EP0218505A1 - Kraftanlage mit mehreren durch Verdichter mit hin- und hergehendem Kolben aufgeladenen Dieselbrennkraftzylindern - Google Patents

Kraftanlage mit mehreren durch Verdichter mit hin- und hergehendem Kolben aufgeladenen Dieselbrennkraftzylindern Download PDF

Info

Publication number: EP0218505A1
Authority: EP; European Patent Office
Prior art keywords: lights; engine; cylinder; installation according; compressor
Prior art date: 1985-09-11
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.): Granted

Application number

EP86401989A

Other languages

English (en)

French (fr)

Other versions

EP0218505B1 (de

Inventor

Henry Benaroya

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.)

1985-09-11

Filing date

1986-09-11

Publication date

1987-04-15

1986-09-11 Application filed by Individual filed Critical Individual

1986-09-11 Priority to AT86401989T priority Critical patent/ATE48023T1/de

1987-04-15 Publication of EP0218505A1 publication Critical patent/EP0218505A1/de

1989-11-15 Application granted granted Critical

1989-11-15 Publication of EP0218505B1 publication Critical patent/EP0218505B1/de

Status Expired legal-status Critical Current

Images

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
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- 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
- F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
- 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
- F02B71/00—Free-piston engines; Engines without rotary main shaft
- F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
- F02B71/06—Free-piston combustion gas generators per se
- 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
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

