Rakh cycle engine

Description

BACKGROUND OF INVENTION

In researching the present invention, I discovered many patents that took advantage of waste heat to increase mechanical work and engine efficiency. Most of these patents selected water as the injected liquid. None of the other patents, however, made use of superheated injected liquids. The liquid entering a relatively low pressure cylinder when compared with the liquid's saturation pressure at the injected temperature is indeed superheated for an instant after being injected. The physical calculations of temperature and pressure show that the temperature of the injected liquid if water is the selected substance needs to be within a fairly close proximity to the critical temperature in order to increase pressure of the mixture. Water has such a high latent heat of vaporization that it can easily over cool the compressed gas and result in a decrease of pressure. No engine will be as efficient as it is without injecting water, if both temperature and pressure decrease before the power stroke begins expansion. Typically, in engine patents that I reviewed, ambient water was converted to steam using waste heat of combustion gasses. Each, typically, also used internal combustion from an Otto or Diesel cycle to generate the heat. The present invention does not use internal combustion for its heat source. A ‘carrier gas’ is heated outside the engine, via solar, a typical water heater, or exhaust recovery heat. A liquid is also pre-heated externally or by purchasing/renting an insulated, pressurized container of the hot liquid. The present invention is somewhat more like a battery powered motor than an internal combustion engine. Some combination of liquid and carrier gas should permit the use of ambient heating of the carrier gas while supplying a pressurized, stored ‘thermos’ of liquid heated to near its critical temperature as the only energy input necessary. Presently, the demonstrated RAKH Cycle Engine prefered configuration uses argon carrier gas with hot water as the injected liquid.

References Cited
U.S. Patent Documents

	770468	September, 1904	Lake	60/674
	917317	April, 1909	Lake	60/674
	924100	June, 1909	Nichols	123/191
	1032236	July, 1912	Patten	60/650
	1739255	December, 1929	Niven	123/193
	1926463	September, 1933	Stoddard	60/650
	2062013	November, 1936	Opolo	123/193
	2791881	June, 1954	Denker	60/619
	3006146	October, 1961	Jackson	60/649
	3867816	February, 1975	Barrett	60/682
	3,964,263	Jun. 22, 1976	Tibbs	60/712
	4,270,351	Jun. 2, 1981	Kuhns	60/517
	4,322,950	Apr. 6, 1982	Jepsen	60/712
	4,326,388	Apr. 27, 1982	McFee	62/324.6
	4,402,193	Sep. 6, 1983	McFee	62/304
	4,553,397	Nov. 19, 1985	Wilensky	60/649
	4,691,523	Sep. 8, 1987	Rosado	60/649
	5,035,115	Jul. 30, 1991	Ptasinski	60/712
	5,983,640	Nov. 16, 1999	Czaja	60/674

SUMMARY OF THE INVENTION

The engine and its thermodynamic cycle, which is described herein, will be called the RAKH CYCLE ENGINE. The said engine cycle involves a gas or mixture of gasses that are herein referred to as the ‘carrier gas’ and a superheated liquid, which vaporizes but does not burn. The purpose of the carrier gas is to bring thermal energy into a volume where compression is used to concentrate thermal energy at a higher temperature. A liquid is then injected. In an engine cycle, the liquid must be superheated above its saturation temperature corresponding to the pressure that the carrier gas attains at its maximum compression. The carrier gas must be much hotter than the injected liquid in order to force heat to be transferred into the injected liquid rapidly. Heat that is transferred from the carrier gas will cool the carrier gas resulting in a lower temperature and pressure. Transfer of the heat from the carrier gas into the liquid, on the other hand, will greatly increase the volume of the injected liquid, through converting it into a vapor. The temperature of the liquid will increase while the temperature of the carrier gas will decrease. The decrease of temperature is moderated by further compression of the carrier gas due to displacement from the vapor produced forcing the carrier gas into a smaller volume. All of the experimental results, which I have derived by calculation, have always resulted in a lower temperature from the end of event one up through to the end of mixture temperature equalization in event three. This theoretical observation may prove false in practice however, for real liquids that are injected at pressures above their critical point into a carrier gas that is also compressed to a point that is above the critical pressure of the liquid. Some real gasses and liquids exhibit an overall increase in pressure upon vaporization of the liquid in the mixture. The compression phase end temperature of the carrier gas before liquid injection decreases after temperature equalization of the mixture. The present invention may also use substances injected above their critical temperature and pressure. Those superheated substances are still considered as liquids for. The best choice of carrier gas would not condense at the peak cycle pressure. The purpose of the carrier gas is to carry heat into the cycle, which is transferred to a liquid injected at a later point in the cycle after the carrier gas is compressed. Calculations are very difficult because of changing gamma values for the liquid and carrier gas. The preferred implementation uses Argon as the carrier gas and water as the injected liquid. The gamma value for Argon is nearly constant at varying temperatures. FIGS. 1 through 3 illustrate the prefered implementation of a closed four-cycle, piston driven RAKH Cycle Engine.

