WO2018195630A1

WO2018195630A1 - Combined diesel and binary isothermal-adiabatic cycle engine and process for controlling the thermodynamic cycle of the combined cycle engine

Info

Publication number: WO2018195630A1
Application number: PCT/BR2018/050126
Authority: WO
Inventors: Marno Iockheck; Saulo Finco; LUIS Mauro MOURA
Original assignee: Associação Paranaense De Cultura - Apc
Priority date: 2017-04-26
Filing date: 2018-04-24
Publication date: 2018-11-01
Also published as: BR102017008573A2

Abstract

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

Description

"DIESEL AND BINARY-ISOTHERMIC-ADIABIC COMBINED CYCLE MOTOR AND CONTROL PROCESS FOR THE THERMODYNAMIC COMBINED CYCLE MOTOR CYCLE"

TECHNICAL FIELD OF THE INVENTION

[001] The present invention relates to a combined cycle thermal motor formed by one unit operating with the interconnected diesel cycle and integrated with the other unit operating with the binary cycle of three isothermal 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 of closed thermodynamic systems are external combustion engines such as Stirling cycle, Ericsson cycle, Rankine cycle with closed circuit working fluid, Brayton heat cycle or external combustion, Carnot cycle. The energy that enters this system is heat. The energies that come out of this system are the mechanical working energy and part of the heat dissipated, but no matter comes out of these systems, as occurs 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 also 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 have been invented and designed by uniting in the same system two motor concepts conceived in the nineteenth century, based on open thermodynamic systems or closed thermodynamic systems, the best known are the combined cycles of a 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 major disadvantages of today's combined cycles, considering the second machine 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 be controlled, and the heating energy of the liquid phase and the latent phase change state cannot be converted into working energy, they 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.

OBJECTIVES OF THE INVENTION

[012] The major problems of the state of the art, specifically with regard to combined cycles, lie precisely in the second unit forming systems, which is usually a Rankine cycle machine. an old machine whose thermodynamic processes impose losses through the need to change the physical state of the working fluid, the heat of the liquid phase, the heat of transformation, the latent heat, the 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, 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 motors is necessary. engine efficiency is no longer dependent solely on temperatures. The hybrid system concept and differential and binary cycles, the very characteristic that underlies this new combined cycle concept, eliminates the reliance on efficiency exclusively at 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 a Diesel cycle unit with a binary-isothermal-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 disposed of 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 a diesel cycle engine 31 which performs a four process diesel cycle and a binary isothermal adiabatic cycle turbine engine 320 which performs a three isothermal process cycle. and four adiabatic processes, and so that the input energy, by combustion, performs an isobaric expansion process on the diesel cycle unit, an isochoric cooling process when the exhaust goes straight to the environment or isobaric or adiabatic when using heat exchangers. for other purposes which provides energy for the isothermal process of expansion of the binary cycle unit, this in turn performs an isothermal cooling process giving to the environment the energy that the system together has not converted to work and so that both the cycles have a conversion into common final work. These are therefore combined-cycle motors that are completely different from today's combined-cycle motors, which are based solely on open or closed systems. In figure 3 The general concept of the invention is shown and in Figure 4 the graphs showing the integration of both thermodynamic cycles forming the combined cycle are shown. In addition to the combination of the diesel and torque cycle, the present invention further contemplates the use of an auxiliary turbine 315 to perform work by means of an adiabatic process with residual energy and a compressor 314 for air pressurization in the combustion engine combustion chambers. Diesel internal.

[016] The present invention brings important developments for the conversion of thermal energy to 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. to utilize the energies of these phases in conversion. Some of the main advantages of the torque-isothermal-adiabatic combined diesel cycle which can be seen are the absence of physical phase shift elements of the working fluid and its associated losses, the absence of condensation and vaporization elements, therefore the no losses associated with latent heat of the working fluid, no circuits, pumps, control elements for fluid phase change processes and their associated losses, and consequently no volume, materials and mass , weight, of the elements that make up such projects. Therefore, the innovation presented by the combined cycle Diesel with torque is significant. [017] Combined-cycle engines based on the integration of a diesel-cycle engine 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 an engine. Working with closed-circuit gas, considering the complete system, this closed-circuit working gas concept with respect to the external environment indicates that the system should be sealed, or in some cases leaks may be allowed provided they are compensated. Suitable materials for this technology should be noted, which are similar in this respect to Brayton, 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 accompanying figures demonstrate the main features and properties of the new combined cycle concept, more specifically a system consisting of a Diesel cycle unit with a binary-isothermal-adiabatic cycle unit, and are represented as follows:

Figure 1 demonstrates in block diagram a current combined cycle system consisting of a Diesel cycle unit with a Rankine cycle unit. Plants designed with this philosophy today are used to improve mechanical and energy efficiency in traction systems, vehicles such as trucks, machines, ships;

Figure 2 demonstrates in block diagram a combined cycle system designed on the basis of the new thermodynamic system concept consisting of a known Diesel cycle unit with a cycle unit. binary-isothermal-adiabatic. Theoretically, systems designed with this philosophy for mechanical power generation will have higher efficiency than combined cycle systems with Rankine or organic Rankine based on the theoretical analysis of the second machine cycle that forms the system, among the losses that cease to exist, the absence of changing the physical state of the working fluid is a significant item; the energy conservation process provided by the binary subsystem conservation subsystem reinforces the possibilities of increasing overall efficiency;

Figure 3 is a diagram of a system consisting of a 31 diesel cycle engine with a binary isothermal adiabatic cycle turbine engine. 320 forming the combined cycle Diesel and torque;

Figure 4 shows respectively the curves of the pressure and volumetric displacement graph of the Diesel cycle 41 and the curves of the pressure and volumetric displacement graph of the binary-isothermal-adiabatic cycle 45;

Figure 5 shows the conventional diesel cycle with one isobaric process, two adiabatic processes and one isochoric process.

DETAILED DESCRIPTION OF THE INVENTION

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

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

[021] There are conditions necessary for the binary cycle motor cycle to be formed by isothermal and adiabatic processes, the first is related to the conversion unit compressor rotors 325. and conservation 324, these must be designed to carry the gas in the adiabatic processes at the pressure that corresponds in the process to its return to the temperature of the isothermal exchanger 319 and that the heat exchanger 319 is designed so that the heat exchange with the gas is efficient and thermally isonomic, that is. The internal chambers of the exchanger must be designed with isonomic characteristics in the gas temperature throughout, allowing, of course, pressure differentials as the working gas flow occurs, unlike the heat exchangers of the isobaric units, these in turn. Instead, to exemplify, they must be designed for pressure, not temperature, equality.

[022] Figure 3 also shows the main elements that configure a diesel 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 The low temperature isothermal binary cycle unit compression is the most external because the efficiency of the binary cycle unit increases the lower the temperature of the isothermal process that occurs in the heat exchanger 328, unlike other diesel engine needs. Heat exchanger 36 is used for cooling pressurized air by compressor 31. Another heat exchanger, radiator 35 is the main cooling element of the diesel engine, hydraulic and electric units. A 329 fan is used to force ventilation and improve heat exchange, cooling. A coolant, typically water, pump 37 circulates the fluid within the internal combustion engine to keep it in safe thermal conditions, aided by a thermostat-type sensor 38 for temperature control. Mixing of pressurized air with part of the exhaust gas takes place in mixer 39 and goes to a manifold 32 which injects into the combustion chambers of the diesel engine the mixture of air with part of the exhaust gas. 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. Diesel engine power shaft 33 is the main element for bringing mechanical force to the transmission case 34. [023] Figure 4 shows the graphs of pressure and volumetric displacement that in their union form the combined cycle, a process composed by the combination of two cycles, one Diesel and the other isothermal-adiabatic, where the first cycle, the cycle Diesel is formed by four processes, or also called thermodynamic transformations, being an isobaric process or transformation, two adiabatic processes and an isochoric process, 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 stage of the adiabatic expansion process (4-5), can gain isobaric characteristics and the energy input to the turbine is described as follows. The combustion system 42 performs an isobaric expansion process (3-4). Following expansion, an adiabatic process proceeds (4-5 '), from this point heat transfer occurs to exchanger 319 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 turbine rotor 315. then another adiabatic but compression process (2-3) ending the diesel cycle. The piped energy for the binary cycle turbine engine is defined by process (5'-5) indicated by 43, the piped energy for turbine rotor 315 is defined by process (5-2) indicated by 44.

