IT202100006404A1 - IMPROVED STEAM ENGINE, WITH DOUBLE CENTER OF ROTATION PISTON - Google Patents

Description

Title: ?Improved steam engine, with double center of rotation piston?

DESCRIPTION

Technical field

The present invention relates to a steam engine with a piston with a double center of rotation configured to perform a thermodynamic cycle, close to the Carnot cycle.

State of the art

? Is a steam engine known from the state of the art, with a piston with a double center of rotation which rotates within a compartment with a double cavity? substantially cylindrical, resulting in a closed thermodynamic cycle of exploitation of the temperature and pressure of the steam, to obtain useful mechanical work, passing through the different temperatures and pressures in the various phases of the thermodynamic cycle. The steam engine includes an expansion chamber and a compression chamber in fluid communication with a boiler which supplies pressurized fluid to the inlet of the expansion chamber and receives compressed fluid from the compression chamber. The chambers are also in fluid communication with a condenser. Specifically, the condenser receives the expanded fluid from the expansion chamber as an inlet and, following the condensation of the expanded fluid, supplies the condensed fluid to the inlet of the compression chamber. This steam engine? for example described in the Italian patent N. 102016000123578. In this way, the steam engine is able to carry out a thermodynamic cycle having the following phases:

a) a heating of the fluid in a special exchanger / boiler to the upper temperature Tv,

b) subsequent introduction into the expansion chamber, ideally at boiler pressure, until the volume Vi or optimal mass is reached for the cycle via a valve which regulates the quantity,

c) an ideally adiabatic expansion of the fluid introduced into the expansion chamber until the final expansion volume Vf is reached,

d) introduction of the expanded fluid into the condenser with temperature reduction to the lower level Tc,

e) the condensed output by gravity? and / or by pressure wave enters compression chamber with volume Vc,

f) the condensate is compressed by the rotor and when the boiler pressure is exceeded, via a one-way valve, which in the practical case ? a reed valve, is re-entered into the heater, closing the cycle.

Problems of the Prior Art

The known machine in the realization of the thermodynamic cycle in collaboration with other elements such as boiler and condenser has shown an impulsive type operation due to the alternation of the expansion and compression phases. In other words, the thermodynamic cycle created by the steam engine produces a continuous series of temperature and pressure transients.

The thermodynamic cycle takes place in the phases in which the exhausted steam at the end of the expansion enters the condenser from which the condensate comes out (biphasic water/steam) which the machine compresses in the boiler where it is heated again up to the state of steam to be re- introduced, via a regulating valve, into the expansion chamber of the machine to restart the cycle. This leads to the creation of pressure waves in the ?low pressure/temperature? in the area of the condenser indicated in figure 10. These pressure waves are due to the reduction of the volume of the fluid leaving the expansion chamber Ve (with an impulsive trend) which, entering the condenser undergoes a reduction in volume, causing a suction effect by the ducts 75 and 76 and by the motion of the rotor itself which varies the distribution of the internal volumes accentuating the phenomenon.

Figures 5-10 show the steam engine of the known art, the pressure waves and/or the undesired pressure changes are represented with a wavy arrow, while the desired flow? represented with straight arrows. The generation of pressure waves ? due to two main phenomena:

i) the first phenomenon that prevents a continuous flow of the condensate leaving the condenser towards the compression chamber of the machine? due to the ?puff? or pulse of vapor leaving the expansion chamber entering the condenser. Specifically, the steam pulse that reaches the condenser in contact with the cold surfaces undergoes a drastic decrease in volume. This causes a drop in pressure, drawing part of the fluid from the previous cycle back into the condenser from the connection ducts between the expansion chamber and the compression chamber. Such a recall effect ? accentuated due to the fluid accumulated in the connecting duct with the compression chamber, where is it ? accumulated.

ii) the second disturbance phenomenon is due to the variation of the subdivision, during rotation, of the internal volumes of the machine. The rotor acts like a bellows, sucking in and expelling during the arc of rotation. The total internal volume of the rotor chamber ? always kept the same. During one phase of the rotation, the expanding volume increases, the remaining volume decreases by the same amount. The fluid in the center of the machine with its decrease in volume increases the pressure. The consequence ? a puff or impulse of fluid from the machine towards the condenser along the connecting duct between the condenser and the compression chamber in the opposite direction to that intended to compress the condensate in the boiler (figures 5 and 6). In a second phase of the rotation, the same phenomenon occurs but in the opposite direction where the central part of the rotor, with the decrease in the suction volume, has a suction effect from the connection duct between the condenser inlet and the chamber outlet of expansion.

