WO2009011002A2

WO2009011002A2 - Steam engines with unitary efficiency

Info

Publication number: WO2009011002A2
Application number: PCT/IT2008/000371
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: ITRM20070390A1; WO2009011002A3

Abstract

BEFORE and/or AFTER the ISOTHERMOBARIC phases (dT=0),(dp=0), of BOILING, the PHYSICAL STATE of a MIXTURE M=(M'+M'), formed by a LIQUID (M') with its VAPOR (M'), is defined (GIBBS) by STATE EQUATIONS of the type p=f(T,x) that include the PRESSURE (p), TEMPERATURE (T) and CONCENTRATION (x=M'/M) of (M). In particular, all the TRANSFORMATIONS p=f(T,x0) at constant concentration (dx=0) occur (fig.3) on the LINE of EQUAL CONCENTRATION (FC),(dx=0), between the two CURVE LIMITS (AC)3(BC), of the FIELD (ACBA). In these transformations we obtain the FIRST SIDES (OP),(dx=0), of the unexpected ENTROPIC CYCLES (O,P,3,4,5,O) where the EFFICIENCY increases ∀(x0>0), becoming UNITARY ∀(x0≥x5), from the CYCLE (5,M,3,4,5),(fig.5) to the CYCLE (N,3,4,5,N),(fig.7). These particular THERMAL CYCLE (figs 5,7), without CONDENSATION, may have a REMARKABLE application in the use of REFRIGERATOR FLUIDS at temperatures (e.g. FREON) where energetic EXCHANGES (δQ,δL) may almost be FREE, attaining (might we say) the utopist SECOND TYPE of PERPETUAL MOTION.

Description

DESCRIPTION of the Industrial Invention ENTITLED: "STEAM ENGINES WITH UNITARY EFFICIENCY"

DESCRIPTION

In the Entropic-Plane Ω(T,S) the main Aggregation States (figs.1,2) of the Matter (e.g. H₂O), Solid (S), Liquid (L), Vapor (V), Gas (G), and the Field of Existence (ACBA) of the MIXTURE M=(M'+M") of CONCENTRATION X=(WM), formed by a LIQUID M'(x=0) with its VAPOR M"(x=l), whose "PHYSICAL-STATE" depends (GIBBS) on two VARIABLES, therefore may be expressed by the following "CLAPEYRON-DIFFERENTIAL" as a function of the TRIPLET (Pressure-Temperature-Concentration), which is RESOLVED with INTEGRALS of type p=f(T,x), the Specific Volumes v(m³/kg) being v'(T),v"(T) r(T) and the Transformation Heat r(J/kg) of the two Phases (M', M"):

Furthermore we include the SATURATED VAPOR produced by the LATENT HEAT during "BOILING", defined by the ISOTHERMOBARS (dT=0) and (dp=O) in the Subsets of the Interval (O≤x≤l) on the horizontals of (ACBA), where the pair of CONSTANTS (T,p) render the other variables (Enthalpy, Entropy, Concentration, Volume etc.) UNDETERMINED. ALL the Transformations p=f(T,x) at constant CONCENTRATION (dx=0) occur on the lines of equal CONCENTRATION (FC),(dx=0) between the 2 Curve-Limits (AC) and (BC) of (ACBA), taking into account that in these CASES (dx=0) any ISOTHERMAL increase in PRESSURE (dT=0),(Δp≠0) requires an adequate ISOBARIC increase in TEMPERATURE (dp=O),(ΔT≠O) until BOILING starts again, as long as p=f(T,x) V(X=X₀). To those lines of equal CONCENTRATION (FC),(dx=0) belong the FIRST-SIDES (OP),(dx=0),(dp=0) of new THERMAL-CYCLES (O,P,3,4,5,O) where the same WORK (4-5) CANNOT represent the different Enclosed Areas jδQ≥O due to the LATENT HEAT (5-O) thatV(x_o>x₃) INVERTS ITSELF (changing sign) in the Interval (5- N) and thus the ISENTROPES (4-5),(dS=0) DO NOT coincide with the ADIABATICS (δQ=O). Indeed, the THERMAL EXCHANGE (JδQ≥O) becomes the DIFFERENTIAL dQ=TdS of particular 1NVERTIBLE (dS=dQ/T)O(dQ=TdS) PRIMITIVE-THERMALS with ENTROPY dS=dQ/T, which we have RESOLVED in finite terms with STATE EQUATIONS ΔS=f(F,s)=g(p,V) in the MECHANICAL SYSTEMS O(F,s),O(p,V). In these CASES the ISENTROPES (dS=O) form a SET of INTEGRAL CURVES fi(F,s)=g(p,V)=Constant NON-ADIABATIC (δQ≠O), while δQ is EQUAL to the INTERNAL-ENERGY (δQ)v=(dU)_v and/or the ENTHALPY (δQ)_p=(dH)_p along the ISOCHORS (dV=O) and/or the ISOBARS (dp=O), in addition to in the VAPOR-GENERATORS where (dV=O),(dp=O).

