DK173533B1 - Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element - Google Patents
Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element Download PDFInfo
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- DK173533B1 DK173533B1 DK199900056A DKPA199900056A DK173533B1 DK 173533 B1 DK173533 B1 DK 173533B1 DK 199900056 A DK199900056 A DK 199900056A DK PA199900056 A DKPA199900056 A DK PA199900056A DK 173533 B1 DK173533 B1 DK 173533B1
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- cylinder
- lubrication
- pressure
- control unit
- lubricating oil
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
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- 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
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Feedback Control In General (AREA)
Description
DK 173533 B1 iDK 173533 B1 i
Opfindelsen angår en fremgangmåde til smøring af en cylinder i en forbrændingsmotor, hvor mindst en smøreenhed til levering af smøreolie til mindst et smørested på cylinderen styres elektronisk ved hjælp af 5 en tilhørende styreenhed.The invention relates to a method of lubricating a cylinder in an internal combustion engine, wherein at least one lubricant for supplying lubricating oil to at least one lubrication point on the cylinder is electronically controlled by means of an associated control unit.
En sådan fremgangsmåde kendes fra ansøgerens danske patentansøgning 1119/96, hvor smøreenheden har et aktuatorstempel, der driver flere doseringsstempler i en fælles bevægelse for smøring af flere smøresteder 10 på cylinderen, hver gang smøreenheden aktiveres af den elektroniske styreenhed. Den hydraulisk drevne smøreenhed er hurtigtvirkende og leverer smøreolien til smørestederne ved et fordelagtigt højt smøreolietryk.Such a method is known from the applicant's Danish patent application 1119/96, in which the lubricant unit has an actuator piston which drives several dosing pistons in a common movement for lubrication of several lubrication points 10 on the cylinder each time the lubrication unit is activated by the electronic control unit. The hydraulically driven lubricating unit is fast acting and delivers the lubricating oil to the lubrication points at an advantageously high lubricating oil pressure.
Det har i en lang årrække været et ønske at 15 aflevere smøreolien i cylinderen, netop når stemplet passerer forbi smørestedet, se fx dansk patent 81275 fra 1954, svejtsisk patent 406 735 fra 1966, tysk patentskrift 28 27 626 fra 1979 og europæisk patent 0 678 152 fra 1997.For many years, it has been a desire to deliver the lubricating oil in the cylinder, just as the piston passes past the lubrication site, see for example Danish patent 81275 from 1954, Swiss patent 406 735 from 1966, German patent 28 27 626 from 1979 and European patent 0 678 152 from 1997.
20 I praksis har det vist sig overordentligt van skeligt at realisere dette ønske, fordi mange forhold påvirker smøreoliens faktiske afleveringstidspunkt. Der kan gives enkelte eksempler. Tidsforsinkelsen mellem smøreenhedens aktivering og oliens aflevering ved 25 smørestedet afhænger blandt andet af smøreoliens viskositet. Den faktiske tidsforsinkelse er et absolut tidsinterval, medens tidsforsinkelsen for opnåelse af korrekt smøring varierer med motorens omløbstal, Ved de kendte elektronisk aktiverede smøreenheder foretages 30 aktiveringen på basis af krumtapakslens drejestilling.20 In practice, it has proved extremely difficult to realize this desire, because many conditions affect the actual delivery time of the lubricating oil. Some examples can be given. The time lag between the lubrication unit activation and the delivery of the oil at the lubrication site depends, among other things, on the viscosity of the lubricating oil. The actual time delay is an absolute time interval, while the time delay for obtaining proper lubrication varies with the engine turnover number. In the known electronically actuated lubrication units, the activation is made on the basis of the crankshaft turning position.
I drift vrider krumtapakslen sig i større eller mindre grad afhængig af motorens øjeblikkelige belastning og af, hvor langt den pågældende cylinder ligger væk fra signalgiveren, der detekterer akslens drejningsbe-35 vægelse, hvilket introducerer varierende unøjagtigheder 2 DK 173533 B1 i smøringstidspunktet.In operation, the crankshaft rotates to a greater or lesser extent depending on the instantaneous load of the engine and on how far the cylinder in question is away from the signal transducer detecting the rotational movement of the shaft, introducing varying inaccuracies at the time of lubrication.
Den foreliggende opfindelse har til formål at forbedre smøreoliens aflevering til det mindst ene smørested i cylinderen.The present invention aims to improve the delivery of the lubricating oil to the at least one lubrication site in the cylinder.
5 Med henblik herpå er fremgangsmåden ifølge op findelsen ejendommelig ved, at smøreenhedens aktivering i løbet af en eller flere motorcyklusser styres af den elektroniske styreenhed på basis af måling af de varierende cylindertryk i cylinderen, medens motoren 10 kører.For this purpose, the method according to the invention is characterized in that the activation of the lubrication unit during one or more motor cycles is controlled by the electronic control unit on the basis of measuring the varying cylinder pressures in the cylinder while the motor 10 is running.
Målingen af de faktiske cylindertryk i cylinderen giver et retvisende billede af de øjeblikkelige stem-pelbevægelser, hvilket er grundlaget for at kunne aflevere smøreolien i løbet af det meget korte tidsrum, 15 hvor stemplet passerer smørestedet eller smørestederne. Målingerne tilfører den elektroniske styreenhed oplysning om, hvornår stemplet passerer smørestedet, og om tidsintervallet mellem hver passage. Ud fra disse data og eventuelt lagrede oplysninger om den ønskede 20 doseringsmængde og om tidsforsinkelsen fra aktiveringssignalet afgives til smøreolien faktisk leveres til smørestedet beregner styreenheden, hvornår det næste aktiveringssignal skal afgives. Da målingen af de varierende cylindertryk sker, medens motoren kører ved 25 den for smøringen aktuelle driftstilstand, opnås der vedvarende en opdatering af de aktuelle data og dermed en løbende tilpasning af aktiveringstidspunktet efter de øjeblikkelige stempelbevægelser i cylinderen.The measurement of the actual cylinder pressures in the cylinder gives a true and fair view of the instant piston movements, which is the basis for being able to deliver the lubricating oil during the very short period of time in which the piston passes the lubrication point (s). The measurements provide the electronic control unit with information on when the piston passes the lubrication site and on the time interval between each passage. Based on this data and possibly stored information about the desired amount of dosage and whether the time delay from the activation signal is delivered to the lubricating oil is actually delivered to the lubrication site, the controller calculates when the next activation signal should be delivered. Since the measurement of the varying cylinder pressures occurs while the engine is running at the operating state of the lubrication, an up-to-date update of the current data is obtained and thus a continuous adjustment of the activation time according to the instantaneous piston movements in the cylinder.
Det er muligt at måle cylindertrykket ved hjælp af 30 velkendte teknikker, såsom strain-gauges monteret på cylinderdækslets dækseltappe, men en sådan måling af det generelle trykniveau i cylinderen giver kun en relativt grov indikation af stemplets aktuelle position og bevægelse.It is possible to measure the cylinder pressure by 30 well-known techniques, such as strain gauges mounted on the cylinder head cover, but such a measurement of the general pressure level in the cylinder provides only a relatively coarse indication of the current position and movement of the piston.
35 Det foretrækkes, at der ved et trykmålested i 3 DK 173533 B1 cylinderen måles trykvariationerne frembragt af, at stempelringe på et stempel i cylinderen passerer trykmålestedet, og at disse trykmålinger anvendes i forbindelse med styringen af smøreenhedens aktiverings-5 tidspunkt. Der fremkommer markante, karakteristiske trykaendringer, når stempelringene passerer trykmåle-stedet, og trykaendringerne er lokale for området umiddelbart omkring stempelringene. Dette giver en meget præcis måling af stemplets øjeblikkelige position 10 og dermed et præcist udgangspunkt for styreenhedens bestemmelse af smøreenhedens aktivering.It is preferred that at a pressure measuring point in the cylinder, the pressure variations produced by the fact that piston rings on a piston in the cylinder pass the pressure measuring point are measured and that these pressure measurements are used in connection with the control of the lubrication unit activation time. Significant, characteristic pressure changes occur as the piston rings pass the pressure measuring site and the pressure changes are local to the area immediately around the piston rings. This provides a very accurate measurement of the current position 10 of the piston and thus a precise starting point for the control unit's determination of the lubricant's activation.