All of these phenomena cause pressure pulses (or pressure waves) contrary to the desired flow. These changes in pressure in the ?cold zone? of the cycle create a strong disturbance to the path of the condensate towards the compression chamber which must recompress it in the boiler. Is it created like this? a rejection of the condensate leaving the condenser that is difficult? to enter by gravity? in the machine and consequently the compression that takes it back to the boiler is penalized by creating an accumulation in the pipes and in the center of the rotor. This set of phenomena leads, after a transition phase in which the accumulation of condensed fluid increases more and more, to blocking of machine rotation.

Purpose of the Invention

Purpose of the invention in question? that of realizing a steam engine with a piston with a double center of rotation capable of overcoming the drawbacks of the prior art mentioned above.

In particular, ? The object of the present invention is to provide a closed cycle steam engine with a piston with a double center of rotation capable of avoiding the effects of the pressure waves generated during the thermodynamic cycle and at the same time improving the efficiency of the engine itself.

Advantages of the invention

Advantageously, the steam engine allows the desired thermodynamic cycle to be achieved and the flow of the condensed fluid to be optimised.

Advantageously, the steam engine allows the improvement and practical implementation of a thermodynamic cycle with a fluid, water or other fluid, capable of creating a cycle similar to the Carnot cycle, through the phase change between two temperatures Tv of the boiler or other heat source and Tc of the condenser in order to create mechanical energy.

BRIEF DESCRIPTION OF THE FIGURES

Further characteristics and advantages of the present invention will appear more clearly from the indicative and therefore non-limiting description of a preferred but not exclusive embodiment of a closed-cycle steam engine with piston with double center of rotation as illustrated in the accompanying drawings:

figure 1 shows a first perspective view of a steam engine according to an embodiment of the present invention;

figure 2 shows a schematic sectional view of the steam engine in accordance with the embodiment of figure 1;

- figure 3 shows an exploded view of the steam engine in accordance with the embodiment of figure 1;

- figure 4 shows an exploded view of the rotor in accordance with the embodiment of figure 1.

Figure 5 shows a schematic sectional view of a steam engine in accordance with the state of the art in a first angular position of the rotor;

Figure 6 shows a schematic sectional view of a steam engine in accordance with the state of the art in a second angular position of the rotor;

Figure 7 shows a schematic sectional view of a steam engine in accordance with the state of the art in a third angular position of the rotor;

figure 8 shows a schematic sectional view of a steam engine in accordance with the state of the art in a fourth angular position of the rotor and a relative enlargement of the circled area;

Figure 9 shows a schematic sectional view of a steam engine in accordance with the state of the art in a fifth angular position of the rotor;

figure 10 shows a schematic sectional view of a steam engine in accordance with the state of the art in a sixth angular position of the rotor and a relative enlargement of the circled area;

figure 11 shows a schematic sectional view of the steam engine in accordance with the embodiment of figure 1 and a relative enlargement of the circled area; - figure 12 shows a further schematic sectional view of the steam engine in accordance with the embodiment of figure 1.

DETAILED DESCRIPTION

Even if not explicitly highlighted, the individual characteristics described with reference to the specific embodiments must be understood as accessory and/or interchangeable with other characteristics, described with reference to other embodiments.

The present invention relates to a closed-cycle steam engine L with a piston with a double center of rotation illustrated in figures 1-4, 10 and 11, the general characteristics of which are reported in the Italian patent No. 102016000123578.

It should be noted that with respect to patent No. 102016000123578, the solution illustrated in figures 1-4, 10 and 11 has additional components, as better described below, capable of solving the problems of the steam engine of patent No. 102016000123578 illustrated in the figures 5-10 and in the previous paragraphs.

