EP1108118A1 - A system for compressing and ejecting of piston engines - Google Patents

A system for compressing and ejecting of piston engines

Info

Publication number
EP1108118A1
EP1108118A1 EP00930892A EP00930892A EP1108118A1 EP 1108118 A1 EP1108118 A1 EP 1108118A1 EP 00930892 A EP00930892 A EP 00930892A EP 00930892 A EP00930892 A EP 00930892A EP 1108118 A1 EP1108118 A1 EP 1108118A1
Authority
EP
European Patent Office
Prior art keywords
steam
piston
air
compressing
ejecting
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.)
Withdrawn
Application number
EP00930892A
Other languages
German (de)
English (en)
French (fr)
Inventor
Jordan Borislavov Kolev
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
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
Publication of EP1108118A1 publication Critical patent/EP1108118A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01KSTEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00Steam engine plants not otherwise provided for
    • F01K21/04Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas

Definitions

  • the invention relates to the system for compressing and ejecting of piston engines, with a field of application in the transport, in the power engineering and in any field of engineering where engines are used.
  • thermodynamics It is known in the thermodynamics that the perfect cycle of a steam plant is the Carnot cycle realized at set temperatures and having the highest thermal efficiency among all possible thermodynamic cycles, but the modified cycle proposed by Rankine has found application in the steam plants.
  • gas-steam cycles combining the combustion gas and the water steam in gas-turbine plants but the thermal efficiency cannot be higher than the efficiency of each of the component cycles.
  • the gas-steam cycle has a gas-turbine stage in the high-temperature range and a steam-turbine stage in the low-temperature range.
  • the thermal efficiency is higher than the efficiency of each of the separate component cycles (the gas and steam ones) but this considerably complicates the power plant.
  • a gas-steam engine is known, patent RU 2054563 Cl , having a forward- flow steam generator whose outlet is connected to the active nozzle of a mixing camera, and the directing apparatus is placed on the outlet of a Laval nozzle whose inlet is coaxial with the active nozzle located in the mixing camera where the steam mixes with the combustion gas driving the blades of the inward-flow turbine which are fixed to a heat-conducting disk, etc.
  • the gas turbine unit includes a compressor for compressing air, a combustor for burning fuel and a turbine driven by the combustion gas, for driving the compressor.
  • a steam-driven mixer boosts the air and mixes the steam and the air.
  • a heat exchanger is arranged downstream of the turbine for heating the mixed gas from the mixer with heat from the turbine exhaust gas.
  • An air line is provided for introducing a first portion of the compressed air from the compressor to the combustor and for introducing a second portion of the compressed air to the mixer.
  • the mixed gas from the mixer is introduced to the combustor via the heat exchanger.
  • the mixer can include either a steam turbine-driven compressor or an ejector.
  • vapour-air steam engine also known is a vapour-air steam engine, patent US 07/967,289 (WO 94/10427) which utilizes a working fluid consisting of a mixture of compressed uncombusted air components, fuel combustion products, and steam.
  • the working fluid is provided at constant temperature and pressure.
  • the combustion air is supplied adiabatically by one or more stages of compression. At least 40% of all of compressed air is burned.
  • the inert components are injected at high pressure to produce steam and thus provide a vapour required for internal cooling of a turbine or another type system.
  • the problem is solved by connecting in a particular way a steam generator (SG), an ejector (E), a piston engine (PE), a steam-air turbine (T), an air compressor (K), a thermo exchanger (TE), a condenser (C), a piston condensate pump (PC), a sweat-reservoir (SR) and control valves (CV), all this forming the system for compressing and ejecting of piston engines.
  • SG steam generator
  • E ejector
  • PE piston engine
  • T steam-air turbine
  • K air compressor
  • K thermo exchanger
  • C condenser
  • PC piston condensate pump
  • SR sweat-reservoir
  • CV control valves
  • the steam with high pressure comes from the steam generator with a pressure p] (p. l ) and flows out of the ejector nozzle with high velocity expanding in the diffuser to a pressure p2, entraining the compressed air with pressure p to pressure p2 in the cylinders of the piston engine. From (p.2) to (p.3) the air-steam mixture expand isobarically in the engine, performing work to overcome the external resistances.
  • the outflow opening opens and the air-steam mixture with pressure p3 (p.3) expands adiabatically in the working wheel of the turbine-driven compressor to the atmospheric pressure p_ (p.4).
  • the air-steam mixture passes through the condenser cooled by the air sucked from the compressor.
  • the exhaust steam cools in the condenser to its condensing, and the air leaves the condenser with a temperature of 70-80°C.
  • the compressed heated air from (p.5) to (p.6) mixes in the mixing camera of the ejector with the coming steam and increases its pressure to p2 (p.2) at the cylinders of the piston engine.