In this way we obtain the ENTROPIC-CYCLES (O,P,3,4,5,O) where the EFFICIENCY increases V(x_o>0) becoming UNITARY V(x_o>x₅) from the CYCLE (5,M,3,4,5),(fϊg.5) to the CYCLE (N,3,4,5,N),(fig.7), which assume a REMARKABLE importance with the application of "REFRIGERATOR-FLUIDS" at low temperature (e.g. Freon) that in OPTIMAL conditions (with respect to the external temperature) allow almost "FREE" ENERGETIC EXCHANGES (6Q,δL). Here we are dealing with unusual INTUITIVE HYPOTHESES of which we will try to check the presumed RELIABILITY. In every Transformation p=f(T,x), the ENTHALPIC POTENTIAL dH=δQ+vdp defines the ISOBARS (dp=O), the ADIABATICS (6Q=O), the lines of equal concentration (Q_Op), and finally the THERMAL BALANCE (Qi,Q₂) with its EFFICIENCY:

U dp = 0) => dH = δQ

{(£0 = 0) => dH = dL = vdp ⁽¹⁾

LATENT HEAT decreases Q₂=(H₅-H₀) INVERTING itself V(X_0--X₅) (changing SIGN), as the BALANCE (3) of the CYCLE (N,3,4,5,N) demonstrates with the following EQUIVALENCE (Q=L) that produces a UNITARY EFFICIENCY (η=l): Q = (H_N - H₅) + JdH ₊ (H₄ - H₃) = (H_N - H₃) + JdH + (H₄ - H₅) (4)

Apart from the UNITARY-EFFICIENCY, the EQUATION (5) represents the EQUIVALENCE (<=>) between the HEAT (Q) and WORK (L), that is "JOULE'S LAW", common to all THERMAL ENGINES where:

Q = (Q₁ - Q₂) ^ (H₄ - H₁J - (H₅ - H₁J = (H₄ - H₅) = L (6)

We suppose that the EQUIVALENCE (6) represents the Enclosed Areas of ALL the THERMAL CYCLES. In effect this is TRUE in the Enthalpic Cycles (of the previous Patent) but NOT in the ENTROPIC CYCLES (O,P,3,4,5,O), (figs.3,5,7) as the following INTEGRALS of ENTHALPIC HEAT (Q_E) and ENTROPIC HEAT (Qs)demonstrate (2), extended to the FIRST-SIDES (OP)e(FC),(dx=0), obtaining QE=QS only for (OP)e(AC),(x=0) while instead Q_E≠Qs V(OP) g(AC),(x=0), as the MEAN-INTEGRAL Qop≠T_m(S_P-S_o) also CONFIRMS (see tables):

