated in Heat Exchanger No. 1 at T_n by the condensation of Media No. I . Media No. 2 is then passed through a turbine or other engine where mechanical energy is removed, then condensed at ambient temperature in the condenser. The energy of Media No. 2 available for transformation into mechanical energy is the difference of the energy of:

1. Heating, evaporating and superheating of Media No. 2 in the Heat Exchanger No. 3 , and: 2. The energy of condensation of Media No. 1 at ambient temperature in the condenser, or;

Available Energy = E (Heat Exchanger No. I) - E (Condensation at condenser).

The theoretical output of the process is then determined by the product of:

E (a), T_H of Cycle No. I and the per unit available energy of Cycle No. 2. E Mech. Input

If the media for Cycle No. 1 and Cycle No. 2 and operating temperatures are properly selected such that the ratio of

EJa^JT_n of Cycle No. 1 is maximized and the available energy of E Mech. Input

Cycle No. 2 is maximized, then the theoretical mechanical output to mechanical input ratio exceeds unity. Thus, there is a net flow of energy from the ambient environment, which is converted into mechanical energy. The drawings constitute a part of this specification and include exemplary embodiments to the invention, which may be embodied in various forms. BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

For a further understanding of the nature, objects, and advantages of the present invention, reference should be had to the following detailed description, read in conjunction with the following drawings, wherein like reference numerals denote like elements and wherein:

Figure 1 is a schematic diagram of a power cycle.

Figures 2A through 2C are schematic diagrams of various diagrams of the properties in a Carnot cycle.

Figure 3 is a schematic diagram of a refrigeration cycle. Figure 4 is a schematic diagram of a preferred embodiment of the invention. Figure 5 is a pressure - enthalpy diagram for Rl 3. Figure 6 is a pressure - enthalpy diagram for R600.

DETAILED DESCRIPTION

Detailed descriptions of one or more preferred embodiments are provided herein. It is to be understood, however, that the present invention may be embodied in various foπns. Therefore, specific details disclosed herein are not to be interpreted as limiting, but rather as a basis for the claims and as a representative basis for teaching one skilled in the art to employ the present invention in any appropriate system, structure or manner.

Figure 4 is a schematic diagram of a preferred embodiment 10. In this embodiment a heat pump cycle 20 is used as the heat source for a power cycle 30. Heat pump cycle 20 can comprise expansion valve 60, evaporator 70, compressor 40, and a condenser. The condenser can be heat exchanger 50. Power cycle 30 can comprise engine 80, condenser 90, pump 100, and a heat source or boiler. The heat source or boiler can also be heat exchanger 50. In heat pump cycle 20, a first media (Media No. I ) can be vaporized at ambient temperatures, compressed, and condensed at a higher temperature, T₁₁ in heat exchanger

50.

Heat pump cycle 20 is combined with a second cycle 30 in which a second media (Media No. 2) is vaporized at the higher temperature, T_H. Energy can then be extracted from Media No. 2 by flowing it through a mechanical drive turbine or other engine 80, then condensing Media No. 2 at ambient temperature in condenser 90.

Heat pump cycle 20 using Media No. 1 produces a quantity of available energy at T_n equal to the energy of evaporation of Media No. 1 at ambient temperature plus the energy of compression of Media No. 1. Thus, the energy available at X₁₁ compared to the input of mechanical energy is:

E @ T₁₁ = E Evap. + E Mech. Input The ratio of E @ T₁, to E Mechanical Input depends upon the thermodynamic properties of Media No. 1 , the ambient temperature and condensation temperature, T₁₅ at which the cycle is operating.

The second portion of this process is power cycle 30 using Media No. 2. Media No. 2 can be evaporated in heat exchanger 50 at T_H by the condensation of Media No. 1 of cycle 20. Media No. 2 is then passed through turbine or other engine 80 where mechanical energy is removed, then condensed at ambient temperature in condenser 90. The energy of Media No. 2 available for transformation into mechanical energy is the difference of the energy of: 1. Heating, evaporating and superheating of Media No.2 in heat exchanger

50, and:

2. The energy of condensation of Media No. 1 at ambient temperature in condenser 90, or;

Available Energy = E (heat exchanger 50) - E (Condensation at condenser 90). The theoretical output of overall process 10 is then determined by the product of:

E @ T_H of Cycle No. 1 (cycle 20) X the per unit available

E Mech. Input energy of Cycle No. 2. (cycle 30).