I en særlig fordelagtig udførelse ifølge opfindelsen måles de varierende cylindertryk og smøreolietryk ved smørestedet. Dette giver en række fordele. Ved 15 målingen opnås oplysning om cylindertrykket ved smøre-stedet, hvilket betyder, at styreenheden undgår at skulle kompensere tidsmæssigt for stempelbevægelsen mellem måle- og smørestederne, hvilken tidsmæssige korrektion varierer med motorens omdrejningstal.In a particularly advantageous embodiment of the invention, the varying cylinder pressures and lubricating oil pressures are measured at the lubrication site. This offers a number of benefits. At the measurement, information about the cylinder pressure is obtained at the lubrication site, which means that the control unit avoids having to compensate temporarily for the piston movement between the measuring and lubrication points, which temporal correction varies with the engine speed.
20 Endvidere opnås ved samme målested oplysning om det præcise tidspunkt for, hvornår smøreolien afgives ved smørestedet, fordi denne afgivelse resulterer i en tydelig stigning i det målte tryk. Med en sådan måling af smøreoliens faktiske leveringstidspunkt undgås de 25 kendte problemer med at forudsige variationerne i tidsforsinkelsen mellem smøreenhedens aktivering og smøreoliens ankomst til smørestedet.Furthermore, at the same measurement location, information is given about the exact time when the lubricating oil is delivered at the lubrication site, because this release results in a clear increase in the measured pressure. With such a measurement of the actual delivery time of the lubricating oil, the 25 known problems in predicting the variations in the time delay between lubrication unit activation and the lubrication oil's arrival at the lubrication site are avoided.
Endvidere opnås den fordel, at der mellem tryksensoren og gasarterne i cylinderen er en beskyttende 30 mængde smøreolie, der virker kølende og sikrer rimeligt ensartede driftsforhold for tryksensoren. Tilførslen af smøreolie virker endvidere rensende i området omkring tryksensoren og sikrer borttransport af restprodukter fra forbrændingen, hvis disse aflejres ud for tryksen-35 soren.Furthermore, the advantage is obtained that between the pressure sensor and the gases in the cylinder there is a protective amount of lubricating oil which acts cool and ensures reasonably uniform operating conditions for the pressure sensor. Furthermore, the supply of lubricating oil acts purifying in the region of the pressure sensor and ensures the removal of residual products from the combustion if these are deposited next to the pressure sensor.
4 DK 173533 B14 DK 173533 B1
Aktiveringen af smøreenheden kan hensigtsmæssigt afhænge af den aktuelle driftstilstand af cylinderen. Overvågningen af driftstilstanden kan være baseret på et velkendt system, såsom et anti-scuffing system 5 og/eller måling af udvalgte driftstemperaturer på cylinderen, men det foretrækkes, at smøreenheden i løbet af en driftsperiode aktiveres et færre antal gange end antallet af motorcyklusser i driftsperioden, og at ud fra trykmålinger i de motorcyklusser, hvor 10 smøreenheden er inaktiv, tilføres styreenheden trykmåledata til analyse af stempelringenes driftstilstand.The activation of the lubrication unit may conveniently depend on the current operating state of the cylinder. The monitoring of the operating condition may be based on a well-known system, such as an anti-scuffing system 5 and / or measurement of selected operating temperatures on the cylinder, but it is preferred that during the operation period the lubricant be activated a fewer number of times than the number of motor cycles during the operating period. and that from the pressure measurements in the motor cycles where the lubrication unit is idle, the control unit is supplied with pressure measurement data for analysis of the piston rings operating condition.
Når smøringen foregår med korrekt timing i forhold til stempelbevægelsen, kan der i motorcyklusser med smøring med en tryksensor placeret i smørestedet ikke måles 15 trykdata, som kan anvendes til bestemmelse af ringenes driftstilstand, fordi trykstigningen som følge af smøringen overdøver de små trykændringer, der indikerer begyndende driftsproblemer. Ved ikke at smøre i hver motorcyklus på den pågældende cylinder opnås, at 20 trykmålingerne fra motorcyklusserne uden smøreolietilførsel er anvendelige til analyse af stempelringenes driftstilstand. De længere intervaller mellem hver aktivering af smøreenheden giver endvidere den fordel, at smøreoliemængden per aktivering bliver større, 25 hvilket fremmer god smøring, fordi den større mængde smøreolie fordeles mere effektivt langs cylinderens omkreds.When the lubrication takes place at the correct timing relative to the piston movement, in motor cycles with lubrication with a pressure sensor located in the lubrication point, 15 pressure data cannot be measured which can be used to determine the operating state of the rings because the pressure rise due to the lubrication overcomes the small pressure changes which indicate incipient operating problems. By not lubricating in each motor cycle on the cylinder in question, it is achieved that the 20 pressure readings from the motor cycles without lubricating oil supply are useful for analyzing the piston rings operating condition. Furthermore, the longer intervals between each actuation of the lubricant provide the advantage of increasing the amount of lubricating oil per actuation, which promotes good lubrication, because the greater amount of lubricating oil is more efficiently distributed along the circumference of the cylinder.
Tilstandsovervågningen muliggør, at referencedata for de varierende cylindertryk, som indikerer cylin-30 derens normale driftstilstand, oplagres i styreenheden, mens motoren kører. Når en ny motor er kørt ind, kan referencedataene for hver enkelt cylinder registreres og oplagres, så de efterfølgende kan anvendes som sammenligningsgrundlag for, om de løbende målte drifts-35 data indikerer en normal driftstilstand, eller en 5 DK 173533 B1 unormal tilstand, der kræver ændring i driftsbetingelserne, såsom en forøget dosering af smøreolie. Da referencedataene etableres for hver enkelt cylinder på basis af dennes faktiske driftsforhold, kan selv små 5 afvigelser fra den normale drift konstateres. Tilstandsovervågningen kan derfor give besked om unormale driftsforhold på et væsentlig tidligere tidspunkt end de kendte anti-scuffing systemer, der er baseret på detektering af unormale temperaturstigninger i cylin-10 dervæggen.The condition monitoring allows the reference data for the varying cylinder pressures indicating the normal operating state of the cylinder to be stored in the controller while the engine is running. When a new engine has been run in, the reference data for each cylinder can be recorded and stored, so that they can subsequently be used as a comparison basis for whether the continuously measured operating data indicates a normal operating state, or an abnormal state which requires change in operating conditions, such as an increased dosage of lubricating oil. Since the reference data is established for each cylinder on the basis of its actual operating conditions, even small deviations from normal operation can be detected. Therefore, the condition monitoring can report abnormal operating conditions at a significantly earlier time than the known anti-scuffing systems based on detecting abnormal temperature increases in the cylinder wall.
Det foretrækkes, at referencedataene for cylinderens normale driftstilstand opdateres af styreenheden for kompensering for langtidsændringer i de varierende cylindertryk som følge af normalt cylinderslid. En 15 sådan opdatering, der eksempelvis kan ske periodevis, forbedrer styreenhedens mulighed for at detektere små afvigelser fra den normale driftstilstand.It is preferred that the reference data for the normal operating state of the cylinder is updated by the control unit for long-term compensation in the varying cylinder pressures due to normal cylinder wear. Such an update, which may occur periodically, for example, improves the control unit's ability to detect small deviations from the normal operating state.