  • the described path of work of the piston engine with a system for compressing and ejecting shows that a very compact use of the steam enthalpy through a cascade way, namely the path 1-2-3-4 consisting of two adiabats and one isobar.
  • the use of a mixed air-steam cycle allows a sharp decrease in the use of steam in the engine in its full volume, thus increasing considerably the thermal efficiency of the engine, decreasing to a minimum the size of the steam generator and the condenser increasing its mobility.
  • An advantage of the system with compressing and ejecting is that instead of exhaust gas it uses the atmospheric air which cools the condenser and returns back to the engine the heat released at the steam condensation and at the air cooling by the air-steam mixture. This contributes to the sharp increase of the reversibility of the cycle and from there to an increase of the thermal efficiency, taking into account that the steam is used only to compensate the loss of energy in the cycle reversibility (mass flow about 20-30%) but not in the full working volume of the engine as in the steam engine and the steam turbine. It permits to reach a thermal efficiency of 80-85% which would diminish the fuel consumption from 2 to 3 times compared to the actual operational values.
  • the power of the engines with compressing and ejecting is comparable to that of the corresponding with respect to the displacement gasoline or Diesel engine owing to the fact that the operational pressure is equivalent to the effective pressure p e of the internal combustion engines, and the working process is a two-stroke one.
  • the engine cooling and the need of a mechanical transmission for transmit the moment of rotation to the wheels are avoided.
  • Other important advantages are the high wear resistance of the engines with a system for compressing and ejecting as well as the noiseless operation.
  • Fig. 1 shows the thermodynamic process of compressing and ejecting in a p- v diagram.
  • Fig. 2 is a schematic representation of the system for compressing and ejecting.
  • Fig. 3 is a detailed representation of the system for compressing and ejecting. Description of the Preferred Embodiments
  • the system for compressing and ejecting consists of: a condenser 22 on the core of which the air draught hoods 31 are mounted, the rear ones are firmly fixed and the front ones are mounted by means of flat-wire bimetal springs 29, a lever 30 and a spring 28 (see view C).
  • a thermoexchange serpentine 23 is fixed and the lower part is shaped as a condensate reservoir 25 into which a float 26 and a needle float 27 is mounted, and is connected via a tube to the sweat-reservoir 3 in which a condensing serpentine 2 is mounted on which outlet a control valve 7 is mounted.
  • the steam generator 14 is connected to the high-pressure part of the ejector 12 whose outlet is connected to the inlet port of the piston engine 24 whose exhaust port is connected to the air-steam turbine 5.
  • the air compressor 4 and the air-steam turbine 5 are mounted forming a turbine-driven compressor and are connected via openings to the condenser 22, the opening of the compressor being closed by a valve 1 connected by means of the air draught hoods 31.
  • the compressor 4 is connected via the thermo exchanger 6 with the low- pressure diffuser 10 of the ejector 12 and this low-pressure diffuser is pressed by the precision spring 8 and is enveloped by the casing ring 9, and in it the low- pressure profile rollers 17 are located having on their cylindrical surface semicylindrical channels with variable section and rugged pins 18 mounted into them. Smaller-size high-pressure profile rollers 16 are mounted into the high- pressure diffuser 11 in which the pushing pins 15 are placed and the diffuser 1 1 is pressed by a spring 13.
  • the cam disk 35 On the crankshaft axle of the piston engine 24, the cam disk 35 is fitted which contacts with the piston condensate pump 32 fixed on a carrier 21 mounted on the axle 20.
  • the piston condensate pump 32 is connected to the drive mechanism 33 coupled to a screw with right-hand thread 40 placed into a nut with right-hand thread 39 and connected with a screw with left-hand thread 44 placed into a nut with left-hand thread 42 by means of a clutch sleeve 41.
  • the nuts 39 and 42 are mounted together into a cutout in the body of regulator 43 and into two oblique cutouts in the triangular plates 45 connected to the pressure regulator 34 via a tube for the steam generator 14 and the four-bar mechanism 19 which is mounted together with the pusher of four-bar mechanism 36, the weight 37 and the V-shaped feet 38.
  • the inlet of the piston condensate pump 32 is connected to the condensate reservoir 25, and the outlet is connected in series with the thermoexchange serpentine 23, the thermo exchanger 6 and the steam generator 14.
  • thermodynamic cycle (fig. 1) consists of the following processes: 1-2 - adiabatic expansion of the steam in the ejector; 2-3 - isobaric expansion of the air- steam mixture in the piston engine; 3-4 - adiabatic expansion of the air-steam mixture in the turbine; 4-5 - isobaric condensation of the steam; 5-6 - adiabatic compression of the air in the compressor.
  • the work of the piston engine is equal to the sum of the works of the compressor and ejector
  • V s the second volume of the engine which is equal to the sum the partial volumes of the steam and the air in the air-steam mixture
  • V s V s s+v s a , or
  • the power of the engine could be determined by the formula:
  • Equation 1 In order to determine the two unknowns - the steam mass flow in the engine m s and the air mass flow m a , one has to work out a second equation, namely for the relation of the adiabatic work in the turbine-driven compressor, from where the relation between m s and m a is found and substituted in Equation
  • the thermal efficiency ( ⁇ ) is used to evaluate the thermal cycle
  • Q 0 - the heat abstracted from the engine equal to Q s - (L e +Lk) , i.e. equal to the difference between the introduced heat and the work performed in the ejector plus the compressor work.
  • a new reversibility factor of the cycle could be introduced, i.e. the ration of the heat returned back from the compressor and the condenser into the engine to the heat introduced with the steam:
  • ⁇ t is at least two times greater than that of the internal combustion engines, the maximum pressure is 5 to 10 times smaller, the maximum temperature is also up to 10-15 times smaller, and the rotational speed is 4-16 times smaller than that of the gasoline and Diesel engines.
  • the system for compressing and ejecting operates as follows: Through the medium of the drive mechanism 33 put into motion by the accelerator pedal of the piston engine 24, the screw with right-hand thread 40 starts turning and by means of the clutch sleeve 41 and the screw with left-hand thread 44 which, by turning the nuts 39 and 42, brings nearer the carriers 21 on which the piston condensate pumps 32 are fixed, and by means of the cam disk 35, a sucking of condensate from the condensate reservoir 25 is performed and it is supplied under pressure via the thermoexchange serpentine 23 an the thermo exchanger 6 into the steam generator 14.
  • the steam obtained in the steam generator flows into the high-pressure area of the ejector 12 where operates the pushing pins 15 and pushes them under the action of the pressure to the low-pressure diffuser 10 creating a clearance ⁇ (see B-B) through which passes the low-pressure air flow from the air compressor 4.
  • the motion of the pushing pins 15 is strictly determined depending on the precision spring 8.
  • the high- pressure profile rollers 16 start turning through the medium of the rugged part, and these rollers ensure, by changing the section of the opening formed at their turning, a high-speed steam flow from the diffuser 1 1 into the diffuser 10.
  • the exhaust port is open; this port is connected via a tube to the air-steam turbine 5 which drives the compressor 4.
  • the waste air-steam mixture passes through the condenser 22 where the steam condenses is collected in the condensate reservoir 25 in which by means of the float 26 and the needle float 27, a constant level is maintained.
  • the humid air from the condenser passes through the condensing serpentine 2 into the sweat-reservoir 3 where a further condensation of the air moisture takes place. The air thus dried leaves the system or flows via the control valve 7 into steam generator 14 to be burned.
  • the air in the system for compressing and ejecting is sucked in to the air compressor 4 through the air draught hoods 31 which are automatically driven by a flat-wire bimetal spring 29 heated by the air-steam mixture in the condenser 22, a lever 30 and a spring 28.
  • the movable air draught hoods 31 are in the lower position (see view C).
  • the cooling air enters through one only cooling sector into the condenser 22.
  • the flat-wire bimetal spring 29 bends and shifts upwards the lever 30 and the spring 28 fixes tightly the hood to the condenser wall.
  • the cooling air enters through three cooling sectors into the condenser 22.
  • the valve 1 serves to switch the compressor 4 to suction not only of atmospheric air but also of air- steam mixture from the condenser at a determined operation mode of the engine as in the case of an fully capsulated system for compressing and ejecting using the engine in vacuum.
  • the four-bar mechanism 19 and the pressure regulator 34 serve to limit the rotational speed and the pressure in the engine. They operate either separately or together, depending on the operational mode of the engine. For example, at low rotational speed and high load, only the pressure regulator operates, and at high rotational speed and load, both of them operate together. Both of them are connected with the triangular plates 45 which have two oblique cutouts where the guides of the nuts 39 and 42 enter. When the pressure into the steam generator 14 exceeds the specified value, it acts through a tube of the pressure regulator 34 and pushes the plate 45 upwards, thus drawing apart the nuts 39 and 42 which move in a cutout into the body of regulator 43 and the nuts, on their part, push the screws 40 and 44 that are fixed to the carriers 21.
  • the stroke of the piston condensate pumps 32 diminishes, as well as the water amounts injected into the steam generator 14.
  • the centrifugal force created by the weights 37 acts on the V-shaped feet 38 and, on their part, shift the pusher of four-bar mechanism 36 and by so doing the four-bar mechanism 19 draws the triangular plate 45 upwards thus drawing apart the nuts 39 and 42 as well as the piston pumps 32 from the cam disk 35, thus reducing the amount of the injected condensate.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Jet Pumps And Other Pumps (AREA)
EP00930892A 1999-06-18 2000-05-25 A system for compressing and ejecting of piston engines Withdrawn EP1108118A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BG10350499 1999-06-18
BG103504A BG63668B1 (bg) 1999-06-18 1999-06-18 Система за компресиране и ежектиране на бутални двигатели
PCT/BG2000/000015 WO2000079104A1 (en) 1999-06-18 2000-05-25 A system for compressing and ejecting of piston engines