If the media for Cycle No. 1 and Cycle No. 2 and operating temperatures are properly

selected such that the ratio of EjgLXn of Cycle No. 1 (cycle 20) is maximized

E Mech. Input

and the available energy of Cycle No. 2(cycle 30) is maximized, then the theoretical mechanical output to mechanical input ratio exceeds unity for overall cycle 10. Thus, there is a net flow of energy from the ambient environment, which is converted into mechanical energy.

One example of a preferred embodiment 10 using specific fluids is shown in Figure 4. This system uses refrigerant No. Rl 1 as the media of Cycle No. 1 (cycle 20), evaporating at an ambient temperature of 70⁰F (21 .1 1⁰C) and condensing in heat exchanger 50 at 190⁰F (87.78⁰C). Refrigerant R600 is used in Cycle No. 2(cycle 30), evaporating in heat exchanger 50 and condensing at the ambient temperature of 70⁰F (21.1 1⁰C). Cycle 20 shows refrigerant entering expansion valve 60 at 70⁰F (21.1 1⁰C), at a pressure of 90 pounds per square inch (620.55 kiiopascals), and having a heat content of 22.4 BTUs per pound (52.1 kilojouies per kilogram). After passing through expansion valve 60 the refrigerant is at a pressure of 13.39 pounds per square inch (92.32 kiiopascals) and maintain a heat content of 22.4 BTUs per pound (52.1 kilojouies per kilogram). It should be noted that depending on the refrigerant used, an expansion turbine may be used in place of expansion valve 60 to enhance performance of the overall process. Next, the refrigerant enters evaporator 70. Fed into evaporator 70 can be water at 70⁰F (21.11⁰C) having a heat capacity of 78.3 BTUs per pound (182.13 kilojouies per kilogram)(or 166.2 BTUs per minute)(2.92 kilowatts). The refrigerant leaves evaporator 70 at 70⁰F (21.1 1⁰C), at a pressure of 13.39 pounds per square inch (92.32 kiiopascals), and having a heat content of 100.72 BTUs per pound (234.27 kilojouies per kilogram). Next the refrigerant is compressed by compressor 40 which can require an input energy of 142 BTUs per pound (330.29 kϋojoules per kilogram) (or 30.146 BTUs per minute)(0.5298 kilowatts). The refrigerant leaves compressor 40 at 200⁰F (93.33⁰C) , at a pressure of 90 pounds per square inch (620.55 kiiopascals), and having a heat content of 1 14.9 BTUs per pound (267.26 kilojouies per kilogram). Finally, the refrigerant passing through heat exchanger 50 where it absorbs heat and leaves at 70⁰F (21. ϊ 1⁰C), at a pressure of 90 pounds per square inch (620.55 kjlopascals), and having a heat content of 22.4 BTUs per pound (52.1 kilojouies per kilogram). The heat loss by the working fluid in heat exchanger 50 can be 92.5 BTUs per pound (215.16 kilojouies per kilogram) (or 196.37 BTUs per minute)(3.45 kilowatts).

Cycle 30 shows a working fluid entering engine 80 (which can be a turbine) at 190⁰F (87.78⁰C), at a pressure of 173.25 pounds per square inch, and having a heat content of 256.374 BTUs per pound (596.33 kilojouies per kilogram). Leaving engine 80 the working fluid can be at 70⁰F (21.3 1⁰C), at a pressure of 31.279 pounds per square inch (215.67 kiiopascals), and having a heat content of 217.017 BTUs per pound (504.782 kilojouies per kilogram). The mechanical output of engine 80 can be 39.357 BTUs per pound (91.544 kilojouies per kilogram) or 39.357 BTUs per minute (0.69 kilowatts). Next, the working fluid can enter condenser 90 and leave at 70⁰F (21.11⁰C), at a pressure of 31.279 pounds per square inch (215.67 kilopascals), and having a heat content of 59.867 BTUs per pound ( 139.251 kilojoules per kilogram). To achieve such a change in properties of the working fluid water at 70⁰F (21.1 1⁰C) can be fed through condenser 90 and exiting at 157.15 BTUs per pound (365.531 kilojoules per kilogram)(or 157.15 BTUs per minute)(2.76 kilowatts). Next, the working fluid is pumped by pump 100 and leaves at 70⁰F (21.1 1⁰C), at a pressure of 194.09 pounds per square inch (1 ,338.25 kilopascals), and having a heat content of 60.22 BTUs per pound (140.07 kilojoules per kilogram). The mechanical input to pump 300 can be 0.3618 BTUs per pound (0.842 kilojoules per kilogram) or 0.3618 BTUs per minute (0.00635 kilowatts). Next, the working fluid enters heat exchanger 50 and exits at 190⁰F (87.78⁰C), at a pressure of 173.25 pounds per square inch (1 ,394.56 kilopascals), and having a heat content of 256.374 BTUs per pound (596.326 kilojoules per kilogram). The heat gain for the working fluid entering heat exchanger 50 can be 196.154 BTUs per pound (456.254 kilojoules per kilogram) (or 196.154 BTUs per minute)(3.45 kilowatts).

