Patent Grant
11143057
The present invention relates to a “heat machine”, comprising a “rotary drive unit” provided with a motion transmission system, and some specific functional configurations thereof, and which, despite having Joule-Ericsson heat cycles as its original reference, supplements and improves them, achieving an innovative combined heat cycle, operating with a mixture of air and aqueous vapour, in order to obtain a greater unit power, a considerable increase in overall efficiency and an efficient lubrication of the cylinder in which the pistons rotate. The present invention further relates to a method for realizing heat cycles.
In particular, the present invention can have application in the production of electrical energy from renewable sources, in the field of the combined generation of electrical energy and heat, in the field of transport and in the automotive sector in general.
Some historical considerations concerning thermodynamic cycles were already set forth in the description of the patent application published with the number WO2015/114602A1 in the name of the same Applicant, and it is therefore deemed useful to mention in the following only the most significant parts tied to the subject matter of the present invention and regarding use as a heat machine characterized by a new “pulsating heat cycle”, whose origin lies in Joule-Ericsson cycles.
Historical Notes on the Ericsson Engine
The first design and production of the Ericsson “hot air” engine took place in 1826, initially without regeneration and with a modest overall efficiency.
In 1833, a new Ericsson engine was built, provided with valves and a heat recuperator, and a considerable increase in overall efficiency was obtained.
In 1853 an Ericsson “hot air” engine was built, which was used on a ship; it was able to generate 220 kW of power with an overall efficiency of 13.3%.
In subsequent years, several thousand Ericsson engines were produced and used on ships and in industrial laboratories in the United States.
Between 1855 and 1860 nearly 3,000 low-power (600 W) Ericsson engines were built. They were sold and used in the United States, Germany, France and Sweden.
These engines possessed high reliability and robustness, so much so that one engine installed in a lighthouse remained in operation for over 30 years after being put into service.
For reasons that have not yet been wholly clarified, the Ericsson engine was then first supplanted by conventional steam engines and then by internal combustion engines, more powerful and compact in size.
Schematic Representation of the Closed-Circuit Ericsson Cycle
The Ericsson cycle, characterized by the use of a reciprocating motion engine operating in a closed circuit, is schematically represented in
E_expansion cylinder;
E1-E2_expansion cylinder inlet-discharge valves;
R_heat exchanger/recuperator;
K_heat exchanger/sink;
C_compression cylinder;
C1-C2_compression cylinder inlet-discharge valves;
H_“thermal fluid” heater.
With reference to said
The Joule cycle, characterized by the use of a turbo-machine with continuous rotary motion, operating in a closed circuit, is schematically represented in
E_expansion turbine;
R_heat exchanger/recuperator;
K_heat exchanger/sink;
C_compression turbine;
H_“thermal fluid” heater.
With reference to said
Overall, various heat machines functioning with diversified thermodynamic cycles have been developed and others are still at an experimental stage.
However, the Applicant has found that even already industrialized solutions have many limitations. This applies, in particular for the engines used to drive small and medium power autonomous electric generators (below 50 KWh).
Today, in practice, the following drive units are customarily used to drive electric generators:
In general, all of the prior art solutions, in addition to the problems of pollution, low efficiency, mechanical complexity and high maintenance costs, are also characterized by a cost-benefit ratio that is not particularly satisfactory, which has greatly limited the dissemination of cogeneration in the market of multi-occupancy buildings and residential dwellings.
The Applicant has also observed that if one wishes to extend the use of such heat machines to vehicles and micro cogeneration in a domestic setting, compactness and overall efficiency are fundamental.
Innovative Solution Proposed by the Applicant.
In this context, the Applicant has set the objective of proposing a new “heat machine” capable of operating with an innovative combined heat cycle using hot air and aqueous vapour, whereby it is possible to exploit greater energy by recovering it during the stages of the cycle itself, with a considerable increase in the unit power and overall efficiency, also solving the large problem of lubricating the cylinder where the pistons of the known drive unit slide.
In particular, compared to Ericsson and Joule cycles, the innovations introduced with the present invention can be identified in three different possible operating configurations of the heat cycle.
In the first configuration, which comprises solely the injection of water downstream of the regeneration, the following results are obtained:
In the second configuration, which comprises the injection of saturated vapour obtained with a recovery of energy downstream of the regeneration, the following results are obtained:
In the third configuration, which comprises the injection of superheated vapour obtained with a recovery of energy downstream of the regeneration and the recovery of energy from the combustion fumes, the following results are obtained:
Therefore, the object at the basis of the present invention, in the various aspects and/or embodiments thereof, is to remedy one or more of the drawbacks of the prior art solutions by providing a new “heat machine” capable of using multiple heat sources and capable of generating a great deal of mechanical energy (work), being able to be used in any place and for any purpose, but preferably for the production of electrical energy.
A further object of the present invention is to provide a new “heat machine” characterized by high thermodynamic efficiency and an excellent power-to-weight ratio.
A further object of the present invention is to propose a new “heat machine” provided with a “drive unit” characterized by a mechanical structure that is simple and can be easily built.
A further object of the present invention is to be able to produce a new “heat machine” characterized by a reduced cost of production.
These objects, and any others that will become more apparent in the course of the following description, are substantially achieved by a new “heat machine” that relies on a “drive unit” characterized by a series of particular aspects.
In one aspect, the present invention relates to a heat machine for realizing a heat cycle, the heat machine operating with a thermal fluid and comprising:
In one aspect, said drive unit is a rotary volumetric expander operating with said thermal fluid.
In one aspect, the heat machine comprises a first section of the drive unit where, following the movement of the two pistons away from each other, the thermal fluid, passing through the inlet opening, is suctioned into the chamber.
In one aspect, the heat machine comprises a second section of said drive unit, where, following the movement of the two pistons towards each other, the previously suctioned thermal fluid is compressed in the chamber and then, on passing through the discharge opening, a pipe and a check valve, it is conveyed into a compensation tank.
In one aspect, the heat machine comprises said compensation tank, configured to accumulate the compressed thermal fluid to make it available, via specific pipes and the check valve, for subsequent use thereof, in a continuous mode.
In one aspect, the heat machine comprises a regenerator, in fluid communication via specific pipes and configured to preheat the thermal fluid prior to its entry into a heater.
In one aspect, the heat machine comprises said heater, configured to superheat the thermal fluid circulating in the serpentine coil (i.e. in the pipe placed around the combustion chamber and defining the heater), using the thermal energy produced by a burner.
In one aspect, the heat machine comprises said burner with a combustion chamber attached thereto, said burner being configured to operate with various types of fuel and being capable of supplying the necessary thermal energy to the heater.