the invention relates to energy production installations comprising at least one diesel engine with several cylinders operating sequentially, supercharged by several reciprocating compressor cylinders supplying the purge air to the engine.
Diesel engines are generally supercharged by a rotary compressor or an alternating compressor whose cylinders operate in an offset manner.
all the cylinders emerge in the same manifold. Consequently, the scanning of the engine cylinders is carried out at a substantially constant intake pressure.
a thermodynamic study of the phenomena which occur during the sweeping shows that the compression work with transfer depends directly on the difference between the average inlet pressure of the sweeping air and the exhaust pressure. Consequently, the work during transfer is determined by the average pressure in the manifold, and not by the discharge pressure of a particular compressor cylinder. It should however be noted that this is only true in the case of an engine and a compressor having several cylinders. In the case of an installation having a single engine cylinder supplied by a single compressor cylinder (such as that described in the document FR-A-1 238 426), the situation is completely different since there is no manifold for mixture feeding several cylinders.
the invention aims in particular to provide an installation in which this work is significantly reduced. To this end, it offers an installation characterized in that each engine cylinder is supplied with purging air from that of the cylinders. compressors whose delivery stroke occurs while the engine scanning lights are closed, via an intake capacity whose volume is equal to several times, typically about five times, the displacement.
the scanning is carried out at a gradually decreasing intake pressure, which reduces the work performed.
the gain thus obtained can be further increased by providing the exhaust pipes of the engine cylinder with a constant section close to the lights, then a slowly increasing section, which makes it possible to cause a rapid drop in the pressure in the engine cylinder, first up to a value of the order of 1.5 Pe (Pe being the pressure prevailing in an exhaust capacity), then up to a value lower than the pressure prevailing in the exhaust capacity, from made of creating a depression wave.
the vacuum in the cylinder may remain until the piston returns until the intake ports are closed.
the invention finds a particularly important application in installations comprising a gas generator with free pistons of the multi-tandem type, associated with a gas turbine.
the generator comprises engine cylinders operating according to a Diesel cycle, belonging to two groups operating in phase opposition, and compressor cylinders also divided into two groups.
This solution has many advantages over those adopted previously when a large fraction of the air flow supplied by the compressors is used for sweeping the motors. However, this interest diminishes as a larger fraction of the flow is used to directly feed the gas turbine.
each engine cylinder delimited by two engine pistons, from a single compressor compartment, chosen so that the delivery stroke coincides with the moment when the lights of the corresponding engine are closed.
the provisions defined above make it possible to significantly reduce the work of the exhaust gases. They can be implemented on a driving cylinder comprising conventional type scanning lights. It is known that, depending on whether the scanning lights are designed so as to provide a radial air jet or an air jet having a tangential component, the flow during the first phase of the scanning takes place according to a different regime . In the first case, the flow of fresh sweeping air is in the form of a central jet, surrounded by an annular wake of hot combustion gases. This solution has the advantage of ensuring efficient scanning. But there is no rotational movement of the fresh gases in the engine.
the invention also aims to provide an installation whose scanning means make it possible to obtain the favorable effects of the rotary movement while ensuring an interesting sweeping of the entire engine cylinder.
the invention in particular proposes an installation in which each engine cylinder comprises scanning lights distributed regularly around the cylinder at one end of the latter and exhaust means, such as lights, also regularly distributed at the other end of the cylinder delimited by two pistons moving in opposite directions, said scanning lights being distributed in two successively uncovered rows, the lights of the row discovered first being arranged so as to provide a jet having a tangential component while the lights second discoveries are provided to provide a jet directed substantially towards the axis.
the two rows are supplied by the same intake capacity, but means are advantageously provided for delaying the arrival of purge air at the lights of the first row. This result can in particular be achieved by providing a winding path or a secondary capacity between a main intake capacity (which directly feeds the lights of the second set) and the lights of the first set.
the first row of lights providing a jet oriented for example at 30 * with respect to the radial direction, establishes a flow of peripheral annular type animated with a high speed of rotation.
the second row causes the appearance of a central jet without rotation ensuring efficient scanning.
each compressor cylinder In a multi-tandem gas generator installation, each compressor cylinder, or at least each compression chamber, has so far been assigned to a determined flow.
certain compressor cylinders provide a primary air flow intended for the engine, while others supply the secondary air flow intended for the turbine.
the sweep ratio (that is to say the ratio between the quantity of air passing through the motors and the displacement of these motors) is fixed or, at least, can only be modified by important steps.
the invention also aims to provide means for more precise adaptation of the scanning ratio to the needs of scanning of the kind defined above.