The working fluid for cycle 20 can be Rl 1. The working fluid for cycle 30 can be R600. The ratios of flow rates for Rl 3 to R600 can be 2.123 to 1. For example, the flow rate of Rl 1 can be 2.123 pounds per minute and the flow rate of R600 can be 1 pound per minute. Figure 5 is a pressure - enthalpy diagram for Rl 1. Figure 6 is a pressure - enthalpy diagram for R600. In both Figures 5 and 6 pressure is on the y-axis and enthalpy is on the x-axis. Tables 1 A and 1 B list various thermophysical properties for Rl 1. Tables 2 A and 2B list various thermophysical properties for R600.

Table IA

Refrigerant 11 (Trichlorofluoromethaπe) Properties of Saturated Liquid and Saturated Vapor

Enthalpy,

Density, Volume, Entropy, Specific Heat e,, Velocity of Viscosity, Thermal Cond,

Temp,* Pressure, BtuΛb-°F ^' tb/ft¹ ft^Λ/lb ^βtu/lb Btu/Ib-°F Sounc Surface c./c l, fl/s lbJCl-h Btu/h- ft '⁰F Tension, Temp *

^«F psia Liquid Vapor Liquid Vapor Liquid Vapor Liquid Vapor Vapor Liquid Vapor Liquid Vapor Liquid Vapor dyne/cm

-166.85a 0,001 1 10.41 2423«. -24.922 73.32S -O.07OS5 0.26467 0.1005 J .1680 _ 352. _ _ __ -166.85

-160.0J) 0.002 109.93 14650. -23.1 16 74.019 -0.06474 0.25940 0.184C 0.1019 1 .1655 - 356. - - - - — -!6θ,00

-150.00 δ.003 109.23 7355.6 -21.267 75.045 -0,05867 0.25235 O.186C 0,1038 , 1620 3953. 361. 35.26 -150.00

-140.00 0,006 108,52 3882.0 -19.398 76.088 -0.05273 0.24597 0.1878 0,1058 .1588 3895. 366. — 34.44 -140.00

-130.00 0.012 107.81 2143.2 -17.51 1 77.149 -0,04692 0.24022 0.1894 0.1077 J .1558 3829. 371. - _ _ _ 33.63 -130,00

-120.00 0.022 107.09 1232,5 - I5.6 IO 78,226 -O.04123 0.23502 0.1909 0,1095 1 .1531 3758, 376. — _ 32,82 - 120.00

-1 10.00 0.037 106.37 735.62 -13.694 79-3 !8 -0.03568 0,23032 0.1922 0.1 1 14 .1506 3684, 381. - - - - 32.0! -1 10,00

-100.00 0,062 105.65 454,14 -11.767 80,425 -0.03024 0,22608 0.1933 0.1 133 , 1482 3609. 386, - _ _ 31.21 -100.00

-90.00 0, 100 104.92 289.15 -9,829 81.546 -0.02493 0.22225 0.1943 0.1 15! 1 .1461 3533. 391. - _ — 30.41 -90.00

-80.00 0.156 104.19 189.37 -7.880 82.681 -O.O I 973 0.2188O 0.1953 0. J 170 .1442 3457. 396. - - - 29.62 -80.00

-70,00 0.239 103.46 127.27 -5.923 83.827 -0,01464 0.21568 0,1962 0.1188 .1425 3382. 400. - - - 28.83 -70.00

-60.00 0.355 102.73 87.583 -3.957 84.986 -0.00966 0.21288 0.1970 0.1206 J410 3308. 405. - - - - 28.04 -60.00

-50.00 0,517 101.99 61.601 -1.983 86.155 -0.00478 ϋ.21036 0.1978 0.1225 .1396 3235. 409. — _ _ 27.26 -50.00