In one aspect, the heat machine comprises a third section of said drive unit, in fluid communication with said heater, via specific pipes, and configured to receive, via the inlet openings, the thermal fluid heated to a high temperature under pressure in the heater so as to have it expand in the chambers, which are delimited by the pistons, respectively, for the purpose of having said pistons rotate and produce work.
In one aspect, the heat machine comprises a fourth section of said drive unit, in fluid communication with the regenerator through the discharge openings and specific pipes, and wherein, due to the reduction in volume of the two chambers brought about by the movement of the two pairs of pistons towards each other, the exhausted thermal fluid is forcedly expelled.
In one aspect, said regenerator, in fluid communication with said drive unit, is configured to acquire heat-energy from the exhausted thermal fluid and to use it to preheat the thermal fluid to be sent to the heater.
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In one aspect the auxiliary recuperator is configured to recover as much energy as possible from the combustion fumes and to transmit it to the fluid circulating in said auxiliary circuit, said energy thus being available for said auxiliary uses.
In one aspect, the heat machine comprises a fan upstream of the burner and configured to draw combustion air from the environment and to send it forcedly to said burner to feed the combustion process.
In one aspect, the heat machine comprises one or more check vales located along the pipes of the heat machine and configured to facilitate circulation of the thermal fluid in a unidirectional manner and prevent the outflow of the thermal fluid in the opposite direction.
In an independent aspect thereof, the present invention relates to a method for realizing a heat cycle, the method operating with a thermal fluid and comprising the steps of:
In one aspect, said plurality of steps comprises:
In one aspect, in said step of arranging a heat machine, said heat machine is in accordance with a combination of one or more of the presents aspects and/or one or more of the accompanying claims.
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In one aspect, the drive unit is substantially composed of:
In one aspect, the annular chamber has a rectangular or square cross section and the pistons, being of mating shape, are respectively rectangular or square.
In one aspect, the annular chamber has a circular cross section (extending toroidally) and the pistons, being of mating shape, have a circular cross section (extending toroidally).
In one aspect, the toroidal cylinder (or annular cylinder) is provided with a number of mutually distinct inlet openings for the entry of a high-temperature thermal fluid into the cylinder and a number of mutually distinct discharge openings for evacuating the exhausted thermal fluid.
In one aspect, each of the six chambers expands three times and contracts three times per each complete revolution (360°) of the primary shaft.
In one aspect, all of the inlet/discharge openings, used for the passage of the thermal fluid, are fashioned on the casing of the toroidal (or annular) cylinder.
In one aspect the toroidal cylinder (or annular cylinder) is provided with one or more inlet openings for the entry of the cooled thermal fluid into the cylinder and one or more discharge openings for evacuating the compressed thermal fluid in the compensation tank.
In one aspect, by means of a manual or automatic angular rotation of the case containing the transmission, relative to the inlet/discharge openings, it is possible to time the phases of the heat cycle to come earlier or later in order to optimize thermodynamic efficiency.
In one aspect, by means of a manual or automatic angular rotation of the case containing the transmission, relative to the inlet/discharge openings, it is possible to time the phases of the heat cycle to come earlier or later in order to enable autonomous starting of the engine apparatus.
In one aspect, the first triad of pistons is an integral part of a first rotor and the second triad of pistons is an integral part of a second rotor.
In one aspect, the three pistons of each of the two rotors are angularly equidistant from one another. In one aspect, the three pistons of each of the rotors are rigidly connected together so as to rotate integrally with one another.
In one aspect, the first secondary shaft is solid and integrally joined at one end with a first three-lobe gear and at the opposite end with the first rotor.
In one aspect, the second secondary shaft is hollow and integrally joined at one end with a respective second three-lobe gear and at the opposite end with the second rotor.
In one aspect, the primary shaft (or drive shaft) is integrally joined with a first and a second three-lobe gear, positioned at 60° from each other.
In one aspect, the transmission of the drive unit comprises:
In one aspect, the first auxiliary shaft is coaxially inserted in the second auxiliary shaft or vice versa.
In one aspect, the axis of the primary shaft is parallel to and appropriately distanced from the axis of the first shaft and second shaft.
In one aspect, each three-lobe gear has concave and/or flat and/or convex connecting portions between its lobes.
In one aspect, each three-lobe gear, as may be inferred from the definition thereof, has a substantially triangular profile.
In all aspects, a rotation having a constant angular velocity of the primary shaft (or drive shaft) brings about a periodic variation in the angular velocity of rotation of the two secondary shafts.
In all aspects, the primary shaft (or drive shaft) brings about a periodic cyclical variation of the angular velocity of the first and second secondary shafts and of the corresponding triads of pistons rotating inside the toroidal cylinder (or annular cylinder), enabling the creation of six distinct rotating chambers with a variable volume and ratio.
In one aspect, the transmission of motion between the pistons and the primary shaft (or drive shaft) is obtained with the train of three-lobe gears which connects the first and second secondary shafts to the primary shaft, characterized in that while the primary shaft (or drive shaft) rotates with a constant angular velocity, the two secondary shafts rotate with an angular velocity that is periodically higher than, equal to or lower than the primary shaft.
In one aspect, without prejudice to the inventive idea, the drive unit can be provided with any system whatsoever for transmitting motion between the two triads of pistons and the primary shaft (such as, for example, the one claimed in U.S. Pat. No. 5,147,191, EP0554227A1 and TW1296023B), it being possible to adopt any mechanism able to transform the rotary motion of the primary shaft, which has a constant angular velocity, into a rotary motion with a periodically variable angular velocity of the two secondary shafts, functionally connected to the two triads of pistons.
In all aspects, the drive unit can be configured, by means of suitable thermal fluid conveying conduits, in such a way that the various components and various sections can be operatively connected with the corresponding inlet/discharge openings of the drive unit.
In one aspect, the drive unit is completely devoid of inlet/discharge valves and the associated mechanisms, since the triads of pistons, by moving in the toroidal cylinder (or annular cylinder), themselves bring about the opening and the closing of the inlet/discharge openings for the thermal fluid.
In one aspect, the heat machine which uses the drive unit can be provided with check valves appropriately positioned in the thermal fluid conveying conduits, in such a way as to optimize the heat cycle by aiding the work of the pistons in the function of opening-closing the inlet/discharge openings.
In one aspect, the heat machine which uses the drive unit can comprise one or more thermal fluid heaters and/or recuperators configured in such a way as to be able to provide all the maximum energy serving to produce the useful work, while recovering as much as possible of all the energy that would otherwise be lost.
In one aspect, the drive unit is connected to a generator capable of producing electrical energy utilizable for any purpose.
In one aspect, the drive unit is capable of producing mechanical energy utilizable for any purpose.
In one aspect, the heat machine which uses the drive unit comprises a heat energy regulating system, configured to regulate the delivery pressure and/or temperature of the thermal fluid in the various stages of the process.
