WO2018195631A1

WO2018195631A1 - Combined otto and binary isobaric-adiabatic cycle engine and process for controlling the thermodynamic cycle of the combined cycle engine

Info

Publication number: WO2018195631A1
Application number: PCT/BR2018/050128
Authority: WO
Inventors: Marno Iockheck; Saulo Finco; LUIS Mauro MOURA
Original assignee: Associação Paranaense De Cultura - Apc
Priority date: 2017-04-26
Filing date: 2018-04-25
Publication date: 2018-11-01
Also published as: BR102017008576A2

Abstract

The present invention relates to a combined cycle heat engine comprised of a unit that operates on the Otto cycle and is interconnected and integrated with another unit that operates on a binary cycle of three isobaric processes and four adiabatic processes.

Description

"OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR AND CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE OF THE COMBINED CYCLE MOTOR"

TECHNICAL FIELD OF THE INVENTION

The present invention relates to a combined cycle thermal motor formed by a unit operating with the Otto cycle interconnected and integrated with the other unit operating with the binary cycle of three isobaric processes and four adiabatic processes.

BACKGROUND OF THE INVENTION

[002] Classical thermodynamics defines three concepts of thermodynamic systems, the open thermodynamic system, the closed thermodynamic system and the isolated thermodynamic system. These three concepts of thermodynamic systems were conceptualized in the nineteenth century in the early days of the creation of the laws of thermodynamics and underlie all motor cycles known to date.

The isolated thermodynamic system is defined as a system in which neither matter nor energy passes through it. Therefore, this concept of thermodynamic system does not offer properties that allow the development of motors.

[004] The open thermodynamic system is defined as a thermodynamic system in which energy and matter can enter and leave this system. Examples of an open thermodynamic system are the Otkins cycle Atkinson cycle internal combustion engines, Sabathe cycle Otto cycle diesel cycle, Brayton diesel cycle internal combustion engine, Rankine exhaust cycle from steam to the environment. The materials that come into these systems are fuels and oxygen or fluid working gas or working gas. The energy that enters these systems is heat. The materials that come out of these systems are combustion or working fluid exhaust, gases, waste; The energies that come out of these systems are the working mechanical energy and part of the heat dissipated.

[005] The closed thermodynamic system is defined as a thermodynamic system in which only energy can enter and leave this system. Examples are closed thermodynamic systems, external combustion engines such as Stirling cycle, Ericsson cycle, Rankine cycle with closed circuit working fluid, Brayton heat cycle or external combustion, Carnot cycle. In this system is the heat. The energies that come out of this system are the working mechanical energy and part of the heat dissipated, but no matter comes out of these systems, as they do in the open system.

[006] Both open and closed systems, all working gas mass is exposed to incoming energy, heat or combustion and all of it is exposed to cooling or cooling, that is, working gas mass is constant in their processes and the difference between them is that in the open system the working gas mass goes through the system and in the closed system the mass remains in the system.

THE CURRENT STATE OF TECHNIQUE

[007] Combined-cycle motors known to date were invented and designed by uniting in the same system two idealized motor concepts in the nineteenth century, based on open thermodynamic systems or closed thermodynamic systems, the best known are the combined cycles of an engine. Brayton cycle engine with a Rankine cycle engine and the combined cycle of a Diesel cycle engine with a Rankine cycle engine. [008] The basic concept of a combined cycle is a system composed of a motor operating by means of a high temperature source so that the heat waste of this motor is the energy that drives a second motor that requires a lower temperature of operation, both forming a combined system of converting thermal energy into mechanical energy for the same common purpose.

[009] The current state of the art reveals combined cycles formed by a Brayton or Diesel cycle main engine running on a main source with a temperature of over 1000 ° C and exhaust gases in the range between 600 ° C and 700 ° C and these gases are in turn piped to power another Rankine cycle engine, usually "organic Rankine" (ORC). The conventional Rankine cycle has water as its working fluid, the organic Rankine cycle uses organic fluids, these are more suitable for projects at lower temperatures than those with the conventional Rankine cycle, so they are usually used in combined cycles.

