DK173288B1 - Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder - Google Patents

Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder Download PDF

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Publication number
DK173288B1
DK173288B1 DK199601119A DK111996A DK173288B1 DK 173288 B1 DK173288 B1 DK 173288B1 DK 199601119 A DK199601119 A DK 199601119A DK 111996 A DK111996 A DK 111996A DK 173288 B1 DK173288 B1 DK 173288B1
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Denmark
Prior art keywords
cylinder
piston
lubricating oil
lubrication
pressure
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DK199601119A
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Danish (da)
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DK111996A (en
Inventor
Peer Bak
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Man B & W Diesel As
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Priority to DK199601119A priority Critical patent/DK173288B1/en
Publication of DK111996A publication Critical patent/DK111996A/en
Priority to DE19743955A priority patent/DE19743955B4/en
Priority to CN97120063A priority patent/CN1081726C/en
Priority to KR1019970052057A priority patent/KR100411409B1/en
Priority to JP27892797A priority patent/JP3382520B2/en
Application granted granted Critical
Publication of DK173288B1 publication Critical patent/DK173288B1/en
Priority to KR1020030034712A priority patent/KR100411834B1/en

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Classifications

    • 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
    • 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
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
    • F16N7/385—Central lubrication systems

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

DK 173288 B1 iDK 173288 B1 i

Opfindelsen angår en cylindersmøreenhed til en flercylindret forbrændingsmotor, der i hver cylinder har et frem- og tilbagegående stempel, hvis stempelringe glider på indersiden af cylunderforingen, hvilken 5 smøreenhed forsyner flere smøresteder på foringens inderside med afmålte doseringer af smøreolie ved hjælp af et antal doseringsstempler, der er længdeforskydelige i tilhørende doseringscylindre.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a cylinder lubrication unit for a multi-cylinder internal combustion engine having in each cylinder a reciprocating piston whose piston rings slide on the inside of the cylinder liner, which lubricates several lubrication points on the inside of the liner with metered doses of lubricating oil. there are longitudinally displaceable in associated metering cylinders.

En sådan cylindersmøringsenhed kendes fra DE-A1-28 10 27 626, hvor doseringsstemplerne er placeret i en række ved bunden af en smøreoliebeholder, der indeholder en aksel, der ud for hvert stempel bærer en drejearm, hvis nedre ende ligger ud for det tilhørende stempel. Ud for den øvre ende af hver drejearm er der en stilleskrue, 15 der begrænser drejningen af drejearmen. Ved at indstille stilleskruen fastlægges udgangsstillingen for det tilhørende stempel og dermed slaglængden for stemplet. Stemplerne drives i en frem- og tilbagegående bevægelse ved hjælp af en roterende kamaksel, der er 20 således lejret i smøreoliebeholderen, at kammen påvirker den bort fra doseringsstemplet vendende side af drejearmens nedre ende. Kamakslen roterer synkront med motorens krumtapaksel og frembringer et doseringsslag for hver motorcyklus, dvs. et slag per omdrejning af 25 motorens krumtapaksel. Hvis der i en driftstilstand for motoren ikke er behov for den maksimale smøreoliemængde, der leveres ved hvert slag af doseringsstemplet, kan et drejeligt anslag bringes til anlæg mod den øvre ende af drejearmen, så doseringsstemplet ikke føres 30 tilbage til udgangsstillingen og dermed er forhindret i at levere olie ved den efterfølgende påvirkning fra kammen på kamakslen.Such a cylinder lubrication unit is known from DE-A1-28 10 27 626, wherein the metering pistons are positioned in a row at the bottom of a lubricating oil container containing a shaft carrying for each piston a pivot arm, the lower end of which lies opposite the piston. . Beside the upper end of each swivel arm there is a adjusting screw 15 which restricts the swivel of the swivel arm. By adjusting the set screw, the starting position of the associated piston is determined and thus the stroke length of the piston. The pistons are driven in a reciprocating motion by means of a rotary cam shaft 20 so housed in the lubricating oil container that the cam acts on the side of the dosing piston facing away from the lower end of the pivot arm. The camshaft rotates synchronously with the engine crankshaft and produces a metering stroke for each motor cycle, ie. one stroke per revolution of the 25 engine crankshaft. If, in an operating state of the engine, the maximum amount of lubricating oil supplied at each stroke of the metering plunger is not required, a swivel stop may be brought into contact with the upper end of the swivel arm so that the metering plunger is not returned to its initial position and thus prevented from to supply oil by the subsequent action of the cam on the camshaft.

Smøreapparatet af denne type er opbygget af mange mekaniske dele og er langsomtvirkende, fordi dosering-35 stemplerne kun kan aktiveres en gang for hver passage 2 DK 173288 B1 af kammen på kamakslen, der roterer synkront med motorens krumtapaksel. Det er desuden en ulempe, at der skal være en mekanisk drivforbindelse mellem krumtapakslen og kamakslen i smøreapparatet. En yderligere 5 ulempe er, at doseringscylindrene fyldes med smøreolie via en kontraventil, hvilket betyder, at smøreoliens viskocitet indvirker på fyldningsgraden i doseringscylindrene. Det er derfor normalt blevet anset for påkrævet at anvende opvarmning af smøreolien i smøreap-10 paratet for at opnå, at den ønskede leveringsmængde så vidt muligt er uafhængig af oliens tilgangstemperatur og af oliens kvalitet.The lubricator of this type is made up of many mechanical parts and is slow acting because the dosing pistons can be actuated only once for each passage of the cam on the camshaft which rotates synchronously with the crankshaft of the motor. In addition, there is a disadvantage that there must be a mechanical drive connection between the crankshaft and the camshaft in the lubricator. A further 5 disadvantage is that the metering cylinders are filled with lubricating oil via a non-return valve, which means that the viscosity of the lubricating oil affects the filling degree of the metering cylinders. Therefore, it has usually been considered necessary to use heating of the lubricating oil in the lubricant to achieve that the desired quantity of delivery is as far as possible independent of the oil supply temperature and the quality of the oil.

Der kendes endvidere en cylindersmøreenhed af det tyske fabrikat Vogele, hvor en trykkilde via en om-15 skifterventil med to stillinger og fire porte er forbundet med en doseringsenhed med to stempler, der har forskelligt tværsnitsareal i de tilhørende cylindre . Den ene ende af enten det ene eller det andet af stemplerne påføres et højt hydrauliktryk på ca. 70 bar, 20 der aktiverer enten det ene eller det andet af stemplerne, idet stemplet med mindst areal aktiveres ved normal drift, mens det andet stempel aktiveres i stedet for det første, når der ønskes en større leveringsmængde af smøreolie. De to ender af det aktive stempel 25 forbindes alternerende til enten en trykkilde eller et dræn for at udføre et leveringsslag. Leveringstrykket svarer til forsyningstrykket, og der sker en omskiftning fra det ene stempel til det andet, når leveringsmængden skal ændres. Det er en ulempe, at der anvendes 30 to doseringsstempler per smøringssted, og at forsyningstrykket til smøreenheden skal svare til leveringstrykket . Vandringen af doseringsstemplerne kan varieres for at ændre smøreenhedens leveringsmængde, men kun når motoren er ude af drift.Also known is a cylinder lubrication unit of the German brand Vogele, where a pressure source via a two-position switch valve and four ports is connected to a two-plunger dosing unit having different cross-sectional area in the associated cylinders. One end of either piston is applied to a high hydraulic pressure of approx. 70 bar, 20 which activates either one or the other of the pistons, the piston having the least area activated during normal operation, while the second piston is activated instead of the first when a larger supply of lubricating oil is desired. The two ends of the active piston 25 are alternately connected to either a pressure source or a drain to perform a delivery stroke. The delivery pressure corresponds to the supply pressure and there is a change from one piston to the other when the delivery quantity has to be changed. It is a disadvantage that 30 two dosage pistons are used per lubrication site and that the supply pressure of the lubrication unit must correspond to the delivery pressure. The migration of the dosing pistons can be varied to change the delivery quantity of the lubricant, but only when the engine is out of service.

35 Den foreliggende opfindelse har til formål at DK 173288 B1 3 anvise en meget driftssikker cylindersmøreenhed, der giver en hurtig og præcis dosering af den ønskede smøreoliemængde og er drevet på en måde, der er mekanisk uafhængig af motorens krumtapaksel.The object of the present invention is to provide a highly reliable cylinder lubrication unit which provides a fast and accurate dosing of the desired lubricating oil quantity and is driven in a manner that is mechanically independent of the engine crankshaft.

5 Med henblik herpå er cylindersmøreenheden ejen dommelig ved, at der på et aktuatorstempel er monteret flere doseringsstempler, at aktuatorstemplet er indsat i en hydraulikcylinder med et hydraulikkammer, som ved hjælp af en styreventil kan forbindes med en trykkilde 10 eller et dræn for hydraulikvæske for derved at længdeforskyde aktuatorstemplet med de tilhørende doserings-stempler, så disse udfører et leveringsslag, der tilfører smørestederne smøreolie.To this end, the cylinder lubrication unit is particularly doomed in that a plurality of metering pistons are mounted on an actuator piston, that the actuator piston is inserted into a hydraulic cylinder with a hydraulic chamber which can be connected to a pressure source 10 or a hydraulic fluid drain by means of a control valve. longitudinally displacing the actuator piston with the associated dosing pistons so that they perform a delivery stroke supplying the lubrication sites with lubricating oil.