Tilstandsovervågningen giver uden videre besked om, hvorvidt trykfaldene over de enkelte stempelringe 20 er normale, hvilket indikerer normal drift. Derudover kan der, om ønsket, opnås en meget fordelagtig overvågning af, om stempelringene drejer rundt om stemplets længdeakse, idet referencedata for de transiente ændringer i de varierende cylindertryk, som er for-25 årsaget af, at et ringgab i en stempelring periodevis passerer forbi trykmålestedet, kan omfattes af styreenhedens referencedata for cylinderens normale driftstilstand. Tilstandsovervågningen kan på basis heraf registrere, med hvilken frekvens hver enkelt stempel-30 ring drejer sig, og hvis frekvensen for en stempelring falder ved kontinuert motordrift, kan styreenheden give signal om, at stempelringen er ved at vise tegn på at sætte sig fast i det tilhørende ringspor.The condition monitoring immediately indicates whether the pressure drops across the individual piston rings 20 are normal, indicating normal operation. In addition, if desired, a very advantageous monitoring of whether the piston rings revolve around the longitudinal axis of the piston can be obtained, with reference data for the transient changes in the varying cylinder pressures caused by a ring gap in a piston ring passing periodically. the pressure gauge location may be included in the control unit reference data for the normal operating state of the cylinder. The condition monitoring can, on the basis of this, record the frequency at which each piston ring rotates, and if the frequency of a piston ring decreases with continuous motor operation, the control unit can signal that the piston ring is showing signs of getting stuck in it. associated ring groove.
Det foretrækkes, at styreenheden styrer smøre-35 enheden til midlertidig dosering af mere smøreolie, 6 DK 173533 B1 hvis målingerne af de varierende cylindertryk indikerer unormal driftstilstand for cylinderen, herunder for stemplet, stempelringene eller cylinderforingen. Ofte vil den midlertidige, ekstra smøreoliedosering være 5 tilstrækkelig til at genetablere den normale driftstilstand. Ved indikation om afvigelser fra den normale driftstilstand kan styreenheden give melding til betjeningspersonalet eller til en central styreenhed om, at driftstilstanden er ved at ændre sig. Dette kan 10 give meget tidligt varsel om, at cylinderen bør efterses og eventuelt repareres, og på baggrund heraf kan eventuelle reservedele bestilles og eftersynet planlægges. For motorens cylindre kan dette muligøre, at de sædvanlige periodiske rutineeftersyn erstattes med 15 eftersyn begrundet i cylinderens faktiske driftsforhold. Eftersynet kan enten være af præventiv karakter, når styreenheden indikerer en mulig fremtidig"driftsforstyrrelse, der ved tidlig indgriben kan hindres i at udvikle sig, eller kan være nødvendig som følge af 20 egentlig fejlmelding af en cylinder.It is preferred that the controller controls the lubricator for temporary dosing of more lubricating oil, if the measurements of the varying cylinder pressures indicate abnormal operating condition of the cylinder, including for the piston, piston rings or cylinder liner. Often, the temporary additional lubricating oil dosage will be sufficient to restore the normal operating state. In the event of an indication of deviations from the normal operating state, the control unit may notify the operating personnel or a central control unit that the operating state is changing. This can give very early warning that the cylinder should be inspected and possibly repaired, and on this basis any spare parts can be ordered and the inspection planned. For the engine cylinders, this may allow the usual periodic routine inspections to be replaced with inspections based on the actual operating conditions of the cylinder. The overhaul can either be of a preventive nature when the control unit indicates a possible future "malfunction which may be prevented from developing in the early intervention, or may be necessary as a result of actual failure of a cylinder.
Traditionelt er smøreoliens dosering indstillet ved, at der på basis af driftserfaringer fra mange motorer er fastsat forudbestemte minimumsdoseringer af smøreolie ved normal, kontinuert drift ved 100% motor-25 belastning. Disse standarddoseringer er tilstrækkeligt store til at kompensere for de variationer i smøringen, som skyldes fremstillingsmæssige tolerancer i smøresystemet og cylinderelementerne.Traditionally, the dosage of lubricating oil is set by the fact that, based on the operating experience of many engines, predetermined minimum doses of lubricating oil are set at normal, continuous operation at 100% engine load. These standard dosages are sufficiently large to compensate for the variations in lubrication due to manufacturing tolerances in the lubrication system and cylinder elements.
Den foreliggende opfindelse giver en hensigts-30 mæssig mulighed for at opnå væsentlige besparelser i smøreolieforbruget derved, at styreenheden automatisk detekterer den nødvendige minimumsdosering af smøreolie til cylinderen ved at mindske doseringen, indtil de målte varierende cylindertryk indikerer, at cylinderens 35 driftstilstand begynder at afvige fra den normale 7 DK 173533 B1 driftstilstand. Minimumsdoseringen for den pågældende cylinder er dermed den dosering, som blev anvendt et passende tidsrum inden afvigelsen fra den normale driftstilstand forekom.The present invention provides a convenient opportunity to achieve significant savings in lubricating oil consumption in that the control unit automatically detects the required minimum dosage of lubricating oil for the cylinder by reducing the dosage until the measured varying cylinder pressures indicate that the operating state of the cylinder 35 is departing from. the normal 7 DK 173533 B1 operating mode. Thus, the minimum dosage for the particular cylinder is the dosage that was used an appropriate amount of time before the deviation from the normal operating condition occurred.
5 Det er muligt at anvende en smøreenhed, som mængdereguleres ved at variere doseringsmængden per aktivering, og så aktivere doseringsenheden med en bestemt frekvens i forhold til motorcyklusserne. Alternativt kan anvendes en smøreenhed, som doserer den 10 samme mængde per aktivering, og smøreenhedens dosering af smøreolie varieres så ved at variere det antal motorcyklusser, som forløber mellem hver aktivering af smøreenheden. Denne form for aktivering af smøreenheden giver den fordel, at doseringsmængden ved den enkelte 15 aktivering kan være en mængde, der er tilstrækkelig stor til at sikre god fordeling af smøreolien i cylinderen.It is possible to use a lubrication unit which is quantity controlled by varying the dosage amount per activation, and then activating the dosage unit at a specific frequency in relation to the motor cycles. Alternatively, a lubricating unit which dispenses the same amount per activation can be used, and the lubricating unit's lubricating oil dosage is then varied by varying the number of motor cycles that pass between each lubricating unit activation. This kind of actuation of the lubricant provides the advantage that the dosage amount at the individual actuation can be an amount sufficient to ensure good distribution of the lubricating oil in the cylinder.
I en valgfri videreudvikling heraf indeholder styreenheden oplysning om flere standardgrupper af 20 motorcyklusser, hvori der i hver enkelt standardgruppe sker en enkelt aktivering af smøreenheden, og smøreenhedens doseringsmængde af smøreolie varieres ved at ændre på sammensætningen af efter hinanden følgende standardgrupper af motorcyklusser. Der kan eksempelvis 25 være standardgrupper på 3, 4, 5 og 6 osv. motorcyklusser, hver med en enkelt aktivering af smøreenheden, og set over en driftsperiode på fx 500 motorcyklusser kan der opnås kontinuert variation af doseringsmængden ved at vælge en passende kombinaion af efter hinanden 30 følgende standardgrupper. Hvis der ved en driftstilstand eksempelvis kun anvendes standardgruppen med én aktivering per 4 motorcyklusser, kan doseringen sættes en anelse ned ved at vælge en standardgruppe med 5 motorcyklusser efter hver fjerde standardgruppe med 4 35 motorcyklusser. Reguleringsteknisk er dette særdeles 8 DK 173533 B1 enkelt at håndtere i styreenheden.In an optional further development thereof, the control unit provides information on several standard groups of 20 motor cycles, in which in each standard group a single activation of the lubricant occurs, and the lubrication unit dosage amount of lubricating oil is varied by changing the composition of successive standard groups of motor cycles. For example, there may be 25 standard groups of 3, 4, 5 and 6, etc. motor cycles, each with a single activation of the lubrication unit, and seen over an operating period of eg 500 motor cycles, continuous variation of the dosage amount can be achieved by selecting an appropriate combination of 30 consecutive standard groups. For example, if, in an operating mode, only the standard group with one activation per 4 motor cycles is used, the dosage can be slightly reduced by selecting a standard group of 5 motor cycles after every four standard groups of 4 35 motor cycles. From a control point of view, this is very easy to handle in the control unit.