Q_E = JdH = (H_P - H₀) Q_s = JTdS = T_1n(Sp - S₀) (7) o o

For these reasons the EFFICIENCY increases in the Interval (0<x<l), becoming UNITARY V(X₀SXs) from the "CYCLE" (5,M,3 ,4,5) (figs.5,6) to the "CYCLE" (N,3,4,5,N) (figs.7,8). In these particular "ENTROPIC CYCLES" (figs.5,7) without CONDENSATION, it is therefore WORTHWHILE employing "REFRIGERATOR-FLUIDS" at Low-FUSION (NH₃, C0₂₎ SO₂, CH₄, C₂H₄, C₂H₆, C₂H₈, CH₃C1, FREONS etc.), which in "OPTIMAL Conditions" (with respect to the environmental temperature) allow almost "FREE" ENERGETIC EXCHANGES (δQ, δL). Unlike other STATE-FUNCTIONS, the Postulates of "CARNOT-CLAUSIUS" define the ENTROPY (S) with the DIFFERENTIAL dS=δQ/T, including the unusual REVERSIBILITY dS<=>δQ that also TRANSFORMS the THERMAL-EXCHANGE δQ into the DIFFERENTIAL dQ=TdS. As this occurs ONLY in CERTAIN CASES, we deduce that the ENTROPY does NOT always represent the "SECOND-LA W-OF-THERMODYNAMICS", or PERHAPS, taking into account (as we will do), the ENGINE that PERFORMS the "CARNOT CYCLE". Let as describe briefly from the generic (O,P,3,4,5,O) (fϊgs.3,4) to the two most representative CYCLES (5,M,3,4,5) (figs. 5,6) and (N,3,4,5,N) (figs.7,8), taking into account possible errors, Gains (fig-4) and Vapor leaks etc. A) ENTROPIC CYCLE (O,P,3A5,O) (figs.3.4V The Feed Pump (P_A) compresses the Mixture (pi),(Ti),(x=Xo) at the Starting-Point O,(p₂),(Ti),(x=x_o) so that it heats (p₂)XT,->T₂)Xx=Xo) along the line of equal concentration and pressure (OP),(x=x_o) until the new Isothermobar (P-3),(p₂),(T₂),(xo≤x≤l) comes into play (in P), so that the Mixture becomes Vapor on the line (P-3),(p₂),(T₂),(x=l), Superheats (3-4),(p₂)XT₂→T₄)Xx=l), Expands (4-5),(p₂→pi),

Condenses (5-O)₁(P_I)₅(T₁)XX_O-SX-SX₅), and finally is transported by the Pump (P_E) into the Well (Z) so that it may return to (P_A).

B) ENTROPIC CYCLE (5.M.3.4.5) (figs. 5 & 61. The Pump (P_A) compresses the Mixture

at the Starting-Point

so that it heats (p₂),(Ti-»T₂)Xx=x₅) along the ling of equal concentration and pressure (5-M),(x=x₅).

Then it Evaporates (p₂),(T₂),(x=l) on the Isothermobar (M-3), Superheats (3-4)Xp₂),(T₂→T₄)Xx=l), Expands (4-5),

and finally is transported by the Pump (P_E) into the Well (Z) so that it may return to (P_A).

C) ENTROPIC CYCLE (N.3A5.N) (fig. 7 & 8). The Feed Pump (P_A) compresses the Vapor (M") (pi),(Ti),(x=l) at the Starting-Point (O=N)Xp₂)XT₁)Xx=I) so that it heats

along the line of equal concentration and pressure (N-3),(x=l) until it reaches the new Isothermobar at the Point (P=3),(p₂),(T₂),(x=l) thus Superheating on the line (3-4)Xp₂)XT₂->T₄),(x=l), Expanding in (4-S)₁(P₂-^P_I)XT₄-J-T₁)XX=X₅), being transported by the Pump (P_E) to the Well (Z), finally completing (in G) the Isothermobaric Evaporation (5-N)XPi)XT₁)Xx=I), before returning to (N),(P_A). At this point we might consider the research at an end, all applications being easily realizable. However, certain of the reliability of the above, it is worthwhile examining further the choice and use of the most suitable fluids, especially those used in REFRIGERATORS, and how these fluids might be used in various systems. We will though proceed briefly with the analysis of the CYCLE (N,3,4,5,N) (figs. 7 & 8) with the employment of 4 FLUIDS (Plates 1,2,3,4); Water (H₂O), Freon-12 (CF₂Cl₂), Ammonia (NH₃) and Carbon-Dioxide (CO₂) in normal Thermodynamic Conditions. In order to simplify the calculations we will apply the following Comparative- Equations for the main variables; Saturated Vapor, Concentration (x₅), Entropy (S₅), Enthalpy (H₅); with a hypothetical Flow m=10(kg/s)=0.1(kg/Cycle), at for example 100 (Cycles/s), that serves only to evaluate the probable mean Power N=mL (kW) and the order of magnitude of the Systems, confirming the respective UNITARY Efficiencies. S₅ -S₁ H₅ -H₁

