WO2009011001A2

WO2009011001A2 - Steam machines, engines and distillers

Info

Publication number: WO2009011001A2
Application number: PCT/IT2008/000370
Authority: WO
Inventors: Luigi Maria Murone
Original assignee: Luigi Maria Murone
Priority date: 2007-07-13
Filing date: 2008-06-03
Publication date: 2009-01-22
Also published as: ITRM20070389A1; WO2009011001A3

Abstract

In essence this PATENT is based on several variants of the RANKINE-HIRN CYCLE (1,2,3,4,5,6,1),(fig.1) generally employed in VAPOR DRIVEN POWER PLANTS. We have DEMONSTRATED (fig.1) that the first SIDE (1,2) is NOT (as one might EXPECT) found in the LIQUID ZONE (L) but on the first curve of EQUAL CONCENTRATION (AC),(x=0), of (ACBA). Moreover, the WORK (enclosed area) does NOT depend upon the ENTHALPY (H1) of the LIQUID (M'), and so may be TRANSLATED upwards on the curve (AC),(x=0), in order to obtain a HEAT GAIN (from high to low temperature) with a consequent INCREASE in EFFICIENCY from 30- 40% in HEAT ENGINES (fig.3) to a UNITARY VALUE (?=1) in DISTILLERS (fig.5) where the condensation energy may be completely RECYCLED. In these HIRN-ENTHALPIC-CYCLES (figs 3,5) HEAT and WORK (enclosed area) are EXACT DIFFERENTIALS (State Functions) incompatible with the SECOND LAW of THERMODYNAMICS.

Description

ENGINES AND DISTILLERS

TITLE

DESCRIPTION of the Industrial Invention ENTITLED: "STEAM MACHINES, ENGINES AND DISTILLERS",

DESCRIPTION

In the Field (ACBA),(fig. 1) the MIXTURE M=(MN-M") of Concentration x=M"/M, formed by a Liquid M' and its Vapor M", becomes VAPOR SATURATED during the PHASES of BOILING, due to the LATENT HEAT created by the ISOTHERMOBARS (dT=0) and (dρ=O) in the Interval (O≤x≤l), on the horizontals of (ACBA), knowing (GIBBS) that the Pair of CONSTANTS (T,p) render the other VARIABLES (Enthalpy, Entropy, Concentration etc.) CONSTANT, yet ALL UNDETERMINED (CLAPEYRON equation), with Arbitrary values in the respective Intervals of (ACBA). In effect only BEFORE and/or AFTER BOILING does the PHYSICAL STATE of the Mixture depend (GIBBS) on two VARIABLES, thus the TRIPLET Pressure-Temperature-Concentration is linked to State-Equations of type p=f(T,x). Moreover ALL the TRANSFORMATIONS P=U[T₅X₀) at a CONSTANT CONCENTRATION (dx=0) occur along lines of equal concentration (FC),(dx=O) between the two Curve-Limits (AC) and (BC) of (ACBA) until the liquid starts to BOIL again, taking into account that in these CASES (dx=0) every Isothermal Increase of PRESSURE (dT=0),(Δp≠0) requires a corresponding Isobaric Increase of TEMPERATURE (dp=O),(ΔT≠O), being p=f(T),(dx=0) V(FQe(ACBA). This is the main NOVELTY, with REMARKABLE but PREDICTABLE THERMODYNAMIC consequences. In addition the First SIDE (l-2),(dp=0) & (X=O) of the HIRN Cycle (l,2,3,4,5,6=l),(fig.l) is NOT (as we might expect) in the LIQUID Zone (L) but on the First line of Equal Concentration (AC),(x=0) of (ACBA) where the LIQUID (M'), always in contact with its VAPOR (M"), increases the MIXTURE (M) in the Generator (G) BEFORE BOILING. Such also happens to the First SIDES (l-2),(dp=0),(x=0) of (unexpected) new THERMAL CYCLES (figs. 3 & 5), named ENTHALPIC CYCLES, ENGINES (l,2,3,4,5,6=l),(fig.3) and DISTILLERS (l,2,3,4,5,5',6',6=l),(fig.5), due to the ENTHALPY (H) of the LIQUID, which may be "OPTIMIZED" moving it onto the First line of Equal Concentration (AC),(x=0) of (ACBA), and obtaining 2 HEAT GAINS (1-1') and (1-1") (bold lines) with the consequent INCREASE in the EFFICIENCY by 30-40% in the "ENGINES" up to becoming "UNITARY" in the "DISTILLERS". In particular (figs. 5 & 6) the DISTILLER can RECYCLE all the HEAT of CONDENSATION (l-l')=(5'-6') absorbing from a UNIQUE-SOURCE enough HEAT in order to obtain the DISTILLATE (Drinking Water) and ENGINES AND DISTILLERS

potential WORK by GAS (4-5'),(p₂→p') and HYDRAULIC (6=l),(p'→p,), making the DISTILLER AUTONOMOUS and independent from other "SOURCES". In essence we are concerned with suitably MODIFYING the THERMODYNAMICS of the RANKINE-HIRN CYCLE.