I en udformning, der kun stiller få krav til mekanisk udstyr og dermed er omkostningsmæssigt fordelagtig at implementere på en motor, især hvis der er 5 tale om retrofit til en allerede eksisterende motor, der ikke i forvejen har udstyr til aftastning af krumtapakslens drejningsbevægelse, er fremgangsmåden ejendommelig ved, at styreenheden umiddelbart efter start af motoren aktiverer smøreenheden på et vilkår-10 ligt tidspunkt i løbet af en motorcyklus, og at styreenheden på basis af måling af de varierende cylindertryk i cylinderen regulerer tidspunktet for smøreenhedens aktivering i en motorcyklus således, at smøreolien løber ud ved smørestedet, medens stemplets ring-15 pakke i stemplets opovergående slag befinder sig ud for smørestedet. I løbet af en ganske kort driftsperiode har styreenheden ud fra målingen af de varierende cylindertryk styr på, hvornår stemplet passerer forbi smørestedet, og derefter kan aktiveringen af smøreen-20 heden på simpel vis justeres ind til at smøreolien afleveres, når stemplet passerer smørestedet.In a design that sets few requirements for mechanical equipment and is thus cost-effective to implement on a motor, especially if there is retrofit to an already existing motor that does not already have equipment for sensing the crankshaft rotation, The method is characterized in that the control unit activates the lubricant immediately after starting the engine at any time during a motor cycle, and that the control unit, on the basis of measuring the varying cylinder pressures in the cylinder, regulates the time of the lubricator's activation in a motor cycle such that the lubricating oil flows out at the lubrication site, while the piston ring-15 pack in the piston's upward stroke is off the lubrication site. During a very short operating period, the control unit, based on the measurement of the varying cylinder pressures, controls when the piston passes past the lubrication site, and then the activation of the lubricant 20 can simply be adjusted to deliver the lubricating oil as the piston passes the lubrication site.
Den foreliggende opfindelse angår endvidere et cylindersmøresystem til en forbrændingsmotor, med mindst en smøreenhed til levering af smøreolie til 25 mindst et smørested på cylinderen og med en styreenhed til elektronisk styring af smøreenheden. Cylindersmøre-sysstemet er ejendommelig ved, at det omfatter mindst en tryksensor til måling af i cylinderen varierende cylindertryk, og at styreenheden via en dataindgang 30 modtager trykmåledata for trykvariationerne i cylinderen ved tryksensoren. Med dette system kan opnås indsamling af data til brug for analysering af cylinderens driftstilstand og justering af smøreenhedens aktivering, hvilket kan anvendes til opnåelse af de 35 ovennævnte fordele. Tryksensoren kan med fordel være 9 DK 173533 B1 placeret i cylinderens side og måle trykket ved et løbefladeområde, hvori stempelringene passerer i løbet af hver motorcyklus, idet de lokale trykvariationer omkring stempelringene giver oplysninger om driftstil-5 standen for hver enkelt ring.The present invention further relates to a cylinder lubrication system for an internal combustion engine, with at least one lubricant for supplying lubricating oil to at least one lubrication point on the cylinder and with a control unit for electronically controlling the lubrication unit. The cylinder lubrication system is characterized in that it comprises at least one pressure sensor for measuring cylinder pressure varying in the cylinder and that the control unit receives via a data input 30 pressure measurement data for the pressure variations in the cylinder at the pressure sensor. With this system, data can be obtained for use in analyzing the cylinder operating state and adjusting the lubricator activation, which can be used to obtain the above mentioned benefits. The pressure sensor may advantageously be located on the side of the cylinder and measure the pressure at a running surface area in which the piston rings pass during each engine cycle, the local pressure variations around the piston rings providing information on the operating state of each ring.
I en hensigtsmæssig udførelsesform omfatter styreenheden et intelligent, selvlærende program til bearbejdning af trykmåledata, såsom et neuralt netværk og/eller et program med generiske algoritmer eller 10 fuzzy-logic. Et sådant program kan på basis af målte data fra cylinderen i drift og ud fra forudbestemte informationer om typiske fejltilstande detektere små afvigelser fra den normale drift og give tidlig besked om en begyndende fejltilstand.In a convenient embodiment, the controller comprises an intelligent, self-learning program for processing pressure measurement data, such as a neural network and / or a program with generic algorithms or fuzzy logic. Such a program, on the basis of measured data from the cylinder in operation and based on predetermined information about typical fault conditions, can detect small deviations from normal operation and give early notification of a starting fault condition.
15 Endvidere angår opfindelsen et tilslutningselement til montering ved et smørested på en cylinder i en forbrændingsmotor og omfattende et hus til indsætning i en boring i cylindervæggen og en i huset udformet kanal, som strækker sig fra en tilslutning for et 20 smørerør til en afgangsåbning ved smørestedet og indeholder en kontraventil, der åbner i retning af afgangsåbningen. Tilslutningselementet er ejendommeligt ved, at en tryksensor står i forbindelse med det kanalafsnit, der strækker sig fra kontraventilen til 25 afgangsåbningen. Når tilslutningselementet er monteret på en cylinder, står tryksensoren således i vedvarende forbindelse med det område, der ligger inden i cylinderen ud for smørestedet. Tryksensoren kan være indbygget i tilslutningselementets hus.The invention further relates to a connection element for mounting at a lubrication point on a cylinder of an internal combustion engine and comprising a housing for insertion into a bore in the cylinder wall and a duct formed in the housing extending from a connection for a lubrication pipe to a discharge opening at the lubrication site. and includes a non-return valve which opens in the direction of the outlet opening. The connection element is peculiar in that a pressure sensor communicates with the duct section extending from the non-return valve to the outlet port. Thus, when the connecting member is mounted on a cylinder, the pressure sensor is in continuous contact with the area within the cylinder adjacent to the lubrication site. The pressure sensor may be built into the housing of the connecting element.
30 Opfindelsen beskrives herefter nærmere med hen visning til den stærkt skematiske tegning, hvorpå fig. 1 viser et deludsnit af en cylinder udformet i overensstemmelse med opfindelsen, fig. 2 en anden udførelsesform for et smøresystem 35 ifølge opfindelsen, 10 DK 173533 B1 fig. 3-6 diagrammer over målte trykforløb i en cylinder i løbet af kompressionsslag, fig. 7 et diagram over et målt trykforløb i samme cylinder i løbet af et ekspansionsslag, 5 fig. 8 og 9 skematisk visning af databehandlings forløb, og fig. 10 et sidebillede af et tilslutningselement ifølge opfindelseen.The invention will now be described in more detail with reference to the highly schematic drawing, in which fig. 1 is a partial section of a cylinder formed in accordance with the invention; FIG. 2 shows another embodiment of a lubrication system 35 according to the invention, FIG. 3-6 diagrams of measured pressure losses in a cylinder during compression stroke; 7 is a diagram of a measured pressure loss in the same cylinder during an expansion stroke; FIG. 8 and 9 are schematic views of the data processing process; and FIGS. 10 is a side view of a connecting element according to the invention.
En i fig. 1 antydet cylinder 1 i en forbrændings-10 motor omfatter en cylinderforing 2, et cylinderdæksel 3 med en udstødsventil 4 og et stempel 5 monteret på toppen af en stempelstang 6. Stemplet har i sin yderside et antal ringnoter med stempelringe 7. Antallet af stempelringe kan variere med motortypen, men der er 15 typisk mindst tre og højst seks stempelringe. For at give korrekt tætning skal ringene have mulighed for at bevæge sig i de tilhørende ringspor, og ringbevægelserne omfatter normalt både en forskydning op og ned i ringsporet og en drejning omkring stemplets længdeakse 20 8.One in FIG. 1, a cylinder 1 in an internal combustion engine 10 comprises a cylinder liner 2, a cylinder cover 3 with an exhaust valve 4 and a piston 5 mounted on top of a piston rod 6. The piston has on its outer side a plurality of ring grooves with piston rings 7. The number of piston rings can be vary by engine type, but there are typically at least three and at most six piston rings. In order to provide proper sealing, the rings must be able to move in the associated ring grooves, and the ring movements usually include both a displacement up and down the ring groove and a rotation about the longitudinal axis of the piston 20 8.