X₅ = (8)

S_N - S₁ H_N - H₁

1) H₂O (Water). ENTROPIC CYCLE (N.3.4.5.N) (Table A. Plate 1. figs. 7 & 8). The Mixture (M), (x=x₅) becomes Vapor (M"),(x⁼l) on the Isothermobar (5-N), so that it heats along the line of equal concentration and pressure (N-3)e(BC), Superheats in (3-4),(p₂),(T₄), and finally Expands in T(4-5). We assign (Table A) T,=20 (⁰C), H,=84, HN=2537, S,=0.296, S_N=8.666, T₂=200(°C), therefore (not included in the table) T₄=400 (⁰C), H₄=3254, S₄=S₅=7.243, in addition to the values (8) of (x₅) and (H₅) and the Flow m=10(kg/s), in order to obtain the Thermal Balance (3) of the Cycle, that is the Work (L) with its Unitary Efficiency (η=l):

X₅ = 2120(kJ/kg) (9)₀

Q = (H_N - H₅J ₊ (H₃ - H_N) + (H₄ - H₃) = (H₄ - H₅) = L (9),

JQ = (H₄ - H₅) = L = 1134 (kJ/kg) |₇ = L/Q = 1 ; N = mL = 11340 (kW)

Displacing the First-Side (N-3),(x=l) on the Curve-Limit of the Liquid (l-2)e(AC),(x=0) we obtain the corresponding HIRN-CYCLE (1,2,3,4,5,1) where the Condensation (5-1) allows the same WORK L=(H₄-H₅)= 1134(kJ/kg) with an EFFICIENCY (η=0,36) inferior by (l-0.36)=64% compared with the previous (η=l):

2) CF₂Cl₂ (Freon-12). ENTROPIC CYCLE (N.3.4.S.N) (Table B. Plate 2. figs. 7 & 8). The Mixture (M),(x=x₅) Evaporates (M"),(x=l) along the Isothermobar (5-N), then heats on the line of equal concentration and pressure (N-3)e(BC), Superheats (3-4), and finally Expands (4-5). We assign (Table B) T,=-70(⁰C), H,=359, H_N=539, Srθ.938, S_N=4.842, T₂=+10(°C), in addition to (not included in the table) T₄=+30(°C), H₄=590, S₄=S₅=4.790, and finally the Flow m=10(kg/s)=0.1(kg/Cycle) with the following results:

x₅ = ~|- = 0.94 ; H₅ = X₅ (H_N - H₁J ₊ H₁ = 528(kJ/kg) (H)₀

3) NH₂ (Ammonia^') ENTROPIC CYCLE ^3.4.5.N-) (Table C, Plate 3. figs. 7 & 8~). The Mixture (M),(x=x₅) Evaporates (M"),(x=l) along the Isothermobar (5-N), Heats on the line of equal concentration and pressure (N-3)e(BC), Superheats (3-4),(in S), and finally Expands (4-5). We assign (Table C) T,=-60(°C),

H_N=1591, S_!=3.084, S_N=9.842, T₂=+100(°C), in addition to (not included in the table) T₄=150 (⁰C), H₄=1890, S₄=S₅=8.25, and finally the Flow m=10(kg/s)=0.1(kg/Cycle):

X₅ = 1^=^ = 0,76 ; H₅ = X₅ (H_N - H₁) + H₁ = 1245(kJ/kg) (12)₀ o_N - O,

JQ = (H₄ - H₅) = L = 645 (kJ/kg) [η = L/Q = l ; N = mL = 6450 (kW)

