DK176924B1 - Hydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubrication - Google Patents
Hydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubrication Download PDFInfo
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- DK176924B1 DK176924B1 DKPA200701104A DKPA200701104A DK176924B1 DK 176924 B1 DK176924 B1 DK 176924B1 DK PA200701104 A DKPA200701104 A DK PA200701104A DK PA200701104 A DKPA200701104 A DK PA200701104A DK 176924 B1 DK176924 B1 DK 176924B1
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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
- F01M13/00—Crankcase ventilating or breathing
- F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
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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
- F01M13/00—Crankcase ventilating or breathing
- F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
- F01M2013/0422—Separating oil and gas with a centrifuge device
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Description
DK 176924 B1 iDK 176924 B1 i
Hydraulisk smøreapparat til et doseringssystem for cylindersmøreolie samt hydraulikstempel til brug i sådan smøreapparatHydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubricator
Opfindelsens områdeFIELD OF THE INVENTION
Den foreliggende opfindelse angår et hydraulisk smøreapparat til et doseringssystem 5 for cylindersmøreolie, for eksempel i skibsmotorer, hvilket doseringssystem omfatter et hydrauliskdrevet smøreapparat til levering af smøreolie og omfattende mindst et hydraulikstempel og som kan sættes under tryk med hydraulikolie, et antal doseringsstempler samt en fordelerplade, der ved sin ene side er i kontakt med nævnte doseringsstempler, og som ved sin anden side er i kontakt med nævnte mindst ene hydrau-10 likstempel til forskydning af fordelerpladen for aktivering af doseringsstempleme.The present invention relates to a hydraulic lubricator for a cylinder lubricating oil dispensing system, for example in ship engines, which dispensing system comprises a hydraulically lubricated lubricating oil delivery apparatus and comprising at least one hydraulic piston and which can be pressurized with hydraulic oil, a plurality of dispensing pistons and a distributor plate. which, on one side, is in contact with said dosing pistons and which on its other side is in contact with said at least one hydraulic piston for displacing the distributor plate for activating the dosing pistons.
Opfindelsen angår endvidere et hydraulikstempel til brug i et sådan smøreapparat. Opfindelsens baggrund 1 traditionelle cylindersmøringssystemer, hovedsageligt til store 2-slagsdieselmotorer, 15 anvendes der to eller flere centrale smøreapparater, der hver sørger for smøring af steder på en enkelt eller flere cylindere, dvs. ved tilførsel af mængder af olie under tryk gennem respektive forbindelsesledninger til de forskellige steder, der skal smøres, med relevante tidsintervaller. Se for eksempel DK/EP 0678152. Disse relevante intervaller kan typisk være, når stempelringene er anbragt modsat det relevante smø-20 ringssted i løbet af kompressionsslaget, når stemplet bevæger sig opad.The invention further relates to a hydraulic piston for use in such a lubricator. BACKGROUND OF THE INVENTION In conventional cylinder lubrication systems, mainly for large 2-stroke diesel engines, two or more central lubricators are used, each providing lubrication of locations on a single or multiple cylinders, i. by applying quantities of oil under pressure through respective connecting lines to the various sites to be lubricated, at relevant time intervals. See, for example, DK / EP 0678152. These relevant intervals may typically be when the piston rings are positioned opposite the relevant lubrication site during the compression stroke as the piston moves upward.
Smøreapparateme er traditionelt udformet som pumpeenheder, der er monteret i nær tilslutning til deres respektive cylindre, og som er forbundet med et fødereservoir for smøreolie og med smøresteder i form af olieinjiceringsdyser på forskellige steder af 25 cylindervæggen. Hver pumpeenhed omfatter flere stempelpumper, der forsyner forskellige smøresteder med olie, og som drives af en fælles, roterende styreaksel med påsatte knaster. Ved akslens rotation samvirker knasterne med trykhoveder på respektive aksialt forskydelige stempler, der er fjederbelastede i retning mod styreakslen, således at stemplerne ved akslens rotation vil udføre frem- og tilbagegående bevægel-30 ser for aktivering af stempelpumpernes stempler.The lubricators are traditionally designed as pump units mounted in close proximity to their respective cylinders and connected to a lubricating oil reservoir and to lubrication points in the form of oil injection nozzles at various locations of the cylinder wall. Each pump unit comprises a plurality of piston pumps which supply different lubrication points with oil and which are driven by a common, rotary control shaft with attached lugs. In the rotation of the shaft, the camshafts interact with pressure heads on respective axially displaceable pistons spring-loaded in the direction of the steering shaft, so that the pistons, during rotation of the shaft, will perform reciprocating movements for actuation of the piston pump pistons.
DK 176924 B1 2DK 176924 B1 2
Smøreapparater har i en lang årrække arbejdet under den driftsbetingelse, at afgangstrykket fra stempelpumperne ikke har skullet være særligt stort, idet det er en fast standard, at olien skal injiceres i cylinderen under det opadgående returslag af motorstemplet, dvs. under kompressionsforløbet, men dog inden det efterfølgende arbejds-5 slag ved den antændte forbrænding. Det har herved været aktuelt at arbejde med injektions- eller pumpetryk af størrelsesordenen 10 bar.Lubricators have for a number of years worked under the operating condition that the discharge pressure from the piston pumps should not be very high, as it is a fixed standard that the oil must be injected into the cylinder during the upward return stroke of the motor piston, ie. during the compression process, but before the subsequent work-stroke of the ignited combustion. Hereby it has been relevant to work with injection or pump pressures of the order of 10 bar.