Den cylindriske inderside af cylinderforingen 1 udgør en løbeflade 9 for stempelringene. Løbefladens nedre ende ligger ud for underkanten af den nederste stempelring i stemplets bunddødpunkt, og løbefladens 25 øvre ende ligger ud for overkanten af den øverste stempelring i stemplets topdødpunkt. Stempelringene og cylinderforingen fungerer kun korrekt, hvis der løbende sker en passende tilførsel af smøreolie til løbefladen.The cylindrical inside of the cylinder liner 1 constitutes a running surface 9 for the piston rings. The lower end of the running surface is adjacent to the lower edge of the lower piston ring at the bottom dead center of the piston, and the upper end of the running surface 25 lies opposite the upper edge of the upper piston ring at the top dead center of the piston. The piston rings and cylinder liner only function properly if there is a continuous supply of lubricating oil to the running surface.
I en krydshovedmotor adskiller en mellembund bundkarret 30 fra cylindrene, så der er behov for separat cylinder-smøring, hvilket foretages med en smøreenhed 10, der eksempelvis kan være af den type, der er beskrevet i ansøgerens DE-A 19743955, hvor en elektronisk aktiveret og hydraulisk drevet aktuator driver flere doserings-35 stempler i et fælles leveringsslag, eller eksemplevis 11 DK 173533 B1 kan være en mekanisk drevet pumpe i kombination med elektronisk udløsning af hvert doseringsvolumen af smøreolie som beskrevet i EP-B 0 678 152.In a cross-head motor, an intermediate bottom vessel 30 separates from the cylinders so that separate cylinder lubrication is required, which is done with a lubricating unit 10 which may be, for example, of the type described in applicant DE-A 19743955, where an electronically activated and hydraulically driven actuator drives multiple dosing pistons in a common delivery stroke, or for example 11 may be a mechanically driven pump in combination with electronic release of each dosing volume of lubricating oil as described in EP-B 0 678 152.
Smøreenheden 10 kan levere smøreolie til flere 5 smøresteder 11 på samme cylinder eller på flere cylindre. I sidstnævnte tilfælde aktiveres smøreenheden med timinger, der er afpasset efter henholdsvis den ene og den anden cylinder. På store motorer vil der typisk være mindst én smøreenhed per cylinder, og smøresteder-10 ne tilsluttet smøreenheden vil typisk ligge ved samme længdeposition (niveau) i cylinderforingen, men fordelt over dennes omkreds. Hvis der ønskes smøring i flere niveauer og/eller smøring med mere end en type smøreolie, vil der typisk anvendes flere smøreenheder per 15 cylinder.The lubricating unit 10 can supply lubricating oil to several 5 lubricating points 11 on the same cylinder or on several cylinders. In the latter case, the lubrication unit is activated with timings adapted to the one and the other cylinder respectively. On large engines, there will typically be at least one lubrication unit per cylinder, and the lubrication sites connected to the lubricant unit will typically be at the same length position (level) in the cylinder liner but distributed over its circumference. If multi-level lubrication and / or lubrication with more than one type of lubricating oil is desired, more than one lubrication unit per 15 cylinder is typically used.
Forbrændingsmotoren kan være en langsomtgående, totakts krydshovedmotor med et maksimalt omdrejningstal i intervallet 60-275 rpm, en ydelse per cylinder i intervallet 300-6000 kW, en cylinderboring i inter-20 vallet 25-100 cm og en slaglængde i intervallet 90-300 cm. Opfindelsen kan også med fordel anvendes på firtakt motorer med tryksmøring af cylindrene.The internal combustion engine can be a slow-moving, two-stroke cross-head motor with a maximum speed in the range of 60-275 rpm, a performance per cylinder in the range of 300-6000 kW, a cylinder bore in the range of 25-100 cm and a stroke in the range of 90-300 cm. . The invention can also advantageously be applied to four stroke engines with pressure lubrication of the cylinders.
Smøreenheden 10 er forbundet med smørestederne 11 via ledninger eller smørerør 12, og i nærheden af 25 smørestedet er der en kontraventil 13, som kun tillader tilstrømning til smørestedet og hindrer det relativt høje cylindertryk i løbet af arbejdsslaget i at udbrede sig til smøreenheden. Når smøreolien afleveres til smørestedet på cylindersiden af kontraventilen, over-30 tiger smøreolietrykket det øjeblikkelige tryk i cylinderen ved smørestedet. Smørestedet kan eksempelvis være beliggende således, at dette cylindertryk vil være i intervallet fra 5 til 30 bar, hvilket giver mulighed for at anvende en tryksensor, der måler over et rela-35 tivt lille trykinterval og har ægte nulpunkt, dvs. en 12 DK 173533 B1 tryksensor uden signalforstærkning.The lubrication unit 10 is connected to the lubrication points 11 via lines or lubrication pipes 12, and in the vicinity of the lubrication site there is a non-return valve 13 which only allows inflow to the lubrication site and prevents the relatively high cylinder pressure during the work stroke from spreading to the lubrication unit. When the lubricating oil is delivered to the lubrication site on the cylinder side of the check valve, the lubricating oil pressure exceeds the instantaneous pressure in the cylinder at the lubrication site. For example, the lubrication site may be located such that this cylinder pressure will be in the range of 5 to 30 bar, which allows the use of a pressure sensor which measures over a relatively small pressure range and has a true zero point, ie. a 12 DK 173533 B1 pressure sensor without signal amplification.
Mellem mindst ét af smørestederne og den tilhørende kontraventil er tilsluttet en tryksensor 14 (trykpick-up) , der som følge af sin tilslutning på 5 leveringssiden af kontraventilen måler cylindertrykket umiddelbart ud for smørestedet. En signalledning 15 fra tryksensoren 14 overfører trykmåledata til en dataindgang 16 i en styreenhed 17, der på basis af måledataene og eventuelle oplagrede data bestemmer, hvornår smøre-10 enheden skal aktiveres, og i overensstemmelse hermed afgiver styresignal via en signalledning 18 til smøreenheden 10, der forsynes med smøreolie gennem en ledning 19. I fig. 1 er antydet, at styreenheden 17 styrer to smøreenheder 10, der begge kan smøre den 15 samme cylinder. Af hensyn til timingen af smøreenhedens aktivering i forhold til stempelbevægelsen er det muligt kun at anvende en enkelt tryksensor 14, men det foretrækkes at anvende mindst én tryksensor for hver smøreenhed 10, fordi der så opnås kontrol af funktions-20 dueligheden af hver af smøreenhederne.Between at least one of the lubrication points and the associated check valve is connected a pressure sensor 14 (pressure pick-up) which, as a result of its connection on the delivery side of the check valve, measures the cylinder pressure immediately outside the lubrication site. A signal line 15 from the pressure sensor 14 transmits pressure measurement data to a data input 16 of a control unit 17 which, on the basis of the measurement data and any stored data, determines when the lubricating unit must be activated, and accordingly gives control signal via a signal line 18 to the lubricating unit 10. provided with lubricating oil through a conduit 19. In FIG. 1 it is suggested that the control unit 17 controls two lubricating units 10, both of which can lubricate the same cylinder. In view of the timing of lubrication unit activation relative to the piston movement, it is possible to use only a single pressure sensor 14, but it is preferable to use at least one pressure sensor for each lubrication unit 10 because control of the performance of each of the lubrication units is then achieved.
I den efterfølgende beskrivelse af andre udførelsesformer anvendes for enkelheds skyld samme henvisningstal som ovenfor for elementer af samme art.In the following description of other embodiments, for the sake of simplicity, the same reference numerals as above are used for elements of the same kind.