Med denne udformning af cylindersmøreenheden er 15 anvendelsen af drejelige aksler med tilhørende akseltræk mv. undgået, hvilket giver en væsentlig forenkling af enheden, og samtidig er doseringsstemplernes drev i mekanisk henseende helt uafhængig af motorens krumtapaksel. Det er en betydelig fordel, at doserings-20 stemplerne er monteret på aktuatorstemplet og kan bevæges frem og tilbage af dette. I forhold til de tidligere anvendte cylindersmøreapparater er driftssikkerheden forbedret i og med, at der ikke anvendes en drejelig kam for hvert doseringsstempel, men i stedet 25 et enkelt aktuatorstempel, der bevæger alle doseringsstemplerne i enheden uden indbyrdes drejende dele. På drivsiden er der således kun et fælles element, i stedet for et element for hvert doseringsstempel. I forhold til en smøreenhed af typen Vdgele er smøreen-30 heden ifølge opfindelsen forenklet i betydelig grad, ved at der kun anvendes et doseringsstempel per smøre-sted, og ved at et fælles aktuatorstempel driver alle enhedens doseringsstempler.With this design of the cylinder lubrication unit, the use of swivel shafts with associated shaft features, etc. is used. avoided, which significantly simplifies the unit, and at the same time, the drive piston drives are mechanically independent of the engine crankshaft. It is a significant advantage that the metering pistons are mounted on the actuator piston and can be moved back and forth by this. Relative to the previously used cylinder lubricators, reliability is improved by not using a swivel cam for each metering plunger, but instead a single actuator plunger which moves all the metering plungers in the unit without mutually rotating parts. Thus, on the drive side, there is only one common element, instead of one element for each dosing piston. Compared to a Vdgele type lubrication unit, the lubrication unit of the invention is greatly simplified by using only one dosing piston per lubrication site and by a common actuator piston driving all of the unit's dosing pistons.

Det foretrækkes, at aktuatorstemplets tværsnits-35 areal i hydraulikcylinderen er væsentligt større end 4 DK 173288 B1 summen af de tilhørende doseringsstemplers tværsnitsarealer i doseringscylindrene. Aktuatorstemplets relativt store areal på drivsiden gør det muligt at frembringe et leveringstryk, der er større end cylin-5 dertrykket ved smørestedet på tidspunktet for smøreoliens indtræden i cylinderen, ved hjælp af et fordelagtigt lavt tryk i den drivende hydraulikvæske. I en særlig foretrukken udførelsesform er aktuatorstemplets tværsnitsareal mindst 4 gange, fortrinsvis fra 6 til 15 10 gange, større end summen af doseringsstemplernes arealer. Med disse arealforhold kan leveringstrykket være på eksempelvis 80 bar eller større med et drivtryk i hydraulikvæsken på eksempelvis 10 bar eller mindre.It is preferred that the cross-sectional area of the actuator piston in the hydraulic cylinder is substantially greater than the sum of the cross-sectional areas of the associated metering pistons in the metering cylinders. The relatively large area of the actuator piston on the drive side makes it possible to produce a delivery pressure greater than the cylinder pressure at the lubrication point at the time of the lubricating oil's entry into the cylinder by means of an advantageously low pressure in the driving hydraulic fluid. In a particularly preferred embodiment, the cross-sectional area of the actuator piston is at least 4 times, preferably from 6 to 15, 10 times greater than the sum of the areas of the dosing pistons. With these area conditions, the delivery pressure can be, for example, 80 bar or greater with a driving pressure in the hydraulic fluid of, for example, 10 bar or less.

Dette lave drivtryk kan tilvejebringes ved hjælp af 15 helt sædvanlige fødepumper, der har et fordelagtigt lille energiforbrug. Det lave hydrauliktryk tillader også, at ledningsnettet på leveringssiden ikke behøver at være dimensioneret og samlet som et højtrykssystem.This low propulsion pressure can be provided by means of 15 conventional feed pumps which have an advantageous low energy consumption. The low hydraulic pressure also allows the wiring on the supply side not to be sized and assembled as a high pressure system.

Styreventilen kan være elektronisk aktiverbar ved 20 hjælp af styresignaler modtaget fra en motor- eller cylinderstyreenhed. Elektronisk aktiverbare ventiler er hurtigtvirkende standardkomponenter, såsom solenoide-ventiler, der uden videre kan styres af en elektronisk controller, der også kan styre andre cylinderelementer.The control valve may be electronically actuated by means of control signals received from a motor or cylinder control unit. Electronically actuated valves are fast-acting standard components, such as solenoid valves, which can be easily controlled by an electronic controller that can also control other cylinder elements.

25 Når aktuatorstemplet er påvirket af en fjeder, hvis fjederkraft på aktuatorstemplet er rettet hen mod stemplets udgangsstilling, foretrækkes, at ventilen har tre porte og to stillinger. Hvis aktuatorstemplet i stedet føres tilbage til udgangsstillingen ved hjælp af 30 hydraulisk trykpåvirkning på en stempelflade, der vender bort fra udgangsstillingen, kan ventilen have fire porte og to stillinger.When the actuator piston is actuated by a spring whose spring force on the actuator piston is directed to the starting position of the piston, it is preferred that the valve has three ports and two positions. If, instead, the actuator piston is returned to its initial position by means of 30 hydraulic pressure on a piston surface facing away from the initial position, the valve may have four ports and two positions.

Det er ønskeligt, at cylindersmøreenheden kan omstilles til at levere en større mængde smøreolie ved 35 visse driftsforhold for motoren. En udførelsesform, der DK 173288 B1 5 er videreudviklet specielt med henblik på at muliggøre omstilling mellem forskellige leveringsmængder på simpel vis, er ejendommelig ved, at aktuatorstemplet er opdelt i et primært stempel og et sekundært stempel, at 5 det primære og det sekundære stempel mellem sig afgrænser et sekundært hydraulikkammer, at doserings-stemplerne er monteret på det sekundære stempel, at det sekundære stempel er forskydeligt sammen med det primære stempel fra en udgangsstilling til en mellem-10 stilling, hvori yderligere fremadgående forskydning af det primære stempel er blokeret af et stopelement, og at det sekundære stempel er forskydeligt fremad fra mellemstillingen, når trykket i det sekundære hydraulikkammer overstiger et forudbestemt aktiveringstryk.It is desirable that the cylinder lubrication unit can be adjusted to deliver a greater amount of lubricating oil under certain operating conditions of the engine. An embodiment that DK 173288 B1 5 is further developed specifically to enable conversion between different delivery quantities in a simple manner is peculiar in that the actuator piston is divided into a primary piston and a secondary piston, that the primary and the secondary piston between a secondary hydraulic chamber defines that the metering pistons are mounted on the secondary piston, that the secondary piston is displaceable together with the primary piston from an initial position to an intermediate position, wherein further forward displacement of the primary piston is blocked by a stop element and that the secondary piston is displaceable forward from the intermediate position when the pressure in the secondary hydraulic chamber exceeds a predetermined actuation pressure.

15 Når cylindersmøreenheden skal give en relativt lav leveringsmængde, holdes hydrauliktrykket lavere end aktiveringstrykket for det sekundære stempel. I denne driftstilstand forskyder aktuatorstemplet doseringsstemplerne en afstand svarende til afstanden fra 20 udgangsstillingen til mellemstillingen ved hver aktivering. Når motorens driftsforhold fører til, at cylinderforingen skal tilføres mere smøreolie, såsom ved ændring af motorens belastning, øges hydrauliktrykket til at være større end nævnte aktiveringstryk. Når 25 smøreenheden aktiveres, og det primære stempels bevægelse standses af stopelementet, er hydrauliktrykket ved smøreenhedens tilgang for hydraulikvæske og dermed også hydrauliktrykket i det sekundære hydraulikkammer større end aktiveringstrykket for det sekundære stem-3 0 pel, og dette vil derfor fortsætte med at drive doseringsstemplerne fremad, hvilket øger den doserede smøreoliemængde ved hver aktivering af smøreenheden.15 When the cylinder lubrication unit is to provide a relatively low delivery amount, the hydraulic pressure is kept lower than the activation pressure of the secondary piston. In this mode of operation, the actuator piston displaces the metering pistons a distance corresponding to the distance from the initial position to the intermediate position at each activation. When the engine operating conditions cause the cylinder liner to be fed more lubricating oil, such as by changing the engine load, the hydraulic pressure is increased to be greater than said activation pressure. When the lubrication unit is activated and the movement of the primary piston is stopped by the stop element, the hydraulic pressure at the lubricant's approach for hydraulic fluid and thus also the hydraulic pressure in the secondary hydraulic chamber is greater than the activation pressure of the secondary piston, and this will therefore continue to drive the metering pistons. forward, increasing the amount of lubricated oil at each lubrication unit activation.

Cylindersmøreenheden kan have et indre kammer, der står i forbindelse med en smøreoliekilde, og hver 35 doseringscylinder kan have en tilgangskanal, der ligger DK 173288 B1 6 foran stemplets forreste endeflade og forbinder doseringscylinderen med det indre kammer, når aktuator-stemplet står i sin udgangsstilling, og smøreolieleveringen fra doseringscylinderen begynder så, når dose-5 ringsstemplet passerer forbi tilgangskanalen og af-spaerrer denne. Med denne udformning af smøreenheden styrer doseringsstemplet åbningen og lukningen af tilgangskanalen, så denne kan udformes som en simpel, åben boring uden nogen kontraventil. Dette giver den 10 fordel, at leveringsmængden fra doseringscylinderen er uafhængig af smøreoliens viskocitet, fordi olievolumenet foran doseringsstemplet i det øjeblik, hvor tilgangskanalen afspærres helt af doseringsstemplet, er fuldstændig konstant og uafhængig af viskocitetsfor-15 hold. Doseringsstemplet skal før hvert leveringsslag være placeret i en udgangsstilling, hvor tilgangs-kanalen er i det mindste delvis blotlagt. Efter afslutningen af et leveringsslag trækkes doseringsstemplet tilbage til udgangsstillingen, og i løbet af 20 den tilbagegående bevægelse skabes der vakuum i doseringscylinderen foran doseringsstemplet. Når tilgangskanalen blotlægges, fyldes doseringscylinderen hurtigt med smøreolie, der strømmer fra det indre kammer via tilgangskanalen ind i doseringscylinderen 25 under samtidig udligning af vakuummet. Vakuummet fremskynder cylinderfyldningen, og dette er også en fordel ved udførelsesformen.The cylinder lubrication unit may have an inner chamber communicating with a lubricating oil source, and each dosing cylinder may have an inlet channel located in front of the front end face of the plunger and connecting the dosing cylinder to the inner chamber when the actuator plunger is in its initial position. , and the lubricating oil delivery from the metering cylinder then begins as the metering piston passes past the inlet channel and interlocks it. With this design of the lubrication unit, the metering plunger controls the opening and closing of the inlet channel so that it can be designed as a simple, open bore without any check valve. This gives the advantage that the amount of delivery from the metering cylinder is independent of the viscosity of the lubricating oil, because the oil volume in front of the metering piston at the moment the supply channel is completely blocked by the metering piston is completely constant and independent of viscosity ratio. The dosing plunger must, before each delivery stroke, be placed in an initial position where the access channel is at least partially exposed. At the end of a delivery stroke, the metering plunger is withdrawn to its initial position, and during the reciprocating movement, a vacuum is created in the metering cylinder in front of the metering plunger. When the inlet duct is exposed, the metering barrel is rapidly filled with lubricating oil flowing from the inner chamber via the inlet duct into the metering barrel 25 while simultaneously equalizing the vacuum. The vacuum speeds the cylinder filling and this is also an advantage of the embodiment.