[010] Some of the main disadvantages of the current combined cycles, considering the second machine as a Rankine or organic Rankine cycle engine are the changing of the physical state of the working fluid, that is, there is a liquid phase required by the thermodynamic cycle processes that must controlled, and the heating energy of the liquid phase and the latent phase state change cannot be converted into working working energy, are losses imposed by the Rankine concept. This system requires engine items that imply more processes, more weight, more control and more losses, liquid reservoirs, steam generation reservoir, condenser cooler type, condensation reservoir, fluid flow pump in liquid state, control valves of liquid and gaseous processes. This set of features entails additional weight, additional volume, additional thermal losses, reduced overall efficiency and therefore higher pollution rates, higher implementation costs and lower sustainability indices in these projects.

[011] The current state of the art as of 2011 has revealed a new concept of thermodynamic system, the so-called hybrid thermodynamic system, and this new system concept has become the basis of support for new motor cycles, cycle motors. differential and non-differential binary cycle motors so that these new motor cycles have significant advantages for the creation of new combined cycles. Combined cycles of a Brayton cycle engine with a differential cycle motor, Brayton cycle engine with a binary cycle engine, Diesel cycle engine with a differential cycle engine, Diesel cycle engine with a binary cycle motor can be exemplified. , Otto cycle motor with a differential cycle motor, Otto cycle motor with a binary cycle motor and some other variations.

OBJECTS OF THE INVENTION

[012] The major problems of the state of the art, specifically as regards combined cycles, lie precisely in the second unit that forms the systems, this is generally a Rankine cycle machine, an old machine whose thermodynamic processes impose losses through the need for exchange of physical state of working fluid, heat of liquid phase heating, heat of transformation, latent heat, mechanical units, reservoirs, valve systems, condensers, pumps that add weight, volume, losses and costs.

[013] The aim of the invention is to eliminate some of the existing problems. To minimize other problems and offer new possibilities, to achieve these objectives, a new concept of thermal motors has become indispensable and the creation of new motor cycles is necessary. engine efficiency is no longer dependent solely on temperatures. The hybrid system concept and differential cycles and binary cycles, the very characteristic that underlies this new combined cycle concept, eliminates the dependence of efficiency exclusively on temperature. Eliminating the need to change the physical state of work fluids is now representative to reduce machine volume, weight and cost. Therefore the combined cycle formed by an Otto cycle unit with a binary-isobaric-adiabatic cycle unit is an important, viable evolution for the future of combined cycle systems.

DESCRIPTION OF THE INVENTION

[014] Combined-cycle motors are characterized by having two separate thermodynamic units integrated forming a system such that the energy discarded by the main unit is the power source of the secondary unit and both have an integration of the final mechanical work.

[015] The present concept considers a thermodynamic unit formed by an Otto31 cycle motor, which performs a four-process Otto cycle and a binary-isobaric-adiabatic cycle turbine motor 320, which performs a three-process cycle and isobaric. four adiabatic processes, and so that the input energy by combustion performs an isocoric process of temperature increase in the Otto cycle unit, an isocoric cooling process when exhaust goes straight to the environment or isobaric or adiabatic when using heat exchangers for other purposes which gives energy to the isobaric process of expansion of the binary cycle unit, this in turn performs an isobaric cooling process giving to the environment the energy that the combined system has not converted to work and so that both cycles have a conversion to common final work. Therefore, these are combined-cycle motors that are completely distinct from today's combined-cycle motors, which are based solely on open or closed systems. Figure 3 shows the The general concept of the invention and Figure 4 show the graphs of the integration of both thermodynamic cycles forming the combined cycle. In addition to the combination of the Otto cycle and torque, the present invention further contemplates the use of an auxiliary turbine 315 to perform work by an adiabatic process with residual energy and a compressor 314 for air pressurization in the combustion chambers of the engine. internal combustion Otto.