In one aspect, the drive unit can be configured so as to function with an original Joule-Ericsson operating cycle, as the drive unit can perform functions of compressing and expanding the thermal fluid.
In one aspect, the “heat machine” which uses the drive unit is configured to function with a new “pulsating heat cycle” using hot air and aqueous vapour, featuring unidirectional continuous motion of the thermal fluid.
In one aspect, the drive unit is suitable for being employed as an apparatus capable of producing mechanical energy using flows of thermal fluid heated with any source of heat.
In one aspect, the heating of the circulating thermal fluid can be achieved using a fuel burner (for example a gas burner) or any other external source of heat, such as, for example: solar energy, biomass, unrefined fuel, high-temperature industrial waste, or another source suitable for heating the thermal fluid itself to the minimum necessary temperature.
Additional features will become more apparent from the following detailed description of the heat machine of the present invention and of some preferred embodiments of the use thereof, regarding, respectively:
It should be noted first of all that the gas preferably used as a thermal fluid is common “air”; however, without prejudice to the inventive idea, any other gas that is better suited and more compatible with aqueous vapour can be used, as is presented and described below.
It is also useful to point out that, in the “rest” condition, the thermal fluids used (normally air and water) are at the same temperature as the surrounding environment and that in closed-circuit solutions, inside the cylinder and pipes, a pressure other than atmospheric pressure could also be chosen where appropriate.
In its completeness, the new heat cycle is carried out, in a continuous mode, in a number of steps of thermodynamic variation of the fluid: introduction, compression, heating, vaporization, superheating, expansion (which produces useful work), expulsion, and condensation, as described below for the five main configurations of the heat machine according to the present invention, which are given by way of non-limiting example.
The most complete functional configuration of the heat machine, represented in
In this configuration, where the start of the cycle is made to coincide with the suction of cooled air, the heat machine comprises:
In particular, the motion of the circulating fluid in the heat machine is conditioned by the rotary movement of the pistons, which, by bringing about the opening/closing of the inlet/discharge openings, generate the very particular high-frequency “pulsating” effect that characterizes this new heat cycle. For example, a rotation speed of 1,000 rpm of the primary shaft corresponds to exactly 100 pulses per second of the circulating thermal fluid).
With reference to the accompanying diagrams and drawings, it is noted that the same are provided solely by way of illustration and not by way of limitation; in them:
With reference to
The drive unit 1 comprises a casing 2 which internally delimits a seat 3.
In the non-limiting embodiment illustrated, the casing 2 is made up of two half-parts 2a, 2b joined together.
Housed in the seat 3 there is a first rotor 4 and a second rotor 5, which rotate around a same axis “X-X”.
The first rotor 4 has a first cylindrical body 6 and three first elements 7a, 7b, 7c which extend radially from the first cylindrical body 6 and are rigidly connected or integral therewith.
The second rotor 5 has a second cylindrical body 8 and three second elements 9a, 9b, 9c which extend radially from the second cylindrical body 8 and are rigidly connected or integral therewith.
The elements 7a, 7b, 7c of the rotor 4 are angularly equidistant from one another, i.e. each element is spaced apart from the adjacent element on average by an angle “a” of 120° (measured between the planes of symmetry of each element).
The elements 9a, 9b, 9c of the rotor 5 are angularly equidistant from one another, i.e. each element is spaced apart from the adjacent element on average by an angle “a” of 120° (measured between the planes of symmetry of each element).
The first and second cylindrical bodies 6, 8 are set side by side at respective bases 10, 11 and are coaxial.
The three first elements 7a, 7b, 7c of the first rotor 4 moreover extend along an axial direction and have a projecting portion disposed in a position that is radially external to the second cylindrical body 8 of the second rotor 5.
The three second elements 9a, 9b, 9c of the second rotor 5 moreover extend along an axial direction and have a projecting portion disposed in a position that is radially external to the first cylindrical body 6 of the first rotor 4.
The three first elements 7a, 7b, 7c are alternated with the three second elements 9a, 9b, 9c along the circumferential extent of the annular chamber 12.
Each of the first and second elements 7a, 7b, 7c, 9a, 9b, 9c has, in a radial section (
Each of the first and second elements 7a, 7b, 7c, 9a, 9b, 9c has an angular size, given purely by way of approximation and not by way of limitation, of about 38°.
Peripheral surfaces that are radially external to the first and second cylindrical bodies 6, 8 delimit, together with an inner surface of the seat 3, an annular chamber 12.
The annular chamber 12 is therefore divided into variable-volume “rotating chambers” 13′, 13″, 13′″, 14′, 14″, 14′″ by the first and second elements 7a, 7b, 7c, 9a, 9b, 9c. In particular, each variable-volume “rotating chamber” is delimited (besides by the surface radially internal to the casing 2 and the surface radially external to the cylindrical bodies 6, 8) by one of the first elements 7a, 7b, 7c and one of the second elements 9a, 9b, 9c.
In the first
In the variant in
Between inner walls of the annular chamber 12 and each of the aforesaid first and second elements 7a, 7b, 7c, 9a, 9b, 9c there remains an interspace such as to permit the rotary movement of the pistons 4, 5 and sliding of the elements 7a, 7b, 7c, 9a, 9b, 9c in the chamber 12 itself.
The first and second elements 7a, 7b, 7c, 9a, 9b, 9c are the pistons of the drive unit 1 illustrated and the variable-volume rotating chambers 13′, 13″, 13′″, 14′, 14″, 14′″ are the chambers for the compression and/or expansion of the working fluid of said drive unit 1.
The inlet or discharge openings 15′, 16′, 15″, 16″, 15′″, 16′″ (of suitable size and shape) are fashioned in a wall radially external to the casing 2; they open into the annular chamber 12 and are in fluid communication with conduits external to the annular chamber 12, illustrated further below.
Each inlet or discharge opening 15′, 16′, 15″, 16″, 15′″, 16′″ is angularly spaced in an appropriate way so as to adapt to the requirements of each different individual functional configuration of the drive unit 1.
The drive unit 1 further comprises a primary shaft 17 parallel to and distanced from the rotation axis “X-X” and rotatably mounted on the casing 2 and a transmission 18 mechanically interposed between the primary shaft 17 and the rotors 4, 5.
The transmission 18 comprises a first auxiliary shaft 19 onto which the first rotor 4 is keyed and a second auxiliary shaft 20 onto which the second rotor 5 is keyed. The first and second auxiliary shafts 19, 20 are coaxial with the rotation axis “X-X”. The second auxiliary shaft 20 is tubular and houses within it a portion of the first auxiliary shaft 19. The first auxiliary shaft 19 can rotate in the second auxiliary shaft 20 and the second auxiliary shaft 20 can rotate in the casing 2.