I en særlig enkel udførelsesform er hydraulikvæsken smøreolie, det indre kammer er tilsluttet 30 drænporten for hydraulikvæske, og smøreolietrykket ved drænporten er større end det omgivende lufttryk uden for smøreenheden. Ved at anvende smøreolien som hydraulikvæske skal cylindersmøreenheden kun tilsluttes ét ledningssystem. Det indre kammer holdes fyldt med 35 smøreolie ved det forholdsvist lave tryk, der hersker DK 173288 Bl 7 ved drænporten, og aktuatorstemplet behøver ikke at være afskærmet over for dette tryk, der er væsentligt lavere end smøreoliens leveringstryk til smøreenheden.In a particularly simple embodiment, the hydraulic fluid is lubricating oil, the inner chamber is connected to the hydraulic fluid drainage port, and the lubricating oil pressure at the drainage port is greater than the ambient air pressure outside the lubrication unit. By using the lubricating oil as hydraulic fluid, the cylinder lubrication unit must only be connected to one conduit system. The inner chamber is filled with 35 lubricating oil at the relatively low pressure prevailing at the drainage port, and the actuator piston need not be shielded against this pressure which is substantially lower than the lubricating oil supply pressure to the lubrication unit.

Det er også en fordel, at en del af den smøreolie, der 5 har været anvendt til fremdrivning af aktuatorstemplet ledes ind i det indre kammer og forbruges i doserings-cylindrene, idet returoliemængden fra smøreenheden derved bliver mindst mulig.It is also an advantage that a portion of the lubricating oil which has been used to propel the actuator piston is fed into the inner chamber and consumed in the metering cylinders, thereby minimizing the return oil quantity from the lubricating unit.

Det kan være ønskeligt, at de doserede smøreolie-10 mængder til de smøresteder, der betjenes af én smøreenhed, er individuelt indstillelige, så smøreolieforbruget kan finindstilles og derved minimeres. For at opnå dette kan doseringscylindrene være monteret i smøreenheden med mulighed for individuel længdeindstilling af 15 monteringspositionen og/eller doseringsstemplerne kan være monteret på aktuatorstemplet med mulighed for individuel indstilling af afstanden mellem doserings-stemplets forende og aktuatorstemplet.It may be desirable that the dosed lubricating oil volumes for the lubrication sites operated by one lubrication unit are individually adjustable so that lubricating oil consumption can be fine tuned and thereby minimized. To achieve this, the metering cylinders may be mounted in the lubrication unit with the possibility of individual length adjustment of the mounting position and / or the metering pistons may be mounted on the actuator piston with the possibility of individually adjusting the distance between the end of the metering piston and the actuator piston.

Den foreliggende opfindelse angår endvidere en 20 fremgangsmåde til styring af smøreolieleveringsmængden fra en cylindersmøreenhed. Fremgangsmåden er ejendommelig ved, at et hydraulisk drevet aktuatorstempel anvendes til samtidig længdeforskydning af flere doseringsstempler, der er monteret på aktuatorstemplet, 25 at smøreenheden aktiveres ved mindst et forudbestemt tidspunkt i løbet af en motorcyklus i den tilhørende cylinder, så at aktuatorstemplet bevæges i det mindste en forudbestemt afstand i doseringsstemplernes længderetning, hvorved en grunddosis af smøreolie leveres fra 30 hvert doseringsstempel til dettes tilhørende smørested ved cylinderen, og at smøreenheden valgfrit kan styres således, mens motoren kører, at der til hvert smørested afgives en smøreoliemængde, der er større end grunddosisen.The present invention further relates to a method for controlling the amount of lubricating oil delivery from a cylinder lubrication unit. The method is characterized in that a hydraulically driven actuator piston is used for simultaneous longitudinal displacement of several dosage pistons mounted on the actuator piston, that the lubricator is actuated at least for a predetermined time during a motor cycle in the associated cylinder, so that the actuator piston is moved at least a predetermined distance in the longitudinal direction of the dosing pistons, whereby a basic dose of lubricating oil is supplied from each dosing piston to its associated lubricating point at the cylinder, and the lubricating unit can be optionally controlled so that the engine is running to deliver to each lubrication point a quantity of lubricating oil greater than the basic dose. .

35 Anvendelsen at et aktuatorstempel til at forskyde DK 173288 B1 8 flere doseringsstempler giver de ovennævnte fordele i form af en hurtigtvirkende, enkel og meget driftssikker smøreenhed. Aktiveringen af smøreenheden ved et forudbestemt tidspunkt af motorcyklussen muliggør, at 5 smøreolien tilføres, når stemplet i cylinderen befinder sig i en passende stilling ud for smørestederne, eksempelvis i en stilling, hvor stemplets afsnit med stempelringene befinder sig ud for de smøresteder, der tilføres smøreolie. Afgivelsen af en forudbestemt 10 grunddosis af smøreolie til hvert smørested ved den fremadgående bevægelse af aktuatorstemplet og muligheden for valgfrit at styre smøreenheden til at afgive en større smøreoliemængde opfylder de smørebehov, som forekommer ved cylindersmøring i en forbrændingsmotor, 15 nemlig at cylindersmøringen ved normal kørsel med konstant motorbelastning bør ske med en forholdsvis lav, veldefineret mængde, der typisk kan være proportional med motorbelastningen, mens der ved belastningsændringer eller ved konstaterede unormale cylin-20 derforhold kan afgives en større smøreoliemængde.The use of an actuator piston to displace multiple dosage pistons provides the above advantages in the form of a fast-acting, simple and highly reliable lubrication unit. The activation of the lubrication unit at a predetermined time of the motor cycle enables the lubricating oil to be supplied when the piston in the cylinder is in a suitable position next to the lubrication points, for example in a position where the piston section with the piston rings is adjacent to the lubrication points applied to lubricating oil. . The delivery of a predetermined 10 doses of lubricating oil to each lubrication site by the forward movement of the actuator piston and the option of optionally controlling the lubricant to deliver a greater lubricating oil quantity satisfies the lubrication requirements encountered by cylinder lubrication in an internal combustion engine, namely, the cylinder lubrication by normal lubrication. constant engine load should be done at a relatively low, well-defined amount, which may typically be proportional to the engine load, while a higher lubricating oil quantity can be delivered at load changes or at abnormal cylindrical conditions.

Det foretrækkes, at grunddosisen af smøreolie svarer til leveringsmængden til smørestedet i løbet af én motorcyklus ved en driftstilstand, hvor motoren har lavt smøringsbehov, og at den større smøreoliemængde 25 afgives fra smøreenheden ved driftstilstande, hvor motoren har større smøringsbehov, ved at doseringsstemplerne bevæges et længere stykke end den forudbestemte afstand, fortrinsvis som følge af at hydrauliktrykket i en trykkilde, der er tilsluttet aktuator-30 stemplets hydraulikkammer, øges til at være større end et forudbestemt aktiveringstryk. Når smøreenheden drives ved hjælp af denne fremgangsmåde, leveres den ønskede smøreoliemængde ved en enkelt aktivering af aktuatorstemplet, både når der skal doseres en lille og 35 en større smøreoliemængde. Dette giver en fordelagtig DK 173288 Bl 9 enkel styring af smøreenheden. Endvidere opnås med denne fremgangsmåde mulighed for at én enkelt smøreenhed kan anvendes til smøring på flere cylindre eller til smøring på samme cylinder ved flere smøresteder end 5 smøreenheden har doseringsstempler ved at der på smøreenhedens afgangsside er et antal omskiftningsventiler, der forbinder smøreenheden til de smøre-steder, hvortil smøreolien skal føres ved den aktuelle aktivering af aktuatorstemplet. Den hurtigtvirkende 10 smøreenhed kan i løbet af en brøkdel af en motorcyklus levere smøreolien til et første sæt af tilkoblede smøresteder, hvorefter omskiftningsventilen (-ventilerne) kan koble smøreenheden til et andet sæt af smøre-steder, hvorefter aktuatorstemplet aktiveres, osv.It is preferred that the base dose of lubricating oil corresponds to the delivery amount to the lubrication site during one engine cycle at an operating state where the engine has a low lubrication requirement and that the greater lubricating oil quantity 25 is dispensed from the lubricant at operating conditions where the engine has a greater lubrication requirement by the dosing pistons. longer than the predetermined distance, preferably due to the hydraulic pressure in a pressure source connected to the actuator 30 piston hydraulic chamber increasing to be greater than a predetermined actuation pressure. When the lubricating unit is operated by this method, the desired amount of lubricating oil is delivered by a single actuation of the actuator piston, both when a small and a large lubricating oil quantity is to be dosed. This provides an advantageous control of the lubrication unit. Furthermore, this method provides for the possibility that a single lubrication unit can be used for lubrication on several cylinders or for lubrication on the same cylinder at more lubrication points than the lubrication unit has metering pistons, because on the discharge side of the lubricant there are a number of switching valves connecting the lubricant to the lubrication unit locations to which the lubricating oil is to be supplied when the actuator piston is actuated. The fast acting lubricating unit can, during a fraction of a motor cycle, deliver the lubricating oil to a first set of switched lubrication points, after which the switching valve (s) can connect the lubricating unit to a second set of lubrication points, after which the actuator piston is activated, etc.