The first event of the RAKH CYCLE is adiabatic compression of a carrier gas to increase its temperature via input of mechanical energy similar to a diesel cycle compressing air to a temperature hot enough to ignite fuel via adiabatic compression. The purpose of this compression in the RAKH cycle, however, is to concentrate the thermal heat via an increase in temperature to force rapid transfer of energy to the liquid injected in event two.

The second event in this thermodynamic cycle is the injection of liquid into a nearly constant volume of the gas at the end of the first event. If the cycle is used in an engine, the liquid will be heated to some sufficient temperature, such that part of the liquid flashes into the gasseous phase due to the excess thermal energy of the liquid enthalpy beyond that of the liquid at its saturation temperature for the pressure in the cylinder (or turbine) arrived at by the mixture.

Event three in the cycle is equalization of temperature prior to the rapid expansion event, which follows. This third event happens very fast within the same constant volume (shown in FIG. 4) and includes the transfer of thermal energy from the carrier gas to the injected liquid, which had not yet completely flashed to a gas. If there is a sufficient temperature difference to allow heat to transfer from the carrier gas to the liquid at its saturation temperature and pressure, further vaporization will occur. Complete vaporization is not required for this event. The mixture's pressure may go down during this event. Pressure and or the temperature may be above the critical point for the liquid at the point of injection or after the temperature equalization of event three. In an engine, the sum of partial pressures must exceed the pressure at the end of event 1 or the engine will not run with out power input to the cycle. Power to volume is low in any case. The fourth event is adiabatic expansion of the mixture. This adiabatic expansion will typically be back down to the original volume found at the beginning of event one. A turbine engine application may have the advantage over the piston engine since the final volume of a piston engine is geometrically constrained to equal event one's starting volume. Values at each point of expansion that are shown in Listings 1 through 6 were calculated as if the liquid had been injected at those points as though they were the end points of the compression. The physical path to the end compression point makes no difference on theoretical adiabatic end pressure and temperature. Listings 1 to 6 are listings of the theoretical results using a computer program.

The fifth event, is the exhausting of the mixture. The exhaust mixture should be captured into a condenser designed to handle separation of the mixture into its separate components to increase efficiency. The RAKH Cycle, however, does not require a condenser, but does assume a continuous supply of carrier gas and liquid from some source at a constant temperature and pressure. Burning a little oxygen in a predominantly hydrogen carrier gas would provide adequate hot hydrogen carrier gas having a little superheated steam mixed in with it.

Event six is the induction of the carrier gas, which brings the cycle back to the initial conditions of event one whenever the cycle is running in a steady state. This sequence of six events will be repeated as a continuous thermodynamic cycle, which will be referred to as the RAKH CYCLE without regard for which starting point is arbitrarily picked for event 1. FIG. 5 is a typical engine Pressure Volume (PV) diagram showing pressure during through each event in the cycle.

Engines using this cycle are RAKH Cycle Engines. Refrigeration machines using this cycle with appropriate working substances selected for refrigeration, are referred to as RAKH refrigerators.

The selection of the carrier gas and liquid are major variables impacting the cycle efficiencies. Ability for the combination to produce power, is a very narrow margin between operable and non-operability for a RAKH Cycle Engine. The variability of gamma for the real gasses is what allows the cycle to work below the critical point. The gamma value is the ratio of the specific heat at constant pressure to the specific heat at constant volume. For a small adiabatic change of volume, the change of pressure is dependent upon gamma in the relationship: P2=P1 times (V1/V2) raised to the gamma power where P1 is the starting pressure, V1 represents the starting volume, and V2 is the final volume. This is also frequently referred to as the compression ratio. If gamma is 2 and the compression ratio is 10 then the adiabatic final pressure will be P1 times 100 (10 squared) and not simply P1 times 10 as might have otherwise been expected. I selected carrier gasses that had a very nearly constant gamma for ease of calculation in the illustrated computer listings. Hydrogen may be the best bet for a carrier gas for efficiency in heating previously mentioned and because it is fairly easy to separate from the hydrogen-steam mixture.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1-3 Show the complete essential elements of the preferred implementation of a closed cycle RAKH Cycle Engine.

FIG. 1 Illustrates the carrier gas storage and heating system elements which deliver engine induction carrier gas to the heat converting mechanical work engine.

