Combined internal combustion engine with regenerator

 

(57) Abstract:

Usage: in the engines, both stationary and mobile installations with a combined internal combustion engine, for example, in diesel power plants. The essence: a combined internal combustion engine comprises a piston part, a power turbine on the same shaft with the compressor charge air and regenerator. Exhaust gases from the cylinder, the piston portion received in the power turbine, and then, after passing through the regenerator and kladas, are released into the environment. The air passing through the compressor, is heated in the regenerator and enters the cylinder piston parts. The invention provides significantly increase the efficiency of the combined internal combustion engines. table 2., 2 Il.

The invention relates to engine and can be used for both stationary and mobile installations.

Known hybrid engines, consisting of a piston internal combustion engine, gas turbine and compressor. Exhaust gases in internal combustion engines to operate a gas turbine and a compressor that supplies compressed air into the cylinder of a piston engine [1,S. 15].

However, in these engines the temperature of the gases emerging from the ha is these gases".

Closest to the proposed engine is combined engine containing a piston portion, a power turbine on the same shaft with the compressor charge air and the heat exchanger is a charge air cooler. Exhaust gases from the reciprocating part is fed to the input of the power turbine, and then out into the environment. Atmospheric air is fed to the input of the compressor, comes out of it with a higher temperature, passes through a heat exchanger-cooler and cooled enters the piston part. To the second input of the heat exchanger-cooler is supplied with a cooling fluid and heated it goes into the environment [1,S. 17].

The disadvantage of this engine is also high temperatures of exhaust gases emitted into the environment from the power turbine, and heat losses to the environment with cooling fluid leaving the heat exchanger-cooler, in addition, the cost of additional energy to supply cooling fluid to the heat exchanger. All this lowers the efficiency of the engine.

The aim of the invention is to increase the efficiency of the combined engine by reducing the heat loss from the combined internal combustion engine, contains piston part, a power turbine on the same shaft with the compressor charge air and the heat exchanger with the exhaust gases from the reciprocating part is fed to the input of the power turbine, and the air passing through the compressor and through the heat exchanger, is served in the piston part according to the invention, the heat exchanger acts as a regenerator, a second input which serves exhaust gases from the output of the power turbine, and are released into the atmosphere from the second output of the regenerator.

In Fig. 1 presents the proposed scheme combined internal combustion engine with a regenerator, where 1 - piston unit; 2 - power turbine; 3 - compressor; 4 - regenerator; 5 - shaft connecting the power turbine and the compressor inlet air.

thermodynamic cycle of the proposed motor coordinates temperature - entropy (t-S) shown in Fig.2, where 1-2 is isentropic compression of air in the compressor, 2-a - Isobaric heating of air in the regenerator, a-c - adiabatic compression in the cylinder, piston parts, c-z - isochoric the supply of heat in the cylinder, z-b - adiabatic expansion in the cylinder, b-a - isochoric pressure drop in the cylinder by conversion of potential energy of the gas into kinetic energy photoperiod turbine constant pressure, 3-4 - adiabatic expansion of the gas in the turbine, 4-5 - Isobaric cooling of the gas in the regenerator, the heat is given to the air coming from the compressor, 5-1 - Isobaric exhaust heat into the environment.

The gas parameters at the endpoints of the processes of the cycle are given in table.1.

In other variants of the proposed motor the supply of heat in the cylinder piston unit may be Isobaric or mixed, and power turbine can be "pulsed".

The calculation cycle is produced for 1 kg of air, the adiabatic exponent which K=1,4, and the gas constant R=0,287 kJ/kgK. The warmth in the Isobaric processes rasschityvaet according to the formula , and isochoric , where t1and t2- temperature at the beginning and at the end of the process.

Entropy is equal to zero at 0oC and 760 mm RT.article The degree of regeneration in the ideal thermodynamic process is equal to one.

Heat, supplied from the outside, qcz= 559 kJ/kg Heat allotted outward, g5-1= 107 kJ/kg (q2=q5-1). Useful work of l0=452 kJ/kg Thermal efficiencyt=0,809.

Comparison of the cycles of the proposed engine and a prototype produced for 1 kg of gas with the same initial parameters of atmospheric air (point 1S="ptx2">

The gas parameters at the endpoints of the process cycle engine of the prototype are presented in table.2.

thermodynamic cycle of the engine of the prototype consists of the following processes: 1-2 - adiabatic compression of air in the compressor, 2-a - Isobaric cooling air in the heat exchanger-cooler, a-c - adiabatic compression in the cylinder piston parts, c-z - isochoric the supply of heat in the cylinder, z-b - adiabatic expansion in the cylinder, b-a - isochoric pressure drop in the cylinder by conversion of potential energy of the gas into kinetic energy of the flow, a-3 - Isobaric expansion of the gas in the pipeline with the transformation of the kinetic energy of the flow into potential energy before the turbine constant pressure, 3-4 - adiabatic expansion of the gas in the turbine, 4-1 - Isobaric exhaust heat into the environment.

Heat, supplied from the outside, qcz= 1090 kJ/kg Heat allotted outward, q4-1+ a2-a= 352 kJ/kg. Useful work l0=736 kJ/kg Thermal efficiencyt= 0,677.

The temperature of the gas emitted into the environment engine prototype, much higher than in the proposed engine (300 >121oC) in addition, in the engine prototype has the exhaust heat into the environment by the heat exchanger on the stage efficiency)

[(0,809-0,677)/0,677]100=19,5%.

When comparing the proposed combined engine and engine prototypes were designed and analyzed thermodynamic cycles (idealized, as is customary in thermodynamics). Considering the irreversible energy losses, i.e., when the transition to actual cycles, engine efficiency will decrease, but the quality ratio between the compared efficiency will continue.

The disadvantages of the proposed combined internal combustion engine with regenerator should include less specific useful work (452 < 736 kJ/kg of gas). In order to increase the useful work to bring it to the magnitude of the work accomplished in the prototype, it is necessary to increase the airflow in 736/452=1.63 times. This will lead to an increase (ceteris paribus) the height of the blades of the turbine and compressor in =1.27 times, and the linear dimensions of the cylinder piston parts = 1.18 times. This increase can be considered relatively minor, especially for stationary engines is not as specific gravity, as efficiency.

Combined internal combustion engine with a regenerator containing a piston portion, a power turbine on the same shaft with the compressor and the heat exchanger, and the output of the exhaust geom

with the first inlet of the heat exchanger, the first output of which is connected to the input piston part and the second output with the atmosphere, wherein the heat exchanger is connected to a second input with the output power of the turbine, performs the function of the regenerator.

 

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