Publications (1)

Publication Number Publication Date
EP1108118A1 true EP1108118A1 (en) 2001-06-20

Family

ID=3927801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00930892A Withdrawn EP1108118A1 (en) 1999-06-18 2000-05-25 A system for compressing and ejecting of piston engines

Country Status (13)

Country Link
EP (1) EP1108118A1 (zh)
JP (1) JP2003502567A (zh)
CN (1) CN1313928A (zh)
AU (1) AU4902100A (zh)
BG (1) BG63668B1 (zh)
BR (1) BR0006871A (zh)
CA (1) CA2340638A1 (zh)
CZ (1) CZ2001995A3 (zh)
IL (1) IL141237A0 (zh)
MX (1) MXPA01001835A (zh)
PL (1) PL346056A1 (zh)
WO (1) WO2000079104A1 (zh)
ZA (1) ZA200102199B (zh)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10054022A1 (de) 2000-11-01 2002-05-08 Bayerische Motoren Werke Ag Verfahren zum Betreiben einer Wärmekraftmaschine
US20070102672A1 (en) * 2004-12-06 2007-05-10 Hamilton Judd D Ceramic radiation shielding material and method of preparation
FR2922608B1 (fr) * 2007-10-19 2009-12-11 Saipem Sa Installation et procede de stockage et restitution d'energie electrique a l'aide d'une unite de compression et detente de gaz a pistons
CN101684737A (zh) * 2008-09-27 2010-03-31 冯显刚 热能循环利用组合动力机械
EP2253807A1 (en) * 2008-10-29 2010-11-24 Vítkovice Power Engineering a.s. Gas turbine cycle or combined steam-gas cycle for production of power from solid fuels and waste heat
CN103492818B (zh) * 2010-12-10 2016-08-10 蒸汽发生器公司 通用热力发动机
CN103953470B (zh) * 2014-03-21 2016-06-29 哈尔滨工程大学 一种增压柴油机进气道增湿装置
FI127654B (en) * 2014-05-21 2018-11-30 Finno Energy Oy Electricity generating system and method
UA141780U (uk) * 2019-10-21 2020-04-27 Іван Іванович Котурбач Дизель-парова електростанція