FIG. 2 shows a compact, high volume W9 piston type implementation of a RAKH Cycle Engine.

FIG. 3 illustrates the exhaust recovery system that returns dry carrier gas back to the carrier gas storage and heating system of FIG. 1.

FIGS. 4-6 show the thermodynamic sequence of Pressure, Temperature, and Volume at initial conditions, compression, and superheated liquid injection for a piston. FIG. 4 shows mass, and initial P, V, and T, at the beginning of compression. FIG. 5 shows P, V, and T, at TDC after maximum compression and; FIG. 6 at Top Dead Center (TDC) after liquid injection, at the start of the power stroke using the 4-stroke RAKH cycle engine described in FIGS. 1-3 and the set of initial conditions selected in the last computer printout listing, listing 6.

Listings 1-6 are computer program listings which show power and efficiency variations and the thermodynamic conditions of the RAKH Cycle Engine Run at uniform incremental points of the cycle under variations of compression ratio, initial carrier gas induction temperatures, and liquid injection quantities for water injected near the critical temperature at 704 degrees F.

COMPUTER LISTINGS

Listing 1 is a computer printout for 8:1 compression at 1200 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133; Cv = .075165; gamma = 1.769441

T2 = 7760.784 deg. F. & P2 = 2813.341 psia; Head Vol. = 62.5 cc;

CR = 8:1; free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = 1.37449

Thermal energy per power cycle to heat Argon = .2049907 BTUs

Assumed free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 7.598673E−02 BTUs

Mechanical work done to compress the Argon is −928.0307 ft-lbs

************************* Event 2 **********************************

At TDC, inject .06 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 95.81733% % Mole mass H2O = 4.18267%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .06 grams of Saturated vapor at 2784.7 psia = .390925 cc

So, Argon is further compressed and now occupies only 62.10907 cc

The cylinder pressure however, decreases to 2784.7 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 7638.407

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 5692.219 deg. F.

8:1 Compression of Argon starting @ 1200 deg. F. & 71 psia

Calculating partial volumes of .06 grains Water vapor & 1.37449 grams Argon

yields 4.551353 & 57.94865 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 62.5 at TDC.

Angle	Temp. F.	PSIA	Cyl Vol		Steam	Argon

90	5692.219	2983.976	62.5	4.5513	SUP	57.94865
80	5415.021	2657.699	66.60092	4.9205	SUP	61.68034
70	4747.316	1959.702	78.80437	5.9693	SUP	72.83501
60	3973.675	1307.761	98.53674	7.6205	SUP	90.91614
50	3265.964	851.2669	124.8817	9.8463	SUP	115.0354
40	2691.061	564.1493	156.6411	12.607	SUP	144.0338
30	2241.762	387.6474	192.4153	15.710	SUP	176.7049
20	1897.452	278.4525	230.6973	19.435	SUP	211.2621
10	1624.841	208.0506	269.9732	22.626	SUP	247.347
0	1416.888	163.8102	308.8161	28.522	SUP	280.2934
−10	1254.789	132.4055	345.9635	32.056	SUP	313.9067
−20	1131.672	110.5387	380.3672	33.588	SUP	346.7791
−30	1035.548	93.85143	411.2137	31.029	SUP	380.1843
−40	963.3055	82.05675	437.9155	25.810	SUP	412.1045
−50	908.7077	74.63467	460.0805	22.649	SUP	437.4312
−60	868.5814	69.51414	477.4703	20.515	SUP	456.955
−70	841.2895	66.18478	489.955	19.153	SUP	470.801
−80	827.2404	64.29819	497.4729	18.418	SUP	479.0547
−90	820.8011	63.6814	499.9999	18.153	SUP	481.8467
Exhaust pressure of the binary mixture is 63.6814 psia at 820.8011 degrees F.
Work done is 947.6757 ft-lbs;
Estimated W-9 Horsepower @ 3600 RPM = 9.644 hp
Estimated heat for Argon = 55.3475 BTU/sec and for liquid = 20.51642 BTU/sec
Theoretical Efficiency = 8.983552%

COMPUTER LISTINGS

Listing 2 is a computer printout for 8:1 compression at 1400 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133; Cv = .075165; gamma = 1.769441

T2 = 8751.396 deg. F. & P2 = 2813.341 psia; Head Vol. = 62.5 cc; CR = 8:1;

free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = 1.22667

Thermal energy per power cycle to heat Argon = .2235992 BTUs

Free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 7.598673E−02 BTUs

Mechanical work done to compress the Argon is −928.0307 ft-lbs

************************* Event 2 **********************************

At TDC, inject .06 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 95.3368% % Mole mass H2O = 4.663202%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .06 grams of Saturated vapor at 2784.7 psia = .3909251 cc

So, Argon is further compressed and now occupies only 62.10907 cc

The cylinder pressure however, decreases to 2784.7 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 8614.273

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 6153.344 deg. F.