-40.00 0,738 101.25 44.203 O.OOO 87.335 0.00000 0.20810 0.1986 0.1243 .1384 3 :63. 4.4. - - - 26.49 -40.00

I -30.00 1,032 100.50 32.310 1.991 88.524 0.0046? 0.20608 0.1994 0.1262 .1374 3093. 418. — - - 25,72 -30.00

-20.00 1.419 99.75 24.022 3.989 89.721 0,00928 0.20427 U.2002 0.1280 , 1366 3024. 422. 1.889 0,0222 0.0595 - 24.95 -20.00 I

-10.00 1,918 99.00 18.143 5.997 90,927 0.01330 0.20267 0.201 ! 0,1298 J360 2955. 426, 1.782 0.0227 0.0587 - 24.19 -10,00

0.00 2,554 98.24 13.903 8.013 92.139 0.0t823 0.20124 0.2020 0, 1316 .1356 2888. 430. 1,678 0,0231 0.0579 - 23.43 0.00

5.00 2.931 97.86 12.233 9,024 92.747 0.02041 0.20059 0.2024 0.1325 .1354 2855. 432. 1.627 0.0233 0.0575 - 23.05 5.00

!0.OO 3.352 97.48 ! 0.798 10,038 93.357 0.02258 0.19998 0.2029 0.1334 .1354 2822. 433. 1.578 0.0236 0.0571 - 22.68 10.00

!5.OO 3.822 97.09 9.5606 1 1.054 93.967 0.02473 0.1994 ! 0.2033 O. S343 .1353 2789. 435. 1.529 0.0238 O.0567 - 22,30 15.00

20.00 4.343 90,71 8.4906 ] 2,072 94.579 0.02686 0.19887 0.2038 U.1352 ,1354 2757. 437. 1,482 0.0240 0.0563 - 21.93 20.00

25.00 4.920 96.32 . 7.5621 13.093 ys.192 0.02898 O.19S37 0.2043 0.136) .1355 2725. 438. 1.436 0.0243 0.0559 - 21.56 25.00

30.00 5.557 95.93 6,7536 14.1 17 95.806 0.03108 ϋ.19790 0.2048 0.1370 1.1356 2693. 440. 1.390 0,0245 0,0555 - 21.19 30.00

35-00 6.25? 95.54 6.0477 15,143 96.420 0.03316 0.19747 0,2053 0.1379 1.1358 2661. 442. 1.347 0.0247 0.0551 O.OO47O 20.82 35.00

40.00 7.03! 95. ! 4 5.42?4 16.172 97.035 0.03523 0, 19706 0,2059 0, 1388 1.1361 2629. 443. 1.304 0.0250 0.0548 0.00475 20,45 40.00

45.00 7.876 94,75 4.8863 17.203 97.650 0.03728 0.19668 0.2064 0.1397 1.1364 2598. 444. 1.262 0,0252 0.0544 0.00480 20.08 45.00

50.00 8.800 94.35 4.4080 18.238 98.265 0,03931 0.19633 0,2070 O. l4o6 1.1368 2567, 446. 1.222 0.0254 0,0540 0.00485 1972 50.00

55.00 9.809 93.95 3-9856 19.275 98.880 0,04134 0.19601 0.2075 0, 1415 1. S373 2536, 447. 1.183 0.0256 0.0536 0.00490 19.35 55.00

60.00 10.907 93.55 3.6116 20.315 99.495 0,04334 0.19571 0.2081 0.1424 U378 2505. 448. 1.145 0.0259 0.0532 0.00495 18.99 60,00

65.00 12.099 93.14 3.2795 21 ,358 100.109 0.04534 0.19543 0,2087 0.1433 U385 2474. 450. 1.109 0,0261 0.0528 0.00501 18.63 65.00

70.00 8,27 70.00

13.392 92.73 2.9841 22.405 100.723 0.04732 0.19518 0,2093 0.1442 1.1392 2444. 451. 1.073 ϋ.0264 0.0524 0.00506 1

74.67b 14.696 92.35 2.7369 23.386 101.297 ϋ.04956 U.19496 0.2099 U.145 ! 1.1599 2415. 452. 1.041 0.0266 0.0521 0,00511 17.94 74.67

75.00 14,790 92.33 2.7206 23,455 101.337 0.04928 0,19495 0.2100 0.1452 1.1400 2413. 452. 1.039 0.0266 0.0521 0.00512 π.91 75.00

O:O268 0.0517 0.00517 17.56 80.00

80.00 16.301 91.91 2,4851 24.507 101.949 0.05124 D.19473 O.2 SO6 O. S461 1.1409 2383. 453. 1,006

85.00 17.929 91.50 2,2741 25-564 102.560 0.05318 0,19454 0.2113 0,1470 1.1419 2353. 454. 0.974 0.0271 0,0513 0.00523 17,20 85.00 528 16.85 90.00