[024] Binary cycle 45 is coupled, integrated with the diesel cycle. 41, so that the diesel cycle energy disposal process (5 '-5) is the binary cycle input energy and all the processes that form the binary cycle occur simultaneously. The energy discarded from the diesel cycle forms the isothermal expansion process (ab), starting from point (b) of the binary cycle two processes occur, an adiabatic expansion process (bc) of the binary cycle engine conversion unit and an adiabatic process. (b-c ') of the binary cycle motor adiabatic expansion processes occur two isothermal compression processes, starting from point (c) of the binary cycle occurs an isothermal compression process (cd) of the binary engine power conversion unit and starting from point (c ^' ) a process of isothermal compression (c'-d ') of the energy conservation unit, ending the isothermal compression processes two adiabatic compression processes occur, starting from point (d) of the binary cycle an adiabatic compression process (da) of the torque-cycle engine power conversion and an adiabatic compression process (d '-a) of the torque-cycle engine servicing unit, completing torque-cycle 45. Therefore, under ideal, lossless conditions, energy enters combustion in the Diesel cycle, indicated by 42, part of the waste energy 44, is fed by an adiabatic process to a turbine rotor 315, the remaining part of the waste energy 43 of the cycle. clo Diesel feeds the binary cycle 45, the energy discarded from the binary cycle is ideally lossless, 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 Diesel cycle when it is integrated with the binary-isothermal-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-isothermal-adiabatic cycle shown step by step. step, with three isothermal processes and four adiabatic processes.

Table 2

Figure 5 shows the ideal diesel cycle pressure and volume graph, considering an engine without accessories, is a cycle formed by an isobaric combustion heating process (3-4). an adiabatic expansion process (4-5), an isochoric cooling process (5-2), and an adiabatic compression process (2-3). When implanting mechanical changes in the engine, the addition of a 315 turbine and a 319 heat exchanger, there is also a change in the thermodynamic cycle, the process (5-2) is no longer isochoric because there is a turbine to move that 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.

[027] The combined diesel-torque-isothermal-adiabatic cycle is the junction of a cycle called Diesel, whose cycle is formed by one-to-one processes sequentially, with a seven-process binary-isothermal-adiabatic cycle. all perform simultaneously and this system has the energy input by combustion of Diesel, an isobaric process (3-4), as shown in Figure 4. indicated in 41, of expansion and heating represented by the expression (a).

Qi = ^ _y ir _qc - T ₃ ) (a)

[028] In equation (a), (Q,) represents the total system input energy, in "Joule", (n) represents the number of mol belonging to the Diesel cycle unit, (R) represents the universal gas constant. (Τ ^) represents the maximum "Kelvin" gas temperature at process point (4), figure 4, indicated by 42, (T ₃ ) represents the temperature at isobaric process starting point (3), figure 4, and (y) represents the adiabatic expansion coefficient. [029] Discarding energy not converted to work by the main machine, the Diesel cycle, is the input energy of the secondary, binary-cycle machine 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, it was considered isobaric in the following equation.

[030] The binary cycle secondary machine input energy is represented by the expression (c), where (Tq) is the isothermal input temperature of the binary cycle unit.

[031] Diesel cycle machine output energy minus turbine 315 energy is equal to binary cycle machine input energy according to equation (c).

Turbine input energy 315, (Q _t ) is an adiabatic process and is represented by the expression (d).

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

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

[035] The theoretical final demonstration of the combined diesel-torque-isothermal-adiabatic cycle efficiency is given by the expression (g), whereas characterizing that the combined cycles of a machine

based on the open or closed system with a hybrid based machine have as efficiency parameter also the number of moles or mass, inherited characteristic of the hybrid based machine, and therefore do not have their efficiencies exclusively temperature dependent.

APPLICATION EXAMPLES

[036] Cycle engines combined by the integration of a Diesel cycle unit with a hybrid-based engine, for example a binary-isothermal-adiabatic cycle turbine engine, have some important applications, the most obvious being their application in transport vehicles using diesel as a fuel, whether on land or sea. Hybrid-based engine technology brings numerous properties that are especially interesting to these designs, the flexibility when operating temperatures, the lack of a number of elements that are required in open and closed-based engines, providing volume and weight. reduced, and controllability, ie the ability to to operate over a wide range of rotation and torque. Therefore torque-combined diesel-cycle technology applies to cargo vehicles, trucks, vessels, boats, ships and rail.