Indenfor de sidste år er det bragt i forslag at effektivisere smøringen ved at injicere olien gennem trykforstøvningsdyser for opnåelse af en olietågesmøring under stem-10 plets opadgående bevægelse. Herved tilføres olien dog ved et langt højere tryk til sikring af en fin forstøvning gennem trykforstøvningsdyser, f.eks. et tryk på op til 100 bar eller mere.In recent years, it has been proposed to streamline lubrication by injecting the oil through pressure atomizing nozzles to obtain an oil mist lubrication during piston upward movement. Hereby, however, the oil is supplied at a much higher pressure to ensure a fine atomization through pressure atomizing nozzles, e.g. a pressure of up to 100 bar or more.
Endvidere er der igennem de seneste år en tendens til at der - i højere grad - produce-15 res elektronisk baserede dieselmotorer, og på disse motorer har man ljemet det mekaniske træk, der traditionelt anvendes til at drive mekaniske smøreapparater.Furthermore, in recent years there has been a tendency - to a greater extent - to produce electronically based diesel engines, and on these engines have crippled the mechanical feature traditionally used to operate mechanical lubricators.
Smøresteder vil således som omtalt i nærværende ansøgning omfatte olieinjicerings-dyser og/eller trykforstøvningsdyser.Thus, as discussed in this application, lubrication sites will comprise oil injection nozzles and / or pressure spray nozzles.
20 I begge systemer er styreakslen drevet gennem en direkte eller indirekte mekanisk kobling med motorens krumtapaksel, hvorved det er muligt at etablere drivkraft til pumpeaktiveringen og samtidig opnå en synkronisering mellem motorens krumtapaksel og smøreapparatets styreaksel.In both systems, the steering shaft is driven through a direct or indirect mechanical coupling to the crankshaft of the motor, thereby enabling drive power to be applied to the pump actuation and at the same time to achieve synchronization between the crankshaft of the motor and the control shaft of the lubricator.
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En pumpeenhed kan for eksempel omfatte et kasseformet apparathus, hvorfra der udgår forbindelsesrør til smørestedeme på den tilhørende motorcylinder, f.eks. i et antal på 6-24.For example, a pump unit may comprise a box-shaped apparatus housing from which connecting pipes are provided to the lubrication points on the associated engine cylinder, e.g. in a number of 6-24.
30 Stemplerne betjenes traditionelt ved hjælp af aktiveringsknaster/vippearme på en gennemgående styreaksel, der roteres synkront med motorens krumtapaksel. Stemplerne er 5ederpåvirkede i retning mod aktiveringsknasteme. Der er tilvejebragt en stille-skrue, som definerer yderpositionen for en tilknyttet aktiveringsknast. Stilleskrueme DK 176924 B1 3 kan betjenes til fastlæggelse af individuelle operative slaglængder af stemplerne og dermed de tilhørende ydelser af de enkelte stempelpumper.30 The pistons are traditionally operated by means of actuating knobs / rocker arms on a continuous steering shaft that is rotated synchronously with the engine crankshaft. The pistons are actuated towards the actuating cams. A set screw is provided which defines the outer position of an associated actuator. The set screws DK 176924 B1 3 can be operated to determine individual operating strokes of the pistons and thus the associated services of the individual piston pumps.
Da cylindersmøreolien typisk skal doseres med én portion pr. motoromdrejning, er 5 den eneste mulighed for at afpasse doseringen at ændre på pumpernes slaglængde. Et system hertil er for eksempel beskrevet i dansk patentansøgning 4998/85. Dette system betjener sig af en kurveskivemekanisme til afpasning af pumpeslaglængden i afhængighed af motorbelastningen. Ændring i denne afhængighed kan kun ske ved at udskifte kurveskiverne til nye, med en anden overføringsfunktion.As the cylinder lubricating oil typically has to be dosed with one portion per engine speed, 5 is the only option to adjust the dosage to change the stroke length of the pumps. A system for this is described, for example, in Danish patent application 4998/85. This system operates by a curve disc mechanism for adjusting the pump stroke length depending on the engine load. This dependency can only be changed by replacing the wafer discs with new ones with a different transfer function.
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Det har også været foreslået at justere pumpeslaglængden ved hjælp af en styrbar motor, f.eks. en stepmotor. Dette har været anvendt til punktsmøring, men denne lader sig vanskeligt etablere i forbindelse med konventionelle smøreapparater. Et sådant system er for eksempel beskrevet i international patentansøgning nr. WO 02/35068 15 Al.It has also been proposed to adjust the pump stroke using a controllable motor, e.g. a stepper motor. This has been used for spot lubrication, but it is difficult to establish in connection with conventional lubricators. Such a system is described, for example, in International Patent Application No. WO 02/35068 15 A1.
Endvidere kendes der også fra tysk offentliggørelsesskrift DE 28 27 626 et smøresystem, der er baseret på, at smøreolie tilføres i afmålte kvantiteter til forudbestemte tidsintervaller gennem åbninger i cylindervæggen. Der er ikke her anvist nogen mu-20 lighed for en trinløs styring af den dosering, der skal foretages på de enkelte smøresteder.Furthermore, from German publication specification DE 28 27 626 a lubrication system is known which is based on the supply of lubricating oil in measured quantities at predetermined intervals of time through openings in the cylinder wall. There is no possibility here of a stepless control of the dosage to be made at the individual lubrication sites.