90.00 19.681 91.08 2.0846 26.624 £03-170 0,0551 ! 0.19437 0.21 19 0.1479 1.1429 2323. 455. 0,943 0,0273 0.0509 0,00 95.00 1441 21.563 90.66 1.9142 27.687 103.778 0.05703 0.19421 0.2126 0.1489 1. 2293. 456. 0.913 0.0276 0.0505 0.00534 16,49 95.00

^•lemoe ratures ire on the IT S-90 scale ϊ » triple point b • normal boiling pulni c - critical point

Table IB

Refrigerant II (Trichlorofluoromethane) Properties of Saturated Liquid and Saturated Vapor

Enthalpy, Entropy,

Density, Volume, Specific Heat c_p, Velocity of Viscosity, Therma ! Coπd, Ib-'F Surface

Temp/ Pressure, Blu/lb Btu/lb-°F lb/ft^J ft'/lb Btu/ Sound l, ft/s Ib_nZfVh

, c Jc, , BtuΛi- ft-°F Tension Temp,*

⁰F psia Liquid Vapor Liquid Vapor Liquid Vapor Liquid Vapor Vapor Liquid Vapor Liquid Vapor Liquid Vapor dyne/cm ⁰F

100.00 23J8! 90.23 1.7605 28.754 104.384 0.05894 0.19407 0.2 J 34 0.1498 1.1454 2263. 456, 0.884 0.0278 0,0502 O.OO54O 16.14 100.00

105.00 25,743 89.8! 1.6217 29.825 104,989 0.06083 0. 19394 0.2141 0, 1508 1.1468 2234. 457. 0.856 0.0281 0.0498 0.00546 15.79 105.00

110.00 28.053 89.38 1.4960 30.900 105.591 0.06272 0.19383 0.2149 0.1 518 1.1483 2204, 458. 0.829 0.0283 0,0494 0,00552 15.45 πo.oo

115.00 30,520 88,94 1.3821 31.978 106.191 0.06459 0.19374 0.2156 0.1528 1.1500 2174, 458, 0.804 0.0286 0.0490 0.00559 _ 1 15.00

120.00 33.150 88,5 J 1.2787 33.060 106,788 0,06646 0.19365 0.2164 0.1538 1.1517 2145. 459. ϋ.778 0.0288 0.0486^' 0.00565 ^' 120.00

125,00 35.950 88.07 1.1846 34.147 107,382 0.06832 0.19358 0,2172 0. 1548 1.1536 2 1 1 5. 459- 0.754 0.0291 0.0483 0.00572 125.00

130.00 38,926 87.62 1.0988 35.238 107.974 O.O7IM7 0.19352 0.2181 0.1558 1.1557 2086. 459. 0.731 ϋ.0293 0.0479 0.00578 - 130.00

! 35.00 42.087 87. ( 7 1.0205 36.333 108.562 0.07200 0.19346 0.2189 0. 1569 1.1579 2057. 459. 0.708 0.0296 0.0475 0.00585 135.00

140.00 45.439 86.72 0.9489 37.433 109.146 0.07383 0.19342 0.2198 0.1580 U602 2027. 459. 0.687 0.0299 0.0471 0,00592 - 140.00

145.00 48.989 86.26 0^,8833 38.537 109,727 0.07565 0. 19339 0.2207 0.1591 1.1628 1998. 460, 0.666 0.0302 0.0468 O.0O599 - 145,00

150.00 52,745 85.80 0.8232 39.646 1 10.304 0.07747 0.19336 0,2217 U.1602 1.1655 1969. 459. U.646 0.0304 0.0464 0.00606 - 150,00

160,00 60,905 84,86 0,7172 41.878 1 1 1.445 0.08107 0.19333 0.2236 0.1626 1.171 5 1910. 459. 0.607 0.0310 0.0456 0.00621 - 160.00

H¹ S 70,00 ^' 69.979 83.91 0.6273 44.130 1 12.566 0,08464 0.19333 0.2257 0.1650 Ϊ . S 783 1851. 458. 0.572 0.O316 0.0449 0.00637 - 170,00

O 180.00 80.030 82.93 0.5506 46.403 1 13.666 0.08819 0, 19334 0.2279 0, 1677 1. 1861 1793. 457, 0,539 0.0322 0.0442 0.00654 - 180,00 i 190.00 91.120 81 ,93 0.4849 48,699 1 14.743 0.09 * 7! 0.19337 0.2303 O. I7O5 1. 1950 1734. 456. 0.508 0.0328 0.0434 0,00671 - 190,00