[016] The present invention brings important developments for the conversion of thermal energy into mechanics by the concept of the combination of two distinct thermodynamic cycles. The vast majority of combined cycles have as their secondary engine a Rankine or organic Rankine cycle steam turbine engine. Figure 1 shows that the Rankine cycle has losses inherent in the concept of the processes that form its cycle, not allowing a significant portion of energy to be converted into work. The Rankine and Organic Rankine cycles require the exchange of the physical phase of the working gas, that is, there is a liquid process phase requiring condensing elements, evaporation and auxiliary pump systems, and all these elements and processes impose losses and impossibility. Some of the main advantages of the Otto-isobaric-adiabatic combined-cycle combination which can be seen are the absence of physical phase exchange elements of the working fluid and their associated losses, the absence of condensation and vaporization elements, therefore also the absence of losses associated with the latent heat of the working fluid, the absence of circuits, pumps, control elements destined to the processes of physical phase exchange of the fluid and their associated losses and which consequently , the lack of volume, materials and mass, weight, of the elements that compose such project s. Therefore, the innovation presented by the combined cycle Otto with binary is expressive.

[017] Combined-cycle motors based on motor integration cycle engines with a binary-cycle engine may be constructed of materials and techniques similar to conventional combined-cycle engines, such as the secondary, binary-cycle unit consisting of a closed-loop gas engine, considering the complete system, this concept Closed-circuit working gas with respect to the external environment indicates that the system must be sealed, or in some cases leaks may be permitted provided they are compensated. Suitable materials for this technology should be noted, which are similar in this respect to Bra ton, Stirling or Ericsson cycle engine design technologies, all with external combustion. The working gas depends on the project, its application and the parameters used, the choice of gas may be diversified, each one will provide specific characteristics, as an example may be suggested the gases: helium, hydrogen, nitrogen, dry air, neon, among others. others.

DESCRIPTION OF DRAWINGS

[018] The attached figures show the main features and properties of the new combined cycle concept, more specifically a system formed by an Otto cycle unit with a binary-isobaric-adiabatic cycle unit, and are represented as follows:

Figure 1 demonstrates in block diagram a current combined cycle system formed by an Otto cycle unit with a Rankine cycle unit. Systems designed with this philosophy today are used to improve mechanical and energy efficiency in traction systems, vehicles such as automobiles.

Figure 2 demonstrates in block diagram a combined cycle system designed based on the new thermodynamic system concept formed by a known Otto cycle unit with a binary-isobaric-adiabatic cycle unit. Theoretically, systems designed with this The philosophy of mechanical force generation will be superior to the combined cycle systems with Rankine or organic Rankine based on the theoretical analysis of the cycle of the second machine forming the system, among the losses that cease to exist, the absence of exchange of the physical state of the fluid. Since this work is a significant item, the energy conservation process provided by the conservation subsystem belonging to the binary cycle reinforces the possibilities of increasing overall efficiency.

Figure 3 is a diagram of a system composed of an Otto31 cycle engine with a binary-isobaric-adiabatic cycle turbine engine 320 forming the combined cycle Otto and torque.

Figure 4 shows the Otto 41 cycle pressure and volumetric displacement graph curves and the binary-isobaric-adiabatic cycle pressure and volumetric graph curves 45 respectively.

Figure 5 shows the conventional Otto cycle with two isocoric processes and two adiabatic processes.

DETAILED DESCRIPTION OF THE INVENTION

[019] The Otto-torque-isobaric-adiabatic combined-cycle engine is a system composed of an open thermodynamic system-based engine concept, an Otto-cycle internal combustion engine, designed in the 19th century, with a thermodynamic-based engine hybrid, the non-differential binary-isobaric-adiabatic cycle, idealized in the 21st century, so that the energy discarded by the first, the Otto cycle internal combustion engine, is the energy that drives the second, the binary cycle engine.