15 I en alternativ fremgangsmåde er grunddosisen af smøreolie mindre end leveringsmængden til smørestedet i løbet af én motorcyklus, aktuatorstemplet aktiveres til at foretage flere frem- og tilbagegående slag i løbet af en motorcyklus, og den større smøreoliemængde 20 afgives ved at aktuatorstemplet aktiveres et større antal gange i løbet af én motorcyklus. Den hurtigtvirkende smøreenhed kan aktiveres mange gange i løbet af en enkelt motorcyklus, og dette giver mulighed for at vælge grunddosisen per aktivering til at være mindre 25 end den mindste smøreoliemængde, der skal leveres i løbet af ét op- og nedadgående stempelslag i motorcylinderen og så aktivere aktuatorstemplet det antal gange, der giver en samlet levering, der svarer til smørebehovet. Når smørebehovet midlertidigt ændres som 30 følge af ændrede driftsforhold for motoren, kan cylindersmøringen tilpasses det aktuelle behov i små trin, der svarer til grunddosisen. Dette giver en meget præcis smøring ved alle driftsforhold og er let at styre ved hjælp af en elektronisk styreenhed, der 35 aktiverer smøreenheden det antal gange, der passer til DK 173288 B1 10 behovet.In an alternative method, the basic dose of lubricating oil is less than the amount of delivery to the lubrication site during one motor cycle, the actuator piston is activated to make several reciprocating blows during a motor cycle, and the larger lubricating oil quantity 20 is released by activating a larger number of actuator piston. times over one motor cycle. The fast-acting lubricating unit can be activated many times over a single engine cycle, and this allows the basic dose per activation to be less than 25 the minimum amount of lubricating oil to be delivered during one up and down stroke of the engine cylinder and then select activate the actuator piston the number of times that provides a total supply that corresponds to the lubrication requirement. When the lubrication requirement is temporarily changed as a result of changing engine operating conditions, the cylinder lubrication can be adjusted to the current need in small steps corresponding to the basic dose. This gives a very precise lubrication in all operating conditions and is easy to control by means of an electronic control unit which activates the lubrication unit the number of times that suits the DK 173288 B1 10 need.

Det foretrækkes, at et frem- og tilbagegående slag med maksimal slaglængde af aktuatorstemplet udføres på mindre end 60 ms, fortrinsvis mindre end 4 0 ms. Da en 5 fuld motorcyklus i en stor totakts krydshovedmotor typisk tager fra 0,25 til l s, kan cylindersmøreenheden i det mindste aktiveres fra 3 til 16 gange, fortrinsvis fra 6 til 25 gange, i løbet af en motorcyklus. Der kan med en sådan hurtigtvirkende smøreenhed foretages 10 smøring med meget præcise mængder og med meget præcis timing i forhold til stemplets position i cylinderen.It is preferred that a reciprocating stroke with maximum stroke length of the actuator piston be performed in less than 60 ms, preferably less than 40 ms. Since a 5 full motor cycle in a large two-stroke cross-head motor typically takes from 0.25 to 1 s, the cylinder lubrication unit can be activated at least from 3 to 16 times, preferably from 6 to 25 times, during a motor cycle. With such a fast acting lubricating unit, 10 lubrication can be done with very precise quantities and with very precise timing in relation to the position of the piston in the cylinder.

Det er også muligt at smøre i flere niveauer på en cylinder og/eller at smøre flere cylindre med samme smøreenhed. Det ses også umiddelbart, at smøreenheden 15 er tilstrækkeligt hurtigtvirkende til at foretage præcis smøring af cylindre i en firtaktsmotor, der eksempelvis kan udføre en fuld motorcyklus i løbet af fra 0,6 til 0,1 s.It is also possible to lubricate in several levels on one cylinder and / or to lubricate several cylinders with the same lubrication unit. It is also readily apparent that the lubricating unit 15 is sufficiently fast acting to perform precise lubrication of cylinders in a four-stroke engine which, for example, can perform a full engine cycle in the range of 0.6 to 0.1 seconds.

Eksempler på opfindelsen forklares herefter 20 nærmere med henvisning til den skematiske tegning, hvorpå fig. 1 viser et diagram over et cylindersmøreolie-system til en forbrændingsmotor, fig. 2 i længdesnit en skitse af en trykstyrings-25 enhed i smøreoliesystemet i fig. 1, fig. 3 et længdesnit gennem en første udførelses-form for en cylindersmøreenhed ifølge opfindelsen, fig. 4 og 5 et længdesnit gennem henholdsvis en anden og en tredie udførelsesform for en cylindersmøre-30 enhed ifølge opfindelsen, og fig. 6 et planbillede af et stempelbærende åg set fra snitlinien VI-VI i fig. 4.Examples of the invention are then explained in more detail with reference to the schematic drawing, in which fig. 1 is a diagram of a cylinder lubricating oil system for an internal combustion engine; FIG. 2 is a longitudinal sectional view of a pressure control unit of the lubricating oil system of FIG. 1, FIG. 3 is a longitudinal section through a first embodiment of a cylinder lubrication unit according to the invention; FIG. 4 and 5 show a longitudinal section through a second and a third embodiment of a cylinder lubrication unit according to the invention, respectively. 6 is a plan view of a piston bearing yoke seen from section line VI-VI of FIG. 4th

I fig. 1 ses et cylindersmøreoliesystem til en totakts krydshovedmotor, der kan være en fremdrivnings-35 motor i et skib eller en stationær elkraftproducerende DK 173288 B1 11 motor. Motoren er flercylindret, og for overskueligheds skyld er der i figuren kun vist to af motorens cylindre l. Cylinderforingens indre diameter kan typisk være beliggende i intervallet fra 25 til 100 cm, og det i 5 foringen op- og nedgående stempel kan typisk bevæges med en slaglængde beliggende i intervallet fra 90 til 300 cm og kan typisk være forsynet med fra tre til fem tryktætnende stempelringe, der glider på foringens inderside. Cylindersmøringen har til formål at op-10 retholde en smøreoliefilm på cylinderforingens inderside, så friktionen mellem stempelringene og foringens inderside holdes passende lav.In FIG. Figure 1 shows a cylinder lubricating oil system for a two-stroke cross-head motor, which may be a propulsion engine in a ship or a stationary electric power producing engine. The engine is multi-cylinder and for the sake of clarity, only two of the engine's cylinders are shown in the figure. The inner diameter of the cylinder liner can typically be in the range of 25 to 100 cm, and the piston up and down the piston can typically be moved with a strokes located in the range of 90 to 300 cm and can typically be provided with from three to five pressure-sealing piston rings sliding on the inside of the casing. The purpose of the cylinder lubrication is to maintain a lubricating oil film on the inside of the cylinder liner so that the friction between the piston rings and the inside of the liner is kept suitably low.

Hver cylinderforing har flere smøresteder 2, hvor der doseres smøreolie til foringens inderside ved hjælp 15 af en eller flere cylindersmøreenheder 3. En tilgangsledning 4 til hvert smørested har nær sin udmunding i foringen en kontraventil 5, der forhindrer cylindertrykket i at slå tilbage i ledningen, når der ikke leveres smøreolie. Af hensyn til fordelingen af smøre-20 olien i foringens omkredsretning er flere smøresteder, såsom fra to til fem eller flere, jævnt fordelt i en række i foringens omkredsretning. Foringen kan have flere sådanne rækker af smøresteder beliggende i forskellige niveauer i foringens længderetning. Smøre-25 enheden 3 kan forsyne samtlige smøresteder på den tilhørende cylinder med smøreolie, der kan for hver cylinder være to eller flere smøreenheder, der forsyner hver sin række af smøresteder, eller en smøreenhed kan forsyne smøresteder på flere cylindre, hvis der på 30 smøreenhedens afgangsside er en omskifteventil, der skiftevis forbinder smøreenheden med smørestederne på hver af de tilhørende cylindre.Each cylinder liner has a plurality of lubrication points 2, where lubricating oil is dosed to the inside of the liner by means of one or more cylinder lubricating units 3. An inlet line 4 for each lubrication site has a check valve 5 near its outlet in the liner which prevents cylinder pressure from regressing into the line. when no lubricating oil is supplied. For the sake of distributing the lubricating oil in the circumferential direction of the casing, several lubrication points, such as from two to five or more, are evenly distributed in a row in the circumferential direction of the casing. The liner may have several such rows of lubrication points located at different levels in the longitudinal direction of the liner. The lubricating unit 3 may provide all lubrication points on the associated cylinder with lubricating oil, which for each cylinder may be two or more lubricating units, each providing a number of lubrication points, or a lubricating unit may supply lubrication points on several cylinders if outlet side is a switch valve that alternately connects the lubrication unit to the lubrication points on each of the associated cylinders.

Ved normal motordrift ligger forbruget af smøreolie til cylindersmøring i intervallet fra 0,4 til 0,9 35 g/kWh, typisk omkring 0,6 g/kWh. Cylinderydelsen kan DK 173288 B1 12 eksempelvis ligge i intervallet fra 400 kW til 5800 kW, hvilket kræver en typisk smøreoliemængde per cylinder på fra 240 til 3480 g/h.In normal engine operation, the consumption of lubricating oil for cylinder lubrication ranges from 0.4 to 0.9 35 g / kWh, typically about 0.6 g / kWh. For example, the cylinder performance may range from 400 kW to 5800 kW, which requires a typical lubricating oil quantity per cylinder of 240 to 3480 g / h.

Cylindersmøreenhederne 3 er tilsluttet en trykkil-5 de for hydraulikvæske i form af en trykledning 6, der er forbundet med en afgangsledning 7 fra to motordrevne trykpumper 8, hvoraf den ene er aktiv og den anden er en reservepumpe, og et dræn for hydraulikvæske i form af en returledning 9, der leder overskydende olie til 10 en tank 10. Tanken 10 har en udluftning 11 og en påfyldningsledning 12. De to pumper 8 er på tilgangssiden parallelforbundne til en fødeledning 13 fra tanken 10, og i fødeledningen er der før hver pumpe en af spær rings vent il 14 og et grovfilter 15, det typisk 15 kan have en maskestørrelse på fra 100 til 200 μτη. På afgangssiden er trykpumperne 8 via hver sin kontraventil 16 parallelforbundne til trykledningen 6, og et finfilter 17 med en typisk maskestørrelse på fra 10 til 50 μτη sikrer olien passaende renhed. Pumperne 8 og de 20 tilhørende ventiler 14 styres af en elektronisk styreenhed 18, der ved hjælp af et antal ikke viste strømningsindikatorer indsat i ledningerne, eller som det beskrives nedenfor ved hjælp af trykket i ledningen 6, kan overvåge pumpernes driftstilstand. Hvis den aktive 25 pumpe svigter, omskifter styreenheden de to ventiler 14 og igangsætter reservepumpen. En akkumulator 19 udjævner eventuelle trykstød, som måtte forekomme i ledningen 6 ved aktiveringen af smøreenhederne 3.The cylinder lubricating units 3 are connected to a hydraulic fluid pressure source 5 in the form of a pressure line 6, which is connected to a discharge line 7 from two motor driven pressure pumps 8, one of which is active and the other a backup pump and a hydraulic fluid in the form of a return line 9 conducting excess oil to 10 a tank 10. The tank 10 has a vent 11 and a filling line 12. The two pumps 8 are parallel to the supply side 13 to a feed line 13 from the tank 10, and in the feed line there is before each pump. one of blocking valves 14 and a coarse filter 15, typically 15 may have a mesh size of from 100 to 200 μτη. On the discharge side, the pressure pumps 8 are connected via parallel check valve 16 to the pressure line 6, and a fine filter 17 with a typical mesh size of from 10 to 50 μτη ensures the purity of the oil. The pumps 8 and 20 associated valves 14 are controlled by an electronic control unit 18 which can monitor the operating condition of the pumps by means of a number of flow indicators not shown in the lines, or as described below by the pressure in the line 6. If the active 25 pump fails, the control unit switches the two valves 14 and initiates the backup pump. An accumulator 19 smoothes any pressure shocks that may occur in line 6 upon actuation of the lubricating units 3.