4) CO₂ (Carbon-Dioxide) ENTROPIC CYCLE (N.3.4.5.N) (Table D. Plate 4. figs. 7 & 81. The Mixture (M)(x=x₅) Evaporates (M")(x=l) on the Isothermobar (5-N), Heats on the line of equal concentration and pressure (N-3)e(BC) and Superheats (3-4). Then it Expands T(4-5). We assign (Table D) T,=-50(°C), H,=314, H_N=651, S,=3.777, S_N=5.288, T₂=+10(°C), in addition to (not included in the table) T₄=50(°C), H₄=709, S₄=S₅=5.192, and finally the Flow m=10(kg/s)=0.1 (kg/Cycle) as follows:

X₅ = — |^ = 0.936 ; H₅ = X₅ (H_N - H₁) + H₁ = 629(kJ/kg) (13)₀

The research supposes the effective possibility of realizing all the ENTROPIC CYCLES (figs. 3,5,7) described in this Patent and Summarized in A), B) and C), with any possible apparatus suitably modified, for example an apparatus that facilitates the Transformations of equal concentration and pressure of the First Sides (OP) e (FC), (dx=O), taking into account the Gains (fig. 4) obtained by the transmission of Heat from the Upper Zone (S) to the Lower Zone (E) of the Generator (G). These new THERMAL CYCLES concern all "VAPOR SYSTEMS", including "DISTILLERS" and in particular "REFRIGERATION-SYSTEMS" that function by inverting several Transformations. The characteristic principal of these systems consists in the fact that in the FIRST SIDES (OP)(2(AC),(dx=0) we obtain dH=δQ≠TdS, and thus (see tables) ΔH≠T_mΔS. This means (figs. 3,5 & 7) that the same WORK L=(H₄-H₅) cannot represent the Enclosed Areas (δQ≠TdS) and therefore does NOT DEPEND on the "ENTROPY" (dS=δQ/T) of the Fluid. In every case the EFFICIENCY increases V(X₀X)) reaching the UNITARY value (η=l),V(xs≥Xo) from the "CYCLE" (5,M,3,4,5),(figs. 5,6) to the "CYCLE" (N,3,4,5,N),(figs. 7,8) where the ENERGETIC EXCHANGE (Heat δQ and Work δL) becomes practically "FREE" with the employment of suitable "REFRIGERATOR FLUIDS" at low temperature, positioning (at least partly) the respective "ENTROPIC DIAGRAMS" at temperatures under the External Temperature (TE). Furthermore, by using suitable MECHANISMS the position of the extreme ISOTHERMOBARS (1-N), (2-3) with respect to the External Temperature (T_E) and the Critical Point (C) can easily be OPTIMIZED in REAL-TIME, in order to transform instant by instant all the ABSORBED HEAT into FIRST ORDER ENERGY. We repeat that here we are concerned with an authentic "ABSOLUTE TRUTH" essentially based on the TRUE "Concept of ENTROPY", a STATE FUNCTION S=f(F,s)=g(p,V) incompatible with the POSTULATES of "CARNOT" and "CLAUSIUS", that is to say with the "SECOND-LAW-OF-THERMODYNAMICS", an extraordinary unforeseen result that realizes (let us say it) the so- called "SECOND TYPE of PERPETUAL MOTION".

Claims

PATENT CLAIMS

1) The ENTROPIC CYCLES with UNITARY EFFICIENCY specified above, of which we CLAIM all possible MODIFICATIONS and APPLICATIONS concern an ABSOLUTE NOVELTY INCOMPATIBLE with the SECOND LAW OF THERMODYNAMICS where the First Sides (OP),(dp=0),(ΔTτiO) belong to the lines of equal concentration (FC),(dx=0) between the Curve-Limits (AC) and (BC) of (ACBA), while the THERMAL EXCHANGE (Q_0P) produces an ISOBARIC increase of TEMPERATURE (dp=O),(ΔT≠O) until BOILING starts again which OCCURS on the ISOTHERMOBARS (P-3),(dp=0),(dT=0),(x_o<x≤l) of the SATURATED VAPOR. In these CASES the LATENT HEAT (5-O), (dp=O),(dT=O), (x_o≤x≤l) INVERTS itself (changing SIGN) at the POINT (5),(x=x₅) while the EFFICIENCY increases V(x>0) becoming UNITARY V(x_o≥x₅) from the CYCLE (5,M,3,4,5) (fig. 5) to the CYCLE (N,3,4,5,N) (fig. 7). In particular, the First Side (l-2),(dp=0),(ΔT≠0) of the RANKINE-HIRN CYCLE does not occur as one EXPECTS in the LIQUID Zone (L) but on the First adjacent line of equal CONCENTRATION (AC),(dp=0),(ΔT≠0) of (ACBA).