In order to trace the cycles (Table A), (Plates 1 & 2), (figs. 1, 3 & 5) we made use of the Variables (p,v,T,H,S), linked by the Enthalpic Potential dH=5Q+vdp, to define the Isobaric dp=O and Adiabatic δQ=O transformations, the THERMAL BALANCE (Q₁) and (Q₂), and the EFFICIENCY (η) of the SYSTEM, as a function of the three ENTHALPIC MAGNITUDES (H,,H₄,H₅):

However the "WORK" L=(H₄-H₅) does not depend on the "ENTHALPY" (H₁) of the Liquid, so that it may vary H*≠Hj on the CURVE Limit ξ'=(AC),(x=0) _of the LIQUID with the following values for EFFICIENCY (η*≠η):

This means that (figs. 3 & 5) the ENTHALPY (Hi) of the Liquid can effectively be OPTIMIZED (H*) on the Curve Limit (AC), obtaining (bold lines) two HEAT-GAINS Q*=(H*-H₁)=(l-l")+(l-l')^>0, one subtracted Q"=(l-l")>0 from the VAPOR (4-4') and the other LATENT from CONDENSATION Q'=(l-1 ')>0, both of these RECYCLED in the Economizer (E), making the BALANCE (2) and (3) of the previous "CYCLES" (figs. 3 & 5) assume the following FORM, taking into account that, in these CASES (Thermal Increase) cMΔT kcal, M kg OfH₂O from Zero to T⁰C, or 2M kg from Zero to T/2°C (in general n M kg from Zero to T/n°C, n≥l) can be recycled:

~

In this way we obtain the above-named (figs. 3 & 5) "ENTHALPIC CYCLES", that, like the RANKINE-HIRN CYCLES are based on the two extreme "ISOTHERMOBARS" (5-6),(2-3) & (5'-6'),(2-3) of the "SATURATED VAPOR", situated at a maximum distance of (5-6)<->(2-3) (figs. 3 & 4) in the "ENGINES", or (figs. 5 & 6) almost ENGINES AND DISTILLERS

coincident (5'-6')→(2-3) in the "DISTILLERS", where the WORK (4-5') (Enclosed Area) may diminish (L→O) until the SYSTEM becomes AUTONOMOUS, with the possible addition of a HYDRAULIC Turbine (T_o),(p'->pi). We will describe briefly the two most interesting ENTHALPIC CYCLES (figs. 3 & 5), highlighting the Transformations at constant concentration and pressure of the First-Sides (l-2),(x=0),(dp=0)e(ξ'=AC),(x=0) and the respective HEAT GAINS Q*=(Q'+Q")<≡(ξ') of the THERMAL BALANCE (4), that leave that WORK unchanged (L*=L) but increase the EFFICIENCY in the "ENGINES" (η*>η), V(Q*>0), and in the DISTILLERS until the UNITARY value (η*=l),V(Q*≥Q₂).

A) ENTHALPIC CYCLE "ENGINE" (1.2.3.4.5.6«n. (Plate 1). (figs. 3 & 4). The Feed Pump (P_A) compresses the Liquid (M'),(p0,(T,),(x=0) at the Starting-Point

and thus Heats it (in E) along the line of equal concentration and pressure (l-2),(p₂),(Ti→T₂)e(ξ'=AC),(x=0), utilizing the Heat (l-l")=(4-4') subtracted from the VAPOR (3-4'), the LIQUID then Evaporates on the Isothermobar (2-3),(p₂),(T₂),(x->l), Superheats (3-4),(p₂),(T₂→T₄),(x=l), Expands in the Turbine (4-5),(p₂→pi),(T₄→T₁),(x→x₅), and finally Condenses (in K) along the Isothermobar (5-6),(pi),(Ti),(x-»0). In the Balance (4) the Gain Q*=(Q") increases the Work Efficiency by 30-40% (4-5) (enclosed area).