[020] Figure 3 presents the system featuring an Otto and torque-isobaric-adiabatic combined-cycle engine. This system consists of a machine that operates on the Otto cycle, integrated, interconnected with another machine that operates on a binary cycle and so that its cycles thermodynamic are also integrated as shown in Figure 4. The system of Figure 3 shows an Otto 31 cycle internal combustion engine coupled to a binary-isobaric-adiabatic cycle turbine engine 320. The Otto cycle engine has its discharge manifold 331, hot gas exhaust, connected to a heat exchanger 319, in this exchanger there is a binary cycle working gas circulation line that enters the point (a) being heated inside the exchanger and exits the point (b), entering the proportional three-way control valve 326, and this valve directs part of the gas to the turbine rotor of the power converter 321 and part of the gas to the turbine rotor of the power conservation unit 322, the turbine rotor of the conservation unit 322 conducts the working gas to the thermally insulated chamber 323, entering at the point (c ') where the isobaric compression process is performed, leaving the gas at the point (d') following p for the power conservation unit 324 compressor rotor, which in turn drives the gas with its associated conserved energy back into the isobaric expansion chamber 319. The power conversion unit turbine rotor 321 drives Its fraction of the working gas coming from the control valve 326 to the cooling chamber 328 is separated from the other cooling and cooling systems and situated at the coldest end of the forced fan air flow, ie at the outermost point. the engine boundary with the environment, and the gas entering point (c) inside chamber 328, where the isobaric compression and cooling process is performed, the gas exiting at point (d) following to the compressor compressor rotor. power conversion unit 325, and this in turn, returning the gas to the inlet of the isobaric expansion and heating chamber 319, completing the binary thermodynamic cycle of the system. The mechanical energy converted by the binary cycle unit on shaft 327, this shaft is coupled directly or indirectly to all compression and turbine rotors, 314, 315, 321, 322, 324 and 325, and is coupled to main mechanical shaft 33, of the Otto cycle unit by means of a gearbox 34 for Transmission of the torque power of the torque cycle unit adding to the shaft 33 of the main motor 31. As part of the mechanical unit of the torque cycle engine, there is also a 315 turbine rotor, where an adiabatic process is performed, through which they pass the exhaust gases from the Otto engine, immediately after passing through the heat exchanger 319, the gas exiting the exchanger, enters the turbine rotor 315, it is connected to the main shaft of the torque cycle motor, with the function of driving the rotor from compressor 31, and from turbine rotor 315, the gas flows to an exhaust gas circulation control type 312 (EGR) with the function of directing part of the 315 turbine rotor outlet gases the combustion chambers of the Otto engine via mixer 39, reducing emissions of nitrous oxides, NOx, another part of the gases, when leaving unit 312, goes to the environment 316. Also being part of the mechanical unit of the binary cycle engine, there is a compressor rotor 31 which pressurizes ambient air into the Otto engine combustion chambers, air 317 first passes through filter 313, enters compressor rotor 314, passes through a chiller 36 and thereafter to mixer 39 which mixes pressurized air with part of the combustion gases by injecting them into the Otto 31 engine combustion chambers.

[021] Figure 3 also shows the main elements that make up an Otto engine, at 318 the engine cooling air intake and all systems requiring cooling, the heat exchanger 328 is the outermost element and is the chamber isobaric compression of the binary cycle unit is the most external because the efficiency of the binary cycle unit increases the lower the temperature of the isobaric process that occurs in the 328 changer, unlike other Otto engine needs. Heat exchanger 36 is used for cooling pressurized air by compressor 314. Another heat exchanger, radiator 35 is the main cooling element of the Otto engine, hydraulic and electrical units. A 329 fan is used to force ventilation and improve heat exchange, cooling. A coolant, usually water, pump 37 circulates the fluid within the internal combustion engine to keep it in safe thermal conditions, aided by a thermostat type 38 sensor for temperature control. Mixing pressurized air with part of the exhaust gas occurs in mixer 39 and proceeds to a distributor 32 which injects into the combustion chambers of the Otto engine. Line 330 is an engine coolant return pipe. Line 310 is a duct that conducts part of the combustion gases from the regulator (EGR) to the mixer 39. The combustion waste gases are driven by line 311 from the manifold 331, through the heat exchanger 319 and following turbine rotor input 315. Otto engine power shaft 33 is the main element for bringing mechanical force to the transmission case 34.

[022] Figure 4 shows the graphs of the pressure and volumetric displacement that in their union form the combined cycle, a process composed by the combination of two cycles, one Otto and another binary-isobaric-adiabatic, where the first cycle, the cycle Otto is formed by four processes, or also called thermodynamic transformations, being two isochoric processes and two adiabatic processes, which occur one by one sequentially, but with the integration with other mechanical elements, the processes may vary as in the case of this invention. . The introduction of a turbine rotor alters the isocoric process, making it, in short, adiabatic and the final step of the adiabatic expansion process (4-5), can gain isobaric characteristics by describing the energy input to the The combustion system 42 performs an isochoric compression and heating process (3-4), following which expansion proceeds with an adiabatic process (4-5 '), from this point heat transfer to the exchanger 319 occurs. generating the isobaric segment (5'- 5) or depending on the design or regulation parameters, it may be isothermal or adiabatic, or variable, ending the expansion with another adiabatic process (5-2) next to the 315 turbine rotor, in followed by another adiabatic but compression process (2-3) ending the Otto cycle. THE The energy channeled to the torque-cycle turbine engine is defined by process 5'-5 indicated by 43, the energy channeled to the turbine rotor 315 is defined by process 5-2 indicated by 44.