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB272777A (en) * 1926-12-08 1927-06-23 Frank Robinson Improvements in and connected with the supply of fluid to fluid expansion engines
US3861151A (en) * 1974-04-12 1975-01-21 Toshio Hosokawa Engine operating system
FR2389767A1 (en) * 1977-05-06 1978-12-01 Alsthom Atlantique Gas turbine powered by waste heat - has heated water injected into compressed air to reduce operating temp
GB2080431B (en) * 1980-07-16 1984-03-07 Thermal Systems Ltd Reciprocating external combustion engine
US4492085A (en) * 1982-08-09 1985-01-08 General Electric Company Gas turbine power plant
RU2054563C1 (ru) 1991-07-08 1996-02-20 Александр Андреевич Фомин Парогазовый двигатель
US5617719A (en) 1992-10-27 1997-04-08 Ginter; J. Lyell Vapor-air steam engine
JPH0826780B2 (ja) 1993-02-26 1996-03-21 石川島播磨重工業株式会社 部分再生式二流体ガスタービン
GB2307277A (en) * 1995-11-17 1997-05-21 Branko Stankovic Combined cycle powerplant with gas turbine cooling

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0079104A1 *

Also Published As

Publication number Publication date
BG63668B1 (bg) 2002-08-30
IL141237A0 (en) 2002-03-10
WO2000079104A1 (en) 2000-12-28
BG103504A (en) 2000-12-29
CZ2001995A3 (cs) 2001-09-12
BR0006871A (pt) 2001-08-07
MXPA01001835A (es) 2002-04-08
ZA200102199B (en) 2001-12-19
AU4902100A (en) 2001-01-09
CA2340638A1 (en) 2000-12-28
PL346056A1 (en) 2002-01-14
CN1313928A (zh) 2001-09-19
JP2003502567A (ja) 2003-01-21

Similar Documents

Publication Publication Date Title
CN101027468B (zh) 组合式兰金与蒸汽压缩循环
US6672063B1 (en) Reciprocating hot air bottom cycle engine
KR101126962B1 (ko) 원심 압축기에 의한 동력 생성
US7028476B2 (en) Afterburning, recuperated, positive displacement engine
US20080041056A1 (en) External heat engine of the rotary vane type and compressor/expander
JPH11270352A (ja) 吸気冷却型ガスタービン発電設備及び同発電設備を用いた複合発電プラント
EA014465B1 (ru) Система теплового двигателя
CA2376594A1 (en) High efficiency, air bottoming engine
CA2404259A1 (en) An engine
CN112368464B (zh) 用于回收废热的系统及其方法
WO1987001414A1 (en) Shaft power generator
EP1108118A1 (en) A system for compressing and ejecting of piston engines
US20020073712A1 (en) Subatmospheric gas-turbine engine
CA3158402A1 (en) Plant based upon combined joule-brayton and rankine cycles working with directly coupled reciprocating machines
JPH08193504A (ja) 動力プラントの複合サイクル
EA038808B1 (ru) Тепловая машина, предназначенная для выполнения тепловых циклов, и способ выполнения тепловых циклов посредством такой тепловой машины
RU2631849C1 (ru) Силовая установка и парогазогенератор для этой силовой установки (два варианта)
EA003122B1 (ru) Двигатель или насос с рычажным механизмом
RU2170357C1 (ru) Способ повышения экономичности тепловых и холодильных комбинированных установок
SU909238A1 (ru) Энергоустановка с глубоким охлаждением отработанных газов
CN100455781C (zh) 湿压缩-后表冷-回热循环燃气轮机
RU2056584C1 (ru) Паровой котел с агрегатом наддува и способ получения пара в котле с агрегатом наддува
RU2044900C1 (ru) Двигатель внутреннего сгорания
KR20220062023A (ko) 고 열 회수가 구비된 조합된 열역학적 사이클
RU52931U1 (ru) Замкнутая паротурбинная установка на низкокипящих веществах

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: RO

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20010320