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WO2016114683A1 - Moteur à combustion interne et procédé de fonctionnement - Google Patents

Moteur à combustion interne et procédé de fonctionnement Download PDF

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Publication number
WO2016114683A1
WO2016114683A1 PCT/RU2015/000010 RU2015000010W WO2016114683A1 WO 2016114683 A1 WO2016114683 A1 WO 2016114683A1 RU 2015000010 W RU2015000010 W RU 2015000010W WO 2016114683 A1 WO2016114683 A1 WO 2016114683A1
Authority
WO
WIPO (PCT)
Prior art keywords
isochoric
expansion
engine
cycle
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/RU2015/000010
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English (en)
Russian (ru)
Inventor
Борис Львович ЕГОРОВ
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Individual
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Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to PCT/RU2015/000010 priority Critical patent/WO2016114683A1/fr
Publication of WO2016114683A1 publication Critical patent/WO2016114683A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to engine
  • thermodynamic cycle is closest to the cycle, described in the application JV ° PCT RU2014 / 000720 for two-stroke internal combustion engines with isothermal compression and a separate combustion chamber. But the difference of the proposed cycle is the use of heat recovery of exhaust gases, that is, it is a regenerative isothermal cycle, which significantly increases its efficiency.
  • the implementation of the cycle is proposed to be implemented in an engine with an opposed arrangement of communicating pairs of cylinders and counter-movement of the pistons. Unlike traditional engines with this arrangement, the proposed engine cylinders are located with axial displacement for
  • the main goal of the proposed method is to increase engine efficiency
  • thermodynamic cycle internal combustion through the use of a more efficient thermodynamic cycle and its implementation in a device whose design allows to minimize thermal, mechanical and gas-dynamic losses.
  • thermodynamic cycle (Fig. 1, 2): isothermal compression - isochoric heat supply - isothermal (isobaric) expansion - adiabatic expansion - isobaric (isochoric) heat removal.
  • This cycle like the Stirling or Ericsson cycle, is also regenerative, or rather partially regenerative.
  • the heat of the exhaust gases is used to heat the working fluid to a temperature of self-ignition after isothermal compression before being allowed into the engine cylinders.
  • the lower part of the cycle diagram (under the dashed line) is similar to the ideal Stirling cycle.
  • an ideal Stirling cycle has the same efficiency as an ideal Carnot cycle, i.e. the maximum possible for a given temperature difference.
  • an ideal Carnot cycle i.e. the maximum possible for a given temperature difference.
  • isochoric heat input is used instead of heating the working fluid as a result of adiabatic compression (isoentropic compression).
  • isentropic compression is more effective, since entropy does not increase as a result of it, and, therefore, in this case, the efficiency of the entire proposed cycle would be similar to the efficiency of an ideal Carnot cycle for a given temperature difference.
  • adiabatic compression in this case will be difficult and less practical due to the significant complexity of the design, increased compression work, mechanical and heat losses, and
  • the theoretical efficiency of the proposed cycle will be as close as possible to the efficiency of the ideal Carnot cycle, and differ only in the amount of losses due to increased entropy during isochoric heat supply, graphically depicted in the diagram as a triangle formed by the isochoric heat supply line and two dashed lines of the imaginary cycle Carnot (Fig. 3).
  • isothermal and adiabatic expansion can be replaced, by analogy with the real Otto cycle, with polytropic expansion, or by analogy with the real Sabate-Trinkler cycle, with isobaric and polytropic
  • isothermal compression up to 30% higher than the efficiency of reciprocating compressors. Effective implementation of the cycle is possible with a degree of pressure increase in the process of isothermal compression from 20 and above.
  • the temperature at the end of isothermal compression in a screw compressor is about 100 ° C or slightly higher. If it is not possible to compress to a given pressure in a single-stage compressor, a two-stage screw compressor or a single-stage screw compressor with an additional supercharger of any suitable design with or without an intercooler can be used.
  • the regenerator can be heated by an additional device operating on the principle of a pre-heater, and the engine itself is equipped with a glow plug similar to diesel engines.
  • the working fluid After heating with exhaust gases, the working fluid is injected directly into the engine cylinders under a pressure of 25 atm. and higher.
  • the intake period should be approximately 15-20 ° of crankshaft rotation. At the same time, they ensure optimal filling, including at high speeds, by correctly selecting the cross section of the intake valve (s).
  • the communicating opposed cylinders are located with axial displacement for the possibility of placing poppet valves, and the opposing pistons counter-move not synchronously, but with a certain advance angle to allow the intake and isochoric supply of thermal energy directly inside the cylinders (Fig. 4, 5, 6 )
  • the piston of cylinder 1 (Fig. 4) reaches TDC and the piston of cylinder 2 is approximately 25-35 ° to TDC
  • the working fluid is inlet through the inlet valve (s) of cylinder 1.
  • the inlet lasts about 15-20 ° of crankshaft rotation.
  • fuel injection can also be started.
  • the start of injection is carried out with a certain advance angle or even delay, depending on the speed of the crankshaft. So at the maximum speed, the injection can be started simultaneously with the intake of the working fluid or even before it. But the ignition delay phase must end after closing the intake valve or at the same time as it closes.
  • High inlet pressure and flow of the working fluid from cylinder 1 to cylinder 2 and vice versa will provide maximum charge turbulence for high-quality mixing with the injected fuel and more efficient and complete combustion.
  • the piston of cylinder 1 will already be 25-35 ° after TDC, which is also more effective from the point of view of mechanics than the effect of maximum pressure on the piston in TDC.
  • the regenerator can also perform the functions of a catalytic converter when coating its surfaces
  • the exhaust valve is closed before opening the intake valve.
  • Figure 11 shows a comparative theoretical thermal calculation of the proposed cycle and the Sabate-Trinkler cycle for a turbocharged diesel engine with a compression ratio of 18.5.
  • the same values of the expansion polytropic and heat capacities, close to those of real diesel engines, are taken for clarity.
  • the thermal efficiency of the proposed cycle significantly exceeds the thermal efficiency of the Sabate-Trinkler cycle and can reach 0.78, which does not contradict the theory, since the efficiency of the ideal Carnot cycle for a given temperature difference (293K and 2457K) will be approximately 10% higher .
  • the mode of the proposed engine is push-pull and without compression in the expansion cylinders; therefore, much less cylinder volume is needed for the same power than for a diesel engine.
  • the liter capacity of the proposed engine will be approximately 2 times greater than the diesel engine.
  • the mechanical efficiency of a screw compressor can be 0.98, and the mechanical The adiabatic compression efficiency in ICE cylinders is at best 0.9.
  • the compression work in the proposed engine will be approximately 3 times less than in a diesel engine with the same power.
  • the maximum pressure in the cylinders of the proposed engine is approximately 2 times lower than in the cylinders of a diesel engine. From all this it follows that the mechanical efficiency of the proposed engine will be significantly higher than the mechanical efficiency of the diesel engine.
  • FIG. 1 TS diagram (temperature-entropy) of the proposed theoretical cycle.
  • FIG. 2 PV diagram (pressure-volume) of the proposed theoretical cycle.
  • FIG. 3 Comparative TS diagram of the proposed cycle and the ideal Carnot cycle.
  • FIG. 4, 5, 6 Schematic representation of engine operation during inlet, expansion, and exhaust.
  • FIG. 7 General diagram of a device operating according to the proposed method.
  • FIG. 8 Scheme of the expansion machine of the proposed device.
  • FIG. 9 Variant of inlet valve with hydraulic actuator.
  • FIG. 10 Diagram of the hydraulic drive of the intake valve.
  • FIG. 11 Comparative calculation of the engine working on the proposed cycle and the diesel engine working on the Sabate-Trinkler cycle. Description of an embodiment of the invention
  • the implementation of this method of operation can be carried out in a device, a diagram of which is shown in FIG. 7.
  • the device contains the following main elements: expansion cylinders 1 and 2, inlet valve 3, exhaust valve 4, nozzle 5, regenerator 6, separator 7, compressor 8, fan 9, compressor cooling radiator 10, fuel tank 11, high pressure fuel pump 12.
  • the design of the device may consist mainly of well-known technical solutions.
  • a screw compressor with oil or water injection, equipped with a cooling system and separation of the injected liquid can be standard or with a lightweight housing.
  • the regenerator which is a heat exchanger, can be supplemented by a pre-heating system and a system of neutralizing harmful substances.
  • the engine power system is generally similar to direct injection diesel systems.
  • the expansion machine or the engine itself actually consists of two opposed blocks of the known
  • FIG. 9 shows an inlet valve with a hydraulic actuator.
  • the cam of the hydraulic drive is located on the flywheel or behind the flywheel (Fig. 10).
  • the exhaust valve has an almost standard design of a side poppet valve with a lower camshaft (Fig. 8).