Endvidere kendes der for eksempel fra GB 834533 A, DK 173512 Bl eller CH 673506 A5 systemer af den indledningsvis nævnte type, hvor en hydraulisk cylinder 25 via en fordelerplade eller lignende konstruktion påvirker flere doseringsstempler. Der vil i disse konstruktioner være én hydraulisk cylinder til aktiveringen. Dette medfører driftsstop for samtlige doseringsstempler, hvis den hydrauliske cylinder svigter. 1 forbindelse med traditionel cylindervægsmøring har det hidtil været praksis at an-30 vende simple ljederbelastede kontraventiler, som kan modstå det interne tryk i cylinderen, men som giver efter for et blot lidt højere, eksternt injiceringstryk. I forbindelse med trykforstøvningsindsprøjtning er det dog ønskeligt og nødvendigt, at ventilsyste- DK 176924 B1 4 met kun åbner ved et meget højere olietryk, for at olieinjiceringen straks fra begyndelsen kan antage karakter af en trykforstøvningsindsprøjtning.Furthermore, GB 834533 A, DK 173512 B1 or CH 673506 A5 systems of the type mentioned above are known, for example, in which a hydraulic cylinder 25 via a distributor plate or similar construction influences several dosing pistons. In these designs there will be one hydraulic cylinder for the actuation. This results in shutdown of all metering pistons if the hydraulic cylinder fails. In connection with traditional cylinder wall lubrication, it has hitherto been the practice of using simple leather-loaded check valves which can withstand the internal pressure in the cylinder, but which give way to a slightly higher, external injection pressure. However, in connection with pressure spraying, it is desirable and necessary that the valve system only opens at a much higher oil pressure, so that the oil injection can assume the nature of a pressure spraying right from the beginning.
Der er tidligere i dansk patentansøgning PA 2005 01629 foreslået et hydraulisk drevet 5 smøreapparat samt en fremgangsmåde for dosering af cylindersmøreolie af den indledningsvis nævnte type. Med det princip, som er beskrevet i nævnte patentansøgning, er det muligt at etablere cylindersmøringen på en måde, således at der kan opnås en fleksibel elektronisk styring samt en central trinløs styring af doseringen til smørestederne. Endvidere kan der også opnås en præcis samt enkelt styring af timing-10 tidspunkt. Der er også i dette system beskrevet anvendelsen af en fordelerplade.Previously, in Danish Patent Application PA 2005 01629, a hydraulically driven lubricator and a method for dosing cylinder lubricating oil of the type mentioned above have been proposed. With the principle described in said patent application, it is possible to establish the cylinder lubrication in such a way that flexible electronic control as well as a central stepless control of the dosage to the lubrication points can be obtained. Furthermore, precise and simple timing-10 time control can also be obtained. The use of a distributor plate is also described in this system.
Ved de hydrauliske systemer ønsker man at udnytte udvekslingsforholdet mellem tværsnitsareal for det mindst ene hydrauliske stempel og doseringsstempleme Således anvises det i DK 173512 Bl, at det hydrauliske stempel har et tværsnitsareal, der er 15 mindst 4 gange og fortrinsvis 6 til 15 gange større en tværsnitsarealerne for doseringsstemplerne for at etablere de nødvendige trykforhold i smøreolien. Store arealforhold er ufordelagtige, da det medfører store pladskrav. 1 forbindelse med forsøg med disse kendte smøreapparater har man observeret pro-20 blemer med, at smøreapparatet ikke kan levere smøreolien hurtigt nok til brug for forstøvningsdyser, for eksempel af den type, der er beskrevet i EP 1 129 275. Dette har blandt andet været observeret i forbindelse med smøreapparater af den type, der er anvist i DK 173512 Bl til trods for at der i den anviste teknik netop har været søgt en løsning med opnåelse af et hurtigtvirkende cylindersmøresystem, der kan give hurtig 25 og præcis dosering helt ud i smørestedet på foringens inderside. Der har været foretaget forsøg med at øge trykket i hydrauliksystemet; men det viste sig, at det stort set ikke havde nogen effekt. Årsagen var blandt andet, at magnetventiler i systemet ikke havde tilstrækkelig kapacitet. Magnetventilerne lader sig ikke udskifte på let måde, og derfor kan problemet ikke løses blot ved udskiftning af magnetventilerne.In the hydraulic systems, it is desired to utilize the ratio of cross-sectional area of the at least one hydraulic piston to the metering pistons. Thus, in DK 173512 B1, the hydraulic piston has a cross-sectional area which is 15 at least 4 times and preferably 6 to 15 times larger than the cross-sectional area. for the dosing pistons to establish the necessary pressure ratios in the lubricating oil. Large area conditions are disadvantageous as it results in large space requirements. In connection with experiments with these known lubricants, problems have been observed in that the lubricant cannot deliver the lubricating oil quickly enough to use for atomizing nozzles, for example of the type described in EP 1 129 275. This has been, inter alia, observed in connection with lubricators of the type disclosed in DK 173512 B1 despite the fact that a solution has been sought in the art just for obtaining a fast-acting cylinder lubrication system that can provide fast and precise dosing all the way to the lubrication site on the inside of the casing. Attempts have been made to increase the pressure in the hydraulic system; but it turned out that it had virtually no effect. The reason was, among other things, that solenoid valves in the system did not have sufficient capacity. The solenoid valves cannot be easily replaced and therefore the problem cannot be solved simply by replacing the solenoid valves.
30 Det har været ønskeligt at løse problemet for at kunne anvende effektive trykforstøvningsdyser i eksisterende og i nyudviklede cylindersmøresystemer.It has been desirable to solve the problem in order to use effective pressure atomizing nozzles in existing and newly developed cylinder lubrication systems.
DK 176924 B1 5DK 176924 B1 5
Opfindelsens formålThe object of the invention
Det er formålet med den foreliggende opfindelse at afhjælpe ovennævnte ulemper og at anvise et hydraulisk drevet smøreapparat, hvormed det er muligt at tilvejebringe et meget driftsikkert og billigt system, hvor det er muligt at få leveret smøreolien hurtigt 5 nok ved et højt driftstryk, så risikoen for fejlfunktion er elimineret eller mindsket.It is the object of the present invention to alleviate the above-mentioned drawbacks and to provide a hydraulically driven lubricator, which makes it possible to provide a very reliable and inexpensive system where it is possible to deliver the lubricating oil quickly enough at high operating pressure so that the risk for malfunction is eliminated or diminished.