I fig. 2 ses en cylinder i en motor, der har en 25 udførelsesform med to smøreenheder 10 per cylinder, hvor smørestederne 11 rundt langs cylinderens omkreds skiftevis er tilsluttet den ene og den anden smøreenhed. Hvis den ene af smøreenhederne skulle svigte, kan den anden smøreenhed aktiveres til at dosere mindst det 30 dobbelte af sin normale smøreoliemængde og dermed holde cylinderen i normal drift, indtil svigttilstanden er udbedret.In FIG. 2, a cylinder is seen in an engine having an embodiment with two lubricating units 10 per cylinder, the lubrication points 11 being alternately connected to the lubrication unit around the circumference of the cylinder. If one of the lubricating units should fail, the other lubricating unit can be activated to dose at least 30 times its normal lubricating oil quantity and thus keep the cylinder in normal operation until the failure condition is rectified.
Hver af smøreenhederne 10 er tilknyttet en tryksensor 14, som er placeret ved smøresteder, der er 35 adskilt fra hinanden i omkredsretningen, og hensigts- 13 DK 173533 B1 mæssigt ligger diametralt modsat hinanden. Når måledataene fra tryksensorerne anvendes til tilstandsanalyse af stempelringene, jvf. nedenfor, giver de to tryksensorer mulighed for på enkel vis at konstatere, om et 5 afvigende trykforløb målt ved den ene tryksensor skyldes passage af et ringgab, hvilket konstateres ved måling af normalt trykforløb ved den anden tryksensor, eller om det skyldes en fejltilstand ved stempelringen, der giver afvigende trykforløb ved begge sensorer. De 10 to sensorer forbedrer også driftssikkerheden, fordi korrekt drift af smøreenhederne 10 kan opretholdes, selv om den ene tryksensor fejler. Smøresystemets driftssikerhed kan endvidere højnes ved, at smøreenhederne som back-up også kan styres af en anden styre-15 enhed, såsom styreenheden 10 hørende til en anden cylinder på motoren. Der kan være én styreenhed 10 for hver cylinder, eller styreenheden 10 kan være fælles for en gruppe af cylindre eller for hele motoren.Each of the lubricating units 10 is associated with a pressure sensor 14 which is located at lubrication points 35 which are spaced apart in the circumferential direction, and suitably diametrically opposite to each other. When the measurement data from the pressure sensors is used for condition analysis of the piston rings, cf. below, the two pressure sensors allow to easily determine if a 5 deviating pressure loss measured by one pressure sensor is due to the passage of a ring gap, which is found by measuring normal pressure loss at the second pressure sensor, or whether it is due to a failure condition of the piston ring, which gives divergent pressure losses at both sensors. The two sensors also improve reliability because proper operation of the lubricating units 10 can be maintained even if one pressure sensor fails. Furthermore, the operational safety of the lubrication system can be increased by the fact that the lubrication units as a back-up can also be controlled by another control unit, such as the control unit 10 belonging to another cylinder on the engine. There may be one control unit 10 for each cylinder, or the control unit 10 may be common to a group of cylinders or to the entire engine.
De i fig. 3-6 viste diagrammer viser trykforløb 20 målt i løbet af stemplets kompressionsslag i en trykladet totakts dieselmotor som funktion af tiden. Tryksensorens er placeret ved smørestedet, og dens nulpunkt er justeret ind efter ladelufttrykket. Stemplet har fire stempelringe. I fig. 3 ses et trykforløb a målt i en 25 motorcyklus uden smøreolietilførsel ved målestedet.The 3-6 show the pressure loss 20 measured during the piston's compression stroke in a pressurized two-stroke diesel engine as a function of time. The pressure sensor is located at the lubrication point and its zero point is adjusted to the charge air pressure. The piston has four piston rings. In FIG. 3 shows a pressure loss a measured in a 25 cycle cycle without lubricating oil supply at the measurement site.
Kurven har et tydeligt maksimum ved b, der viser tidspunktet ti for, hvornår den øverste stempelring passerer målestedet. Kort tid derefter har kurven maksima c, d, e, der på karakteristisk måde viser 30 passagen af de tre øvrige stempelringe i form af en lille trykstigning efterfulgt af et mærkbart trykfald.The curve has a clear maximum at b, showing the time ten for when the upper piston ring passes the measuring point. Shortly thereafter, the curve has maxima c, d, e, which characteristically show the passage of the other three piston rings in the form of a small pressure rise followed by a noticeable pressure drop.
Efter passagen af det opovergående stempel ses cylindertrykket ud for målestedet at være stort set upåvirket af de væsentligt højere tryk, som er til stede 35 i forbrændingskammeret over stemplet. Hvis målestedet 14 DK 173533 B1 ikke er beliggende ved løbefladen i cylinderen, men fx måler trykbelastningen på cylinderdækslet, opnås der globale data for stemplets position, men ikke lokale data for trykvariationer ved de enkelte stempelringe.After the passage of the upward piston, the cylinder pressure next to the metering point appears to be largely unaffected by the substantially higher pressures present in the combustion chamber above the piston. If the measuring point 14 DK 173533 B1 is not located at the running surface of the cylinder, but for example measures the pressure load on the cylinder cover, global data is obtained for the position of the piston, but not local data for pressure variations at the individual piston rings.
5 I fig. 4-6 ses eksempler på målte trykforløb f, g og h, når smøringen er henholdsvis for tidlig, korrekt og for sen. I alle tre tilfælde frembringer leveringen af smøreolien til smørestedet en markant trykstigning ved et tidspunkt t2 og passagen af den første stempel-10 ring et markant trykfald ved tidspunktet ti. Det er ønskeligt, at leveringen af smøreolie sker i tidsrummet mellem ti og tidspunktet e for passagen af den nederste stempelring. En sådan korrekt timing er vist i fig. 5.5 In FIG. 4-6, examples of measured pressures f, g and h are shown when the lubrication is premature, correct and too late. In all three cases, the delivery of the lubricating oil to the lubrication site produces a marked increase in pressure at a time t 2 and the passage of the first piston ring a significant pressure drop at the time t1. It is desirable that the delivery of lubricating oil takes place in the period between ten and time e of the passage of the lower piston ring. Such correct timing is shown in FIG. 5th
De målte trykvariationer kan anvendes til præcis 15 adaptiv styring af smøreoliens doseringstidspunkt i forhold til stempelpassagen, idet styreenheden korrigerer smøreenhedens aktivering, indtil tidspunkterne ti og t2 er i det væsentlige sammenfaldende.The measured pressure variations can be used for precise adaptive control of the lubrication oil dosing time relative to the piston passage, the controller correcting the lubrication unit activation until the times t1 and t2 are substantially coincident.
Det foretrækkes, at der leveres smøreolie, medens 20 i det mindste de tre øverste stempelringe passerer forbi smørestedet, og arealet af udløbsåbningen ved smørestedet er afpasset således efter den leverede smøreoliemængde per aktivering af smøreenheden, at dette opnås ved fuld motorbelastning (Maximum Conti-25 nuous Rating) . Når motoren kører ved lav belastning, bevæger stemplet sig langsommere forbi smørestedet, og da smøreoliens udstrømningsperiode ofte holdes uændret, kan styreenheden aktivere smøreenheden med periodevis forsinkelse, fx ved hver anden eller hver tredie 30 aktivering, så at leveringen ved smørestedet først starter, når første stempelring har passeret. Derved smøres både i toppen og bunden af stemplets ringpakke.It is preferred that lubricating oil be delivered while at least 20 of the top three piston rings pass the lubrication site and the area of the outlet opening at the lubrication site is adjusted to the amount of lubricating oil delivered per actuation of the lubrication unit to achieve this at full engine load (Maximum Conti-25 nuous Rating). When the engine is running at low load, the piston moves more slowly past the lubrication site, and since the lubrication oil outflow period is often kept unchanged, the control unit can activate the lubrication unit with periodic delay, eg at every second or every third activation, so that delivery at the lubrication site starts only when the first piston ring has passed. This lubricates both the top and bottom of the piston ring package.