B) ENTHALPIC CYCLE "DISTILLER" (1.23A.5'.6'.6*1\ (Plate 2), (figs.5 & 6). The Liquid (MO₅(P_t)₅(T₁), & (x=0), Compressed at the Starting-Point (6«l),(pi->p₂),(T]), is Heated along the line of equal concentration and pressure (l-2),(p₂),(T₁-»T₂),(x=O)e(ξ')_; using the Heat Q"=(l-l")=(4-4') subtracted from the Vapor (3-4'), then Evaporates (Boiling) on the Isothermobar (2-3),(p₂),(T₂),(x→l), Superheats (3-4),(p₂),(T₂->T₄),(x=l), and Expands in the Turbine (4-5'),(p₂→p'),(T₄-yr), before proceeding on the Condensation Isothermobar (5'-6'),(p'),(T'),(x->0), with the possible application of the Condenser (K), surrendering the Gain Q'=(l-l')<(5'-6') to the Liquid (M'),(x=0) along the line of equal concentration and pressure (l-2),(p₂),(T₂)e(AC),(x=0).

The Unitary Efficiency (η*=l) is obtained by Optimizing the positions of the Isothermobars (5'-6'),(2-3) with respect to Critical-Point, while the Work L=(4-5') (enclosed area) diminishes (L→0) until (L>0) the "DISTILLER" becomes "AUTONOMOUS", separating DRINKING WATER (Z) from the Contaminated-Liquid (P_A). ENGINES AND DISTILLERS

Moreover, the same Unitary Efficiency (η*=l) is obtained more easily (figs. 5 & 6) at Lower Pressures (pi<p'<P2), equating the Areas Under (Q⁺=Ch) the two Curves of Condensation (5'-6') and Cooling (6'-6).

C) "SIMPLE" ENTHALPIC DISTILLER (figs. 5 & 6\ In the limit (p'->p₂),(L→0), we can substitute the TURBINE (T) with a REDUCER (R), while the UNITARY Efficiency is obtained more easily by RECYCLING all the CONDENSATION HEAT (l-l')=(5'-6') with the possible application of both GAINS (Q"+Q') and an added HYDRAULIC Turbine (T₀), (p'→Pi) that links the Well (Z) to the Outgoing Liquid (M').

In short, in the First Sides (l-2),(p₂),(T,→T₂)e(AC),(x=0) of the ENTHALPIC CYCLES (figs. 3 & 5), the ENTHALPY (H) of the Liquid can OPTIMIZE the THERMAL BALANCE (4) with one or both of the GAINS Q*=(Q"+Q') RECYCLED in the Economizer (E), thus causing an increase in the EFFICIENCY until the UNITARY value.

In particular the DISTILLER can RECYCLE all of the CONDENSATION-HEAT Q'=(l-l')=(5'-6') with UNITARY Efficiency, absorbing from a UNIQUE SOURCE only the MISSING HEAT, that is the HEAT needed to produce the "DISTILLATE" (Drinking Water) and the WORK necessary for the operation of the DISTILLER. For these REASONS and for the "Predictable-Consequences", an "EXPERIMENTAL TRUTH" arises that will put into discussion the ENTROPY of CLAUSIUS, an unusual DIFFERENTIAL dS=δQ/T where the THERMAL EXCHANGE δQ also becomes a DIFFERENTIAL dQ=TdS that occurs in particular TRANSFORMATIONS and thus dS=δQ/T cannot ALWAYS represent the "SECOND LAW OF THERMODYNAMICS". At this point, certain of the RELIABILITY of the above, the RESEARCH may be considered concluded. However it is worthwhile continuing the study to consider the possible applications and the choice of the most suitable Thermodynamic- Fluids, including those of Refrigerators, together with the use of these Fluids in various SYSTEMS. We will (even if it is unnecessary) give some indicative examples of the previous ENTHALPIC CYCLES A), B), C) for Water (H₂O), with the respective Thermal Balances (2) and (4), using Table A and the following Comparative Equations (5) that link the Concentration (x), the Entropy (S_x) and the Enthalpy (H_x) of the Mixture (M), assuming a Hypothetical Flow m=10(kg/s)=0,l(kg/Cycle), at a rate of, for example, 100 (Cycles/s), that determines the average Power N=mL (kW) and the order of Magnitude of the System. ENGINES AND DISTILLERS

S_x — S H_x — H

(5)

S"-S' H"-H'

In the Entropic Plane Ω(T, S) we have traced (Table A), (Plates 1 & 2) the ENTHALPIC CYCLES of the WATER (H₂O), assigning the two Isothermobars of the SATURATED VAPOR (5-6X(P₁)XT₁) and (2-3),(p₂),(T₂), in addition to (not included in the table) the Superheating T₄(⁰C), H₄(kJ/kg), the Isentropic S₄=S₅(kJ/kgK), and the ENTHALPIES of the Liquid (H',H")e(ξ⁽). Thus, with (5) we calculate the Coordinates of the end of the Expansion (X₅)XH₅), the HEAT-GAINS Q*=(Q',Q")<≡(ξ'), and finally the corresponding HIRN-THERMAL BALANCES (2) and the ENTHALPY (4), having the same Work ^=L=H₄-H₅) but different EFFICIENCIES (η*>η). 1) RANCHINE-HIRN "NORMAL" CYCLE (1.2.3.4.5.6« D (Table A. Plate 1. figs. 1 & 2). On the lower Isothermobar (1-E) we assign:

S_J=0.296, S_E=8.666; then on the upper Isothermobar (2-3): T₂=200(°C), p₂=16 (arms), in addition to (not included in the table) T₄=400(°C), HU=3256, S₄=S₅=7.243; and the Flow m=10(kg/s). Finally (in 5) we calculate (x₅), (H₅) and the Balance (2) of the HIRN-CYCLE: χ₌ S₅ -S_{1 ^} 7.243 - 0.296 ^ ₃₃

(6)1 5 S₁₁ -S, 8.666 -0.296

H₅ = X₅[H _E - H₁)+ H₁ = 0.83(2537 - 84)+ 84 = 2120(U/ kg) (6)2

[Q₁ [Q₂

ENGINES AND DISTILLERS

1-A) ENTHALPIC CYCLE "ENGINE" (l.l".2.3.4.5.6«n (Table A. Plate 1. figs. 3 & 4).

The most suitable ENTHALPIC CYCLE ENGINE is obtained by applying to the previous HIRN-CYCLE the maximum HEAT GAIN Q"=(l-l")=(H"-H,)=(852-84)=768, RECYCLED from the Upper-Area (S) to the Lower- Area (E) of the Generator (G), with an Efficiency (η*=0.47) that turns out to be higher than 30% with respect to (η=0.36):

A further increase in the Efficiency (η*), until 30-40%, is obtained if the corresponding "THERMAL CYCLES"

(HIRN and ENTHALPIC) occupy greater Areas in the Field (ACBA) of the Mixture (M).

2) HIRN CYCLE "displaced UPWARDS" (l'.2.3.4.5.6'«r\ (Table A. Plate 2. figs. 5 & 6).

On the lower Isothermobar (6'-E') we assign: Ti=300(°C), p,=87.6 (atms), H,=1345, H_E=2749, S)=3.255, S_E=5.705; on the upper Isothermobar (2-3): T₂=350(°C), p_z=168.6 (atms); and then (not included in the table) T₄=400(°C),

H₄=2930, S₄=S₅=5.777; and the Flow m=10(kg/s). Finally (in 5') we calculate (x₅), (H₅) and the Balance (2) of the

HIRN CYCLE:

_ S₅ - S_{X =} 5.777 - 3.255 x (S)₁ ~ S_s - S₁ ^~ 5.705 -3.255 ⁼

H₅ = x₅(H_E -H₁)+ H₁ = 1 (2749-1345) + 1345 = 2749(kJ/kg) (8) '2

\ r_Ql ^x -( )fc*-H.¹HC ∞rø 'kg) (8)

2-B) ENTHALPIC CYCLE "DISTILLER" (UM".2.3.4.5',6'. 6^1), (Table A. Plate 2, figs. 5 & 61

From the above the ENTHALPIC CYCLE DISTILLER is obtained by displacing the Starting-Point downwards

(6*1), (T=IOO⁰C), (p=1.033 atms), so that HEAT-GAIN {V-6) REDUCES (Q₂=1404) to Q'=(H,-419)=926, with an

EFFICIENCY (η*=0,27) higher than 145% with respect to the EFFICIENCY (η=0.11) of the starting HIRN-

CYCLE:

η^*= — — = ^i = 0.27 (9)

Qx - Q 1585 -926 ENGINES AND DISTILLERS

This EFFICIENCY may become UNITARY (η*=l) by Recycling both GAINS Q*=(Q"+Q')⁼(Q₂=1404), Q'=926<(Q₂) and Q"=(1404-926)=478. In such a way the DISTILLER absorbs only the HEAT necessary to produce the HOT-DRINKING WATER (at 100⁰C and 1 arm) and the WORK (L=I 81) needed to make it AUTONOMOUS: η^__L_₌ «ⁱ _{= 1 (10)}

Q₁ -Q^* 1585-1404

In these cases we need to perfection the Optimization of the 2 extreme Isothermobars (5'-6'), (2-3) and the Starting- Point (6«l)e(AC), (x=0) with respect to the Critical Point (C) reducing to a minimum (L→O) the WORK L=(4-5') (enclosed area), possibly substituting the Turbine (T) with a Pressure-Reducer. In addition (fig. 6) it is worth using the Jump in Pressure

through a HYDRAULIC TURBINE (T₀) that connects the Well (Z) to the Outgoing Liquid.