[023] Binary cycle 45 is coupled, integrated with cycle Otto 41, so that the energy disposal process (5'-5) of the Otto cycle is the input energy of the binary cycle, and all processes that form the binary cycle occur simultaneously. The energy discharged by the Otto cycle forms the isobaric expansion process (ab), starting from point (b) of the binary cycle two processes occur, an adiabatic expansion process (bc) of the binary cycle motor conversion unit and an adiabatic process. expansion cycle (b-c ') of the binary cycle engine conservation unit, the adiabatic expansion processes are completed two isobaric compression processes, starting from point (c) of the binary cycle an isobaric (cd) compression process occurs. Starting from point (c ') of the torque motor energy conversion unit, an isobaric compression process (c'-d') of the energy conservation unit occurs, finalizing the isobaric compression processes two adiabatic compression processes occur, starting from point (d) of the binary cycle, there is an adiabatic compression process (da) of the binary cycle motor power conversion unit and an adiabatic process of compression (d'-a) of the torque-cycle engine servicing unit completing the torque-cycle 45. Therefore, under ideal, lossless conditions, the energy enters the Otto cycle, indicated by 42, part of the discarded energy 44, an adiabatic process feeds a turbine rotor, 315, remaining part of the discarded energy 43 of the Otto cycle feeds the binary cycle 45, the discarded energy of the binary cycle is, ideally without losses, the total energy lost, indicated by 46.

Table 1 shows the processes (3-4, 4-5 ', 5'-5, 5-2, 2-3) that form the Otto cycle when it is integrated with the binary-isobaric-adiabatic cycle, shown step by step. Table 1

Table 2 shows the seven processes (ab, bc, b-c ', cd, c'-d', da, d'a) that form the non-differential binary-isobaric-adiabatic cycle shown step by step. step, with three isobaric processes and four adiabatic processes.

Table 2

Figure 5 shows the graph of pressure and volume of the optimal Otto cycle, considering a motor without accessories, is a cycle formed by two isochoric processes, one by combustion heating (3-4) and one by exhaust cooling (5-2). ), an adiabatic expansion process (4-5) and an adiabatic compression process (2-3). When implementing mechanical changes to the engine, the addition of a 315 turbine and a 319 heat exchanger, there is also a change in the thermodynamic cycle, process (5-2) is no longer isochoric as there is a moving turbine which together with the 319 heat exchanger and a control system, will produce changes in this region of the thermodynamic cycle and this change may vary depending on the operation in which the engine will be running. This paper proposes an approximation considering the mechanical and process essentials that characterize the idea.

The combined cycle Otto with binary-isobaric-adiabatic is the junction of a cycle called Otto, whose cycle is formed by processes that are carried out one by one sequentially, with a binary-isobaric-adiabatic cycle of seven processes which are all perform simultaneously and this system has the energy input by combustion in the Otto cycle by an isochoric process (3-4), as shown in Figure 4, indicated in 41, of compression and heating represented by the expression (a).

[027] In equation (a), (Qi-) represents the total system input energy, in "Joule", (n) represents the number of mol belonging to the Otto cycle unit, (R) represents the universal gas constant (T _q ) represents the maximum "Kelvin" gas temperature at process point (4), figure 4, indicated by 42, (T3) represents the temperature at the initial isocoric process point (3), figure 4 , and (y) represents the adiabatic expansion coefficient.

[028] Discarding energy not converted to work by the main machine, the Otto cycle, is the input energy of the secondary machine, binary cycle plus 315 turbine power, and the expression of the discarded energy supplied to the units. later is represented by expression (b), considering the isobaric process (5'-5), depending on the control, this process may be isothermal or adiabatic, in this case considered isobaric in the following equation.