A first three-lobe gear 23 is keyed onto the primary shaft 17. A second three-lobe gear 24 is keyed onto the primary shaft 17 next to the first. The second three-lobe gear 24 is mounted on the primary shaft 17 angularly offset relative to the first three-lobe gear 23 by an angle “A” of 60°. The two three-lobe gears 23 and 24 rotate together jointly with the primary shaft 17.
A third three-lobe gear 25 is keyed onto the first auxiliary shaft 19 (so as to rotate integrally therewith) and the teeth thereof precisely enmesh with the teeth of the first three-lobe gear 23.
A fourth three-lobe gear 26 is keyed onto the second auxiliary shaft 20 (so as to rotate integrally therewith) and the teeth thereof precisely enmesh with the teeth of the second three-lobe gear 24.
Each of the above-mentioned three-lobe gears 23, 24, 25, 26 has approximately the profile of an equilateral triangle with rounded vertices 27 and connecting portions 28, interposed between the vertices 27, which can be concave, flat or convex.
Changing the shape of the vertices 27 and connecting portions 28 of the gears makes it possible to pre-establish the value of the angular periodic movement of the auxiliary shafts 19, 20 during their rotary motion.
The structure of the transmission 18 is such that during a complete revolution of the primary shaft 17 the two rotors 4, 5 also carry out a complete revolution, but with periodically variable angular velocities, offset from each other, which induce the adjacent pistons 7a, 9a; 7b, 9b; 7c, 9c to move away and toward one another three times during a complete 360° revolution. Therefore, each of the six variable-volume chambers 13′, 13″, 13′″, 14′, 14″, 14′″ expands three times and contracts three times at each complete revolution of the primary shaft 17.
In others words, pairs of adjacent pistons of the six pistons 7a, 7b, 7c; 9a, 9b, 9c are movable, during their rotation at a periodically variable angular velocity in the annular chamber 12, between a first position, in which the two faces of the adjacent pistons lie substantially next to each other, and a second position, in which the same faces are angularly spaced apart by the maximum allowed. Purely by way of example, in the first position the two faces of the adjacent pistons are angularly spaced apart from each other by about 1°, whereas in the second position the two same faces are angularly spaced apart from each other by about 81°.
The six variable-volume chambers 13′, 13″, 13′″, 14′, 14″, 14′″ are made up of a first group of three chambers 13′, 13″, 13′″ and a second group of three chambers 14′, 14″, 14′″. When the three chambers 13′, 13″, 13′″ of the first group have the minimum volume (pistons next to each other at the minimum reciprocal distance) the other three chambers 14′, 14″, 14′″ (of the second group) have the maximum volume (pistons at the maximum reciprocal distance).
For the purpose of better clarifying and highlighting the innovative aspects of the present invention, the five main functional configurations will be described below in a precise and detailed manner.
In order to describe the operation of the new heat machine (121), configured to operate with a “pulsating heat cycle” according to the present invention, it is necessary to start off by noting that in the drive unit (1), in each of the six periodically variable-volume chambers (13′,13″,13′″,14′,14″,14′″), each delimited by the two pistons adjacent to each other and rotating inside the annular cylinder, the diversified suction, compression, expansion and expulsion functions are performed periodically.
For the sake of simplicity, in the following five descriptions (A, B, C, D, E), the path followed by the thermal fluid in the different sections of the heat engine (121) will be explained as if a single complete heat cycle were involved. In reality, for each revolution of the drive shaft (corresponding to a revolution angle of) 360° no fewer than six complete heat cycles are carried out.
A. Detailed Description of the Heat Machine 121 Operating According to the Functional Configuration Represented in the
Compared to the Joule-Ericsson cycles on their own and the sole “drive unit”, the novelty introduced with this configuration regards the realization of a “combined” operating cycle, where the thermal fluid is a mixture of air and water (transformed into vapour); this ensures the lubrication of the cylinder (where the pistons slide) and enables a higher unit power to be obtained, albeit with a slight decrease in overall efficiency.
With reference to
A1_Setting into Motion.
Noting first of all that all control and regulating devices are powered via a specific auxiliary electric line (not represented), the start-up of the heat machine 121 takes place in the following manner:
The air suctioned from the environment at temperature T1′, passes into the pipe 93, passes through the suctioning opening 15′″ and, following the movement of the two pistons 9c-7c away from each other, it is suctioned into the chamber 13′″.
A3_Step of Compression and Recovery of the Suctioned Air.
Following the movement of the two pistons 7c-9a towards each other, the previously suctioned air is compressed in the chamber 14′″ (up to the limit, which is normally preset with a minimum ratio of 1:4 and a maximum ratio of 1:20), undergoes an increase in temperature from T1′ to T2, passes through the discharge opening 16′″, the pipe 44′ and the check valve 44a and ends up in the compensation tank 44, where it remains available for immediate use.
A4_Step of Preheating the Compressed Thermal Fluid.
With the intermittency determined by the rotation of the pistons and the resulting opening/closing of the inlet openings 15,15″, the air flows out from the tank 44, passes through the pipe 44″ and the check valve 44b, travels through the pipe 44″, and passes into the regenerator 42 (where it undergoes an increase in temperature from T2 to T2′).
A5_Step of Injecting Distilled Water into the Air Conduit.
The air, exiting from the regenerator 42, travels through the pipe 42′, passes through the check valve 42a and passes into the pipe 42′″.
The distilled water is drawn from the tank 97a, travels through the pipe 97″, is brought to a high pressure in the metering pump 97b and, at temperature Tc, is conveyed into the pipe 97′″ and, by means of the injector 97, it is introduced into the pipe 42′″ where, as a result of mixing, the mixture thus formed undergoes a decrease in temperature from T2′ to T2″.
A6_Step of Superheating the Circulating Thermal Fluid.
The mixed thermal fluid travels through the pipe 97′, passes through the heater 41 (adjacent to the combustion chamber 40A and provided with the multi-fuel burner 40), where it receives heat-energy and increases in temperature from T2″ to T3.
A7_Step of Expanding the Superheated Thermal Fluid and Producing Useful Work.
When the pistons 7a-7b, by rotating in the annular cylinder in the direction of motion indicated by the arrows, open the inlet openings 15-15″, the superheated thermal fluid flowing through the pipes 41′-41″-41′″ is introduced into the expansion chambers 13′ and 13″, where it is expanded (decreasing in temperature from T3 to T4) and, by making the pistons rotate, produces useful work.
A8_Step of Expulsion and of Recovering Energy from the Exhausted Thermal Fluid.