Claims

ENGINES AND DISTILLERS

PATENT CLAIMS

1) The ENTHALPIC CYCLES of the "STEAM MACHINES" as defined above (Title, Description, Tables and Drawings), of which we CLAIM all possible VARIANTS and APPLICATIONS in the field of RESEARCH, taking into account possible MODIFICATIONS, concern an authentic "ABSOLUTE NOVELTY" incompatible with the "SECOND LAW OF THERMODYNAMICS", based essentially on the INCORRECT interpretation of the RANKINE-HIRN-CYCLE (figs. 1 & 2), demonstrating that its First-SIDE (l-2),(dp=0) is not found (as expected) in the Liquid Zone (L) but on the line of equal concentration and pressure (x=0), (dp=O), belonging to the Curve Limit (AC),(x=0) of (ACBA), with REMARKABLE but predictable THERMODYNAMIC consequences.

2) The ENTHALPIC CYCLES of the above CLAIM are characterized by the fact (figs. 3 & 5) that their First- Sides (l-2),(dp=0),(ΔT≠0) belong to the Curve Limit (AC),(x=0) of (ACBA), where the ENTHALPY of the LIQUID (H₁) can be OPTIMIZED (H*>H,)e(AC) recycling two HEAT GAINS (1-1'),(M"), (bold lines) from High to Low TEMPERATURE, while the WORK (4-5),(4-5') (enclosed area) acquires an EFFICIENCY 30-40% greater than with the corresponding RANKINE-HIRN CYCLE (figs. 1 & 2).

3) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 6), (Plate 2) that in the DISTILLERS the EFFICIENCY can become UNITARY (η*=l) by RECYCLING all the Latent-Heat of CONDENSATION Q₂=(5'-6'), through one or both of the GAINS (1-1'X(I-I"), in addition to OPTIMIZING the positions of the extreme ISOTHERMOBARS (5'-6'),(2-3) and the Starting-Point (6=1) with respect to the Critical Point (C).

4) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 6), (Plate 2) that in the SIMPLE DISTILLERS it is opportune to reduce to a minimum the WORK (enclosed area), almost eliminating it altogether (L-»0), allowing just enough to make the DISTILLERS AUTONOMOUS, separating the POTABLE WATER (Z) from the CONTAMINATED LIQUID (P_A), favored by the GAINS (Q"+Q') and HYDRAULIC TURBINE (T_o),(p'→p0 that adds USEFUL WORK.

5) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 6), (Plate 2) that in the SIMPLE DISTILLER the EFFICIENCY can become UNITARY (η*=l) by RECYCLING only the Latent Heat of CONDENSATION (1-1')≤(Q₂) or both GAINS (1-1'),(1-1"), also when the WORK is negligible (L→O) and thus it is opportune to substitute the Turbine (T) with a Pressure Reducer (R). ENGINES AND DISTILLERS

6) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 3 & 5), (Plate 1 & 2) that other than the HEAT-GAINS (l-l'),(l-l")<=(AC),(x=0) the EFFICIENCY can be improved by possible VARIANTS applied to modern SYSTEMS, in particular so-called STEAM TAPPING systems.

7) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 6), (Plate 2) that the most advantageous DISTILLER ENGINE, with the maximum EFFICIENCY is obtained by OPTIMIZING the 3 Pressures (pi<p'<P₂) until the maximum WORK is produced (enclosed area) with the maximum GAIN (Q*≤Q₂).

8) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 6), (Plate 2) that in the SIMPLE DISTILLER the two Pressures (p'<p₂) may almost become coincident (p'-»P₂) in such a way as to obtain the minimum WORK (enclosed area) with the maximum GAIN (Q*≤Q₂).

9) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 3 & 5), (Plate 2) that in the HEAT GAIN Q"=(l-l")e(ξ'), common for all Enthalpic Cycles, it is opportune to employ an AUTONOMOUS CIRCUIT in parallel, where the CIRCULATING LIQUID, oriented by a DIRECTOR (N) and aided by a LUNG (M) of INERT-GAS, is moved by the external PUMP (P) at a constant PRESSURE (p*) high enough (p*>p₀) with respect to p_o=f(T_o) of the SATURATED VAPOR.

10) The ENTHALPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 3,4,5,6) that in the previous EXPLANATION (Summary, Description and Drawings) we have adopted the same SYMBOLOGY as in the most common TECHNICAL MANUALS, omitting (for brevity) the respective scientific definitions.