The dual center piston type steam engine L comprises a stator A and a rotor B and preferably a flywheel W configured to overcome dead spots during the cycle. Specifically, the motor L comprises a first and a second element A2, A3 defining the stator body A1. In other words, the first and second elements A2, A3 define the sides of the stator body A1 which in turn defines the stator A. With regard to the rotor B, this comprises a first semi-cylindrical element B1 on which the pressure of the fluid acts which creates the rotation or driving torque, equipped with a shaft for the power take-off, a second semi-cylindrical element B2 which acts as a compression element and a third element B3 configured to couple the first and second semi-cylindrical elements B1, B2. It should be noted that the stator A, the rotor B and the relative flywheel W substantially have the structural characteristics of a steam engine with a double rotation center piston described in the international patent applications WO 2004/020791 A1, WO 2010/031585 A1 and W02014/083204A1.

The stator A and the rotor B define an expansion chamber Ve and a compression chamber Vc. Specifically, inside the stator body A1 ? defined an expansion compartment 1 inside which ? formed the expansion chamber Ve and a compression compartment 2 inside which? formed the compression chamber Vc.

? to note that the expansion chamber Ve ? configured to receive a pressurized fluid, for example steam, and expand it by turning rotor B.

The expansion chamber Ve comprises an inlet opening 71 and an outlet opening. The entrance opening 71 ? configured to receive the pressurized fluid and the? outlet opening? configured to expel the fluid expanded in the expansion chamber Ve from the expansion chamber Ve itself. Preferably, the expansion chamber Ve comprises an outlet duct connected to the relevant outlet opening and ? configure to expel the fluid from the expansion chamber Ve by directing it towards a condenser D, as it will be? clarified below. The expansion chamber Ve comprises an inlet conduit connected to the relative inlet opening 71 and configured to convey the pressurized fluid inside the expansion chamber Ve, for example, from a boiler or a heating element F.

In accordance with an embodiment illustrated in figures 2, 11 and 12, the compression chamber Vc comprises an inlet opening and an outlet opening 73. The inlet opening ? configured to receive a fluid to be compressed inside the compression chamber Vc, while the outlet opening 73 expels the compressed fluid from the compression chamber Vc. Preferably, the compression chamber Vc comprises an inlet duct connected to the relative inlet opening and configured to convey a fluid to be compressed, coming, for example, from a condenser D. The expansion chamber Ve also comprises an outlet duct connected to the relative outlet opening 73 and configured to convey the compressed fluid from the compression chamber Vc to the boiler or to the heating element F.

Preferably, the compression chamber Vc comprises, at the outlet opening 79, an outlet valve 78 configured to regulate the outlet of the compressed fluid and direct it to the outlet duct towards the boiler or the heating element F. Specifically, the valve outlet valve 78 has a limiting limit switch 79 as a function of the pressure of the compression chamber Vc and the pressure downstream of the outlet valve 78. It should be noted that the outlet valve 78 ? configured to allow the compressed fluid, having reached and/or exceeded the pressure downstream of the outlet valve itself 78 (for example the pressure of the heating element or of the boiler F) to be expelled from the compression chamber Vc, for example, by introducing it into the ?heating element o in the boiler F. Furthermore, the outlet valve 78 prevents any fluid injections from the outlet duct towards the compression chamber Vc. Preferably, the outlet valve 78 comprises a carbon fiber reed valve. It should be noted that, according to the present invention, the outlet valve 78 is a one-way valve.

In accordance with a preferred embodiment, the steam engine L comprises a heating element or boiler F configured to produce the fluid under pressure and in fluid communication with the inlet channel of the expansion chamber Ve and the outlet channel of the chamber of compression Vc. Specifically, the heating element F comprises at least one outlet, configured to supply the steam engine L with the fluid under pressure and an inlet configured to receive a fluid to be heated from the steam engine L. As illustrated in the embodiment of figure 11 and 12, the engine also comprises a first inlet connection duct 72 configured to place the outlet of the heating element F in fluid communication with the inlet duct of the expansion chamber Ve and a second outlet connection duct 74 configured to place the inlet of the heating element F in fluid communication with the outlet duct of the compression chamber Vc. It should be noted that the heating element F can? provide for an additional inlet to supply the fluid to be heated in order to make up for any losses.