Den aktive pumpe 8 leverer en konstant mængdestrøm 30 af smøreolie ved et tryk, der er større end det højest ønskelige tryk ved tilgangen til smøreenhederne 3. Trykket i trykledning 6 nedreguleres til den øjeblikkeligt ønskede størrelse ved hjælp af en trykstyringsenhed 20, der i afhængighed af det ønskede tryk bort-35 dræner en større eller mindre del af smøreolien til DK 173288 B1 13 returledningen 9.The active pump 8 delivers a constant flow of lubricating oil 30 at a pressure greater than the highest desirable pressure at the access to the lubricating units 3. The pressure in pressure line 6 is down-regulated to the instantaneously desired size by a pressure control unit 20 which, depending on the desired pressure removes a greater or less part of the lubricating oil to the return line 9.

Trykstyringsenheden er vist mere detaljeret i fig.The pressure control unit is shown in more detail in FIG.

2 og er ved to porte 21 og 22 forbundet med henholdsvis trykledningen 6 og returledningen 9. En tryktransducer 5 23 måler løbende trykket i ledningen 6 og signaler herom afleveres til styreenheden 18 via en signalledning 24. En styreventil 25 med tre porte og to stillinger, såsom en magnetventil af solenoidetypen, kan forbinde porten 21 med enten en modtryksventil 26, der 10 åbner ved et indstilleligt, forudbestemt maksimumtryk, eller en modtryksventil 27, der åbner ved et indstilleligt, forudbestemt minimumstryk. Disse tryk indstilles til at svare til det højst ønskede og det lavest ønskede driftstryk i trykledningen 6. Som eksempler på 15 anvendelige tryk kan nævnes, at ventilen 26 kan åbne ved et tryk på 20 bar, og ventilen 27 kan åbne ved et tryk på 5 bar. Afstrømssiden af begge ventilerne 26, 27 er forbundet med porten 22. Styreventilen 25 modtager fra styreenheden 18 styresignaler via en ledning 28.2 and is connected at two ports 21 and 22 to the pressure line 6 and the return line 9 respectively. A pressure transducer 5 23 continuously measures the pressure in the line 6 and signals thereto are delivered to the control unit 18 via a signal line 24. A control valve 25 with three ports and two positions, such as a solenoid-type solenoid valve, the port 21 may connect to either a counterpressure valve 26 which opens at an adjustable, predetermined maximum pressure, or a counterpressure valve 27 which opens at an adjustable, predetermined minimum pressure. These pressures are set to correspond to the highest desired and lowest desired operating pressure in the pressure line 6. As examples of 15 usable pressures, it can be mentioned that the valve 26 can open at a pressure of 20 bar and the valve 27 can open at a pressure of 5 bar. The downstream side of both valves 26, 27 is connected to port 22. Control valve 25 receives control signals from control unit 18 via line 28.

20 Trykket i ledningen 6 kan styres til at antage ethvert ønsket niveau mellem maksimum- og minimumstrykkene ved at omskifte styreventilen 25 mellem dennes to stillinger med en passende skiftefrekvens. Hver gang ventilen 26 er forbundet med trykledningen 6, bringes 25 trykket heri nærmere til maksimumtrykket, og hver gang ventilen 27 er forbundet med trykledningen 6, bringes trykket heri nærmere minimumstrykket. Der er således tale om en af styreenheden 18 frekvensstyret trykregulering ved hjælp af styreventilen 25. Det foretrækkes 30 af hensyn til forbrændingsmotorens sikkerhed, at styreventilen 25 står i den stilling, hvor porten 21 er forbundet til ventilen 26, når der ikke løber en magnetiseringsstrøm i ledningen 28. Ved svigt i et element i den elektroniske trykstyring fører dette til, 35 at trykket i ledningen 6 indstiller sig på maksimum- 14 DK 173288 B1 trykket.The pressure in the conduit 6 can be controlled to assume any desired level between the maximum and minimum pressures by switching the control valve 25 between its two positions with a suitable switching frequency. Each time the valve 26 is connected to the pressure line 6, the pressure herein is brought closer to the maximum pressure, and each time the valve 27 is connected to the pressure line 6, the pressure herein is brought closer to the minimum pressure. Thus, it is a frequency controlled pressure control of the control unit 18 by means of the control valve 25. It is preferred for the sake of the safety of the internal combustion engine that the control valve 25 is in the position where the port 21 is connected to the valve 26 when no magnetizing current is flowing in. conduit 28. In the event of failure of an element in the electronic pressure control, this causes the pressure in conduit 6 to adjust to the maximum pressure.

Som alternativ til anvendelsen af pumper med fast leveringsmængde og trykstyring med en enhed af nævnte art kan pumperne styre trykket i ledningen 6 ved hjælp 5 af leveringsmængden. Trykstyringsenheden kan alternativt være en proportionalventil, der indstiller trykket i afhængighed af et spændingsniveau modtaget fra styreenheden.As an alternative to the use of fixed delivery pumps and pressure control with a unit of said kind, the pumps can control the pressure in the conduit 6 by means of 5 the supply quantity. Alternatively, the pressure control unit may be a proportional valve which adjusts the pressure depending on a voltage level received from the control unit.

Styreenheden 18 er tilsluttet en spændingsfor-10 syning indikeret ved en ledning 29, og den modtager via et antal ledninger 30-32 oplysning om motorens øjeblikkelige driftstilstand. Der kan eksempelvis være tale om, at ledningen 30 tilfører signaler for motorens belastning, eksempelvis et signal fra motorens regula-15 tor, at ledningen 31 tilfører signaler for krumtapakslens drejningsbevægelse, der eksempelvis kan stamme fra en såkaldt incremental encoder og kan indeholde information om krumtapakslens øjeblikkelige drejestil-ling, og at ledningen 32 tilfører signaler om eventuel-20 le specielle driftsforhold, der kan nødvendiggøre smøring med forhøjet oliemængde for en eller flere af motorens cylindre.The control unit 18 is connected to a voltage supply indicated by a line 29 and it receives via a number of lines 30-32 information about the current operating state of the motor. For example, the conduit 30 may provide signals for the engine load, for example, a signal from the motor controller, the conduit 31 supply signals for the crankshaft rotational movement which may, for example, originate from a so-called incremental encoder and may contain information about the crankshaft instantaneous turning position and the conduit 32 provides signals of any special operating conditions that may necessitate increased oil lubrication for one or more of the engine's cylinders.

Styreenheden kan endvidere fra tryktransduceren 24 modtage oplysning om det øjeblikkelige tryk i ledningen 25 6. Via ledninger 33, 34 og ikke viste ledninger til ventilerne 14 kan styreenheden 18 styre drivmotorerne for og tilkoblingen af trykpumperne 8. Styreventilen 25 styres som nævnt via ledningen 28 af styreenheden 18.The control unit can further receive information from the pressure transducer 24 about the instantaneous pressure in the line 25 6. Via lines 33, 34 and wires not shown for the valves 14, the control unit 18 can control the drive motors and the connection of the pressure pumps 8. The control valve 25 is controlled as mentioned via the line 28 by the control unit 18.

Via ledninger 35, 36 er styreenheden forbundet med en 30 styreventil 37 i hver smøreenhed 3. Hvis styreenheden detekterer unormale driftsforhold kan et alarmsignal afgives via en ledning 38. Af sikkerhedsmæssige grunde kan tryktransduceren 25 og eventuelt også andre komponenter i smøresystemet være dubleret ved hjælp af en 35 eller flere reservekomponenter af samme type, der kan DK 173288 B1 15 tage over i tilfælde af svigt i en komponent.Via wires 35, 36, the control unit is connected to a control valve 37 in each lubrication unit 3. If the control unit detects abnormal operating conditions, an alarm signal can be output via a line 38. For safety reasons, the pressure transducer 25 and possibly other components of the lubrication system can be duplicated by means of a 35 or more spare components of the same type that can take over in the event of a failure of a component.

Styreenhedens driftsovervågning af cylindersmør ingen kan eksempelvis omfatte en kontrol af, at der med tryktransduceren 25 detekteres en tryksvingning i 5 trykledningen 6 umiddelbart efter, at et aktiverings-signal er afgivet til en styreventil 37. Denne tryksvingning viser, at den tilhørende smøreenhed udfører et doseringsslag, som forbruger smøreolie fra ledningen 6. Hvis den forventede tryksvingning udebliver, kan 10 styreenheden afgive alarmsignal om en mulig defekt i en bestemt cylindersmøreenhed.For example, the control unit operating monitoring of cylinder butter none may comprise a check that a pressure fluctuation 25 is detected in the pressure line 6 immediately after an activation signal is delivered to a control valve 37. This pressure fluctuation shows that the associated lubricant performs a metering stroke. consuming lubricating oil from line 6. If the expected pressure fluctuation fails, the 10 control unit may sound an alarm signal of a possible defect in a particular cylinder lubrication unit.