8:1 Compression of Argon starting @ 1400 deg. F. & 71 psia

Calculating partial volumes of .06 grams Water vapor & 1.22667 grams Argon

yields 4.858467 & 57.64153 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 62.5 at TDC.

Crank Angle	Temp. F.	PSIA	Cyl Vol	Steam	Argon

90	6153.344	2999.854	62.5	4.8584	SUP	57.64153
80	5862.012	2672.399	66.60092	5.2606	SUP	61.34026
70	5153.316	1971.232	78.80437	6.3964	SUP	72.40793
60	4326.985	1315.87	98.53674	8.1837	SUP	90.35295
50	3575.412	856.8443	124.8817	10.600	SUP	114.2809
40	2964.404	568.0646	156.6411	13.612	SUP	143.0291
30	2475.762	390.3107	192.4153	16.938	SUP	175.4763
20	2105.5	280.4383	230.6973	20.979	SUP	209.7177
10	1816.841	209.6149	269.9732	24.602	SUP	245.3707
0	1590.476	165.1332	308.8161	30.892	SUP	277.9238
−10	1414.789	133.8045	345.9635	34.761	SUP	311.2022
−20	1279.843	111.3988	380.3672	36.596	SUP	343.7709
−30	1175.548	94.80654	411.2137	34.345	SUP	376.8687
−40	1095.426	82.59328	437.9155	28.434	SUP	409.4808
−50	1035.117	74.75674	460.0805	24.783	SUP	435.2975
−60	992.4648	69.61333	477.4703	22.471	SUP	454.9989
−70	962.9454	66.27042	489.955	20.988	SUP	468.9663
−80	945.4143	64.37533	497.4729	20.152	SUP	477.3203
−90	938.8011	63.75652	499.9999	19.869	SUP	480.1304
Exhaust pressure of the binary mixture is 63.75652 psia at 938.801 degrees F.
Work done is 953.8967 ft-lbs;
Estimated W-9 Horsepower @ 3600 RPM = 12.697 hp
Estimated heat for Argon = 60.37178 BTU/sec and for liquid = 20.51642 BTU/sec
Theoretical Efficiency = 11.09368%

COMPUTER LISTINGS

Listing 3 is a computer printout for 10:1 compression at 1200 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133 Cv = .075165 gamma= 1.769441

T2 = 9300.61 deg. F. & P2 = 2764.002 psia; Head Vol. = 50 cc; CR = 10:1;

free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = .9098739

Thermal energy per power cycle to heat Argon = .1356981 BTUs

Free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 6.332228E-02 BTUs

Mechanical work done to compress the Argon is -758.6626 ft-lbs

************************* Event 2 **********************************

At TDC, inject .05 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 94.79099% % Mole mass H2O = 5.209018%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .05 grams of Saturated vapor at 2732.787 psia = .3402922 cc

So, Argon is further compressed and now occupies only 49.65971 cc

The cylinder pressure however, decreases to 2732.787 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 9141.189

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 6281.403 deg. F.

10:1 Compression of Argon starting @ 1200 deg. F. & 47 psia

Calculating partial volumes of .05 grams Water vapor & .9098739 grams Argon

yields 4.185383 & 45.81462 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 50 at TDC.

Angle	Temp. F.	PSIA	Cyl Vol		Steam	Argon

90	6281.403	2961.447	50	4.1853	SUP	45.8146
80	5912.367	2556.354	54.21809	4.6300	SUP	49.5880
70	5050.044	1754.167	66.77021	5.8883	SUP	60.8818
60	4106.926	1084.716	87.06635	7.8927	SUP	79.1735
50	3294.834	663.436	114.1641	10.626	SUP	103.5371
40	2663.506	419.4027	146.8309	13.996	SUP	132.8349
30	2186.437	278.9729	183.6271	18.161	SUP	165.4661
20	1825.887	195.0003	223.0029	22.377	SUP	200.6253
10	1545.998	144.5772	263.401	29.013	SUP	234.3875
0	1334.585	110.1319	303.3537	31.682	SUP	271.6711
−10	1173.009	85.30632	341.5625	25.712	SUP	315.8498
−20	1050.427	69.7062	376.9491	19.498	SUP	357.4505
−30	956.1718	59.6932	408.6769	15.727	SUP	392.9495
−40	884.814	52.40205	436.1416	13.106	SUP	423.0352
−50	830.8615	47.46509	458.9399	11.402	SUP	447.5375
−60	794.1226	44.09988	476.8266	10.295	SUP	466.5308
−70	768.5775	41.89244	489.6679	9.5812	SUP	480.0866
−80	753.5972	40.63806	497.4006	9.1804	SUP	488.2202
−90	749.0366	40.22953	499.9999	9.0537	SUP	490.9461
Exhaust pressure of the binary mixture is 40.2295 psia at 749.0366 degrees F.
Work done is 778.1189 ft-lbs,
Estimated W-9 Horsepower @ 3600 RPM = 9.551 hp
Estimated heat for Argon = 36.6385 BTU/sec and for liquid = 17.0970 BTU/sec
Theoretical Efficiency = 12.5612%