Beskrivelse af opfindelsenDescription of the Invention
Dette opnås ifølge den foreliggende opfindelse med et hydraulisk smøreapparat af den indledningsvis nævnte type, der er særpræget ved, at hydraulikstemplet har en indre boring forløbende i hydraulikstemplets forskydningsretning, at boringen er forsynet 10 med en indsats omfattende en indsatscylinder, hvori der er tilvejebragt et hult indsatsstempel, som er i kontakt med en forsyningsåbning for hydraulikolien.This is achieved in accordance with the present invention with a hydraulic lubricator of the type mentioned initially, characterized in that the hydraulic piston has an inner bore extending in the displacement direction of the hydraulic piston, that the bore is provided with an insert comprising an insert cylinder in which a hollow is provided. insert piston which is in contact with a supply opening for the hydraulic oil.
Hydraulikstemplet ifølge opfindelsen er ligeledes særpræget ved, at det har en indre boring forløbende i hydraulikstemplets forskydningsretning, at boringen er forsynet 15 med en indsats omfattende en indsatscylinder, hvori der er tilvejebragt et hult indsatsstempel, som er i kontakt med en forsyningsåbning for hydraulikolien.The hydraulic piston according to the invention is also characterized in that it has an internal bore extending in the displacement direction of the hydraulic piston, that the bore is provided with an insert comprising an insert cylinder, in which is provided a hollow insert piston in contact with a supply opening for the hydraulic oil.
Nærværende opfindelse kan anvendes i forbindelse med et apparat, som beskrevet i de ovenfor omtalte patentskrifter, hvor der anvendes hydrauliske smøreapparater med en 20 fordelerplade.The present invention can be used in connection with an apparatus as described in the above-mentioned patents, in which hydraulic lubricators with a distributor plate are used.
Imidlertid vil nærværende opfindelse også kunne anvendes i forbindelse med andre former for smøreapparater og andre fremgangsmåder, hvor man baserer sig på hydraulisk smøring ved anvendelse af hydrauliksteinpier, der benyttes til påvirkning af ind-25 sprøjtningsenheder omfattende doseringsstempler for cylindersmøreolien, og hvor et eller flere hydraulikstempler påvirker en fordelerplade, der benyttes til aktivering af doseringsstempleme.However, the present invention may also be used in conjunction with other types of lubricators and other methods based on hydraulic lubrication using hydraulic stone pipes used to actuate injection units comprising metering pistons for the cylinder lubricating oil and one or more hydraulic pistons. affects a distributor plate used to activate the dosing pistons.
Det har således vist sig, at indsatsen giver en ændret diameter på hydraulikstemplet og 30 dermed sikres det, at hydraulikstemplet kan flyttes hurtigere og dette forbedrer tryk- og flow-forholdene væsentligt, så man kan opnå væsentligt forbedret tryk og flow i forstøvningsdyserne og dermed en forbedret performance for smøresystemet. Endvidere sikrer det modificerede hydraulikstempel, at flow-kapaciteten ikke stiller for sto- DK 176924 B1 6 re krav til magnetventiler i systemet for at opnå det optimale tryk og flow til forstøvningsdyserne. Dette opnås på en teknisk enkel måde, der kan tilpasses til brug i eksisterende systemer blot ved at modificere det eller de anvendte hydraulikstempler.Thus, it has been found that the insert gives a changed diameter of the hydraulic piston and thus it is ensured that the hydraulic piston can be moved faster and this improves the pressure and flow conditions substantially, so that significantly improved pressure and flow can be achieved in the spray nozzles and thus a improved performance of the lubrication system. Furthermore, the modified hydraulic piston ensures that the flow capacity does not meet higher requirements for solenoid valves in the system to obtain the optimum pressure and flow for the atomizing nozzles. This is achieved in a technically simple way that can be adapted for use in existing systems simply by modifying the hydraulic piston (s) used.
5 Der vil således være behov for en mindre mængde hydraulikolie til aktivering af dose-ringsstempleme og herved fas en tilstrækkelig og hurtig levering af smøreolien til forstøvningsdyseme.Thus, a smaller amount of hydraulic oil will be needed to activate the dosing pistons and thereby provide a sufficient and rapid delivery of the lubricating oil to the spray nozzles.
Ifølge en yderligere udførelsesform er smøreapparatet og hydraulikstemplet ifølge 10 opfindelsen særpræget ved, at indsatsstemplet er skruet ind i en boring gennem hvilken hydraulikolien leveres. Herved sikres en tæt forbindelse med levering af hydraulikolien til det reducerede tværsnitsareal, som er tilvejebragt inde i indsatsstemplets bund.According to a further embodiment, the lubricator and hydraulic piston according to the invention are characterized in that the insert piston is screwed into a bore through which the hydraulic oil is delivered. This ensures a close connection with the delivery of the hydraulic oil to the reduced cross-sectional area which is provided inside the bottom of the insert piston.
15 Ifølge en yderligere udførelsesform er smøreapparatet og hydraulikstemplet ifølge opfindelsen særpræget ved, at udvekslingsforholdet mellem tværsnitsarealet af det mindst ene hydrauliske stempel og tværsnitsarealet for doseringsstempleme er mindre end 7 og fortrinsvis mindre end 5.According to a further embodiment, the lubricator and hydraulic piston according to the invention are characterized in that the exchange ratio between the cross-sectional area of the at least one hydraulic piston and the cross-sectional area of the metering pistons is less than 7 and preferably less than 5.