Et eksempel på udformningen af cylindersmøreenheden 3 er vist i fig. 3. Styreventilen 37 er monteret i et hus 39, der omfatter en første part 39a med en 15 tilslutning 40 for trykledningen 6 og en tilslutning 41 for retur ledningen 9 og en anden part 39b med doseringscylindre 42 samt en dæksel- eller endepart 39c med en tilslutning 43 for hver af tilgangsledningerne 4 til de smøresteder, der samtidig tilføres olie fra do-20 seringscylindrene. Husparterne er boltet sammen ved hjælp af ikke viste bolte, der er isat fra dækselsiden og er skruet fast i gevindbundhuller i den første part 39a.An example of the design of the cylinder lubricant unit 3 is shown in FIG. The control valve 37 is mounted in a housing 39 comprising a first portion 39a having a connection 40 for the pressure line 6 and a connection 41 for the return line 9 and a second portion 39b with metering cylinders 42 as well as a cover or end portion 39c having a connection 43 for each of the inlet lines 4 to the lubrication points which are simultaneously supplied with oil from the metering cylinders. The housing parts are bolted together by bolts not shown which are inserted from the cover side and screwed into threaded holes in the first part 39a.

Et aktuatorstempel 44 er indsat i en som hydrau-25 likcylinder virkende udboring i den første part 39a, så stemplets endeflade og udboringen afgrænser et hydraulikkammer 45, der via en kanal 46 står i forbindelse med en afgangsport 47 i styreventilen. Stemplets symmetriakse forløber parallelt med længdeakserne i 30 doseringscylindrene. Styreventilen 37 har endvidere en tilgangsport 48, der står i vedvarende forbindelse med trykledningen 6, og en drænport 49, der står i vedvarende forbindelse med returledningen 9. En ventilglider 50 kan indtage to stillinger, nemlig den i figuren 3 5 viste, hvor afgangsporten 47 er i forbindelse med DK 173288 B1 16 drænporten 49, og en stilling, hvor afgangsporten er i forbindelse med tilgangsporten 48. Ventilglideren er af en trykfjeder 51 forbelastet til at indtage den førstnævnte stilling. Når en spole 52' magnetiseres, for-5 skydes ventilglideren hen til afspærring af porten 49.An actuator piston 44 is inserted into a bore acting as a hydraulic cylinder in the first portion 39a, so that the end face of the piston and the bore define a hydraulic chamber 45 which communicates via a channel 46 with a discharge port 47 in the control valve. The axis of symmetry of the piston runs parallel to the longitudinal axes of the 30 dosing cylinders. The control valve 37 further has an inlet port 48 which is in continuous communication with the pressure line 6 and a drainage port 49 which is in continuous communication with the return line 9. A valve slider 50 can occupy two positions, namely the one shown in Figure 35, where the outlet port 47 is in connection with DK 173288 B1 16 drainage port 49, and a position where the outlet port is in connection with the inlet port 48. The valve slider is preloaded by a pressure spring 51 to take the first position. When a coil 52 'is magnetized, the valve slider is shifted to shut off gate 49.

Stemplet 44 har i området uden for hydraulikcylinderen en radialt udragende krave, der virker som et åg 52, hvorpå doseringsstempler 53 er monteret. Doseringsstemplerne har i deres bagender to udragende kraver, 10 der griber fat på begge sider af stemplets krave 52, når doseringsstemplerne ved monteringen skubbes på plads i udefter åbne recesser 54 i stemplets krave 52, se i fig. 6, hvor det ene stempel 53 er fjernet for at vise den tilhørende recess 54. Denne monteringsmåde 15 fikserer doseringsstemplerne længdeuforskydeligt på aktuatorstemplet, men tillader løbende finindstilling af doseringstemplerne i radial- og omkredsretningen, så de opretholder fuld koaksialitet med doseringscylindrene 42 .Piston 44 has a radially projecting collar in the region outside the hydraulic cylinder acting as a yoke 52 on which metering pistons 53 are mounted. The dosing pistons have two protruding collars in their rear ends, 10 which grip both sides of the piston collar 52 when the dosing pistons are pushed into place in outwardly open recesses 54 in the piston collar 52, see FIG. 6, where one piston 53 is removed to show the associated recess 54. This mounting method 15 fixes the metering pistons longitudinally slidable on the actuator piston, but permits continuous fine-tuning of the metering pistons in the radial and circumferential directions to maintain full coaxiality with the metering cylinders 42.

20 Huset 39 har et indre kammer 55, der via åbninger 56 i aktuatorstemplet og en kanal 57 er i vedvarende strømningsforbindelse med tilslutningen 41 til returledningen, så trykket heri, der eksempelvis kan være beliggende i intervallet fra 1 til 3 bar, holder det 25 indre kammer fyldt med smøreolie. Kammeret 55 har en rundtgående not 58, der skærer doseringscylindrene, hvorved der på enkel vis til hver cylinder er frembragt en tilgangskanal, der forbinder doseringscylinderen med kammeret 55, når doseringsstemplerne står i den i 30 figuren viste udgangsstilling. Alternativt kan der til hver doseringscylinder være en udboring, som udgør nævnte kanal.The housing 39 has an inner chamber 55 which, through openings 56 in the actuator piston and a duct 57, is in continuous flow communication with the connection 41 to the return line, so that the pressure herein, for example being in the range of 1 to 3 bar, keeps the 25 internal. chamber filled with lubricating oil. The chamber 55 has a circular groove 58 which intersects the metering cylinders, thereby simply providing to each cylinder an inlet channel connecting the metering cylinder to the chamber 55 when the metering pistons are in the initial position shown in the figure 30. Alternatively, for each metering cylinder there may be a bore constituting said channel.

Hver doseringscylinder har ved sin afgangsende en kontraventil i form af en fjederbelastet kugle 59, der 35 sikrer, at smøreolien kun kan løbe ud af cylinderen.Each metering cylinder has at its exit end a non-return valve in the form of a spring-loaded ball 59 which ensures that the lubricating oil can only run out of the cylinder.

DK 173288 Bl 17DK 173288 Pg 17

Et stopelement 60 fastlægger aktuatorstemplets slaglængde ved hver aktivering ved at stemplets forende støder an mod stopelementets endeflade. En trykfjeder 61 forbelaster aktuatorstemplet i retning af udgangs-5 stillingen og holder stopelementet i anlæg mod en stilleskrue 62, der er indskruet i et gevind i endeparten 39c, så en yderligere indskruning af stilleskruen begrænser aktuatorstemplets slaglængde og dermed den af doseringsstemplerne leverede smøreoliemængde per 10 aktivering. Stilleskruen kan være forsynet med en skala, der viser sammenhængen mellem skruens indstilling og den leverede smøreoliemængde.A stop member 60 determines the stroke length of the actuator piston at each actuation by the front end of the piston abutting the end face of the stop element. A compression spring 61 preloads the actuator piston toward the starting position and holds the stop member against a set screw 62 which is screwed into a thread at the end portion 39c so that a further screw in the set screw limits the stroke length of the actuator piston and thus the amount of lubricating oil supplied by the dosing pistons. activation. The adjusting screw may be provided with a scale showing the relationship between the setting of the screw and the amount of lubricating oil supplied.

Når styreenheden afgiver signal om aktivering af smøreenheden magnetiseres spolen 52', og ventilglideren 15 50 sætter hydraulikkammeret i forbindelse med trykledningen 6, så tryksat smøreolie strømmer ind i kammeret 45 og længdeforskyder aktuatorstemplet og de herpå monterede doseringsstempler mod venstre i figuren. Ved den indledende bevægelse passerer doseringsstemplernes 20 forreste endeflader forbi tilgangskanalerne og af-spærrer disse, hvorefter leveringen af smøreolie til smørestederne begynder. Når aktuatorstemplet støder an mod stopelementet 60 standser leveringen. Derefter omstilles ventilglideren 50 til at forbinde returled-25 ningen 41 med trykkammeret 45, så olien heri presses ud og aktuatorstemplet tilbageføres til udgangsstillingen af fjederen 61. Ved den tilbagegående bevægelse af doseringsstemplerne opstår der vakuum i doserings-cylindrene 42, indtil stempelendeme blotter tilgangs-30 kanalerne, og smøreolie fra det indre kammer strømmer ind i cylindrene.When the control unit gives a signal to activate the lubrication unit, the coil 52 'is magnetized and the valve slider 15 50 connects the hydraulic chamber with the pressure line 6 so that pressurized lubricating oil flows into the chamber 45 and the longitudinal displacement actuator piston and the dosing piston mounted to the left in the figure. In the initial movement, the front end faces of the metering pistons 20 pass past the inlet channels and shut off, after which the delivery of lubricating oil to the lubrication sites begins. When the actuator piston abuts the stop element 60, the delivery stops. Thereafter, the valve slider 50 is switched to connect the return line 41 to the pressure chamber 45 so that the oil therein is squeezed out and the actuator piston is returned to the starting position of the spring 61. In the reciprocating movement of the metering pistons, vacuum is created in the metering cylinders 42 until the piston ends expose the inlet 30 channels, and lubricating oil from the inner chamber flows into the cylinders.

Ved den efterfølgende beskrivelse af alternative udførelsesformer anvendes samme henvisningstal som overfor for elementer med samme funktion, og kun 35 forskellene i forhold til den første udførelsesform DK 173288 B1 18 beskrives.In the following description of alternative embodiments, the same reference numerals are used as for elements having the same function, and only the 35 differences with respect to the first embodiment DK 173288 B1 18 are described.

I fig. 4 ses en udførelsesform, hvor aktuator-stemplet er opdelt i et primært stempel 44a og et sekundært stempel 44b. Det primære stempel er indsat i 5 en udboring i det sekundære stempel, så der mellem disse er afgrænset et ringformet sekundært hydraulikkammer 63, der via en langsgående kanal 64 i det primære stempel står i vedvarende forbindelse med hydraulikkammeret 45. Det primære stempel 44a har et 10 centralt element 65, der passerer gennem endevæggen i det sekundære stempel. Aktuatorstemplets rundtgående krave 52 er beliggende på det sekundære stempel 44b, hvorved doseringsstemplerne følger bevægelsen af dette.In FIG. 4 shows an embodiment in which the actuator piston is divided into a primary piston 44a and a secondary piston 44b. The primary piston is inserted into a bore in the secondary piston, so that there is defined between them an annular secondary hydraulic chamber 63 which, via a longitudinal channel 64 in the primary piston, is in continuous communication with the hydraulic chamber 45. The primary piston 44a has a 10 central element 65 passing through the end wall of the secondary piston. The circumferential collar 52 of the actuator piston is located on the secondary piston 44b, whereby the dosing pistons follow the movement thereof.