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un moteur à combustion interne fonctionnant selon le cycle thermodynamique théorique suivant: compression isotherme, amenée isochore de chaleur, détente isothermique ou isobarique, détente adiabatique, évacuation isobarique ou isochore de l'énergie thermique. L'amenée isochore d'énergie thermique se fait partiellement en utilisant la chaleur des gaz usés dans un régénérateur (6). La compression isotherme se fait dans un compresseur (8) avec un refroidissement interne de l'air comprimé. L'admission de la charge, l'injection de carburant et la détente du fluide de travail se font dans le moteur en utilisant les cylindres opposés (1, 2). Les paires communicantes de cylindres présentent un décalage axial permettant de disposer les soupapes. Le piston du cylindre avec la soupape d'admission se déplace à l'encontre du piston du cylindre avec la soupape d'échappement selon l'angle d'avance. L'admission du fluide de travail, l'injection de carburant et la combustion isochore se font immédiatement dans les cylindres du moteur.
PCT/RU2015/000010 2015-01-15 2015-01-15 Moteur à combustion interne et procédé de fonctionnement Ceased WO2016114683A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/RU2015/000010 WO2016114683A1 (fr) 2015-01-15 2015-01-15 Moteur à combustion interne et procédé de fonctionnement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/RU2015/000010 WO2016114683A1 (fr) 2015-01-15 2015-01-15 Moteur à combustion interne et procédé de fonctionnement