Når smøreolien ikke leveres i løbet af stemplets passage forbi målestedet på løbefladen, kan der som 35 vist i fig. 3 opnås detaljerede data for stempelringe- DK 173533 B1 15 nes tilstand, idet trykfaldene ved passagen af hver enkelt stempelring kan verificere ringenes korrekte funktion. Som følge af, at ringene roterer i ringsporene, og at ringene kan have et skråt forløbende 5 ringgab, hvori gas strømmer forbi ringen, fremkommer der for den enkelte ring periodevise transiente måledata, der resulterer i trykmålinger, hvor trykfaldet over ringen er væsentlig mindre end normalt. Da stempel-ringen roterer langsomt, sker passagen i løbet af en 10 række motorcyklusser og med et genkendeligt forløb.When the lubricating oil is not delivered during the passage of the piston past the measuring point on the running surface, as shown in FIG. 3, detailed data is obtained for the condition of the piston rings, as the pressure drops at the passage of each piston ring can verify the correct functioning of the rings. Due to the fact that the rings rotate in the ring grooves and that the rings may have a sloping annular gap in which gas flows past the ring, periodic transient measurement data for the individual ring results in pressure measurements where the pressure drop across the ring is substantially less than normally. As the piston ring rotates slowly, the passage occurs over a series of 10 cycles and with a recognizable course.
I fig. 7 ses et trykforløb målt i løbet af stemplets ekspansionsslag. Den lodrette linie markeret ved i viser, at stempelringene passerer ned forbi tryksensoren, der blotlægges for trykket i forbræn-15 dingskammeret, og efter nogle indledende tryksvingninger mindskes trykket i et jævnt forløb ned til ladelufttrykket. I styreenheden kan disse oplysninger om trykforløbet ved den øjeblikkelige driftstilstand anvendes til justering af udstødsventilens åbnings-20 tidspunkt.In FIG. 7 shows a loss of pressure measured during the expansion stroke of the piston. The vertical line marked by i shows that the piston rings pass down past the pressure sensor exposed to the pressure in the combustion chamber, and after some initial pressure fluctuations, the pressure decreases in a smooth course down to the charge air pressure. In the control unit, this information on the pressure flow at the instantaneous operating state can be used to adjust the opening time of the exhaust valve.
I den elektroniske styreenhed 17 kan de indsamlede trykmåledata gemmes og analyseres, og et eksempel herpå er i skematisk form vist i fig. 8, hvor informationerne 20 overført via signalledningen 15 oplagres i et trin 25 21, eventuelt efter en frafiltrering af uønskede informationer. I et trin 22 analyseres et passende udsnit af dataene for bestemmelse af tidspunktet ti, og i et trin 23 foretages en tilsvarende bestemmelse af tidspunktet t2, hvorefter styreenheden i et trin 24 ved 30 en sammenligning af tidspunkterne ti og t2 afgør, om en tids- eller anden korrektion af aktiveringssignalet til smøreenheden er nødvendig, og derefter afgives styresignaler 25 på den ønskede måde til smøreenheden. Analysen foretaget i trin 24 kan være baseret på 35 forudbestemte kriterier, evt suppleret med informatio- 16 DK 173533 B1 ner om en eller flere driftsparametre for motoren, såsom den øjeblikkelige belastning, eller afgivne ordre om belastningsændringer, eller manuelt afgivne ordre om ekstrasmøring osv. I fig. 2 er med en signalledning 26 5 antydet, at styreenheden kan modtage ydre signaler af denne art.In the electronic control unit 17, the collected pressure measurement data can be stored and analyzed, and an example of this is shown in schematic form in FIG. 8, where the information 20 transmitted via the signal line 15 is stored in a step 25 21, possibly after filtering out unwanted information. In a step 22, an appropriate section of the data for determining the time t1 is analyzed, and in a step 23 a corresponding determination of the time t2 is made, after which the controller in a step 24 at 30 compares the time points t1 and t2 or other correction of the lubricating actuator signal is necessary, and then control signals 25 are output to the lubricator in the desired manner. The analysis performed in step 24 may be based on 35 predetermined criteria, optionally supplemented with information on one or more engine operating parameters, such as the instantaneous load, or issued load change order, or manually issued extra lubrication order, etc. In FIG. 2 is indicated by a signal line 26 5 that the control unit can receive external signals of this kind.
Et andet eksempel på styreenhedens behandling af trykmåledata er skitseret i fig. 9, hvor der efter frafiltrering af støj og uønskede informationer i et 10 trin 27 kan foretages en analyse i et trin 28 af, om informationerne er egnede som referencedata for de varierende cylindertryk ved cylinderens normale driftstilstand, og hvis dette er tilfældet kan disse tilbageføres til trin 21 og oplagres til senere brug ved 15 eventuel frafiltrering og analyse i de efterfølgende trin. Referencedataene kan opdateres, og der kan ved analysen ved opdatering ske en sammenligning med forudbestemte, forventede ændringer for at undgå, at en begyndende fejltilstand indbygges i referencedataene.Another example of the controller's processing of pressure measurement data is outlined in FIG. 9, where after filtering out noise and unwanted information in a step 27, an analysis can be made in a step 28 of whether the information is suitable as reference data for the varying cylinder pressures at the normal operating state of the cylinder and if so, they can be returned to step 21 and stored for later use by 15 possible filtering and analysis in subsequent steps. The reference data can be updated, and the analysis can be compared with predetermined, expected changes in order to avoid having an incipient error state built into the reference data.
20 Analysen i trin 28 kan ske ved hjælp af et intel ligent, selvlærende program, såsom et neuralt netværk og/eller et program med generiske algoritmer eller fuzzy-logic. Programmer af denne art er velkendte til tilstandsovervågning og analyse. Når en motor leveres 25 kan programmet være oplært og indjusteret ved hjælp af standard drifts- og fejltilstande for cylindrene i den pågældende motortype, og efter indkøringen af cylindrene kan programmet ved analyse af de levende informationer fra trykmåledata fra den kørende motor fore-30 tage finindjustering af programmet og bestemme referencedataene for den tilhørende cylinder. Når dette er sket, og styreenheden kører i normal drift, kan der i et trin 29 bestemmes informationer til brug ved styringen af motoren samt signaler til aktivering af 35 smøreenheden.The step 28 analysis can be done using an intel ligent, self-learning program, such as a neural network and / or a program with generic algorithms or fuzzy logic. Programs of this kind are well known for condition monitoring and analysis. When an engine is delivered 25, the program can be trained and adjusted using standard operating and fault conditions for the cylinders of that particular engine type, and after running in the cylinders, the program can fine-tune the analysis of the live pressure measurement data from the running engine. of the program and determine the reference data for the associated cylinder. When this has happened and the controller is operating in normal operation, in step 29, information for use in controlling the motor as well as signals for activating the lubricator may be determined.
17 DK 173533 B117 DK 173533 B1
Et i fig. 10 vist tilslutningselement 30 har en tilslutning 31 for smørerøret 12, der via en kanal 32 i tilslutningselementets hus 33 står i forbindelse med en afgangsåbning 34. I kanalen 32 er der en kontra-5 ventil 35, der åbner i retning af afgangsåbningen. En tryksensor 36 er beliggende i forbindelse med kanalen 32 mellem kontraventilen og afgangsåbningen. Tryksensoren er en standardkomponent og kan eksempelvis omfatte en strain-gauge. Det er naturligvis muligt at 10 placere tryksensoren som en selvstændig enhed, men sammenbygningen med tilslutningselementet giver god beskyttelse mod skadelige påvirkninger og en nem montering, idet et tilslutningselement normalt er påkrævet for at føre en smørekanal ind gennem cylinder-15 væggen, der kan være en væg i cylinder foring eller vægge i både en cylinderforing og en kølekappe.One in FIG. 10, a connection element 30 shown in the lubrication tube 12 communicates via a channel 32 in the housing element 33 of the connection element 34 with an outlet opening 34. In the channel 32 there is a counter-valve 35 which opens in the direction of the outlet opening. A pressure sensor 36 is located in connection with the channel 32 between the check valve and the outlet opening. The pressure sensor is a standard component and may comprise, for example, a strain gauge. Of course, it is possible to position the pressure sensor as an independent unit, but the assembly with the connection element provides good protection against harmful influences and an easy mounting, since a connection element is usually required to pass a lubrication duct through the cylinder wall which can be a wall in cylinder liner or walls in both a cylinder liner and a cooling jacket.