Claims

1) "DIESEL AND TINARY-ISOTHERMIC-ADIABATHIC 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 Diesel cycle (31); interconnected to another machine operating on a binary cycle (320). and so that their thermodynamic cycles are also integrated, where a diesel-cycle internal combustion engine (31) is coupled to a binary-isothermal-adiabatic cycle turbine engine (320), the diesel-cycle engine having 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 converter 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 isothermal compression process is performed, following to the compressor rotor of the energy conservation unit (324), conducting the gas with its conserved associated energy to the heating isothermal expansion chamber (319), the turbine rotor of the power conversion unit (321) conducts its working gas fraction to the cooling chamber (328). ) is separated from the other cooling systems and is located at the coldest end of the forced air flow of the fan, and the gas entering point (c) inside the chamber (328), where the isothermal compression process is performed. and cooling, following to the compressor rotor of the power conversion unit (325). and by returning the gas to the inlet of the isothermal expansion and heating chamber (319), completing the binary-isothermal-adiabatic thermodynamic cycle of the system, the mechanical force of the shaft (327) of the binary cycle turbine engine is coupled. to the main mechanical shaft (33). of cycle unit By means of a transmission gearbox (34) of the main engine (31), a turbine rotor (315) is connected to the main shaft of the torque-cycle engine with the function of driving the compressor rotor (314). ), and from the turbine rotor (315), the gas flows to an exhaust gas circulation control unit (312), type (EGR), with the function of directing part of turbine (315) to the combustion chambers of the diesel 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 pressurizing the combustion chambers of the diesel engine (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 combustion chambers of the diesel engine (31) via the distributor (32). ).

2) "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC 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 diesel cycle (31). interconnected to another machine operating on a binary cycle (320), and so that its thermodynamic cycles are also integrated.

3) "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC COMBINED CYCLE ENGINE" according to claims 1 and 2, characterized in that it consists of a diesel-cycle internal combustion engine (31) coupled to a binary-cycle turbine engine isothermal adiabatic (320).

4) "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a diesel cycle engine (31) with a discharge manifold (331) connected to a heat exchanger 319, and exchanger 319 has a binary cycle working gas circulation line. 5) "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC 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 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 energy conservation unit (322).

6. "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a conservation unit turbine rotor which conducts the working gas to the insulated chamber. thermally (323), where the isothermal compression process is performed.

7. "DIESEL AND BINARY-ISOTHERMIC ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a compressor of the energy conservation unit (324) connected to the outlet of the isolated chamber (323). . with the function of conducting the gas with its conserved associated energy into the isothermal expansion chamber (319).

8. "DIESEL AND TINARY-ISOTHERMIC-ADIABATHIC 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 isothermal compression and cooling process is performed.

9. "DIESEL AND BINARY ISOTHERMIC ADIABATHIC CYCLE MOTOR" according to claim 1, characterized in that it is consisting of a compressor rotor of the energy conversion unit (325), which is designed to drive the gas into the isothermal expansion and heating chamber (319), completing the binary-isothermal-adiabatic thermodynamic cycle of the system .

10) "DIESEL AND BINARY-ISOTHERMIC 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 engine (31) of the Diesel cycle unit. by means of a transmission gearbox (34).

11. "DIESEL AND TINARY-ISOTHERMIC-ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a turbine rotor (315) connected to the main shaft of the binary cycle motor, with the function of driving the compressor rotor (314).