[029] The input energy of the secondary, binary cycle machine is represented by the expression

[030] The 315 turbine input energy, an adiabatic process and is

represented by the expression (d).

[031] Discarding energy not converted to work by the secondary, binary-cycle machine is represented by the expression (e). This, in the ideal concept, is the total energy discarded in the middle, which does not perform useful work.

[032] The total useful work of the combined cycle system, considering an ideal lossless model, is the difference between energy input and output and is represented by the expression (f) below.

[033] The theoretical final demonstration of the combined cycle efficiency Otto and binary-isobaric-adiabatic is given by the expression (g), characterizing that the combined cycles of a machine based on open or closed system with a machine based on hybrid system have as parameter efficiency, also the number of moles or mass, characteristic inherited from the machine based on the hybrid system, and therefore do not have their efficiencies solely dependent on temperatures.

APPLICATION EXAMPLES

[034] Cycle engines combined by integrating an Otto cycle unit with a hybrid-based engine, for example, a binary-isobaric-adiabatic cycle turbine engine, have some important applications, the most obvious being their application in transport vehicles using the Otto cycle, and gasoline or alcohol as fuel. Hybrid-based engine technology brings numerous properties that are especially interesting to these designs, the flexibility when operating temperatures, the absence of a number of elements that are required in open and closed-based engines, providing volume and weight. reduced, and controllability, that is, the ability to operate over a wide range of rotation and torque. Therefore the combined cycle technology Otto with torque applies to vehicles, especially automobiles.

Claims

1) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR", characterized by the integration of two thermal machines, two thermodynamic cycles, forming a combined system, one of them being a machine operating by the Otto cycle (31); interconnected to another machine operating on a binary cycle (320), and so that its thermodynamic cycles are also integrated, an Otto cycle internal combustion engine (31) coupled to a binary-isobaric-cycle turbine engine where the Otto cycle motor has a discharge manifold (331) connected to a heat exchanger (319), the exchanger (319) has a binary cycle working gas circulation line that enters a proportional three-way control valve (326), and this valve directs part of the gas to the turbine rotor of the power conversion unit (321) and part of the gas to the turbine rotor of the power conservation unit (322), the turbine rotor of the conservation unit (322) conducts the working gas to the thermally insulated chamber (323), where the isobaric compression process is performed, following to the compressor rotor of the energy conservation unit. (324), conducting the gas with its conserved associated energy into the heating isobaric expansion chamber (319), the turbine rotor of the energy conversion unit (321) conducts its fraction of the working gas into the chamber. (328), is separated from the other cooling and cooling systems and is located at the coldest end of the forced fan air flow, and the gas entering point (c) inside the chamber (328), where the isobaric process of compression and cooling, following to the compressor rotor of the energy conversion unit (325), and this one, returning the gas to the inlet of the isobaric expansion and heating chamber (319), completing the thermodynamic cycle. torque-isobaric-adiabatic system, the mechanical force shaft (327) of the binary cycle turbine engine is coupled to the main mechanical shaft (33) of the Otto cycle unit by means of a gearbox. transmission (34) of the main motor (31), a turbine rotor (315) is connected to the main shaft of the binary cycle motor, with the function of driving the compressor rotor (314), and from the turbine rotor (315), the gas flows to an exhaust gas circulation (EGR) control unit (312) with the function of directing part of the turbine rotor outlet gases (315) to the combustion chambers of the Otto engine via mixer (39), a compressor rotor (314) is also connected to the main shaft of the binary cycle engine, which pressurizes air from the suction environment via filter (313), and pressurizes to the Otto engine combustion chambers ( 31) via the cooler (36) and mixer (39) by injecting them together with the portion of the combustion gas from the control element (EGR) (312) into the Otto engine combustion chambers (31) via the distributor (32).

2) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of the integration of two thermal machines, two thermodynamic cycles, forming a combined system, one of which is a machine that operates by the integrated Otto cycle (31) interconnected with another machine operating a binary cycle (320), and so that its thermodynamic cycles are also integrated.

3) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE ENGINE" according to claims 1 and 2, characterized in that it consists of an Otto-cycle internal combustion engine (31) coupled to a binary-cycle turbine engine. isobaric-adiabatic (320).