Forbrændingsmotoren kan også være en firtaktmotor og kan være med trunkstempler.The internal combustion engine can also be a four-stroke engine and can have trunk pistons.
Claims (19)
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK199900056A DK173533B1 (en) | 1999-01-18 | 1999-01-18 | Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element |
| GB0000941A GB2345738B (en) | 1999-01-18 | 2000-01-14 | A method of lubricating a cylinder in an internal combustion engine,and a cylinder lubricating system and a connecting member |
| DE10001518A DE10001518B4 (en) | 1999-01-18 | 2000-01-15 | Method for lubricating a cylinder in an internal combustion engine and a cylinder lubrication system and a connecting element |
| KR10-2000-0001844A KR100405373B1 (en) | 1999-01-18 | 2000-01-15 | A method of lubricating a cylinder in an internal combustion engine, and a cylinder lubricating system |
| CN00100991A CN1125237C (en) | 1999-01-18 | 2000-01-17 | Lubricating method for IC engine cylinder and cylinder lubricating system and connection piece |
| FI20000083A FI113488B (en) | 1999-01-18 | 2000-01-17 | Method for Lubrication of Internal Engine Cylinder and Lubrication System of Internal Engine Cylinder |
| JP2000008604A JP3411874B2 (en) | 1999-01-18 | 2000-01-18 | Cylinder lubrication method for internal combustion engine, cylinder lubrication system, and connecting member |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK5699 | 1999-01-18 | ||
| DK199900056A DK173533B1 (en) | 1999-01-18 | 1999-01-18 | Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| DK199900056A DK199900056A (en) | 1999-09-13 |
| DK173533B1 true DK173533B1 (en) | 2001-02-05 |
Family
ID=8089237
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK199900056A DK173533B1 (en) | 1999-01-18 | 1999-01-18 | Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JP3411874B2 (en) |
| KR (1) | KR100405373B1 (en) |
| CN (1) | CN1125237C (en) |
| DE (1) | DE10001518B4 (en) |
| DK (1) | DK173533B1 (en) |
| FI (1) | FI113488B (en) |
| GB (1) | GB2345738B (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE524665C2 (en) * | 2003-01-17 | 2004-09-14 | Volvo Lastvagnar Ab | Lubrication system for an internal combustion engine |
| KR100750542B1 (en) | 2004-03-31 | 2007-08-20 | 미츠비시 쥬고교 가부시키가이샤 | Internal combustion engine with cylinder lubricating system |
| JP4031772B2 (en) * | 2004-04-16 | 2008-01-09 | 三菱重工業株式会社 | Internal combustion engine with cylinder lubrication device |
| DE102005007406A1 (en) * | 2005-02-18 | 2006-08-24 | Dr.Ing.H.C. F. Porsche Ag | Method for controlling an engine oil pump |
| EP1767751B1 (en) * | 2005-09-23 | 2008-07-30 | Wärtsilä Schweiz AG | Cylinder lubricating device for an engine |
| KR101052555B1 (en) * | 2008-11-19 | 2011-07-29 | 경상대학교산학협력단 | Electronically Controlled Quill System of Cylinder Lubricator and Lubricating System Using the Same Set in a Large Two-stroke Diesel Engine |
| EP2194244A1 (en) * | 2008-12-02 | 2010-06-09 | Wärtsilä Schweiz AG | Lubricating device and method for lubricating a baring surface of a cylinder wall |
| JP5933217B2 (en) * | 2011-10-12 | 2016-06-08 | 株式会社Ihi | Two-cycle engine and method of lubricating two-cycle engine |
| US8739746B2 (en) * | 2012-01-31 | 2014-06-03 | Ford Global Technologies, Llc | Variable oil pump diagnostic |
| KR101506313B1 (en) * | 2012-05-15 | 2015-03-26 | 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 | Cylinder lubrication device |
| FR3029588B1 (en) * | 2014-12-03 | 2017-04-28 | Renault Sas | MANOCONTACT ARRANGEMENT IN A SOLENOID VALVE |
| CN105332762B (en) * | 2015-11-12 | 2017-10-03 | 哈尔滨工程大学 | A kind of boat diesel engine electric-control common-rail type Cylinder lubricating lubricating system |
| KR101704301B1 (en) * | 2015-12-10 | 2017-02-07 | 현대자동차주식회사 | Method and Engine for Preventing Piston Oil Up |
| KR200487868Y1 (en) * | 2016-08-29 | 2018-11-14 | 코프로멕 다이 캐스팅 에스.알.엘. 어 소시오 유니코 | Piston for a die-casting machine |
| CN107544345B (en) * | 2017-09-28 | 2019-08-02 | 中原工学院 | A kind of train wheel track curvilinear motion intelligent lubricating control system |
| JP7309110B2 (en) * | 2017-12-07 | 2023-07-18 | 株式会社三井E&S Du | engine system |
| FR3087888B1 (en) * | 2018-10-31 | 2020-10-09 | Safran Aircraft Engines | DEVICE AND METHOD FOR MONITORING THE LIFETIME OF A HYDRAULIC EQUIPMENT OF AN AIRCRAFT |
| AT524547B1 (en) * | 2021-06-28 | 2022-07-15 | Hoerbiger Wien Gmbh | Reciprocating compressor and method of operating a reciprocating compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK103218C (en) * | 1961-07-18 | 1965-11-29 | Loxhams Engineering Works Ltd | Lubricator for internal combustion engines. |
| CH544299A (en) * | 1971-10-27 | 1973-11-15 | Sulzer Ag | Device for measuring the pressure curve in the combustion chamber of a reciprocating internal combustion engine |
| DE3044255A1 (en) * | 1980-11-25 | 1982-06-24 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg | CYLINDER AND PISTON LUBRICATION DEVICE ON AN INTERNAL COMBUSTION ENGINE |
| JPS6081623A (en) * | 1983-10-13 | 1985-05-09 | Nissan Motor Co Ltd | Structure of change lever |
| DE4208025A1 (en) * | 1992-03-13 | 1993-09-16 | Alfred Siemer | Supply system for lubricant in farm vehicle - incorporates two distributors and microprocessor control unit. |
| JPH0681623A (en) * | 1992-09-01 | 1994-03-22 | Mitsubishi Heavy Ind Ltd | Cylinder lubricating system |
| DK173288B1 (en) * | 1996-10-11 | 2000-06-13 | Man B & W Diesel As | Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder |
-
1999
- 1999-01-18 DK DK199900056A patent/DK173533B1/en not_active IP Right Cessation
-
2000
- 2000-01-14 GB GB0000941A patent/GB2345738B/en not_active Expired - Lifetime
- 2000-01-15 KR KR10-2000-0001844A patent/KR100405373B1/en active IP Right Grant
- 2000-01-15 DE DE10001518A patent/DE10001518B4/en not_active Expired - Lifetime
- 2000-01-17 CN CN00100991A patent/CN1125237C/en not_active Expired - Lifetime
- 2000-01-17 FI FI20000083A patent/FI113488B/en not_active IP Right Cessation
- 2000-01-18 JP JP2000008604A patent/JP3411874B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| GB2345738B (en) | 2003-02-12 |
| KR20000076469A (en) | 2000-12-26 |
| KR100405373B1 (en) | 2003-11-12 |
| DK199900056A (en) | 1999-09-13 |
| FI20000083A0 (en) | 2000-01-17 |
| JP3411874B2 (en) | 2003-06-03 |
| GB2345738A (en) | 2000-07-19 |
| DE10001518B4 (en) | 2008-11-13 |
| JP2000213322A (en) | 2000-08-02 |
| CN1125237C (en) | 2003-10-22 |
| DE10001518A1 (en) | 2000-08-24 |
| CN1261644A (en) | 2000-08-02 |
| FI113488B (en) | 2004-04-30 |
| FI20000083A (en) | 2000-07-18 |
| GB0000941D0 (en) | 2000-03-08 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| B1 | Patent granted (law 1993) | ||
| PUP | Patent expired |
Expiry date: 20190118 |