the invention also proposes to assign some of the compressors of the installation to a single flow and other cylinders to two flows, by providing discharge valves opening into two separate manifolds assigned, one to the flow. primary, the other to secondary flow.
FIGS. 1 to 3 there will be described an operating cycle of an assembly comprising only an engine cylinder 10 and a compressor cylinder 12 of a gas generator with free pistons which may have the general constitution described.
the compressor cylinder 12 contains a piston 14 separating a compression compartment 16 assigned to the primary flow and a compartment 18 assigned to the secondary flow and directly supplying a gas turbine not shown.
the compartment 16 is provided with valves 20 for intake of fresh air and with valves 22 for discharge to an intake capacity 24.
the piston 14 is mechanically coupled to a driving piston 26 delimiting, with a symmetrical piston 28, an engine compartment 30 which, in the position of maximum separation of the pistons 26 and 28, has a volume equal to approximately one fifth of the volume of the capacity 24.
the piston 26 cooperates with scanning lights 32 while the piston 28 cooperates with exhaust lights 34 opening into a pipe 36 supplying an exhaust capacity 38 connected to a high pressure turbine (not shown).
Figure 1 shows in solid lines the position of the movable assembly comprising the pistons 14, 26 and 28 at the time of opening of the exhaust lights 34, that is to say when the puff occurs exhaust. Due to the difference in location of lights 32 and 34, the scanning lights are still closed.
the engine pistons move away from each other.
the compression chamber 16 is in suction, the piston 14 moving away from the plate which carries the valves 20 and 22.
Pc In the intake capacity there prevails a pressure Pc, while the pressure in the compressor compartment 16 is substantially equal to the inlet pressure Pa.
the pressure prevailing in the engine cylinder 30 is substantially equal to 3Pi.
the engine pistons then uncover the scanning lights 32, as indicated in dashes in FIG. 1.
the intake capacity 24 is then in connection with the engine cylinder 30. As soon as the exhaust puff has released the pressure which prevails in the engine below Pc, the intake capacity 24 begins to discharge into the engine to sweep it (dashed arrow in Figure 1).
the compression phase in the engine and the discharge from the compressor 12 to the intake capacity 24 then begins.
the pistons 26 and 28 in dashes in Figure 2
the pistons 26 and 28 successively close the scanning lights 32 then the exhaust lights 34, isolating the engine from the intake capacity .
the compressor 12 during this time charges the intake capacity whose pressure rises.
FIG 5 on which the elements corresponding to those of Figure 1 are designated by the same reference number, shows an intake capacity 24 formed in the cylinder housing 30 and communicating directly with a row of intake lights 32 2 which open radially into the cylinder ( Figure 6).
Another row of lights 32 1 placed so as to be discovered first by the piston 26 during the rebound stroke, are on the contrary oriented obliquely, with an angle relative to the radial plane which will generally be around 30 * ( Figure 7).
the arrangement shown in FIG. 5 acts on two factors. On the one hand, it tends to decrease the total pressure of the peripheral fluid threads, supplied by the lights 32 1 , by reducing their speed. On the other hand, it delays the appearance of the effective flow through these lights 32 1 .
These two results are achieved by having, between the intake capacity 24 and the lights 32 1 , a pipe 40 in baffles, of small volume but of length much greater than the axial interval between the rows 32 1 and 32 2 . This line phase out the flow and causes a pressure drop which reduces the total supply pressure.
the presence of the two rows of lights and of the pipe 40 brings other favorable results.
the total length of the scanning and intake lights 32 1 -32 2 can be increased by about 30% for the same useful displacement.
the phase shift of the flow through the lights 32 1 flattens the tip of the peripheral fresh air front.
the pressure drops in the pipe 40 are used.
a pressure drop of the same order as that caused by the lights 32 1 will be used , which reduces the speed at which the lights pass through.
a ratio which corresponds approximately to that of the distances traveled by the peripheral air streams and close to the axis.
Figure 8 shows the results of a simulation carried out to determine the fronts of invasion of the cylinder 30 by the fresh air when the lights are of the kind shown in Figure 5.
the curves identified by the references 1, 2, 3, 4 and 5 show the edges respectively 2 ms, 6 ms, 10 ms, 16 ms and 20 ms after the start of opening of the second row of lights.
valves with delayed controlled opening or calibrated valves with automatic opening interposed between the intake capacity and the lights 32 of the first set are possible, in particular the use of valves with delayed controlled opening or calibrated valves with automatic opening interposed between the intake capacity and the lights 32 of the first set.
FIG. 9 shows only two compressors among the eight that include such a generator.
the compressor 42 is intended to supply only air to the secondary circuit, via a heat exchanger 44 intended to heat it.
the air having passed through the exchanger 44 is sent to a high pressure gas turbine 46.
At least one other compressor cylinder 12, or at least the other compartment delimited by the compressor piston 14 in the cylinder 12, is mixed in the sense that it supplies air to the primary circuit, which includes a cooler 48 and opens out. in an engine cylinder 30, and in the secondary circuit.
the delivery manifold 50 of the cylinder 12 is separated by a partition 52 into two chambers. In each chamber, several discharge valves 22 of the compressor open. Since the number of these valves is high, often between ten and twenty, there is thus an extremely flexible adjustment mode.