In accordance with a preferred embodiment, the first inlet connection duct 72 and the inlet duct of the expansion chamber Ve define an inlet duct 72 configured to place the outlet of the heating element F and the opening in fluid communication inlet 71 of the expansion chamber Ve.

In accordance with a preferred embodiment, the second outlet connection duct 74 and the outlet duct of the compression chamber Vc define an outlet duct 74 configured to place the outlet opening of the compression chamber Vc in fluid communication with the entrance of the heating element F.

In accordance with a preferred embodiment, the stator body A1 comprises a through hole 70 formed longitudinally in the stator body A1. The stator body A1 comprises an inlet valve 110 housed inside the through hole 70 configured to regulate the passage of the pressurized fluid, for example steam, through the inlet opening 71. Specifically, the inlet valve 110? interposed between the inlet opening 71 and the inlet duct of the expansion chamber Ve to regulate the passage of the pressurized fluid from the heating element F to the expansion chamber Ve.

Preferably the intake valve 110 ? for example a rotary valve 110 made asynchronous through the gears R1, R2, R3, where the gear R1 ? fixed on the crankshaft 80, the gear R3 ? fixed on the rotary valve 110 and the?gear R2 ? fixed on the stator body and coupled to the gears R1, R3, as described in detail in the aforementioned patent applications.

In accordance with a preferred embodiment, the motor comprises a capacitor D configured to at least partially condense the foamed fluid. The condenser ? in fluid communication with the expansion chamber outlet channel Ve and with the compression chamber inlet channel Vc. Specifically, the condenser D comprises an inlet configured to receive the fluid expelled from the expansion chamber Ve and an outlet configured to expel a condensed fluid, preferably also liquid-gas biphasic, and send it to the inlet duct of the compression chamber Vc. The condenser provides for the passage of a fluid at a temperature lower than the temperature of the inlet expanded fluid in order to condense the expanded fluid before sending it to the compression chamber.

As illustrated in the embodiment of figure 11, the engine also comprises a first outlet connection duct 75 configured to place the outlet duct of the compression chamber in fluid communication with the inlet of the condenser D and a second connection duct inlet 76 configured to place the outlet of the condenser D in fluid communication with the inlet duct of the understanding chamber Vc.

In accordance with a preferred embodiment, the first outlet connection duct 75 and the outlet duct of the expansion chamber Ve define an outlet duct 75 configured to place the outlet opening of the expansion chamber Ve in fluid communication with the input of the condenser D.

In accordance with a preferred embodiment, the second inlet connecting duct 76 and the inlet duct of the compression chamber Vc define an inlet duct 76 configured to place the inlet opening of the compression chamber in fluid communication with the ?output of the condenser D.

In this way, in accordance with the described embodiment, the steam engine performs a closed thermodynamic cycle:

a) a heating of the fluid by means of the heating element or boiler F to the upper temperature Tv,

b) a subsequent introduction into the expansion chamber Ve, ideally at boiler pressure, until the volume Vi or optimal mass for the cycle is reached through the valve 110 which regulates the quantity,

c) an ideally adiabatic expansion of the fluid introduced into the expansion chamber Ve until the final expansion volume Vf is reached,

d) the injection of the expanded fluid into the condenser D with the reduction of the temperature to the lower level Tc by means of the heat exchange between the fluid at a lower temperature passing through the condenser and the expanded fluid coming from the expansion chamber Ve,

e) sending of the condensate out of the condenser by gravity? and / or by pressure wave at the compression chamber Vc,

f) compression of the condensate from rotor B and when the boiler pressure is exceeded, via a one-way valve 79 with re-introduction into the heater, closing the cycle.

In accordance with the preferred embodiment of figure 11, the steam engine L, preferably the stator case A1, comprises a connecting duct 77 configured to place the outlet duct of the expansion chamber Ve in fluid communication with the Vc input of the Vc compression chamber. Specifically, the connecting duct 77 puts the outlet opening of the expansion chamber Ve and the inlet opening of the compression chamber Vc into fluid communication.