(4) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of an Ott cycle motor with a discharge manifold (331) connected to a heat exchanger (319), and the exchanger (319) has a binary cycle working gas circulation line. (5) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it comprises a proportional three-way control valve (326) connected to the heat exchanger (319), and This valve directs part of the gas coming from the exchanger (319) to the turbine rotor of the power conversion unit (321) and part of the gas to the turbine rotor of the power conservation unit (322).

6. The "OTTO AND BINARY-ISOBARIC-ADIABIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a turbine rotor of the conservation unit (322) which conducts the working gas to the insulated chamber. (323), where the isobaric compression process is performed.

7) "OTTO AND TORQUE-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it comprises a compressor of the energy conservation unit (324) connected to the isolated chamber outlet (323) , with the function of conducting the gas with its conserved associated energy into the isobaric expansion chamber (319).

8. The "OTTO AND BINARY-ISOBARIC-ADIABIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a turbine rotor of the power conversion unit (321) to drive its fraction of the working gas for the cooling chamber (328), is separated from the other cooling and cooling systems and is located at the coldest end of the forced fan air flow, and the gas entering point (c) inside the cooling chamber (328) ), where the isobaric compression and cooling process is performed.

9) "OTTO AND BINARY-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it is It is constituted by a compressor rotor of the energy conversion unit (325), which has the function of conducting the gas to the inlet of the isobaric expansion and heating chamber (319), completing the binary-isobaric-adiabatic thermodynamic cycle of the system.

10. "OTTO AND TORQUE-ISOBARIC-ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a mechanical power shaft (327) connected directly or indirectly to all compression and turbine rotors. , (314), (315), (321), (322), (324) and (325), and this axis is coupled to the main mechanical shaft (33) of the main motor (31) of the Otto cycle unit. by means of a transmission gearbox (34).

11) "OTTO AND TORQUE-ISOBARIC-ADIABATIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a turbine rotor (315) connected to the main axis of the binary cycle motor, with the function of driving the compressor rotor (314).

12. "OTTO AND TORQUE-ISOBARIC-ADIABATHIC COMBINED CYCLE ENGINE" according to claim 1, characterized in that it comprises an exhaust gas circulation control unit (312) with function of directing part of the turbine rotor outlet gases (315) to the Otto engine combustion chambers via mixer (39).

13. "OTTO AND TORQUE-ISOBARIC-ADIABIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a compressor rotor (314) connected to the main shaft of the torque-cycle motor, with the function of pressurizing ambient air drawn via the filter (313) and pressurizing the combustion chambers of the Otto engine (31) via the cooler (36) and mixer (39) by injecting them together with the portion of the combustion gas coming from the control element ( EGR) (312) for the combustion chambers of the Otto engine (31) via the distributor (32). 14) "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" to perform the combined motor cycle of claims 1 to 13, characterized by a process consisting of the combination of two cycles, one Otto and the other isobaric-adiabatic torque , in their union, form the combined cycle, where the first cycle, the Otto cycle, with the integration with other mechanical elements, the processes may vary as in the case of this invention, the introduction of a turbine rotor alters the isochoric process, taking - In short, adiabatic and the final stage of the adiabatic expansion process (4-5), it can gain isobaric characteristics by being described as follows: the energy input to the system by combustion (42) performs a heating process and isochoric compression (3-4), following expansion, an adiabatic process proceeds (4-5 '), from this point heat transfer occurs to exchanger (319) generating the second isobaric (5'-5) or depending on design or regulation parameters, this may be adiabatic, or variable between adiabatic and isobaric, terminating expansion with another adiabatic process (5-2) near the turbine rotor (315), then another adiabatic but compression process (2-3) ending the Otto cycle, the piped energy for the binary cycle turbine engine is defined by the process (5'-5) indicated by (43), the piped energy for the turbine rotor (315) is defined by process (5-2) indicated by (44), the binary cycle (45) is coupled, integrated with the otto cycle (41), so that the energy disposal process (5 ') -5) of the Otto cycle, is the input energy of the binary cycle, and this forms the isobaric expansion process (ab), and all processes that form the binary cycle occur simultaneously, starting from point (b) of the binary cycle occur. two processes, an adiabatic expansion process (bc) of the binary cycle and an adiabatic expansion process (b-c ') of the binary cycle engine conservation unit, finalized adiabatic expansion processes occur two isobaric compression processes, starting from point (c) of the binary cycle occurs a isobaric compression (cd) of the binary engine power conversion unit and starting from point (c ') an isobaric compression process (c'-d') of the energy conservation unit ends, the isobaric compression processes occur two times. Adiabatic compression processes, starting from point (d) of the binary cycle, there is an adiabatic compression process (da) of the binary cycle engine power conversion unit and an adiabatic compression (d'-a) process of the conservation unit. of the binary cycle motor, ending the binary cycle (45), therefore, under ideal, lossless conditions, the energy (42) enters the Otto cycle (41) by combustion, part of the waste energy, (44), feeds into a adiabatic process a turbine rotor, 315, another portion of the Otto cycle discarded energy (43), feeds the binary cycle, and the discarded binary cycle energy is, ideally without loss, the total energy lost, indicated by (46).