200.00 103.3 1 80,90 0,4283 51.019 1 1 5.793 0.09521 O. J 934 I 0,2328 0.1735 1 ,2052 ϊ 675. 454. 0.479 0,0334 0.0427 0.00689 - 200.00

210.00 1 16,68 79.85 0.3793 53.364 1 16.815 0.09870 ϋ. 19344 0.2356 0.1768 1.2169 161 5. 451. 0.453 0.034 1 O,ϋ4 l9 0.00707 210.00

220.00 131.28 78,77 0.3367 55.736 1 17.805 0, 10216 0.19348 0,2385 0.1804 1 ,2302 1 555. 448. 0.428 0.0347 0,041 2 0.00727 - 22O.UO

230.00 147.18 77,65 0,2996 58.136 1 18.760 0, 10561 0. 19351 0.2418 0.1844 1.2456 1495. 445, 0.404 0.0354 0.0404 0,00748 - 230.00

240.00 164.46 76,50 0,2670 60.567 1 19.677 0.10905 0.19353 0.2453 0.1888 1.2634 1434. 441. 0.383 0.0362 0.0397 0.00769 - 240.00

Table 2 A

Refrigerant 600 (n-Bυtane) Properties of Saturated Liquid and Saturated Vapor

PresDensity, Yo.uvflti, Enthalpy, Entropy, Specific Heat c , Velocity of Viscosity, Thermal Cond,

Surface

Temp,* sure, ib/fl³ Btu/tb lϊtu/Ib ^•°F Btu/lb'°F fΛib c./c. Soiinc l. ft/s Btu/h ^•ft-°F Tension, Temp,*

T psia Liquid Vapor Liquid Vapor Liquid Vapor Liquid Vapor Vapor Liquid Vapor Liquid Vapor Liquid Vapor dyne/cm ⁰F

-!50.00 0.021 43.72 2680.0 -54,034 145.702 -0.14904 0.49595 0.4804 0.2930 1 J323 4976, 548, 1,945 0.0109 0.0991 0,00362 28.19 - 150.00

-140.00 0.038 4339 1536.9 -49.229 148.643 -0.13377 0.48522 0.4807 0.2971 Ϊ .13O4 4906, 556. 1.737 0.01 12 0.0967 0.00381 27.41 -140.00

-130.00 £.066 43,06 9t7.01 -44.419 15 1.622 -0.1 1895 0.47570 0.4815 0.3012 1.1286 4833. 564. 1.564 0.01 (5 0.0943 0,00399 26.64 - 130.00

-120.00 o.πo 42.74 567.05 -39.597 154.636 -0.10455 0.46728 0.4829 0.3055 U268 4757. 572. 1.416 0.01 18 0.0921 0.00419 25.87 -120.00

-1 10.00 0.178 42.41 362.20 -34.759 157.687 -0.09051 0.45985 0,4848 0.3099 1.1251 4678, 579. 1.290 0.012! 0.0901 0,00439 25.1 ! -πo.oo

-I0O.OO 0.278 42,08 238.26 -29.899 160.772 -0.07681 0.45332 0.4873 0.3145 1.1236 4597. 587. 1,182 0.0124 0.0881 0.00459 24,35 -100.00

-90.00 0.413 41.75 160.98 -25.01 1 163.890 -0.06340 0,44759 0.4903 0.3192 1 , 1221 4514, 594. 1.087 0.0127 0.0862 0,00480 23.59 -90.00

-SQ.00 0.626 41.41 1 1 1.45 -20.090 167.042 -0.05027 0,44261 0.4938 0.324! 1.1208 4428, 601. 1.003 0.0130 0,0843 0.00502 22,84 -80.00

-70.00 0.907 4 ! .08 78.895 -15.133 170.225 -0.03739 0.43829 0.4976 0.3292 1.5 196 4341. 608. 0.930 0.0133 0.0826 0.00524 22.10 -70.00

-60.00 1.285 40.74 56.999 -10.134 173,438 -0.02473 0,43458 0.5019 0.3344 1.1 185 4252. 614. 0.865 0.0136 0.0809 0.00547 21.36 -60.00

-50.00 1.786 40.40 41.955 -5.091 176.679 -O.0I 227 0.43143 0.5065 0.3399 1 , 1 177 4161. 620. 0.806 0.0139 0.0793 0.00571 20,63 -50.00