Når styreventilen 37 aktiveres, strømmer tryksat 15 smøreolie ind i begge hydraulikkamrene 45 og 63 og de to stempler længdeforskydes i en i det væsentlige fælles bevægelse mod venstre i figuren. Når endefladen på den centrale element 65 støder an mod stopelementet 60 blokeres den fremadgående bevægelse af det primære 20 stempel 44a. Det sekundære stempel befinder sig samtidig i en mellemstilling, i hvilken det er påvirket af trykkraften fra fjederen 61 og af en modsatrettet kraft, der fremkommer ved, at differenstrykket mellem olietrykkene i trykledningen 6 og i returledningen 9 25 indvirker på det ringformede areal, der udgør endevæggen i hydraulikkammeret 63.When the control valve 37 is actuated, pressurized 15 lubricating oil flows into both hydraulic chambers 45 and 63 and the two pistons are longitudinally displaced in a substantially joint movement to the left of the figure. When the end surface of the central member 65 abuts the stop member 60, the forward movement of the primary piston 44a is blocked. The secondary piston is at the same time in an intermediate position in which it is influenced by the compressive force of the spring 61 and by an opposite force, which results from the differential pressure between the oil pressures in the pressure line 6 and in the return line 9 25 affecting the annular area constituting the end wall of the hydraulic chamber 63.

Hvis trykket i ledningen 6 er lavere end et forudbestemt aktiveringstryk, der netop får kraften på det ringformede areal til at udbalancere fjederkraften 30 med det sekundære stempel i mellemstillingen, vil det sekundære stempel ikke bevæge sig længere frem end til mellemstillingen.If the pressure in conduit 6 is lower than a predetermined actuation pressure that causes the force of the annular area to balance the spring force 30 with the secondary piston in the intermediate position, the secondary piston will not move further than to the intermediate position.

Hvis trykket i ledningen 6 er større end aktiveringstrykket, vil trykkraften på endefladen overvinde 35 fjederkraften, og den fremadgående bevægelse af det DK 173288 B1 19 sekundære stempel vil fortsætte efter blokeringen af det primære stempel. Trykkraften fra fjederen 61 vokser med fjederens sammentrykning. Der kræves derfor i kammeret 63 et højere tryk, kaldet sluttrykket, end 5 aktiveringstrykket for at forskyde det sekundære stempel helt hen til anlæg mod en skulder 66 på den anden part 39b. Ved at styre trykket i ledningen 6 til at antage værdier mellem nævnte aktiveringstryk og sluttrykket kan doseringen af smøreolie reguleres 10 trinløst mellem den grunddosis, der er leveret ved en forskydning til mellemstillingen, og den maksimale dosis, der opnås ved forskydningen af det sekundære stempel helt hen til anlæg mod skulderen 66.If the pressure in the conduit 6 is greater than the activation pressure, the compressive force on the end surface will overcome the spring force and the forward movement of the secondary piston will continue after the blocking of the primary piston. The compressive force of the spring 61 grows with the compression of the spring. Therefore, a higher pressure, called the final pressure, is required in the chamber 63 than the activation pressure to displace the secondary piston all the way to abutment against a shoulder 66 on the second portion 39b. By controlling the pressure in the conduit 6 to assume values between said activation pressure and the final pressure, the dosage of lubricating oil can be adjusted steplessly between the basic dose delivered by a displacement to the intermediate position and the maximum dose obtained by the displacement of the secondary piston completely. to shoulder shoulder 66.

Da aktuatorstemplet 44 i den første udførelsesform 15 vist i fig. 3 også forskydes mod fjederkraften kan der naturligvis også i denne udførelsesform foretages regulering af doseringsmxngden ved hjælp af styring af trykket i ledningen 6. Udførelsesformen i fig. 4 giver dog den fordel, at det ringformede areal på det sekun-20 dære stempel er væsentligt mindre end det fulde areal af aktuatorstemplet, hvilket medfører, at trykændringerne skal være større for at variere doseringsmængderne, og at styringen dermed bliver mere præcis.Since the actuator piston 44 in the first embodiment 15 shown in FIG. 3 can also be displaced against the spring force, of course, in this embodiment, the dosage quantity can also be adjusted by controlling the pressure in the line 6. The embodiment in fig. 4, however, provides the advantage that the annular area of the secondary piston is substantially smaller than the full area of the actuator piston, which means that the pressure changes must be greater to vary the dosage amounts and thus the control becomes more accurate.

Mellem de to husparter 39b og 39c er der i den 25 anden udførelsesform indsat en huspart 39d, der indeholder en strømningsdetektor ud for afgangsåbningen fra hver doseringscylinder. Strømningsdetektoren omfatter en fjederbelastet kugle 67, der forskydes bort fra den viste udgangsstilling, når smøreolie strømmer ud fra 30 cylinderen. Forskydningen af kuglen aktiverer en signalgiver, der afleverer aktiveringssignalet til styreenheden 18. Strømningsdetektoren giver verifikation af olieleveringen til de enkelte smøresteder.Between the two housing portions 39b and 39c, in the second embodiment, a housing portion 39d is provided containing a flow detector off the outlet port of each metering cylinder. The flow detector comprises a spring loaded ball 67 which is displaced away from the indicated position when lubricating oil flows out of the cylinder. The displacement of the ball activates a signal encoder that delivers the activation signal to the control unit 18. The flow detector provides verification of the oil delivery to the individual lubrication points.

Udførelsesformen vist i fig. 5 adskiller sig fra 35 de ovennævnte derved, at olietilførslen til doserings- DK 173288 B1 20 cylindrene 42 sker via tilgangskanaler 68, der fødes fra et kammer 69, der omgiver husparten 39b. Tilgangs-kanalerne er forsynet med kontraventiler 70. Denne udførelsesform er særlig anvendelig, hvis der som 5 hydraulikvæske bruges en anden væske end smøreolie, såsom en tyndere hydraulikolie.The embodiment shown in FIG. 5 differs from the above-mentioned in that the oil supply to the metering cylinders 42 takes place via inlet ducts 68 which are fed from a chamber 69 surrounding the housing portion 39b. The supply ducts are provided with check valves 70. This embodiment is particularly useful if a fluid other than lubricating oil such as a thinner hydraulic oil is used as a hydraulic fluid.

Detaljer fra de ovennævnte udførelsesformer kan kombineres til frembringelse af nye udførelsesformer. Således kan strømningsdetektoren valgfrit anvendes på 10 de tre viste grundudformninger. Der kan også inden for opfindelsens rammer foretages variationer af de elementer, der er vist på tegningen. Eksempelvis kan der i stedet for den mekaniske fjeder 61 anvendes en luftfjeder eller hydraulisk tilbageføring. Styreventilen 15 kan endvidere være mekanisk eller pneumatisk drevet i stedet for den viste elektroniske udførelse. Hvis hydraulikvæsken ikke er smøreolie kan der stadigvæk anvendes et indre oliefyldt kammer, men dette må så forbindes til en selvstændig kilde for smøremiddel, og 20 der skal ikke være nogen kanal 57 til hydrauliksystemet .Details of the above embodiments can be combined to produce new embodiments. Thus, the flow detector can optionally be applied to the three basic designs shown. Variations of the elements shown in the drawing can also be made within the scope of the invention. For example, instead of the mechanical spring 61, an air spring or hydraulic return can be used. Furthermore, the control valve 15 may be mechanically or pneumatically driven in place of the electronic embodiment shown. If the hydraulic fluid is not lubricating oil, an internal oil-filled chamber can still be used, but this must then be connected to an independent source of lubricant, and there must be no channel 57 for the hydraulic system.

Claims (12)