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

13. "DIESEL AND BINARY-ISOTHERMIC-ADIABATHIC COMBINED CYCLE MOTOR" according to claim 1, characterized in that it consists of a compressor rotor (314) connected to the main shaft of the binary cycle motor, with the function of pressurizing ambient air drawn in via the filter (313). and pressurizing the combustion chambers of the diesel engine (31) via the cooler (36) and mixer (39), injecting them together with the portion of the combustion gas from the control element (EGR) (312). into the combustion chambers of the diesel engine (31) via the distributor (32). 14) "CONTROL PROCEDURE FOR THE THERMODYNAMIC CYCLE ENGINE CYCLE CONTROL" to perform the combined engine cycle of claims 1 to 13, characterized by a process consisting of the combination of two cycles, one Diesel and one torque-isothermal-adiabatic . where the first cycle, the Diesel 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, making it, in synthesis, adiabatic and the step. At the end of the adiabatic expansion process (4-5), it can gain isobaric characteristics and is described as follows: The input energy into the system by combustion (42) performs an isobaric expansion process (3-4), following this. 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, this may be isothermal or adiabatic, or variable between adiabatic and isobaric, ending the expansion with another adiabatic process (5-2) next to the turbine rotor (315), then another adiabatic but compression process (2-3) ends. In the Diesel cycle, the piped energy for the binary cycle turbine engine is defined by process (5 '-5) indicated by (43), the piped energy for the turbine rotor (315) is defined by process (5-2). ) indicated by (44) .The torque cycle (45) is coupled, integrated with the Diesel cycle (41), so that the power cycle (5 '-5) of the Diesel cycle is the binary cycle input energy , and this forms the isothermal expansion process (ab), and all processes that form the binary cycle occur simultaneously, starting from point (b) of the binary cycle two processes occur, an adiabatic expansion process (bc) of the conversion unit. of the binary cycle motor and an adiabatic expansion process (b-c ') of the binary cycle motor conservation unit, finished adiabatic expansion processes occur two isothermal compression processes, starting from point (c) of the binary cycle occurs isothermal compression process (cd) of the engine power conversion unit torque and starting from point (c ') there is an isothermal compression process (c ^! -d ^! ) of the energy conservation unit, ending the isothermal compression processes occur two adiabatic compression processes, starting from point (d) of the cycle torque occurs an adiabatic compression process (da) of the binary cycle motor power conversion unit and an adiabatic compression process (d '-a) of the binary cycle engine servicing unit ending the binary cycle (45), therefore, under ideal, lossless conditions, the energy (42) enters combustion in the diesel cycle (41), part of the discarded energy (44), by an adiabatic process feeds a turbine rotor, (315), another part of the energy Discarded from the Diesel cycle (43), feeds the binary cycle, and the discarded energy from the binary cycle is ideally lossless, the total energy lost, indicated by (46).

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

16. "CONTROL PROCESS 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 isobaric expansion process (3- 4).

17) "CONTROL PROCESS FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that after an isobaric expansion (3-4), the expansion proceeds with an adiabatic process (4-5). ^! ) from this At this point heat transfer occurs to the exchanger (319) generating the isobaric segment (5'-5) or depending on the design or regulation parameters, this may be isothermal or adiabatic, or variable assuming properties of both dynamically.

18. "CONTROL PROCEDURE FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that after the adiabatic, isothermal or isobaric expansion process (5 -5), expansion proceeds, ending expansion with another adiabatic process (5-2) near 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 Diesel cycle, another adiabatic process occurs, but of compression (2-3) ending the Diesel 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 Diesel cycle indicated 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 PROCEDURE FOR THE COMBINED CYCLE ENGINE THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process such that the binary cycle (45) is coupled, integrated with the diesel cycle. (41), so that the process of energy disposal (5'-5) of the Diesel cycle, is the input energy of the binary cycle (45), and forms the isothermal expansion process (ab), and all processes that form the binary cycle occur simultaneously.

23) "CONTROL PROCESS FOR THE COMBINED CYCLE MOTOR THERMODYNAMIC CYCLE" according to claim 14, characterized in that a process whereby after the isothermal 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 OF THE COMBINED CYCLE MOTOR" according to claim 14, characterized in that after processes (bc) and (b-c '), two isothermal compression processes occur, starting from point (c) of the torque cycle, occurs an isothermal compression process (DC) of the power conversion unit and the motor torque from the point (C ') is an isothermal compression process ^(c'-d:) energy conservation unit, finalizing the isothermal 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 binary cycle, there is an adiabatic compression process (d-a) of the binary cycle engine power conversion unit and an adiabatic compression process (d'-a) of the torque motor, ending the torque cycle (45).

26) "CONTROL PROCESS FOR THE THERMODYNAMIC CYCLE OF COMBINED CYCLE ENGINE "according to claim 14, characterized in that a process which under ideal conditions, without loss, energy (42) enters combustion in the diesel cycle (41), part of the discarded energy, (44), feeds by an adiabatic process a turbine rotor (315), another part of the energy (43), discarded from the Diesel cycle (41), feeds the binary cycle, and the discarded energy of the binary cycle is, ideally without losses, the same. total energy lost, indicated by (46).