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Engineering & Computer Science (AREA)
Chemical & Material Sciences (AREA)
Combustion & Propulsion (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Supercharger (AREA)
Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Engine Equipment That Uses Special Cycles (AREA)

EP86401989A 1985-09-11 1986-09-11 Kraftanlage mit mehreren durch Verdichter mit hin- und hergehendem Kolben aufgeladenen Dieselbrennkraftzylindern Expired EP0218505B1 (de)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
AT86401989T ATE48023T1 (de)	1985-09-11	1986-09-11	Kraftanlage mit mehreren durch verdichter mit hin- und hergehendem kolben aufgeladenen dieselbrennkraftzylindern.

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
FR8513480A FR2587062B1 (fr)	1985-09-11	1985-09-11	Installation de production d'energie a plusieurs cylindres moteurs a cycle diesel suralimentes par compresseurs alternatifs
FR8513480		1985-09-11

Publications (2)

Publication Number	Publication Date
EP0218505A1 true EP0218505A1 (de)	1987-04-15
EP0218505B1 EP0218505B1 (de)	1989-11-15

Family

ID=9322811

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP86401989A Expired EP0218505B1 (de)	1985-09-11	1986-09-11	Kraftanlage mit mehreren durch Verdichter mit hin- und hergehendem Kolben aufgeladenen Dieselbrennkraftzylindern

Country Status (7)

Country	Link
US (1)	US4748811A (de)
EP (1)	EP0218505B1 (de)
JP (1)	JPS6296732A (de)
AT (1)	ATE48023T1 (de)
DE (1)	DE3666965D1 (de)
DK (1)	DK162946C (de)
FR (1)	FR2587062B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0336955A1 (de) *	1987-10-13	1989-10-18	HAMMETT, Robert B.	Wärmekraftmaschine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
GB2490106A (en) *	2011-04-13	2012-10-24	Ge Prec Engineering Ltd	Forced induction for internal combustion engines

Citations (8)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE753727C (de) *	1940-06-05	1943-05-06
FR957050A (de) *		1950-02-13
FR1238426A (fr) *	1959-07-02	1960-08-12		Perfectionnements apportés aux moyens assurant la stabilité des machines à pistons libres effectuant la compression utile pendant la course de retour
FR1279023A (fr) *	1961-02-03	1961-12-15	Fiat Spa	Perfectionnements aux générateurs de gaz à pistons libres
US3090317A (en) *	1960-06-10	1963-05-21	John E Luderer	Free piston engines
GB1116162A (en) *	1965-05-04	1968-06-06	Benaroya Henry	Improvements in or relating to free piston engines
FR1537511A (fr) *	1966-10-11	1968-08-23	Sulzer Ag	Moteur à combustion interne à piston suralimenté, à cycle à deux temps, avec groupe turbo-compresseur tournant librement
EP0007874A1 (de) *	1978-07-26	1980-02-06	Henry Benaroya	Anlage zur Energieerzeugung mit einem Freikolbengenerator

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
GB765948A (en) *	1954-12-17	1957-01-16	Sulzer Ag	Multi-cylinder two-stroke internal combustion engines having exhaust gas turbo chargers
CA1216159A (en) *	1982-09-27	1987-01-06	Henry Benaroya	Gas turbine power production unit including a free piston gas generator

1985
- 1985-09-11 FR FR8513480A patent/FR2587062B1/fr not_active Expired
1986
- 1986-09-10 DK DK433286A patent/DK162946C/da not_active IP Right Cessation
- 1986-09-11 US US06/906,290 patent/US4748811A/en not_active Expired - Fee Related
- 1986-09-11 EP EP86401989A patent/EP0218505B1/de not_active Expired
- 1986-09-11 DE DE8686401989T patent/DE3666965D1/de not_active Expired
- 1986-09-11 JP JP61212858A patent/JPS6296732A/ja active Pending
- 1986-09-11 AT AT86401989T patent/ATE48023T1/de not_active IP Right Cessation

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
FR957050A (de) *		1950-02-13
DE753727C (de) *	1940-06-05	1943-05-06
FR1238426A (fr) *	1959-07-02	1960-08-12		Perfectionnements apportés aux moyens assurant la stabilité des machines à pistons libres effectuant la compression utile pendant la course de retour
US3090317A (en) *	1960-06-10	1963-05-21	John E Luderer	Free piston engines
FR1279023A (fr) *	1961-02-03	1961-12-15	Fiat Spa	Perfectionnements aux générateurs de gaz à pistons libres
GB1116162A (en) *	1965-05-04	1968-06-06	Benaroya Henry	Improvements in or relating to free piston engines
FR1537511A (fr) *	1966-10-11	1968-08-23	Sulzer Ag	Moteur à combustion interne à piston suralimenté, à cycle à deux temps, avec groupe turbo-compresseur tournant librement
EP0007874A1 (de) *	1978-07-26	1980-02-06	Henry Benaroya	Anlage zur Energieerzeugung mit einem Freikolbengenerator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0336955A1 (de) *	1987-10-13	1989-10-18	HAMMETT, Robert B.	Wärmekraftmaschine
EP0336955A4 (de) *	1987-10-13	1989-12-18	Robert B Hammett	Wärmekraftmaschine.