Following the movement of the pistons 7a-9b and 7b-9c towards each other, the chambers 14′ and 14″ diminish in volume, the exhausted thermal fluid (already expanded in the previous cycle) is expelled from the drive unit 1, passes through the two discharge openings 16′-16″, flows through the pipes 45′-45″-45″, passes through the regenerator 42 (where it surrenders part of the energy-heat still possessed and undergoes a decrease in temperature from T4 to T4′) and then, on passing through the pipe 42″, is discharged into the atmosphere, the heat cycle thus being concluded.
A9_Recovery of Energy with a Reduction in the Temperature of the Combustion Fumes.
Given that the function envisaged for the heat machine is also to provide energy-heat to be destined to auxiliary uses (space heating and/or production of domestic hot water, etc.), before the hot fumes are discharged into the atmosphere (through the conduit 102), all their residual energy is recovered by reducing their temperature as much as possible (it also being possible to recover further energy through their possible condensation). To achieve this purpose, use is made of a specific hydraulic circuit, where the following mode of conveyance is adopted: the incoming thermal fluid (normally water) from the auxiliary uses 103 passes into the pipe 103′ and, pushed by the circulation pump 104, passes into the pipe 104′, reaches the recuperator 101 at the low temperature Tf and then, on passing through it, thanks to the reduction in the temperature of the fumes S from Th7 to Th2, acquires energy-heat and heats up to the higher temperature Tg, so as to be made available, via the pipe 101′, for the auxiliary uses 130, and for the intended purpose.
B. Detailed Description of the Heat Machine 121 Operating According to the Functional Configuration Represented in
Compared to the Joule-Ericsson cycles on their own and the sole “drive unit”, the novelty introduced with this configuration regards the realization of a “combined” operating cycle, where the thermal fluid is a mixture of air and water (transformed into vapour); this ensures the lubrication of the cylinder (where the pistons slide) and enables a higher unit power to be obtained, albeit with a slight decrease in overall efficiency.
With reference to
B1_Setting into Motion the Heat Machine 121.
Noting first of all that all control and regulating devices are powered via a specific auxiliary electric line (not represented), the start-up of the heat machine 121 takes place in the following manner:
The thermal fluid, exiting from the cooler 43 at temperature T1, passes into the pipe 43′, passes through the condensate trap 93 (where the water in the thermal fluid is condensed and separated from the air), passes into the pipe 93′ at temperature T1′, passes through the suctioning opening 15′″ and, following the movement of the two pistons 9c-7c away from each other, is suctioned into the chamber 13′″.
B3_Step of Compression and Recovery of the Suctioned Thermal Fluid.
Following the movement of the two pistons 7c-9a towards each other, the previously suctioned air is compressed in the chamber 14′ (up to the limit, which is normally preset with a minimum ratio of 1:4 and a maximum ratio of 1:20), undergoes an increase in temperature from T1′ to T2, passes through the discharge opening 16′″, the pipe 44′ and the check valve 44a and ends up in the compensation tank 44, where it remains available for immediate use.
B4_Step of Preheating the Compressed Thermal Fluid.
With the intermittency determined by the rotation of the pistons and the resulting opening/closing of the inlet openings 15,15″, the air flows out from the tank 44, passes through the pipe 44″ and the check valve 44b, travels through the pipe 44″, and passes into the regenerator 42 (where it undergoes an increase in temperature from T2 to T2′).
B5_Step of Drawing Condensate Water.
Pushed by the high pressure pump 94, the condensate water previously extracted from the air by the trap 93, flows through the pipes 93″ and 94′ (at temperature T1″).
B6_Step of Injecting the Condensate Water into the Air Conduit.
The air, exiting from the regenerator 42, travels through the pipe 42′, passes through the check valve 42a and passes into the pipe 42′″ where, via the injector 97, the condensate water is introduced. As a result of the mixing of the air with the condensate water, the mixture undergoes a decrease in temperature from T2′ to T2″.
B7_Step of Superheating the Circulating Thermal Fluid.
The mixed thermal fluid travels through the pipe 97′, passes through the heater 41 (adjacent to the combustion chamber 40A and provided with the multi-fuel burner 40), where it receives heat-energy and increases in temperature from T2″ to T3.
B8_Step of Expanding the Superheated Thermal Fluid and Producing Useful Work.
When the pistons 7a-7b, by rotating in the annular cylinder in the direction of motion indicated by the arrows, open the inlet openings 15-15″, the superheated thermal fluid flowing through the pipes 41′-41″-41′″ is introduced into the expansion chambers 13′ and 13″, where it is expanded (decreasing in temperature from T3 to T4) and, by making the pistons rotate, produces useful work.
B9_Step of Expulsion and of Recovering Energy from the Exhausted Thermal Fluid.
Following the movement of the pistons 7a-9b and 7b-9c towards each other, the chambers 14′ and 14″ diminish in volume, the exhausted thermal fluid (already expanded in the previous cycle) is expelled from the drive unit 1, passes through the two discharge openings 16′-16″, flows through the pipes 45′-45″-45′″, passes through the regenerator 42 (where it surrenders part of the energy-heat still possessed and undergoes a first decrease in temperature from T4 to T4′).
B10_Conclusion of the Cycle with Further Cooling of the Exhausted Thermal Fluid.
The thermal fluid passes into the pipe 42″ and reaches the cooler 43, from where the cycle can continue and repeat itself in a continuous mode.
B11_Recovery of Energy with the Optimization of the Process of Preheating the Combustion Air.
The combustion air drawn from the environment is pushed by the fan 92 and passes into the cooler 43, where it acquires energy and increases in temperature from Th1 to Th3, thus facilitating the combustion process.
B12_Recovery of Energy with a Reduction in the Temperature of the Combustion Fumes.
Given that the function envisaged for the heat machine is also to provide energy-heat to be destined to auxiliary uses (space heating and/or production of domestic hot water, etc.), before the hot fumes are discharged into the atmosphere (through the conduit 102), all their residual energy is recovered by reducing their temperature as much as possible (it also being possible to recover further energy through their possible condensation). To achieve this purpose, use is made of a specific hydraulic circuit, where the following mode of conveyance is adopted: the incoming thermal fluid (normally water) from the auxiliary uses 103 passes into the pipe 103′ and, pushed by the circulation pump 104, passes into the pipe 104′, reaches the recuperator 101 at the low temperature Tf and then, on passing through it, thanks to the reduction in the temperature of the fumes S from Th7 to Th2, acquires energy-heat and heats up to the higher temperature Tg, so as to be made available, via the pipe 101′, for the auxiliary uses 130, and for the intended purpose.
C. Detailed Description of the Heat Machine 121 Operating According to the Functional Configuration Represented in
Compared to the Joule-Ericsson cycles on their own and the sole “drive unit”, the novelty introduced with this configuration regards the realization of a “combined” operating cycle, where the thermal fluid is a mixture of air and water (transformed into vapour); this ensures the lubrication of the cylinder (where the pistons slide) and enables a higher unit power to be obtained and an improvement in the overall efficiency.