-40.00 2.438 40.06 31.414 0.000 179.946 0,00000 0.42878 0.5 H4 0.3456 1.1 170 4070. 626. 0.754 0.0143 0.0777 0.00595 19.90 -40.00

-30.00 3.273 39.7 i 23.893 5.142 183.238 0.012iO 0.42659 0.5165 0.3515 1.1 166 3977. 631. 0.706 0.0146 0.0762 0.0062! 19.18 -30.00

-20.00 4.327 39.36 18.436 10,337 186.552 0.02404 0.42483 0.521 'J 0.3576 U 163 3883. 637. 0,663 0.0149 0.0747 0.0O647 18,46 -20.00

-10.00 5.638 39.01 I 4.4 Ϊ6 Ϊ5.5S7 189.887 0.03583 0.42345 0.5275 0,3640 i .1 163 3788. 641. 0,623 0.0153 0.0733 0.00674 17.75 -10.00

0.00 7.251 38.66 1 1.410 20.896 193.240 0.04749 0.42242 0.5334 0.3706 1. 1 166 3693. 646. 0,587 0,0156 0.0719 0.0O70S 17.04 0.00

5,00 8.S84 38.48 t0.194 23.573 194,922 0.05328 0.42203 0.5364 0.3740 1.1 168 3645. 64S. 0.570 0.01 SS 0.0712 0.00716 16,69 5,00

10.00 9.2! I 38,30 9.1329 26.266 196,608 0.05903 0.42171 0.5394 0.3774 1.1 17 ! 3.W. 650. 0.554 0.0159 0.0705 0.00730 16.34 10.00

15.00 i 0.337 38, 12 8.2031 28.974 198.298 0.06475 0.42147 0.5426 0.3810 1 , 1 175 3549. 651. 0.539 0.0161 0.0698 0.00745 16.00 15.00

20.00 1 1,569 37,93 7,3863 31 .698 199.99) 0.07045 0.42130 0.5457 0.3845 1. I S80 3500. 653, 0.524 0.0163 0.0691 0.00760 15.65 20,00

25.00 12.914 37.75 6,6666 34.438 201.686 0.07612 0.421 19 0.5489 03882 1.1 I S5 345?.. 655. 0.509 0,0!65 0.0685 0.00775 1531 25.00

30.00 14.37& 37.56 6.0309 37.194 203.384 0.08176 0,421 15 0.5522 0.3919 1.1 19] 3403. 656, 0.495 0.Qi 66 0.0678 0.00790 14.96 30.00

31.03b 14.696 37.52 5.9090 37 765 203.735 0.08292 0.421 15 0.5528 0.3927 1.1 193 3393. 656. 0.492 0.0167 0.0677 0.00793 14.89 31.03

35.00 ! 5.969 37.38 5.4677 39.967 205.084 0.08738 0.421 17 0.5555 0.3957 U 198 3354. 657, 0.482 0.0168 0.0672 0.00806 14.62 35.00

40.00 17.693 37.19 4.9676 42.757 206.786 0.09297 0.42125 0.5588 0.399S 1.1206 3305. 659. 0.469 0.0170 0,0665 0.00822 14.28 40,00

45.00 59.559 37.00 4,5224 45.564 208.490 0.09854 0.42138 0.5622 0.4035 1. 1215 3256. 660. 0.456 0.0172 0.0659 0.00838 13.94 45.00

50,00 21,574 36.81 4.1251 48.389 210.194 0.10409 0.42156 0.5657 0,4074 1.1225 3207. 661. 0.444 0.0174 0.0652 0.00854 33-61 50.00

55.00 23.746 36.62^' 3.7697 51.231 21 1.899 0.10962 0.42180 0.5692 0.41 15 1.1236 3158. 661. 0,432 0.0176 0.0646 0.00871 13.27 55.00

60.00 26.081 36.42 3.4512 54,091 213.605 0.1 1513 0.42208 0.5728 0.4157 1.1248 3108. 662. 0.421 o.oπs 0,0639 0.00888 12.94 60.00

65.00 28.590 36.23 3, 1649 56.970 215,31 1 0. S 2062 0.42241 0.5764 0.4199 1.126! 3059. 662, 0.410 0,0179 0.0633 0.00905 12.61 65.00

70.0Q 31,279 36.03 2.9072 59.867 217.017 0.12609 0.42278 0.5801 0.4242 1.S276 3009. 663. 0.400 0.018] 0.0627 0.00923 1128 70.00