20 Som konkret eksempel kan nævnes en ændring af et hydraulikstemple af den type, som er vist i Fig. 2 og 3 som følger: - standard hydraulikstempel:20 As a concrete example, a change of hydraulic piston of the type shown in FIG. 2 and 3 as follows: - standard hydraulic piston:
Hydraulik stempel: ø31 mm Doseringsstempel: 5 x ø3,5 25 Udvekslingsforhold = 31Λ2 / (5 x 3,5Λ2) = 15,7 - modificeret hydraulikstempel:Hydraulic piston: ø31 mm Dosing piston: 5 x ø3.5 25 Exchange ratio = 31Λ2 / (5 x 3.5Λ2) = 15.7 - modified hydraulic piston:
Hydraulik stempel-indsats: øl6 mm Doseringsstempel: 5 x ø3,5 Udvekslingsforhold = 16Λ2 / (5 x 3,5Λ2) = 4,2 30Hydraulic piston insert: beer6 mm Dosing piston: 5 x ø3.5 Exchange ratio = 16Λ2 / (5 x 3.5Λ2) = 4.2 30
Med denne ændring er der opnået en cyklus for trykopbygning og trykafVikling af smøreolien til forstøvningsdyserne, som er 50 % hurtigere med hydraulikstemplet ifølge opfindelsen.With this change, a cycle has been achieved for pressure build-up and pressure settling of the lubricating oil for the spray nozzles, which is 50% faster with the hydraulic piston according to the invention.
DK 176924 B1 7DK 176924 B1 7
Ifølge en yderligere udførelsesform er smøreapparatet og hydraulikstemplet ifølge opfindelsen særpræget ved, at der mellem indsatsstemplets yderside og hydraulikstemplets boring er tilvejebragt et dræn for hydraulikolien. Således kan lækolie ledes 5 ud gennem hydraulikstemplet, således at der ikke sker ophobning af hydraulikolie inden i det kammer, hvor hydraulikstemplet er placeres. Hvis dette var tilfældet ville det betyde, at hydraulikolien skal virke på hele tværsnitsarealet inden i kammeret. Derved ville der ikke være et reduceret behov for olieflow, som er basis for opnåelse af den tekniske fordel ved den foreliggende opfindelse.According to a further embodiment, the lubricator and hydraulic piston according to the invention are characterized in that a drain for the hydraulic oil is provided between the outside of the insert piston and the bore of the hydraulic piston. Thus, leakage oil can be discharged through the hydraulic piston so that no hydraulic oil accumulates within the chamber in which the hydraulic piston is placed. If this were the case, it would mean that the hydraulic oil must act on the entire cross-sectional area within the chamber. Thereby, there would be no reduced need for oil flow which is the basis for obtaining the technical advantage of the present invention.
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Ifølge en yderligere udførelsesform er smøreapparatet og hydraulikstemplet ifølge opfindelsen særpræget ved, at hydraulikstemplets boring, indsatscylinderen og indsatsstemplet har et cirkulært tværsnit og er anbragt koncentrisk om en central akse.According to a further embodiment, the lubricator and hydraulic piston according to the invention are characterized in that the bore of the hydraulic piston, the insert cylinder and the insert piston has a circular cross section and is located concentrically about a central axis.
Dette er en særlig enkel udformning der er let at fremstille.This is a particularly simple design that is easy to manufacture.
1515
Ifølge en yderligere udførelsesform er smøreapparatet ifølge opfindelsen særpræget ved, at doseringssystemet omfatter - en forsyningsledning samt en returledning, der er forbundet med smøreapparatet via en eller flere ventiler for levering af hydraulikolie, 20 - en central hydraulikolieforsyningspumpe, der via forsyningsledningen er forbundet med hydraulikcylindre, der hver har et hydraulikstempel og som kan sættes under tryk med hydraulikolie, - et antal indsprøjtningsenheder, der modsvarer et multiplum af cylinderantallet i motoren, og som er forbundet med hver sin doseringscylinder med et doseringsstempel, 25 - en forsyningsledning for cylindersmøreolie.According to a further embodiment, the lubricator according to the invention is characterized in that the dosing system comprises - a supply line and a return line connected to the lubricant via one or more valves for delivery of hydraulic oil, - a central hydraulic oil supply pump connected via the supply line to hydraulic cylinders, each having a hydraulic piston and which can be pressurized with hydraulic oil; - a plurality of injection units corresponding to a multiple of the number of cylinders in the engine and connected to each metering cylinder with a metering piston; 25 - a supply line for cylinder lubricating oil.
Herved sikres den nødvendige forsyning af hydraulikolie og smøreolie. Det bemærkes at der kan anvendes olie for samme forsyningskilde idet samme type olie kan anvendes til smøring og til aktivering af hydraulikstemplet.This ensures the necessary supply of hydraulic oil and lubricating oil. It should be noted that oil can be used for the same supply source as the same type of oil can be used for lubrication and for activating the hydraulic piston.
30 Tegningsbeskrivelse30 Drawing Description
Opfindelsen vil herefter blive forklaret nærmere under henvisning til den medfølgende tegning, hvor DK 176924 B1 8The invention will then be explained in more detail with reference to the accompanying drawing, in which DK 176924 B1 8
Fig. 1 viser en skematisk oversigt over et system med flere smøreapparater ifølge opfindelsen,FIG. 1 is a schematic view of a system of multiple lubricators according to the invention,
Fig. 2 viser et principdiagram for en anden udførelsesform for et system med et smøreapparat ifølge opfindelsen, 5 Fig. 3 viser et længdesnit gennem en udførelsesform for en cylindersmøreenhed, der kan indgå i et smøreapparat ifølge opfindelsen, og Fig. 4 viser en yderligere udførelsesform for et smøreapparat ifølge opfindelsen til brug i det i Fig. 1 viste system.FIG. 2 shows a principle diagram for another embodiment of a system with a lubricator according to the invention; FIG. Fig. 3 is a longitudinal section through an embodiment of a cylinder lubrication unit which can be included in a lubricator according to the invention; 4 shows a further embodiment of a lubricator according to the invention for use in the embodiment of FIG. 1.