With reference to
C1_Setting into Motion the Heat Machine 121.
Noting first of all that all control and regulating devices are powered via a specific auxiliary electric line (not represented), the start-up of the heat machine 121 takes place in the following manner:
The thermal fluid, exiting from the cooler 43 at temperature T1, passes into the pipe 43′, passes through the condensate trap 93 (where the water in the thermal fluid is condensed and separated from the air), passes into the pipe 93′ at temperature T1′, passes through the suctioning opening 15′″ and, following the movement of the two pistons 9c-7c away from each other, is suctioned into the chamber 13′″.
C3_Step of Compression and Recovery of the Suctioned Thermal Fluid.
Following the movement of the two pistons 7c-9a towards each other, the previously suctioned air is compressed in the chamber 14′ (up to the limit, which is normally preset with a minimum ratio of 1:4 and a maximum ratio of 1:20), undergoes an increase in temperature from T1′ to T2, passes through the discharge opening 16′″, the pipe 44′ and the check valve 44a and ends up in the compensation tank 44, where it remains available for immediate use.
C4_Step of Preheating the Compressed Thermal Fluid.
With the intermittency determined by the rotation of the pistons and the resulting opening/closing of the inlet openings 15,15″, the air flows out from the tank 44, passes through the pipe 44″ and the check valve 44b, travels through the pipe 44′, and passes into the regenerator 42 (where it undergoes an increase in temperature from T2 to T2′).
C5_Step of Vaporizing/Superheating the Condensate Water.
Pushed by the high pressure pump 94, the condensate water previously extracted from the air by the trap 93, flows through the pipes 93″ and 94′, passes through the evaporator 95, where it is heated/vaporized (changing in state from a liquid to a vapour, with an increase in temperature from T1″ to Ta).
C6_Step of Injecting the Saturated Vapour into the Air Conduit.
The air, exiting from the regenerator 42, travels through the pipe 42′, passes through the check valve 42a and passes into the pipe 42′ where, via the injector 97, the saturated vapour conveyed in the pipe 95′ is introduced. As a result of the mixing of the air with the saturated vapour, the thermal fluid undergoes an increase in mass and decrease in temperature from T2′ to T2″.
C7_Step of Superheating the Circulating Thermal Fluid.
The mixed thermal fluid travels through the pipe 97′, passes through the heater 41 (adjacent to the combustion chamber 40A and provided with the multi-fuel burner 40), where it receives heat-energy and increases in temperature from T2″ to T3.
C8_Step of Expanding the Superheated Thermal Fluid and Producing Useful Work.
When the pistons 7a-7b, by rotating in the annular cylinder in the direction of motion indicated by the arrows, open the inlet openings 15-15″, the superheated thermal fluid flowing through the pipes 41′-41″-41′″ is introduced into the expansion chambers 13′ and 13″, where it is expanded (decreasing in temperature from T3 to T4) and, by making the pistons rotate, produces useful work.
C9_Step of Expulsion and of Recovering Energy from the Exhausted Thermal Fluid.
Following the movement of the pistons 7a-9b and 7b-9c towards each other, the chambers 14′ and 14″ diminish in volume, the exhausted thermal fluid (already expanded in the previous cycle) is expelled from the drive unit 1, passes through the two discharge openings 16′-16″, flows through the pipes 45′-45″-45′″, passes through the regenerator 42 (where it surrenders part of the energy-heat still possessed and undergoes a first decrease in temperature from T4 to T4′), then passes into the pipe 42″, passes through the evaporator 95, where it again surrenders part of the energy-heat possessed and undergoes a second decrease in temperature from T4′ to T4″, enabling the recovery of useful energy, which is schematically represented in the area Q95 in
C10_Conclusion of the Cycle with Further Cooling of the Exhausted Thermal Fluid.
The thermal fluid passes into the pipe 95″ and reaches the cooler 43, from where the cycle can continue and repeat itself in a continuous mode.
C11_Recovery of Energy with the Optimization of the Process of Preheating the Combustion Air.
The combustion air drawn from the environment is pushed by the fan 92 and passes into the cooler 43, where it acquires energy and increases in temperature from Th1 to Th3, thus facilitating the combustion process.
C12_Recovery of Energy with a Reduction in the Temperature of the Combustion Fumes.
Given that the function envisaged for the heat machine is also to provide energy-heat to be destined to auxiliary uses (space heating and/or production of domestic hot water, etc.), before the hot fumes are discharged into the atmosphere (through the conduit 102), all their residual energy is recovered by reducing their temperature as much as possible (it also being possible to recover further energy through their possible condensation). To achieve this purpose, use is made of a specific hydraulic circuit, where the following mode of conveyance is adopted: the incoming thermal fluid (normally water) from the auxiliary uses 103 passes into the pipe 103′ and, pushed by the circulation pump 104, passes into the pipe 104′, reaches the recuperator 101 at the low temperature Tf and then, on passing through it, thanks to the reduction in the temperature of the fumes S from Th7 to Th2, acquires energy-heat and heats up to the higher temperature Tg, so as to be made available, via the pipe 101′, for the auxiliary uses 130, and for the intended purpose.
D. Detailed Description of the Heat Machine 121 Operating According to the Functional Configuration Represented in
Compared to the Joule-Ericsson cycles on their own and the sole “drive unit”, the novelty introduced with this configuration regards the realization of a “combined” operating cycle, where the thermal fluid is a mixture of air and water (transformed into superheated vapour); this ensures the lubrication of the cylinder (where the pistons slide) and enables a higher unit power to be obtained and an improvement in the overall efficiency.
With reference to
D1_Setting into Motion the Heat Machine 121.
Noting first of all that all control and regulating devices are powered via a specific auxiliary electric line (not represented), the start-up of the heat machine 121 takes place in the following manner:
The thermal fluid, exiting from the cooler 43 at temperature T1, passes into the pipe 43′, passes through the condensate trap 93 (where the water in the thermal fluid is condensed and separated from the air), passes into the pipe 93′ at temperature T1′, passes through the suctioning opening 15′″ and, following the movement of the two pistons 9c-7c away from each other, is suctioned into the chamber 13′″.
D3_Step of Compression and Recovery of the Suctioned Thermal Fluid.
Following the movement of the two pistons 7c-9a towards each other, the previously suctioned air is compressed in the chamber 14′ (up to the limit, which is normally preset with a minimum ratio of 1:4 and a maximum ratio of 1:20), undergoes an increase in temperature from T1′ to T2, passes through the discharge opening 16′″, the pipe 44′ and the check valve 44a and ends up in the compensation tank 44, where it remains available for immediate use.
D4_Step of Preheating the Compressed Thermal Fluid.