Also Published As

Publication number	Publication date
DK162946B (da)	1991-12-30
FR2587062B1 (fr)	1989-11-17
FR2587062A1 (fr)	1987-03-13
DE3666965D1 (en)	1989-12-21
DK433286D0 (da)	1986-09-10
EP0218505B1 (de)	1989-11-15
DK433286A (da)	1987-03-12
DK162946C (da)	1992-05-25
ATE48023T1 (de)	1989-12-15
US4748811A (en)	1988-06-07
JPS6296732A (ja)	1987-05-06

Publication	Publication Date	Title
EP0730706B1 (de)	1997-08-27	Verfahren zur besseren funktion einer aufgeladenen brennkraftmaschine mit luftströmung und motorbau zur realisierung dieses verfahrens
EP2129891B1 (de)	2011-07-20	Aufgeladener verbrennungsmotor
EP0384492B1 (de)	1992-07-01	Steuerungsverfahren für Zweitaktbrennkraftmaschinen
FR2544384A1 (fr)	1984-10-19	Turbomoteur compound perfectionne
EP0075502A1 (de)	1983-03-30	Verfahren zur Anpassung einer Brennkraftmaschine an ihre Betriebsbedingungen und eine so angepasste Maschine
FR2587061A1 (fr)	1987-03-13	Systeme d'admission pour moteur
CH622063A5 (de)	1981-03-13
EP2414652B1 (de)	2013-07-17	Aufgeladener verbrennungsmotor
WO1979000757A1 (fr)	1979-10-04	Perfectionnements a des moteurs deux temps ameliorant la combustion et permettant une reduction de la pollution
FR2772077A1 (fr)	1999-06-04	Moteur a combustion interne
EP0218505B1 (de)	1989-11-15	Kraftanlage mit mehreren durch Verdichter mit hin- und hergehendem Kolben aufgeladenen Dieselbrennkraftzylindern
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FR2547625A1 (fr)	1984-12-21	Dispositif de moteur a six temps et a trois soupapes par cylindre
WO2001051786A1 (fr)	2001-07-19	Procede et dispositif pour ameliorer le fonctionnement a bas regime des moteurs thermiques suralimentes
FR2768177A1 (fr)	1999-03-12	Moteur thermique mono-soupape a quatre temps et injection du carburant dans la chambre de combustion
EP0042335B1 (de)	1984-10-24	Aufgeladene Verbrennungsmaschine, insbesondere Dieselmotor, und Verfahren zum Anlassen dieser Maschine und zu deren Drehzahlregelung
EP1489280A1 (de)	2004-12-22	Aufgeladene Viertakt-Brennkraftmaschine und Verfahren zum Betreiben
EP0754268B1 (de)	1999-05-06	Zweitakt dieselbrennkraftmaschine mit einem spiralförmigen luftanzugskanal
EP1398482A1 (de)	2004-03-17	Aufgeladene Brennkraftmaschine mit einem optimierten Drehmoment bei niedriger Drehzahl
FR2479330A1 (fr)	1981-10-02	Moteur a combustion interne suralimente par turbo-compresseur
EP2674601A1 (de)	2013-12-18	Verfahren zur Spülung der Restabgase durch doppelten Ventilhub für einen Zweitaktmotor, insbesondere vom Dieseltyp
FR2509792A1 (fr)	1983-01-21	Moteur deux temps a balayage a symetrie plane
WO2011034410A1 (fr)	2011-03-24	Moteur à combustion interne de quatre temps avec récupération partielle de l'énergie des gaz issus de la combustion par leur transfert vers la phase de compression suivante
WO1994001663A1 (fr)	1994-01-20	Procede et dispositif d'alimentation d'un cylindre de moteur a combustion interne a deux temps
WO2022144606A1 (fr)	2022-07-07	Cylindre de distribution

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