10 Detaljeret beskrivelse af opfindelsenDetailed description of the invention
Fig. 1 viser et system, der er opbygget i overensstemmelse med angivelserne i PCT/DK2007/000364.FIG. 1 shows a system constructed in accordance with the specifications of PCT / DK2007 / 000364.
Fig. 1 viser skematisk fire cylindre 250, og på hver cylinder er vist otte indsprøjt-15 ningsdyser 251. Smøreapparaterne 252 er forbundet med en central computer 253 med lokale styreenheder 254 typisk for hvert smøreapparat 252. Smøreapparateme 252 vil være indrettet således som forklaret mere detaljeret i det følgende.FIG. 1 schematically shows four cylinders 250, and on each cylinder are shown eight injection nozzles 251. The lubricators 252 are connected to a central computer 253 with local controllers 254 typical of each lubricator 252. The lubricators 252 will be arranged as explained in more detail in FIG. the following.
Den centrale computer 253 er koblet parallelt med en yderligere styreenhed 255, der 20 udgør en backup for den centrale computer. Udover dette er der etableret en overvågningsenhed 256, der overvåger pumpen (kan være en hydraulikpumpe eller en hydraulikstation), en overvågningsenhed 257, der overvåger belastningen og en overvågningsenhed 258, der overvåger krumtapakslens position.The central computer 253 is coupled in parallel with an additional controller 255 which provides a backup for the central computer. In addition, a monitoring unit 256 is established which monitors the pump (may be a hydraulic pump or a hydraulic station), a monitoring unit 257 which monitors the load and a monitoring unit 258 which monitors the position of the crankshaft.
25 I den øvre del af fig. 1 er der vist en hydraulikstation 259, der omfatter en motor 260, der driver en pumpe 261 i en tank 262 for hydraulisk olie. Den hydrauliske station 259 omfatter endvidere en køler 263 og et filter 264. Systemolie pumpes via forsyningsledning 265 frem til smøreapparatet via en ventil 220. Den hydrauliske station er endvidere forbundet med en returledning 266, der ligeledes er forbundet med smøreappa-30 ratet via en ventil.25 In the upper part of FIG. 1, there is shown a hydraulic station 259 comprising a motor 260 driving a pump 261 in a hydraulic oil tank 262. The hydraulic station 259 further comprises a cooler 263 and a filter 264. System oil is pumped via supply line 265 to the lubricator via a valve 220. The hydraulic station is further connected to a return line 266 which is also connected to the lubricating device via a valve. .
DK 176924 B1 9DK 176924 B1 9
Smøreolie fremsendes til smøreapparat 252 via en ledning 267 fra en smøreolieforsyningstank (ikke vist). Smøreolien fremsendes fra smøreapparatet via ledninger 110 til indsprøjtningsdyserne 251.Lubricating oil is sent to lubricator 252 via line 267 from a lubricating oil supply tank (not shown). The lubricating oil is sent from the lubricant via lines 110 to the injection nozzles 251.
5 I Fig. 2 og 3 ses et anlæg af den type, som i princippet kendes fra beskrivelsen til dansk patent nr. DK 173512.5 In FIG. Figures 2 and 3 show a plant of the type known in principle from the description to Danish patent no. DK 173512.
Fig. 2 viser et cylindersmøresystem, hvor to cylindre 2 er vist. Hver af cylinderne 2 er forsynet med fire smøresteder 6, der er forsynet med indsprøjtningsenheder 6’. Hver 10 af smøreenhederne 6’ er via forbindelsesledninger 29 forbundet med en central smøreenhed 30, der er forbundet med en styreventil 31. Styreventilen 31 er via ledningen 32 forbundet med en elektronisk styreenhed 9. Endvidere er der illustreret en trykstyringsenhed 33, der ligeledes via ledninger 34, 35 er forbundet med styreenheden 9, og som via smøreolietilførselsledninger 36, 37 er forbundet med cylindersmøreenhedeme 15 30.FIG. 2 shows a cylinder lubrication system in which two cylinders 2 are shown. Each of the cylinders 2 is provided with four lubrication points 6 provided with injection units 6 '. Each 10 of the lubricating units 6 'is connected via connecting lines 29 to a central lubricating unit 30, which is connected to a control valve 31. The control valve 31 is connected via the conduit 32 to an electronic control unit 9. Furthermore, a pressure control unit 33 is also illustrated, which is also connected via wires. 34, 35 are connected to the control unit 9 and which are connected via the lubricating oil supply lines 36, 37 to the cylinder lubricating units 15 30.
Cylindersmøreenhederne 30 er tydeligere vist i fig. 3.The cylinder lubricating units 30 are more clearly shown in FIG. Third
Tværsnittet i fig. 3 viser, at en central cylindersmøreenhed 30 er forsynet med en til-20 gangsport 38 for smøreolie. Endvidere har den en returport 39 for drivolie, der i den viste udførelsesform er identisk med smøreolien. Styreventilen 31 er forbundet med en ventil 40, som regulerer olietilførsel og -fraførsel. Cylindersmøreenheden 30 omfatter et hydraulisk stempel 41, der er forsynet med flanger 42. Hver af flangerne 42 er i indgreb med doseringsstempler 43, som doserer smøreolie via porte 44 og via for-25 bindelsesledningerne 29 til smørestederne 6, som vist på fig. 2. 1The cross section of FIG. 3 shows that a central cylinder lubricating unit 30 is provided with a lubricating oil supply port 38. Furthermore, it has a drive oil return port 39 which in the embodiment shown is identical to the lubricating oil. The control valve 31 is connected to a valve 40 which regulates oil supply and delivery. Cylinder lubricating unit 30 comprises a hydraulic piston 41 provided with flanges 42. Each of the flanges 42 engages metering pistons 43 which dispense lubricating oil via ports 44 and via the connecting lines 29 to the lubrication points 6, as shown in FIG. 2. 1
Fig. 3 er der således vist et hydraulisk stempel 41 med flanger 42, der virker som en fordelerplade, idet den påvirker flere doseringsstempler 43.FIG. 3, there is thus shown a hydraulic piston 41 with flanges 42 acting as a distributor plate, affecting several dosing pistons 43.