1. Cy 1 i rider smør eenhed (3) til en flercylindret forbrændingsmotor, der i hver cylinder (1) har et frem-og tilbagegående stempel, hvis stempelringe glider på 5 indersiden af cylinderforingen, hvilken smøreenhed forsyner flere smøresteder (2) på foringens inderside med afmålte doseringer af smøreolie ved hjælp af et antal doseringsstempler, der er længdeforskydelige i tilhørende doseringscylindre (42), kendeteg-10 n e t ved, at der på et aktuatorstempel (44; 44a, 44b) er monteret flere doseringsstempler (53), at aktuator-stemplet er indsat i en hydraulikcylinder med et hydraulikkammer (45), som ved hjælp af en styreventil (37) kan forbindes med en trykkilde eller et dræn for 15 hydraulikvæske for derved at længdeforskyde aktuator-stemplet med de tilhørende doseringsstempler, så disse udfører et leveringsslag, der tilfører smørestederne smøreolie.1. Cy 1 in rider lubricating unit (3) for a multi-cylinder internal combustion engine having in each cylinder (1) a reciprocating piston whose piston rings slide on the inside of the cylinder liner, which lubricates several lubrication points (2) on the liner inside with metered doses of lubricating oil by means of a plurality of dosing pistons longitudinally displaceable in associated dosing cylinders (42), characterized in that a plurality of dosing pistons (53) are mounted on an actuator piston (44; 44a, 44b). the actuator plunger is inserted into a hydraulic cylinder with a hydraulic chamber (45) which can be connected by means of a control valve (37) to a pressure source or drain for hydraulic fluid, thereby displacing the actuator plunger with the corresponding dosing plungers for length. a supply stroke which supplies lubricating oil to the lubrication points. 2. Cylindersmøreenhed ifølge krav 1, kende- 20 tegnet ved, at aktuatorstemplets (44; 44a) tværsnitsareal i hydraulikcylinderen er væsentligt større end summen af de tilhørende doseringsstemplers (53) tværsnitsarealer i doseringscylindrene (42).Cylinder lubrication unit according to claim 1, characterized in that the cross-sectional area of the actuator piston (44; 44a) in the hydraulic cylinder is substantially larger than the sum of the cross-sectional areas of the associated dosing pistons (53) in the dosing cylinders (42). 3. Cylindersmøreenhed ifølge krav 2, kende-25 tegnet ved, at aktuatorstemplets tværsnitsareal er mindst 4 gange, fortrinsvis fra 6 til 15 gange, større end summen af doseringsstemplernes arealer.Cylinder lubrication unit according to claim 2, characterized in that the cross-sectional area of the actuator piston is at least 4 times, preferably from 6 to 15 times, greater than the sum of the areas of the dosing pistons. 4. Cylindersmøreenhed ifølge et af kravene 1-3, kendetegnet ved, at styreventilen (37), der 30 hensigtsmæssigt er en ventil med tre porte og to stillinger, er elektronisk aktiverbar ved hjælp af styresignaler modtaget fra en motor- eller cylinderstyreenhed (18) .Cylinder lubrication unit according to one of claims 1-3, characterized in that the control valve (37), which is suitably a valve with three ports and two positions, is electronically actuated by means of control signals received from a motor or cylinder control unit (18). . 5. Cylindersmøreenhed ifølge et af kravene 1-4, 35 kendetegnet ved, at aktuatorstemplet er i DK 173288 B1 ί 22 opdelt i et primært stempel {44a) og et sekundært , stempel (44b), at det primære og det sekundære stempel mellem sig afgrænser et sekundært hydraulikkammer (63) , at doseringsstemplerne er monteret på det sekundære 5 stempel, at det sekundære stempel er forskydeligt sammen med det primære stempel fra en udgangsstilling til en mellemstilling, hvori yderligere fremadgående forskydning af det primære stempel er blokeret af et stopelement (60), og at det sekundære stempel er 10 forskydeligt fremad fra mellemstillingen, når trykket i det sekundære hydraulikkammer overstiger et forudbestemt aktiveringstryk.Cylinder lubrication unit according to any one of claims 1-4, characterized in that the actuator piston is divided into a primary piston {44a) and a secondary piston (44b) in that the primary and the secondary piston between themselves a secondary hydraulic chamber (63) defines that the metering pistons are mounted on the secondary piston, that the secondary piston is slidable together with the primary piston from an initial position to an intermediate position wherein further forward displacement of the primary piston is blocked by a stop member ( 60) and that the secondary piston is displaceable forwardly from the intermediate position when the pressure in the secondary hydraulic chamber exceeds a predetermined activation pressure. 6. Cylindersmøreenhed ifølge et af kravene 1-5, kendetegnet ved, at enheden (3) har et indre , 15 kammer (55) , der står i forbindelse med en smøreolie kilde, at hver doseringscylinder har en tilgangskanal (58), der ligger foran stemplets (53) forreste endeflade og forbinder doseringscylinderen med det indre • kammer, når aktuatorstemplet står i sin udgangsstil-20 ling, og at smøreolieleveringen fra doseringscylinderen begynder, når doseringsstemplet passerer forbi tilgangskanalen og afspærrer denne.Cylinder lubrication unit according to one of claims 1-5, characterized in that the unit (3) has an inner, 15 chamber (55) which communicates with a lubricating oil source, that each metering cylinder has an inlet channel (58) located in front of the piston (53) front face and connecting the metering cylinder to the inner chamber when the actuator piston is in its initial position, and the lubricating oil delivery from the metering cylinder begins as the metering piston passes past the inlet channel and closes it. 7. Cylindersmøreenhed ifølge krav 6, kendetegnet ved, at hydraulikvæsken er smøreolie, at 25 det indre kammer (55) er tilsluttet drænporten (49) for hydraulikvæske, og at smøreolietrykket ved drænporten er større end det omgivende lufttryk uden for smøreenheden (3) .Cylinder lubrication unit according to claim 6, characterized in that the hydraulic fluid is lubricating oil, that the inner chamber (55) is connected to the drainage port (49) for hydraulic fluid and that the lubricating oil pressure at the drainage port is greater than the ambient air pressure outside the lubrication unit (3). 8. Cylindersmøreenhed ifølge et af kravene 1-7, 30 kendetegnet ved, at doseringscylindrene er monteret i smøreenheden med mulighed for individuel • længdeindstilling af monteringspositionen og/eller doseringsstemplerne er monteret på aktuatorstemplet (44; 44a, 44b) med mulighed for individuel indstilling 35 af afstanden mellem doseringsstemplets forende og f DK 173288 B1 23 aktuatorstemplet.Cylinder lubrication unit according to one of claims 1-7, 30, characterized in that the metering cylinders are mounted in the lubrication unit with the possibility of individual length adjustment of the mounting position and / or the metering pistons are mounted on the actuator piston (44; 44a, 44b) with the possibility of individual adjustment 35. of the distance between the front of the dosing piston and the actuator piston. 9. Fremgangsmåde til styring af smøreo lie leve-ringsmængden fra en cylindersmøreenhed (3), kende -tegnet ved, at et hydraulisk drevet aktuator- 5 stempel (44; 44a, 44b) anvendes til samtidig læng deforskydning af flere doseringsstempler (53), der er monteret på aktuatorstemplet, at smøreenheden aktiveres ved mindst et forudbestemt tidspunkt i løbet af en motorcyklus i den tilhørende cylinder (1), så at 10 aktuatorstemplet bevæges i det mindste en forudbestemt afstand i doseringsstemplernes længderetning, hvorved en grunddosis af smøreolie leveres fra hvert doserings-stempel (53) til dettes tilhørende smørested (2) ved cylinderen, og at smøreenheden valgfrit kan styres 15 således, mens motoren kører, at der til hvert smørested afgives en smøreoliemængde, der er større end grunddosisen.Method for controlling the lubricating oil delivery amount from a cylinder lubricating unit (3), characterized in that a hydraulically driven actuator piston (44; 44a, 44b) is used for simultaneous long displacement of several dosing pistons (53), mounted on the actuator piston that the lubricator is actuated at least a predetermined time during a motor cycle in the associated cylinder (1) so that the actuator piston is moved at least a predetermined distance in the longitudinal direction of the dosing pistons, thereby delivering a basic dose of lubricating oil from each dosing piston (53) to its associated lubrication site (2) at the cylinder, and the lubricating unit can be optionally controlled such that while the engine is running, a lubricating oil quantity greater than the basic dose is delivered to each lubrication site. 10. Fremgangsmåde ifølge krav 9,kendetegne t ved, at grunddosisen af smøreolie svarer til 20 leveringsmængden til smørestedet i løbet af én motorcyklus ved en driftstilstand, hvor motoren har lavt smøringsbehov, og at den større smøreoliemængde afgives fra smøreenheden ved driftstilstande, hvor motoren har større smøringsbehov, ved at doseringsstemplerne (53) 25 bevæges et længere stykke end den forudbestemte afstand, fortrinsvis som følge af at hydrauliktrykket i en trykkilde, der er tilsluttet aktuatorstemplets hydraulikkammer (45; 45, 63), øges til at være større end et forudbestemt aktiveringstryk. 3 0Method according to claim 9, characterized in that the basic dose of lubricating oil corresponds to the delivery amount to the lubrication site during one engine cycle at an operating state where the engine has a low lubrication requirement, and that the greater lubricating oil quantity is delivered from the lubricant at operating conditions where the engine has greater lubrication requirement by moving the metering pistons (53) 25 a longer distance than the predetermined distance, preferably due to the hydraulic pressure of a pressure source connected to the actuator piston hydraulic chamber (45; 45, 63) increasing to a greater than a predetermined distance activation pressure. 3 0 11. Fremgangsmåde ifølge krav 9,kendeteg- n e t ved, at grunddosisen af smøreolie er mindre end leveringsmængden til smørestedet i løbet af én motorcyklus, at aktuatorstemplet (44; 44a, 44b) aktiveres til at foretage flere frem- og tilbagegående slag i 35 løbet af en motorcyklus, og at den større smøreolie- DK 173288 B1 24 mængde afgives ved at aktuatorstemplet aktiveres et større antal gange i løbet af én motorcyklus.Method according to claim 9, characterized in that the basic dose of lubricating oil is less than the amount of delivery to the lubrication site during one motor cycle, that the actuator piston (44; 44a, 44b) is activated to make several reciprocating blows in the course of the race. of the motor cycle and that the greater amount of lubricating oil is released by activating the actuator piston a large number of times during one motor cycle. 12. Fremgangsmåde ifølge et af kravene 9-11, kendetegnet ved, at et frem- og tilbagegåen-5 de slag med maksimal slaglængde af aktuatorstemplet (44; 44a, 44b) udføres på mindre end 60 ms, fortrinsvis mindre end 40 ms. 10Method according to one of claims 9-11, characterized in that a reciprocating stroke with maximum stroke length of the actuator piston (44; 44a, 44b) is performed in less than 60 ms, preferably less than 40 ms. 10
DK199601119A 1996-10-11 1996-10-11 Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder DK173288B1 (en)

Priority Applications (6)

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DK199601119A DK173288B1 (en) 1996-10-11 1996-10-11 Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder
DE19743955A DE19743955B4 (en) 1996-10-11 1997-10-04 Cylinder lubrication device for a multi-cylinder internal combustion engine and method for regulating the release of lubricating oil
CN97120063A CN1081726C (en) 1996-10-11 1997-10-10 Cylinder lubrication unit for multicylinder internal combustion engine, and method for controlling dosage from cylinder lubrication unit
KR1019970052057A KR100411409B1 (en) 1996-10-11 1997-10-10 Cylinder Lubrication System for Multi-cylinder Internal Combustion Engine and Lubricant Flow Rate Control Method Therefrom
JP27892797A JP3382520B2 (en) 1996-10-11 1997-10-13 Cylinder lubrication device for multi-cylinder internal combustion engine
KR1020030034712A KR100411834B1 (en) 1996-10-11 2003-05-30 A cylinder lubrication system for a multicylinder internal combustion engine

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DK111996 1996-10-11
DK199601119A DK173288B1 (en) 1996-10-11 1996-10-11 Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder

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DK173288B1 true DK173288B1 (en) 2000-06-13

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JP3382520B2 (en) 2003-03-04
KR100411834B1 (en) 2003-12-18
CN1183509A (en) 1998-06-03
CN1081726C (en) 2002-03-27
KR100411409B1 (en) 2004-04-28
DK111996A (en) 1997-06-04
KR19980032736A (en) 1998-07-25
DE19743955A1 (en) 1998-04-16
JPH10121931A (en) 1998-05-12
DE19743955B4 (en) 2004-06-03

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