75.00 M.157 35.83 2.6747 62.783 218.72! 0.13154 0.42.319 0.5839 0.4286 1.1291 2960. 663. 0.389 0,0183 0.0621 0.0094! U-95 75.00

80.00 37.232 35.63 2.4646 65.719 220,425 0. 13697 0.42364 0.5877 0.433 ! U 308 2910, 663. 0,379 O.tll8S 0.06 Ϊ4 0.00959 1 1.63 80.00

0.370 0.0 S 87 0.060S 0.00977 1 130 85,00

85.00 40.513 35.42 2.2742 68,673 222, 127 0.14239 0.42413 0.5916 0.4377 1.1326 2860. 663.

90.00 44,009 35.22 2, 1015 71 .648 223.827 0. S 4780 0.42465 0.5956 0.4424 1.1346 28 to. 663. 0.360 0.0189 0,0602 0.00996 10,98 90.00 .019! 0.0596 0.01015 10,66 95.00

95.00 47.728 35,Ot 1.9445 74.643 225.524 0.15318 0.42520 0.5997 0.4472 1.1367 2760. 662. 0.351 0

DTH. Aβ .r-» Si a nύrrnn! boil c ■

8 O8O8O8O8Q ^. <". « t oα c Tt ό 4 fq WO "o^"o¹'!"o"^'

d O $ »3τ-

'— V r--.Z <'od- V'o-. H ^ «^^ g^ £^ *^ ∞ M vo)(αNo tc--t φ O «— g ^ t ^ S "; ^ _" r 5^

The performance index of Cycle No. 1 {cycle 20): Q (S T₁,

Q Mech. Input

is 6.534. The per unit available energy of Cycle No. 2 (cycle 30) is 0.2006. The product of these performances, the net mechanical energy output per unit of mechanical energy per input is 6.514 x 0.2006 = 1.307. Thus, the system will sustain its own operation plus produce mechanical energy for other uses by extracting energy from the ambient environment.

The following is a list of reference numerals:

LIST FOR REFERENCE NUMERALS

(Part No.) (Description)

10 preferred embodiment of the present invention

20 refrigeration/heat pump cycle

30 power cycle

40 compressor

50 heat exchanger

60 expansion valve

70 evaporator

80 engine

90 condenser

100 pump

110 pressure

120 enthalpy

130 pressure

140 enthalpy

AU measurements disclosed herein are at standard temperature and pressure, at sea level on Earth, unless indicated otherwise. All materials used or intended to be used in a human being are biocompatible, unless indicated otherwise.

It will be understood that each of the elements described above, or two or more together may also find a useful application in other types of methods differing from the type described above. Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can, by applying current knowledge, readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention set forth in the appended claims. The foregoing embodiments are presented by way of example only; the scope of the present invention is to be limited only by the following claims.

Claims

1. A method of power generation comprising:

(a) a power cycle; and (b) a heat pump cycle, the heat pump cycle supplying heat to the power cycle.

2. The method of claim 1, wherein the power cycle includes a first media and the heat pump cycle includes a second media, the first media being different from the second media.

3. The method of claim2, wherein the first media has a first flow rate and the second media has a second flow rate, the first flow rate being different from the second flow rate.

4. The method of claim 1 , wherein the heat pump cycle includes an expansion valve.

5. The method of claim 1 , wherein the heat pump cycle includes an expansion turbine.

6. The method of claim 3, wherein the first media is R600 and the second media is Rl 1.

7. The method of claim 6, wherein the flow rate of the second media is about two times the flow rate of the second media.

8. The method of claim 1 , wherein the heat pump cycle includes a heat exchanger for rejecting heat and the power cycle uses this heat exchanger as a source of heat.

9. A method of removing heat from a space comprising: (a) a power cycle;

(b) a heat pump cycle, the heat pump cycle supplying heat to the power cycle; and

(c) the heat pump cycle removing heat from the space.

10. A method of adding heat to a space comprising: (a) a power cycle;

(c) the power cycle adding heat to the space.

1 1. A method of removing heat from a material in a process comprising: (a) a power cycle; (b) a heat pump cycle, the heat pump cycle supplying heat to the power cycle; and

(c) the heat pump cycle removing heat from the material.

12. A method of adding heat to a material in a process comprising: (a) a power cycle; (b) a heat pump cycle, the heat pump cycle supplying heat to the power cycle; and

(c) the power cycle adding heat to the material.

13. The invention substantially as shown and described herein.