COMPUTER LISTINGS

Listing 4 is a computer printout for 10:1 compression at 1400 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133; Cv = .075165; gamma= 1.769441

T2 = 10476.78 deg. F. & P2 = 2764.002 psia; Head Vol. = 50 cc; CR = 10:1;

free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = .8120207

Thermal energy per power cycle to heat Argon = .1480163 BTUs

Free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 6.332228E−02 BTUs

Mechanical work done to compress the Argon is −758.6626 ft-lbs

************************* Event 2 **********************************

At TDC, inject .05 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 94.19968% % Mole mass H2O = 5.800325%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .05 grams of Saturated vapor at 2732.787 psia = .3402922 cc

So, Argon is further compressed and now occupies only 49.65971 cc

The cylinder pressure however, decreases to 2732.787 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 10298.16

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 6727.823 deg. F.

10:1 Compression of Argon starting @ 1400 deg. F. & 47 psia

Calculating partial volumes of .05 grams Water vapor & .8120207 grams Argon

yields 4.432171 & 45.56783 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 50 at TDC.

Angle	Temp. F.	PSIA	Cyl Vol		Steam	Argon

90	6727.823	2977.473	50	4.4321	SUP	45.5678
80	6338.564	2570.751	54.21809	4.9082	SUP	49.3098
70	5432.52	1764.889	66.77021	6.2589	SUP	60.5112
60	4438.989	1092.14	87.06635	8.4068	SUP	78.6595
50	3582.834	668.1401	114.1641	11.363	SUP	102.8006
40	2915.923	422.6461	146.8309	15.036	SUP	131.794
30	2400.371	281.1099	183.6271	19.452	SUP	164.1748
20	2020.208	196.4961	223.0029	23.954	SUP	199.0484
10	1719.998	145.9168	263.401	31.284	SUP	232.1168
0	1492.543	111.1008	303.3537	34.328	SUP	269.025
−10	1317.009	85.7609	341.5625	28.119	SUP	313.4429
−20	1182.627	69.81921	376.9491	21.228	SUP	355.7203
−30	1080.743	59.76393	408.6769	17.135	SUP	391.5417
−40	1002.673	52.79094	436.1416	14.416	SUP	421.7255
−50	944.4111	47.52547	458.9399	12.440	SUP	446.4995
−60	902.3192	44.14756	476.8266	11.216	SUP	465.6096
−70	873.3138	41.93295	489.6679	10.429	SUP	479.238
−80	857.5972	40.67531	497.4006	9.9988	SUP	487.4018
−90	851.0366	40.26515	499.9999	9.8487	SUP	490.1512
Exhaust pressure of the binary mixture is 40.2651 psia at 851.0366 degrees F.
Work done is 783.384 ft-lbs;
Estimated W-9 Horsepower @ 3600 RPM = 12.1361 hp
Estimated heat for Argon = 39.96441 BTU/sec and for liquid = 17.0970 BTU/sec
Theoretical Efficiency = 15.03015%

COMPUTER LISTINGS

Listing 5 is a computer printout for 12:1 compression at 1200 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133 Cv = .075165 gamma= 1.769441

T2 = 10770.53 deg. F. & P2 = 2760.743 psia; Head Vol. = 41.6667 cc; CR = 12:1;

free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = .6582066

Thermal energy per power cycle to heat Argon = 9.816456E−02 BTUs

Free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 4.432559E−02 BTUs

Mechanical work done to compress the Argon is −648.5344 ft-lbs

************************* Event 2 **********************************

At TDC, inject .035 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 94.951% % Mole mass H2O = 5.048999%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .035 grams of Saturated vapor at 2734.399 psia = .2378876 cc

So, Argon is further compressed and now occupies only 41.42878 cc

The cylinder pressure however, decreases to 2734.399 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 10615.93

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 7199.492 deg. F.