With the intermittency determined by the rotation of the pistons and the resulting opening/closing of the inlet openings 15′,15″, the air flows out from the tank 44, passes through the pipe 44″ and the check valve 44b, travels through the pipe 44′, and passes into the regenerator 42 (where it undergoes an increase in temperature from T2 to T2′).
D5_Step of Vaporizing/Superheating the Condensate Water.
Pushed by the high pressure pump 94, the condensate water previously extracted from the air by the trap 93, flows through the pipes 93″ and 94′, passes through the evaporator 95, where it is heated/vaporized (changing in state from a liquid to a vapour, with an increase in temperature from T1″ to Ta), travels through the pipe 95′, passes through the superheater 96 (where acquires further energy and increases in temperature from Ta to Tb).
D6_Step of Injecting the Superheated Vapour into the Air Conduit.
The air, exiting from the regenerator 42, travels through the pipe 42′, passes through the check valve 42a and passes into the pipe 42′ where, via the injector 97, the superheated vapour conveyed in the pipe 96′ is introduced. As a result of the mixing of the air with the superheated vapour, the thermal fluid undergoes an increase in energy and increases in temperature from T2′ to T2″, enabling the recovery of useful energy, which is schematically represented in the area Q96 in
D7_Step of Superheating the Circulating Thermal Fluid.
The mixed thermal fluid travels through the pipe 97′, passes through the heater 41 (adjacent to the combustion chamber 40A and provided with the multi-fuel burner 40), where it receives heat-energy and increases in temperature from T2″ to T3.
D8_Step of Expanding the Superheated Thermal Fluid and Producing Useful Work.
When the pistons 7a-7b, by rotating in the annular cylinder in the direction of motion indicated by the arrows, open the inlet openings 15′-15″, the superheated thermal fluid flowing through the pipes 41′-41″-41′″ is introduced into the expansion chambers 13′ and 13″, where it is expanded (decreasing in temperature from T3 to T4) and, by making the pistons rotate, produces useful work.
D9_Step of Expulsion and of Recovering Energy from the Exhausted Thermal Fluid.
Following the movement of the pistons 7a-9b and 7b-9c towards each other, the chambers 14′ and 14″ diminish in volume, the exhausted thermal fluid (already expanded in the previous cycle) is expelled from the drive unit 1, passes through the two discharge openings 16′-16″, flows through the pipes 45′-45″-45′″, passes through the regenerator 42 (where it surrenders part of the energy-heat still possessed and undergoes a first decrease in temperature from T4 to T4′), then passes into the pipe 42″, passes through the evaporator 95, where it again surrenders part of the energy-heat possessed and undergoes a second decrease in temperature from T4′ to T4″, enabling the recovery of useful energy, which is schematically represented in the area Q95 in
D10_Conclusion of the Cycle with Further Cooling of the Exhausted Thermal Fluid.
The thermal fluid passes into the pipe 95″ and reaches the cooler 43, from where the cycle can continue and repeat itself in a continuous mode.
D11_Recovery of Energy with the Optimization of the Process of Preheating the Combustion Air.
The combustion air drawn from the environment is pushed by the fan 92 and passes into the cooler 43, where it acquires energy and increases in temperature from Th1 to Th3, thus facilitating the combustion process.
D12_Recovery of Energy with a Reduction in the Temperature of the Combustion Fumes.
Given that the function envisaged for the heat machine is also to provide energy-heat to be destined to auxiliary uses (space heating and/or production of domestic hot water, etc.), before the hot fumes are discharged into the atmosphere (through the conduit 102), they are first made to pass through the superheater 96 (where their temperature is reduced from Th7 to Th6) and then all their residual energy is recovered by reducing their temperature as much as possible (it also being possible to recover further energy through their possible condensation). To achieve this purpose, use is made of a specific hydraulic circuit, where the following mode of conveyance is adopted: the incoming thermal fluid (normally water) from the auxiliary uses 103 passes into the pipe 103′ and, pushed by the circulation pump 104, passes into the pipe 104′, reaches the recuperator 101 at the low temperature Tf and then, on passing through it, thanks to the reduction in the temperature of the fumes S from Th6 to Th2, acquires energy-heat and heats up to the higher temperature Tg, so as to be made available, via the pipe 101′, for the auxiliary uses 130, and for the intended purpose.
E. Detailed Description of the Heat Machine 121 Operating According to the Most Complete Functional Configuration, Represented in
Compared to the Joule-Ericsson cycles on their own and the sole “drive unit”, the novelty introduced with this configuration regards the realization of a “combined” operating cycle, where the thermal fluid is a mixture of air and water (transformed into superheated vapour); this ensures the lubrication of the cylinder (where the pistons slide) and enables a higher unit power to be obtained and a considerable improvement in the overall efficiency.
With reference to
E1_Setting into Motion the Heat Machine 121.
Noting first of all that all control and regulating devices are powered via a specific auxiliary electric line (not represented), the start-up of the heat machine 121 takes place in the following manner:
The thermal fluid, exiting from the cooler 43 (at temperature T1), passes into the pipe 43′, passes through the condensate trap 93 (where the water in the thermal fluid is condensed and separated from the air), passes into the pipe 93′ at temperature T1′, passes through the suctioning opening 15′″ and, following the movement of the two pistons 9c-7c away from each other, is suctioned into the chamber 13′″.
E3_Step of Compression and Recovery of the Suctioned Thermal Fluid.
Following the movement of the two pistons 7c-9a towards each other, the previously suctioned air is compressed in the chamber 14′ (up to the limit, which is normally preset with a minimum ratio of 1:4 and a maximum ratio of 1:20), undergoes an increase in temperature from T1′ to T2, passes through the discharge opening 16′″, the pipe 44′ and the check valve 44a and ends up in the compensation tank 44, where it remains available for immediate use.
E4_Step of Preheating the Compressed Thermal Fluid.
With the intermittency determined by the rotation of the pistons and the resulting opening/closing of the inlet openings 15,15″, the air flows out from the tank 44, passes through the pipe 44″ and the check valve 44b, travels through the pipe 44′, and passes into the regenerator 42 (where it undergoes an increase in temperature from T2 to T2′).
E5_Step of Vaporizing/Superheating the Condensate Water.
Pushed by the high pressure pump 94, the condensate water previously extracted from the air by the trap 93, flows through the pipes 93″ and 94′ at temperature T1“, passes through the evaporator 95, where it is heated/vaporized (changing in state from a liquid to a vapour, with an increase in temperature from T1” to Ta), travels through the pipe 95″, passes through the superheater 96 (where it acquires further energy and undergoes an increase in temperature from Ta to Tb).
E6_Step of Injection of the Superheated Vapour in the Air Conduit.