The steam engine L comprises a first one-way valve V1 located inside the connecting duct 77 and configured to regulate the passage of fluid from the inlet channel of the compression chamber Vc to the outlet channel of the expansion chamber Ve. Specifically, the first one-way valve V1 allows the fluid to pass from the inlet duct of the compression chamber Vc to the outlet duct of the expansion chamber Ve. Furthermore, the first one-way valve V1 prevents the fluid leaving the expansion chamber Ve from entering the connecting duct 77.

Preferably, the first one-way valve V1 ? configured to switch between a closed fluid-tight configuration and an open configuration to allow the passage of fluid via the connecting conduit 77 from the inlet channel of the compression chamber Vc to the outlet channel of the expansion chamber Ve.

The steam engine comprises a second one-way valve V2 placed inside the inlet channel of the compression chamber Vc and upstream of the first one-way valve V1. The second check valve V2 ? configured to regulate the entry of fluid into the compression chamber Vc, for example, from the condenser. Furthermore, the one-way valve V2 prevents the fluid present in the connection pipe 76 from being sucked towards the condenser D. Specifically, the second one-way valve V2 allows the fluid to enter the compression chamber Vc from the inlet pipe of the compression chamber Vc as well as from the second inlet connection duct 76. In other words, the second unidirectional valve V2 allows the fluid coming from the condenser D to enter the compression chamber Vc avoiding any movements (suction for example) of the fluid in the opposite direction. At the same time, the second one-way valve V2 prevents the fluid present in the inlet duct of the compression chamber and/or in the connection duct 76 from being sucked in by the condenser D. It should be noted that the second one-way valve V2 ? configured to divert any fluids leaving the compression chamber Vc towards the connecting duct 77 and then into the outlet duct of the expansion chamber Ve.

Preferably, the second one-way valve V2 ? configured to switch between a closed fluid tight configuration and an open configuration to allow fluid to pass from the inlet channel to the compression chamber Vc.

Advantageously, the insertion of the valves makes it possible to maintain the original thermodynamic cycle which is? a closed loop with high efficiency why? returns the condensate to the boiler at higher temperatures than those necessary for the cycle of the turbines with lower energy losses.

It should be noted that the first V1 and second one-way valve V2 prevent the occurrence of the first phenomenon i) linked to the contraction of pressure in the condenser which draws the fluid present in the inlet duct of the compression chamber Vc and/or in the duct 76 in the form of condensate , preferably biphasic, from the previous cycle. In fact, the second one-way valve V2 prevents the condensed fluid present in the inlet conduit from migrating towards the condenser D since it blocks the condensed fluid itself in that direction in a fluid-tight manner. However, the V2 one-way valve leaves for? flow the condensate in the correct direction of the cycle cio? from the condenser towards the inlet opening of the compression chamber Vc. Preferably, the compression chamber Vc also comprises an accompanying channel downstream of the inlet opening of the compression chamber inclined so as to facilitate the entry of the condensed fluid avoiding excessive stationary in the inlet channel or in the second connection duct entrance 76.

Furthermore, the second check valve V2 cooperating with the first check valve V1 deflects the pressure wave or puff generated during the reduction of the compression volume and the increase of the expansion volume as the rotor closes like a bellows. Such pressure wave or puff ? deviated and finds an outlet in the connection channel 77 and then in the outlet channel of the expansion chamber Ve. Indeed, the first one-way valve V1 ? configured to open in the direction of the outlet duct of the expansion chamber Ve venting so? pressure wave or puff. It should be noted that the combination of the first one-way valve V1 and the second one-way valve V2 allows the recall effect in the connecting duct 76 to be overcome, also overcoming the second phenomenon ii).