2) The ENTROPIC CYCLES of the previous CLAIM as described in the EXAMPLES A), B) and C) are above all characterized (figs. 3, 5 & 7) by the Transformations of equal CONCENTRATION (FC),(dx=O) of the FIRST SIDES (OP),(dp=0),(ΔT≠0) where the MIXTURE (M),(x=Xo) is SUBMITTED to an ISOTHERMAL COMPRESSION (Δp>O),(dT=O) at the STARTING POINT (O) and then the corresponding ISOBARIC HEATING (ΔT>O),(dT=O) on the line of equal CONCENTRATION (OP),(dp=0),(ΔT≠0), as OCCURS in the FIRST SIDES (l-2),(dp=0),(ΔT≠0) of the previous ENTHALPIC HIRN CYCLES, taking into account that at the STARTING- POINT (0=5) of the particular CYCLE (5,M,3,4,5),(fig. 5) the SATURATED VAPOR becomes DRY.

3) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact that the ENGINES (figs. 4,6,8) can be transformed into DISTILLERS or REFRIGERATOR SYSTEMS by suitably modifying the TRANSFORMATIONS, the APPARATUS and the positions of the extreme ISOTHERMOBARS (1-N) and (2-3). IV) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 3, 5 & 7) that displacing the FIRST SIDE to the right (OP)e(FC),(x=x_o) the Changes of State (5-0) diminish thus increasing the EFFICIENCY.

5) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 7) that V(x_o≥x₅) they occur without CONDENSATION and therefore have UNITARY EFFICIENCY, from the Cycle (5,M,3,4,5) (fig. 5) to the Cycle (N,3,4,5,N) (fig. 7) where the Absorbed Heat (QO becomes almost FREE with the employment ofREFRIGERATOR FLUIDS at low temperature.

6) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 7 & 8) that they can be easily realized in the VARIOUS ways A), B) and D) including the particular CYCLE (N,3,4,5,N), which we consider the most SUITABLE, because they also occur without CONDENSATION (Q₂=O) and thus have UNITARY EFFICIENCY (η=L/Q=l), taking into account that we have ADOPTED the same SYMBOLOGY used in the most common TECHNICAL MANUALS.

7) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 3, 5 & 7) that the employment of Refrigerator Fluids at Low Fusion Temperature (NH₃, CO₂, SO₂, CH₄, C₂H₄, C₂H₆, C₂H₈, CH₃Cl, Freons etc.) allow the positioning of the cycles (at least partly) under the Environmental Temperature (T₂<T_A) so that the corresponding Energy Exchanges (of Heat δQ and Work δL) with the External become practically Free.

8) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact (figs. 5 & 7) that, by using appropriate mechanisms, the collocations of the two extreme Isothermobars (1-N) and (2-3) with respect to the Environmental Temperature can be Optimized in Real-Time so that the total Transformation of the Absorbed Heat occurs in Mechanical Work, realizing in this way the so-called "SECOND TYPE of PERPETUAL MOTION".

9) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact that in Heat Gains from High to Low Temperature, valid for every Cycle, it is convenient to apply an Autonomous Circuit in parallel (fig. 4) where the Circulating Liquid, oriented by a Director (N) and facilitated by a Lung (M) of Inert Gas, is introduced by the Pump (P) at a Pressure (p*) high enough (p*>p) with respect to that ρ=f(T) of the Saturated Vapor.

10) The ENTROPIC CYCLES of the previous CLAIMS are characterized by the fact that in the Heat Gain (fig. 4) it is convenient to RECYCLE the Superheated Vapor (4, 4') that should increase the Isentropic Work (4, 5).