12:1 Compression of Argon starting @ 1200 deg. F. & 34 psia

Calculating partial volumes of .035 grams Water vapor & .6582066 grams Argon

yields 3.331799 & 38.33487 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 41.6667 at TDC.

Angle	Temp. F.	PSIA	Cyl Vol		Steam	Argon

90	7199.492	2954.399	41.66667	3.3317	SUP	38.33487
80	6693.274	2474.644	45.96288	3.7609	SUP	42.20195
70	5581.69	1590.765	58.74744	4.9866	SUP	53.76077
60	4434.087	923.742	79.41944	6.9565	SUP	72.46288
50	3495.073	539.0018	107.019	9.6969	SUP	97.32202
40	2790.533	329.7793	140.2907	13.082	SUP	127.2083
30	2267.495	214.0209	177.7684	16.943	SUP	160.8246
20	1881.981	148.6708	217.8733	23.112	SUP	194.7608
10	1588.337	106.9171	259.0196	25.766	SUP	233.2534
0	1365.485	78.10737	299.7121	18.435	SUP	281.2764
−10	1198.119	61.58424	338.6284	13.282	SUP	325.3464
−20	1069.991	50.85831	374.6704	10.164	SUP	364.5055
−30	972.6651	43.53189	406.9858	8.1669	SUP	398.8188
−40	899.26	38.05911	434.9591	6.7535	SUP	428.2055
−50	843.4289	34.49232	458.1796	5.8702	SUP	452.3094
−60	805.2305	32.01327	476.3975	5.2878	SUP	471.1096
−70	778.4795	30.39824	489.4766	4.9135	SUP	484.5631
−80	764.2328	29.48538	497.3525	4.7102	SUP	492.6423
−90	758.4092	29.18753	499.9999	4.6399	SUP	495.36
Exhaust pressure of the binary mixture is 29.1875 psia at 758.4092 degrees F.
Work done is 666.9431 ft-lbs;
Estimated W-9 Horsepower @ 3600 RPM = 9.0370 hp
Estimated heat for Argon = 26.50443 BTU/sec
Estimated heat for injected liquid = 11.96791 BTU/sec
Theoretical Efficiency = 16.59994%

COMPUTER LISTINGS

Listing 6 is a computer printout for 12:1 compression at 1400 deg. F. starting gas temperature.

Argon @ STP = 39.948 grams for 22.4 liters

Cp = .133 Cv = .075165 gamma= 1.769441

T2 = 12123.84 deg. F. & P2 = 2760.743 psia; Head Vol. = 41.6667 cc; CR = 12:1;

free Ambient = 300 deg. F.

Argon Pres/Temp compensated mass in grams = .5874192

Thermal energy per power cycle to heat Argon = .1070757 BTUs

Free feed Water heat = 268 BTUs per pound

Thermal energy per power cycle to heat Water = 4.432559E−02 BTUs

Mechanical work done to compress the Argon is −648.5344 ft-lbs

************************* Event 2 **********************************

At TDC, inject .035 grams of superheated Water at 704 deg. F.

% Mole mass Argon = 94.37678% % Mole mass H2O = 5.62322%

********************************************************************

Since the injected Water is superheated, some flashes to vapor;

Volume .035 grams of Saturated vapor at 2734.399 psia = .2378876 cc

So, Argon is further compressed and now occupies only 41.42878 cc

The cylinder pressure however, decreases to 2734.399 psia

as a result of all the Water converting to saturated vapor

and the carrier gas temperature changes to 11950.6

Equalizing temperatures, the vapor's temperature goes up to meet

Argon's decreasing temperature at 7714.418 deg. F.

12:1 Compression of Argon starting @ 1400 deg. F. & 34 psia

Calculating partial volumes of .035 grams Water vapor & .5874192 grams Argon

yields 3.532375 & 38.13429 cc respectively after equalizing temperatures.

Sums of the partial volumes must equal the cylinder volume of 41.6667 at TDC.