Enheden 30 har et indstilleligt stopelement 45, som bestemmer vandringen for hy-30 draulikstemplet 41. Stopelementet 45 fastlægger slaglængden for hydraulikstemplet 41 og dermed også for doseringsstempleme 43, der virker som doseringspumper.The unit 30 has an adjustable stop member 45 which determines the travel of the hydraulic piston 41. The stop member 45 determines the stroke of the hydraulic piston 41 and thus also of the metering pistons 43 which act as metering pumps.
DK 176924 B1 10DK 176924 B1 10
En trykfjeder 46 forbelaster hydraulikstemplet 41 i retning af udgangsstillingen. Det indstillelige stopelement 45 er indskruet i et gevind 47 i enhedens endedel 48. Således vil en indskruning af det indstillelige stopelement 45 begrænse slaglængden af hydraulikstemplet 41 og dermed den af doseringsstempleme 43 afgivne smøreolie-5 mængde. Det indstillelige stopelement 45 fungerer således som indstillingsorgan for stempel pumpens slaglængde. Det indstillelige stopelement 45 er forbundet med et elektronisk styret reguleringsorgan 49. Reguleringsorganet 49 er via ledninger 50 forbundet med den centrale elektroniske styreenhed 9. Der vil således være muliggjort en elektronisk styring af stempelpumpens slaglængde, således at det på en fleksibel måde 10 er muligt opnå en central og trinløs styring af den dosering, der skal foretages til de enkelte smøresteder 6.A compression spring 46 preloads the hydraulic piston 41 in the direction of the initial position. The adjustable stop member 45 is screwed into a thread 47 in the end portion 48 of the unit. Thus, screwing in the adjustable stop member 45 will limit the stroke of the hydraulic piston 41 and thus the amount of lubricating oil delivered by the dosing pistons 43. Thus, the adjustable stop element 45 acts as a piston pump adjusting adjuster. The adjustable stop element 45 is connected to an electronically controlled regulator 49. The regulator 49 is connected via wires 50 to the central electronic control unit 9. Thus, electronic control of the stroke of the piston pump will be possible, so that in a flexible manner 10 a central and stepless control of the dosage to be made for the individual lubrication sites 6.
Hydraulikstemplet 41 er cylindrisk og er placeret i et kammer A, der i et traditionelt smøreapparat ville virke som en cylinder, hvori stemplet forskydes. Hydraulikstemplet 15 41 har en central boring B, hvori en indsatscylinder C er monteret. Denne indsatscy linder C er hul og har en indre boring D, hvor et indsatsstempel E er optaget og som afsluttes i en lukket bund F. Indsatsstemplet E er via et gevind G monteret i en åbning H for indføring af hydraulikolien til kammeret A. Indsatsstemplet E har en indre boring igennem hvilken hydraulikolien strømmer for at virke på bunden F i indsatscylin-20 deren. Herved sker der en forskydning af hydraulikstemplet og dermed også flangen 42, således at doseringsstempl eme aktiveres. Hydraulikstemplet 41 har en drænåbning J, således at lækolie kan sive imellem mm mellem ydersiden af indsatscylinderen C og boringen B ud via drænåbningen J. Herved undgås ophobning af olie i kammeret A bag ved hydraulikstemplet 41.The hydraulic piston 41 is cylindrical and is located in a chamber A which in a conventional lubricator would act as a cylinder in which the piston is displaced. The hydraulic piston 15 41 has a central bore B in which an insert cylinder C is mounted. This insert cinder C is hollow and has an inner bore D where an insert piston E is received and terminated in a closed bottom F. The insert piston E is mounted via a thread G in an opening H for introducing the hydraulic oil into the chamber A. The insert piston E has an inner bore through which the hydraulic oil flows to act on the bottom F of the insert cylinder. Hereby, the hydraulic piston and thus also the flange 42 are displaced, so that the metering piston is activated. The hydraulic piston 41 has a drainage opening J, so that leaking oil can leak between mm between the outside of the insert cylinder C and the bore B via the drainage opening J. This prevents the accumulation of oil in the chamber A behind the hydraulic piston 41.
2525
Smøreapparatet, der er vist i Fig. 4 er opbygget af en bundpart 110, hvor magnet ventilerne 115 og 116 til aktivering af apparat sidder monteret. På siden af bundparten 110 er der tilvejebragt forskruninger til henholdsvis system olie tryk tilførsel 142 og systemolietryk retur til tank 143.The lubricator shown in FIG. 4 is constructed of a bottom part 110, where the solenoid valves 115 and 116 for activating the apparatus are mounted. On the side of the bottom portion 110, gaskets for system oil pressure supply 142 and system oil pressure return to tank 143 are provided, respectively.
Drivolien kan tilføres igennem to magnetventiler, hvoraf den ene er en primær magnetventil 116 og den anden er en sekundær magnetventil 115.The drive oil can be supplied through two solenoid valves, one being a primary solenoid 116 and the other a secondary solenoid 115.