15. "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process consisting of the combination of two cycles, one Otto and one binary-isobaric-adiabatic, and the union thereof the combined cycle, where the first cycle, the Otto cycle, with the integration of mechanical elements, turbine rotors and heat exchangers, processes change so that the isochoric process gains adiabatic characteristics (5-2) and the final stage. from the adiabatic expansion process (4-5) obtains isobaric characteristics (5'-5).

16. "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process wherein the input energy into the system by combustion, (42), performs an isochoric heating and compression process. (3-4).

17) "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE OF THE COMBINED CYCLE MOTOR" according to claim 14, characterized by a process where after heating and isocoric compression (3-4), adiabatic expansion (4-5 ') occurs, from this point heat transfer to the exchanger (319) generating the isobaric segment (5'). -5) or depending on design or regulation parameters, this may be isothermal or adiabatic, or variable assuming intermediate properties.

18) "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE MOTOR MOTOR CYCLE" according to claim 14, characterized in that after the adiabatic, isothermal or isobaric expansion process (5'-5), expansion proceeds, ending the expansion with another adiabatic process (5-2) next to the turbine rotor (315).

19) "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that after the adiabatic expansion process (5-2) next to the turbine rotor (315), Within the Otto cycle, another adiabatic process occurs, but of compression (2-3), ending the Otto cycle.

20) "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process where the piped energy to the binary cycle turbine motor is defined by the process (5'-5) of the cycle Ottoindicated by (43).

21. "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process where the energy channeled to the turbine rotor (315) is defined by the adiabatic process (5-2) indicated by (44).

22) "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE OF THE COMBINED CYCLE MOTOR" according to claim 14, characterized by a process such that the binary cycle (45) is coupled, integrated with the Otto cycle (41), so that the energy disposal process (5'-5) of the Otto cycle is the binary cycle input energy (45), and form the isobaric expansion process (ab), and all processes that form the binary cycle occur simultaneously.

23) "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process whereby after the isobaric expansion process (ab) starting from point (b) of the binary cycle occurs two processes, an adiabatic expansion process (bc) of the binary cycle engine power conversion unit and an adiabatic expansion process (b-c ') of the binary cycle engine servicing unit, completed adiabatic expansion processes .

24) "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE MOTOR MOTOR CYCLE" according to claim 14, characterized in that after processes (bc) and (b-c '), two isobaric compression processes occur, starting from point (c) of the binary cycle, an isobaric compression process (cd) of the binary engine power conversion unit and starting from point (c '), an isobaric compression process (c'-d') occurs energy conservation unit, finalizing the isobaric compression processes.

25) "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that after processes (cd) and (c'-d '), two adiabatic compression processes occur , starting from point (d) of the torque cycle, there is an adiabatic compression process (da) of the binary cycle engine power conversion unit and an adiabatic compression process (d'-a) of the engine conservation unit. binary cycle, ending the binary cycle (45). 26. "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE OF THE COMBINED CYCLE MOTOR" according to claim 14, characterized by a process that under ideal, lossless conditions, energy (42) enters the Otto cycle (41) by combustion , part of the discarded energy, (44), by an adiabatic process feeds a turbine rotor, (315), another part of the energy (43), discarded from the Otto cycle (41), feeds the binary cycle, and the discarded energy of the binary cycle is ideally lossless, the total energy lost, indicated by (46).