Publications (1)

Publication Number Publication Date
WO2016114683A1 true WO2016114683A1 (fr) 2016-07-21

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PCT/RU2015/000010 Ceased WO2016114683A1 (fr) 2015-01-15 2015-01-15 Moteur à combustion interne et procédé de fonctionnement

Country Status (1)

Country Link
WO (1) WO2016114683A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018195619A1 (fr) * 2017-04-25 2018-11-01 Associação Paranaense De Cultura - Apc Moteur thermique à cycle différentiel faisant intervenir quatre processus isobares et quatre processus polytropiques avec régénérateur, et procédé de commande pour le cycle thermodynamique de ce moteur thermique
WO2018195618A1 (fr) * 2017-04-25 2018-11-01 Associação Paranaense De Cultura - Apc Moteur thermique à cycle différentiel faisant intervenir quatre processus isobares et quatre processus isothermes, et procédé de commande pour le cycle thermodynamique de ce moteur thermique
PL421942A1 (pl) * 2017-06-19 2019-01-02 Politechnika Krakowska im. Tadeusza Kościuszki Silnik izochoryczny
US10837396B1 (en) 2019-05-14 2020-11-17 Science Applications International Corporation Torque-slewing diesel engine operation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4040400A (en) * 1975-09-02 1977-08-09 Karl Kiener Internal combustion process and engine
SU1444548A1 (ru) * 1987-02-23 1988-12-15 Б. А. Глазунов Поршневой двигатель внутреннего сгорани
SU1590590A1 (ru) * 1988-01-08 1990-09-07 Филиал Научно-Исследовательского И Конструкторско-Технологического Института Тракторных И Комбайновых Двигателей Двигатель внутреннего сгорани
RU2246625C2 (ru) * 2002-06-27 2005-02-20 Закрытое акционерное общество "Научно-производственное объединение "Аркон" Способ работы двигателя внутреннего сгорания и устройство для его осуществления

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4040400A (en) * 1975-09-02 1977-08-09 Karl Kiener Internal combustion process and engine
SU1444548A1 (ru) * 1987-02-23 1988-12-15 Б. А. Глазунов Поршневой двигатель внутреннего сгорани
SU1590590A1 (ru) * 1988-01-08 1990-09-07 Филиал Научно-Исследовательского И Конструкторско-Технологического Института Тракторных И Комбайновых Двигателей Двигатель внутреннего сгорани
RU2246625C2 (ru) * 2002-06-27 2005-02-20 Закрытое акционерное общество "Научно-производственное объединение "Аркон" Способ работы двигателя внутреннего сгорания и устройство для его осуществления

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018195619A1 (fr) * 2017-04-25 2018-11-01 Associação Paranaense De Cultura - Apc Moteur thermique à cycle différentiel faisant intervenir quatre processus isobares et quatre processus polytropiques avec régénérateur, et procédé de commande pour le cycle thermodynamique de ce moteur thermique
WO2018195618A1 (fr) * 2017-04-25 2018-11-01 Associação Paranaense De Cultura - Apc Moteur thermique à cycle différentiel faisant intervenir quatre processus isobares et quatre processus isothermes, et procédé de commande pour le cycle thermodynamique de ce moteur thermique
PL421942A1 (pl) * 2017-06-19 2019-01-02 Politechnika Krakowska im. Tadeusza Kościuszki Silnik izochoryczny
US10837396B1 (en) 2019-05-14 2020-11-17 Science Applications International Corporation Torque-slewing diesel engine operation
US11261821B2 (en) 2019-05-14 2022-03-01 Science Application International Corporation Torque-slewing diesel engine operation

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