Angle	Temp. F.	PSIA	Cyl Vol		Steam	Argon

90	7714.418	2969.924	41.66667	3.5323	SUP	38.1342
80	7173.274	2488.044	45.96288	3.9886	SUP	41.9742
70	6005.69	1600.18	58.74744	5.3040	SUP	53.4433
60	4794.087	929.7141	79.41944	7.4253	SUP	71.9941
50	3802.525	542.8007	107.019	10.385	SUP	96.6333
40	3053.34	332.2596	140.2907	14.051	SUP	126.2389
30	2489.76	215.678	177.7684	18.227	SUP	159.541
20	2079.981	149.9546	217.8733	24.869	SUP	193.0038
10	1766.371	107.7979	259.0196	27.897	SUP	231.1217
0	1527.485	78.36844	299.7121	20.123	SUP	279.5889
−10	1344.46	61.65889	338.6284	14.465	SUP	324.1626
−20	1205.932	50.90034	374.6704	11.079	SUP	363.5905
−30	1098.773	43.55795	406.9858	8.8979	SUP	398.0878
−40	1019.412	38.42031	434.9591	7.4608	SUP	427.4982
−50	959.3326	34.51474	458.1796	6.4075	SUP	451.7721
−60	915.2305	32.03089	476.3975	5.7622	SUP	470.6352
−70	886.4795	30.41343	489.4766	5.3566	SUP	484.12
−80	868.9189	29.49901	497.3525	5.1273	SUP	492.2252
−90	864.4092	29.20099	499.9999	5.0581	SUP	494.9417
Exhaust pressure of the binary mixture is 29.2010 psia at 864.4092 degrees F.
Work done is 671.0901 ft-lbs,
Estimated W-9 Horsepower @ 3600 RPM = 11.073 hp
Estimated heat for Argon = 28.9104 BTU/sec and for liquid = 11.9679 BTU/sec
Theoretical Efficiency = 19.14237%

DETAILED DESCRIPTION

The RAKH Cycle Engine utilizes a novel thermodynamic cycle, which is described here in detail. FIG. 1 shows an insulated storage tank (1) that is initially full of the selected carrier gas. Argon is used as the preferred carrier gas because of its calculation friendly nature of maintaining a nearly constant specific heat. The carrier gas is nearly free of any liquid water when it exits the storage tank because of the ceramic fuel filter (8), which passes gas through it but not water, similar to a common ceramic gasoline fuel filter that allows gasoline to pass through but not water. The carrier gas will pass through the ceramic with negligible back pressure. Excess water can be drained from the storage tank through manual operated valve (9) and may be collected or discarded on exiting through the drain tube after the valve. The carrier gas is drawn though the heater (3) by the intake stroke of the RAKH Engine (see FIG. 2). The heater is warmed by the boron burner (4), which is continuously fed oxygen from tank (6) through the thermostatically controlled regulator valve (7), controlled by thermostat (5). Thermostat (5) is also contains a high voltage spark plug, which sparks during startup only. There is no exit from the burner except through orifices in the boron feeder assembly (11), which plugs the exit automatically with slow draining boria (the glassy solid product of the combustion of boron in oxygen). The close-up particulars of the boron feeder assembly are shown the adjacent drawing detail, which shows the oxygen orifice entering at the right side below and exiting through a little tungsten tube (14), which is bent toward the boron filament at its upper end. This tungsten tube serves to help blow away the glassy boria protective coating formed on the surface of the boron. The intense heat at the tip would melt most other metal tubes that could be used but tungsten is the least likely to melt in this application. A plug of boria should be left in the upper end of the boron feeder assembly. Electrical heating coils (13) will help warm this boria plug which will begin to drain out the boria drain tube (12). Boria (15) flowing out slowly is the only thing that impedes the oxygen. Otherwise, oxygen would exit through the same tube (12). The boria also seals the boron filament entering the burner. The boron feeder assembly (11) boron entry hole diameter must be slightly larger than the largest diameter of the solid boron filament being forced into the boron feeder assembly. There will be virtually no possibility for extrusion since boron is nearly as hard as diamond. FIG. 1 is presented only to show a viable hot gas delivery system, which produces none of the so called greenhouse waste gasses of current carbon fuel based engines. Boron burns to form the solid waste boria and has no exhaust gas!

FIG. 2. shows a compact diesel type engine converted to a RAKH Cycle Engine. The RAKH Cycle Engine intakes a hot carrier gas rather than air through intake port (C) via intake valve (I). Like in a diesel, the carrier gas is then compressed adiabatically, requiring work input from a typical diesel Crankshaft Flywheel (not shown on FIG. 2). At a point very near Top Dead Center for the piston, FIG. 4 shows the thermodynamic results of injecting superheated water (water heated to a point above the saturation temperature with respect to its pressure environment after being injected into the cylinder). FIG. 4 uses the conditions assumed in the listing of FIG. 6. Water stored in pressure vessel (M) flows through high pressure delivery line (L) into injection channel (K) surrounding the inlet of electronically heated and electronically controlled plunger (B) of injector (D) which is like a diesel injector but it injects a superheated liquid, namely water in these illustrated Figures. The water cannot burn, of course, but conditions are so hot in the cylinder that it seems to explode into steam from its own excess enthalpy at the pressure of its new environment within the cylinder and a rapid heating from the adiabatically heated carrier gas. The mixture of steam and the carrier gas have more pressure than the carrier gas did alone, which cause net work output from piston (P) down connecting rod (F) forcing crankshaft connected at crank offset throw (J) to exert a rotational torque on crankshaft (G) with more average force due to pressure increased during the power stroke than that required to compress the carrier gas. Like other 4 stroke engines, the power stroke is followed by the exhaust stroke, which forces the exhaust mixture out through valve (E) and on out Exhaust port (A) to the condenser/dryer system illustrated in FIG. 3.