The air, exiting from the regenerator 42, travels through the pipe 42′, passes through the check valve 42a and passes into the pipe 42′ where, via the injector 97, the superheated vapour conveyed in the pipe 96′ is introduced. As a result of the mixing of the air with the superheated vapour, the thermal fluid undergoes an increase in energy and its temperature increases from T2′ to T2″, enabling the recovery of useful energy, which is schematically represented in the area Q96 in
E7_Step of Superheating the Circulating Thermal Fluid.
The mixed thermal fluid travels through the pipe 97′, passes through the heater 41 (adjacent to the combustion chamber 40A, provided with the multi-fuel burner 40), where it receives heat-energy and increases in temperature from T2″ to T3.
E8_Step of Expanding the Superheated Thermal Fluid and Producing Useful Work.
When the pistons 7a-7b, by rotating in the annular cylinder in the direction of motion indicated by the arrows, open the inlet openings 15-15″, the superheated thermal fluid flowing through the pipes 41′-41″-41′″ is introduced into the expansion chambers 13′ and 13″, where it is expanded (decreasing in temperature from T3 to T4) and, by making the pistons rotate, produces useful work.
E9_Step of Expulsion and of Recovering Energy from the Exhausted Thermal Fluid.
Following the movement of the pistons 7a-9b and 7b-9c towards each other, the chambers 14′ and 14″ diminish in volume, the exhausted thermal fluid (already expanded in the previous cycle) is expelled from the drive unit 1, passes through the two discharge openings 16′-16″, flows through the pipes 45′-45″-45′″, passes through the regenerator 42 (where it surrenders part of the energy-heat still possessed and undergoes a first decrease in temperature from T4 to T4′), then passes into the pipe 42″, passes through the evaporator 95, where it again surrenders part of the energy-heat possessed and undergoes a second decrease in temperature from T4′ to T4″, enabling the recovery of useful energy, which is schematically represented in the area Q95 in
E10_Conclusion of the Cycle with Further Cooling of the Exhausted Thermal Fluid.
The thermal fluid passes into the pipe 95′ and reaches the cooler 43, from where the cycle can continue and repeat itself in a continuous mode.
E11_Optimized Cooling of the Drive Unit 1, with Recovery of Energy.
The water cooled in the recuperator 98 (at temperature Tc) is constantly maintained in circulation by the pump 99, flows through the pipes 98′-99′, passes through a specific interspace 2R formed in the drive unit 1, (where, by performing a cooling action, it undergoes an increase in temperature from Tc to Td), travels through the pipe 2′, passes through the recuperator 100 (where it acquires heat-energy, increasing in temperature from Td to Te), travels through the pipe 100′ and, finally, arrives at the recuperator 98, where its path ends. The interspace 2R constitutes a cooling unit for the drive unit 1. The pipes 2′, 98′, 99′ and 100′ constitute cooling pipes. The interspace 2R (or cooling unit) of the first recuperator 98, the second recuperator 100, the cooling pump 99 and the cooling pipes together constitute a cooling circuit of the heat machine.
E12_Recovery of Energy with the Optimization of the Process of Preheating the Combustion Air.
The combustion air drawn from the environment at temperature Th1 is pushed by the fan 92 and passes into the cooler 43 (where it acquires energy and increases in temperature to Th3), passes into the recuperator 98 (where it acquires further energy and increases in temperature to Th5).
The preheated air is mixed in the burner 40 with the fuel conveyed through the regulation valve 91 and is introduced into the combustion chamber 40A, where the gas, mixed at a high temperature, can undergo optimal combustion, thus reducing harmful emissions.
E13_Recovery of Energy with a Reduction in the Temperature of the Combustion Fumes.
The hot fumes produced by combustion at temperature Th7 are first cooled to temperature Th6 (passing through the superheater 96), then further cooled to temperature Th4 (passing through the recuperator 100) and then, given that the function envisaged for the heat machine is also to provide energy-heat to be destined to auxiliary uses (space heating and/or production of domestic hot water, etc.), before the hot fumes are discharged into the atmosphere (through the conduit 102), all their residual energy is recovered by reducing their temperature as much as possible (it also being possible to recover further energy through their possible condensation). To achieve this purpose, use is made of a specific hydraulic circuit, where the following mode of conveyance is adopted: the incoming thermal fluid (normally water) from the auxiliary uses 103 passes into the pipe 103′ and, pushed by the circulation pump 104, passes into the pipe 104′, reaches the recuperator 101 at the low temperature Tf and then, on passing through it, thanks to the reduction in the temperature of the fumes from Th4 to Th2, it acquires energy-heat and heats up to the higher temperature Tg, so as to be made available, via the pipe 101′, for the auxiliary uses 130, and for the intended purpose.
The pipes 101′, 103′ and 104′ constitute auxiliary pipes. The auxiliary recuperator 101, the auxiliary pump 104 and the auxiliary pipes together constitute a cooling circuit of the heat machine 121.
The invention thus conceived is susceptible of numerous modifications and variants, all falling within the scope of the inventive concept, and the components mentioned may be replaced by other technically equivalent elements.
The invention achieves important advantages. First of all, the invention enables at least some of the drawbacks of the prior art to be overcome.
Furthermore, the heat machine and the associated method according to the present invention are capable of using a variety of heat sources and of generating mechanical energy (work), as they can be employed in any place and for any use, but preferably for the production of electrical energy.
Furthermore, the heat machine according to the present invention is characterized by a high thermodynamic efficiency and an excellent weight-power ratio.
In addition, the heat machine according to the present invention is characterized by a simple, easy to produce structure.
Furthermore, the heat machine according to the present invention is characterized by a reduced production cost.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102017000074290 | Jul 2017 | IT | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/IB2018/054254 | 6/12/2018 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2019/008457 | 1/10/2019 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 2248484 | Bancroft | Jul 1941 | A |
| 4338067 | Greenfield | Jul 1982 | A |
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| 6461127 | Kim | Oct 2002 | B1 |
| 7461626 | Kimes | Dec 2008 | B2 |
| 10280806 | Olivotti | May 2019 | B2 |
| 20170167303 | Olivotti | Jun 2017 | A1 |
| Number | Date | Country |
|---|---|---|
| 29 10 990 | Oct 1980 | DE |
| 0 553 524 | Aug 1993 | EP |
| 2014076637 | May 2014 | WO |
| 2015114602 | Aug 2015 | WO |
| Entry |
|---|
| Sep. 6, 2018 International Search Report issued in International Patent Application No. PCT/IB2018/054254. |
| Sep. 6, 2018 Written Opinion of the International Searching Authority issued in International Patent Application No. PCT/IB2018/054254. |
| Number | Date | Country | |
|---|---|---|---|
| 20200131942 A1 | Apr 2020 | US |