Advantageously, the inclusion of one-way valves V1, V2 has made it possible to transform the problem of pressure waves into an advantage for fluidity. of the cycle. In fact, the pressure wave or puff generated by the compression chamber Vc makes it possible to force the circulation of the fluid in the correct direction of the cycle. In particular, the first one-way valve V1 of Figures 3 and 13 placed in the connecting duct 77 between the outlet of the expansion chamber Ve and the inlet of the compression chamber Vc, favors that the overpressure at the inlet of the compression chamber Vc o in the vicinity? of the same finds its outlet towards the connecting duct 75 so as to favor the correct flow of the fluid inside the cycle through the condenser.

In accordance with a preferred embodiment, the first one-way valve V1 and the second one-way valve V2 comprise reed valves, for example of the motorcycle type. In accordance with alternative embodiments, the first one-way valve V1 and the second one-way valve V2 are of a different type and known to an expert in the sector.

Claims (7)

1. Closed-cycle (L) piston steam engine with dual center of rotation comprising - a stator (A) with a rotor (B) configured to expand and compress a fluid to generate useful mechanical work, the stator (A) and the rotor (B) defining: - an expansion chamber (Ve) configured to expand a fluid under pressure and having an inlet channel for receiving a fluid under pressure and an outlet channel for expelling the expanded fluid from the expansion chamber (Ve), - a compression chamber (Vc) configured to compress a fluid and having an inlet channel for receiving a fluid to be compressed, and an outlet channel for expelling the compressed fluid from the compression chamber; characterized by understanding - a connecting duct (77) configured to place the outlet duct of the expansion chamber (Ve) in fluid communication with the inlet duct of the compression chamber (Vc); - a first one-way valve (V1) located inside the connecting duct (77) and configured to regulate the flow of fluid from the inlet channel of the compression chamber (Vc) to the outlet channel of the expansion chamber (Ve); - a second one-way valve (V2) placed inside the inlet channel of the compression chamber (Vc) and placed upstream of the first one-way valve (V1), said second one-way valve (V2) being configured to regulate the entry into the compression chamber (Vc) from the inlet channel of the compression chamber (Vc) and to divert towards the connection duct (77) fluids and/or pressure waves coming out of the compression chamber (Vc). 2. Steam engine (L) according to claim 1, wherein: - the first check valve (V1) ? configured to switch between a closed fluid-tight configuration and an open configuration to allow the passage of fluid via the connecting conduit (77) from the inlet channel of the compression chamber to the outlet channel of the expansion chamber (Ve); - the second check valve (V2) ? configured to switch between a closed fluid tight configuration to an open configuration to allow fluid to pass from the inlet port to the compression chamber (Vc) The steam engine (L) according to claim 1 or 2, wherein the first one-way valve (V1) and the second one-way valve (V2) comprise reed valves. 4. Steam engine (L) according to any one of claims 1 to 3, wherein the engine comprises a heating element (F) configured to produce by heating the pressurized fluid to be sent to the expansion chamber (Ve) and receive a fluid to be heated, the heating element (F) having an outlet in fluid communication with the inlet channel of the expansion chamber (Ve) to send the pressurized fluid and an inlet in fluid communication with the outlet channel of the compression chamber (Vc) to receive the compressed fluid. The steam engine (L) according to claim 4, wherein the engine comprises - a first inlet connection conduit (72) configured to place the inlet conduit of the expansion chamber (Ve) in fluid communication with the outlet of the heating element (F); - a second outlet connection duct (74) configured to place the outlet duct of the compression chamber (Vc) in fluid communication with the inlet of the heating element (F). 6. Closed-cycle steam engine (L) according to any one of claims 1 to 5, wherein the engine comprises a condenser (D) configured to at least partially condense the expanded fluid and send it to the compression chamber (Vc) , the condenser (D) having an inlet in fluid communication with the outlet channel of the expansion chamber (Ve) to receive the expanded fluid and an outlet in fluid communication with the inlet channel of the compression chamber (Vc) to send the condensed fluid to the compression chambers (Vc). The steam engine (L) according to claim 6, wherein the engine comprises - a first outlet connection conduit (75) configured to place the outlet conduit of the expansion chamber (Ve) in fluid communication with the input of the condenser (D); - a second inlet connection duct (76) configured to place the inlet duct of the compression chamber (Vc) in fluid communication with the outlet of the condenser (D).