FIG. 3 Illustrates the Condenser System, which saves the carrier gas and removes the small volume of vapor in the mixture caused by injecting the superheated liquid. Steam in the preferred implementation presented here. Wet mixture (W) enters the Condenser tank (T) where it is immediately cooled by the spray injection (I) that is pumped into the condenser by continuous centrifugal pump (R), which pumps water from the condenser through water cooled radiator (G). Cooling water (C) comes from virtually any large source of cooling water. Engine induction continually pulls carrier gas (V) out of the condenser through two ceramic disks with high pressure water trapped between those two ceramic disks (similar to the ceramic filter described in FIG. 1). Any water vapor trying to leave the condenser with carrier gas (V) is cooled and trapped in the water between the two ceramic disks. The trapped water is continuously heated by the addition of steam and its volume continuously increases until pressure relief valve (P) releases water back into the condenser hydraulic gear pump (M) continuously pumps water from pressurized hot water tank (B) through water cooled radiator (H) or through bypass line (U) depending on the temperature controlled thermostatic valves (K) and (L). Valve (K) opens when the temperature increases and valve (L) remains open when the temperature is low. The valves are both open at a selectable preset equilibrium temperature so both valves are never closed at the same time. After exiting the throat of the condenser past the pressure relief valve (P), a sleeved (S) U-tube routes the flow back into the throat of the condenser between the two ceramic disks (D) back into tank (B) and into the base of collector dish (Q), which is normally submerged. Another ceramic disk (D) blocks the exit of water via the throat at the upper end of pressurized tank (B). Valve J is a pressure relief valve set to release at a pressure that is only half of the pressure setpoint that opens pressure relief valve (P). If any carrier gas gets transported into tank (B) then it should eventually be released with a small amount of steam back into the condenser. A little steam in the dried carrier gas shouldn't affect operation of the RAKH Cycle Engine. The drawing shows release into the dry gas side rather than back into the condenser to simplify drawing the vent line.

Eventually the liquid at the bottom of the condenser would overflow so a float controller (F) sends a signal to open drain line valve (E) draining to a low pressure air vented overflow tank, not shown on the drawing. Steam trapped between the ceramic disks continually heats tank (B) and preheats the carrier gas a little bit after the spray injection (I) has cooled it for a slight added efficiency bonus in capturing and recycling the carrier gas with a closed cycle.

FIG. 4 shows the theoretical thermodynamic conditions of Pressure, Volume, and Temperature for a single cylinder after the induction stroke at Bottom Dead Center (BDC) for 1 piston given the particular RAKH Cycle Engine configuration and initial conditions selected for computer listing number 6, which follows.

FIG. 5 shows the theoretical thermodynamic conditions of Pressure, Volume, and Temperature after the compression stroke at Top Dead Center (TDC) from the initial state in FIG. 4.

FIG. 6 shows the same piston position at TDC as in FIG. 5 an instant later after the water is injected, showing the final P, V, and T for the mixture.

Listings 1 and 2 computer printouts are for an 8 to 1 compression ratio RAKH Cycle Engine with 0.06 grams of water injected at 704 degrees F.

Listings 3 and 4 computer printouts are for a 10 to 1 compression ratio RAKH Cycle Engine with 0.05 grams of water injected at 704 degrees F.

Listings 5 and 6 computer printouts are for a 12 to 1 compression ratio RAKH Cycle Engine with 0.035 grams of water injected at 704 degrees F.

Listing 1 has 1200 degree F. initial Argon carrier gas temperature and 71 psia intake pressure.

Listing 2 has 1400 degree F. initial Argon carrier gas temperature and 71 psia intake pressure.

Listing 3 has 1200 degree F. initial Argon carrier gas temperature and 47 psia intake pressure.

Listing 4 has 1400 degree F. initial Argon carrier gas temperature and 47 psia intake pressure.

Listing 5 has 1200 degree F. initial Argon carrier gas temperature and 34 psia intake pressure.

Listing 6 has 1400 degree F. initial Argon carrier gas temperature and 34 psia intake pressure.

At TDC for each of these listings, the maximum pressure is close to 3000 psia