30 DK 176924 B1 n I udgangsposition er det den primære magnet ventil 116, der er aktiv. Herved ledes drivolien fra den tilhørende forsynings forskruning 142, til den primære magnetventil 116 og via en omskifterventil 117 ind i apparat gennem en fordelingskanal til gruppen af tilhørende hydraulikstempler.30 DK 176924 B1 n In the initial position, the primary solenoid valve 116 is active. Hereby, the propellant oil is fed from the associated supply screw 142, to the primary solenoid valve 116 and via a switch valve 117 into the apparatus through a distribution channel to the group of associated hydraulic pistons.
5 I tilfælde af at den primære magnetventil 116 fejler, er det muligt automatisk at tilkoble den sekundære magnetventil 115. Denne ventil tilkobles ved at aktivere den sekundære magnetventil 115.5 In the event that the primary solenoid valve 116 fails, it is possible to automatically engage the secondary solenoid valve 115. This valve is actuated by activating the secondary solenoid valve 115.
10 Herved sættes den tilhørende fordelingskanal under tryk. Dette tryk medfører, at omskifterventilen 117 forskydes mod højre, hvorved forbindelsen mellem den primære magnetventil 116 og den tilhørende fordelingskanal afbrydes. Herved bliver trykket fjernet fra de hydraulik stempler, der er tilknyttet denne magnetventil 116.10 This puts the associated distribution channel under pressure. This pressure causes the switch valve 117 to be shifted to the right, thereby severing the connection between the primary solenoid valve 116 and the associated distribution channel. Thereby, the pressure is removed from the hydraulic pistons associated with this solenoid valve 116.
15 Ved aktiveringen af den sekundære magnetventil 115 bliver den tilhørende fordelingskanal og de hertil hørende hydraulikstempler sat under tryk. Dette bevirker, at fordelingspladen 7 herefter drives af olien, der ledes ind i apparatet via den sekundære magnetventil 115.15 When the secondary solenoid valve 115 is actuated, the associated distribution channel and the associated hydraulic pistons are pressurized. This causes the distribution plate 7 to then be driven by the oil which is fed into the apparatus via the secondary solenoid valve 115.
20 Omskifterventilen 117 kan være udstyret med en fjeder 119. Således vil fjederen ved manglende forsyningstryk gennem den sekundære magnetventil, automatisk sende omskifterventilen 117 retur til ovennævnte udgangsposition.The switch valve 117 may be equipped with a spring 119. Thus, in the absence of supply pressure through the secondary solenoid valve, the spring will automatically return the switch valve 117 to the above starting position.
Omskifterventilen kan udstyres med en drøvling, således at denne returnering af om-25 skifterventilen kan forsinkes. På denne måde undgår/begrænser man, at omskifterventilen 117 kører frem og tilbage imellem aktiveringerne. På Fig. 4 er drøvlingen bestemt af en spalte, der er dannet mellem en ”drain-pin” 118 og omskifteventilen 117.The switch valve can be equipped with a throttle so that this return of the switch valve can be delayed. In this way, it is avoided / limited that the switch valve 117 moves back and forth between the actuations. In FIG. 4, the throttle is determined by a gap formed between a drain pin 118 and the switch valve 117.
Når hver af magnetventileme er forbundet med en separat gruppe hydraulikstempler 30 sikres en uafhængighed mellem magnetventilerne. Når der skifter mellem den primære magnetventil 116 og den sekundære magnet ventil 115 vil omskifterventilen 117 sikre at trykket fjernes fra den primære gruppe af hydraulikstempler og derved mulig- DK 176924 B1 12 gøre en drift af den sekundære magnetventil 115 - selv i de tilfælde, hvor den primære magnetventil er stoppet.When each of the solenoid valves is connected to a separate group of hydraulic pistons 30, an independence between the solenoid valves is ensured. When switching between the primary solenoid valve 116 and the secondary solenoid valve 115, the switching valve 117 ensures that the pressure is removed from the primary group of hydraulic pistons, thereby enabling the operation of the secondary solenoid valve 115 - even in those cases where the primary solenoid valve is stopped.
Pos. 121 viser en blændskrue.Pos. 121 shows an aperture screw.
55
Pos. 122 viser en kombineret blændskrue/endestop, der dels virker som endestop for omskifterventilen 117’s pal 120 og dels via en pakning (ikke vist) også har en tætnen-de funktion.Pos. 122 shows a combined aperture screw / end stop, which partly acts as the end stop for switch valve 117's pal 120 and partly through a gasket (not shown) also has a sealing function.
10 Ovenover de hydrauliske stempler 106 er der en fordelerplade 7. Pladen er her vist som en todelt konstruktion med en øvre fordelerpladedel 125 og en nedre fordelerpla-dedel 123. Doseringsstempleme 21 er monteret i/på den øvre fordelerpladedel 125. I apparater, hvor der anvendes forskellige olier til at drive og til at smøre med, er der en stempel-pakning 124 mellem den øvre og nedre fordelerpladedel. Principielt kan man 15 også bruge nøj es med at bruge en slags olie både til drivolie og til smøreolie.10 Above the hydraulic pistons 106 there is a distributor plate 7. The plate is shown here as a two-part construction with an upper distributor plate part 125 and a lower distributor plate part 123. The dosing pistons 21 are mounted in / on the upper distributor plate part 125. In apparatus where When various oils are used to drive and to lubricate, there is a piston gasket 124 between the upper and lower distributor plate members. In principle, one can also just use a kind of oil both for propellant and for lubricating oil.
Hvert hydraulikstempel 106 er cylindrisk og er placeret i et kammer A, der i et traditionelt smøreapparat ville virke som en cylinder, hvori stemplet forskydes. Hydraulikstemplet 106 har en central boring B, hvori en indsatscylinder C er monteret. Denne 20 indsatscylinder C er hul og har en indre boring D, hvor et indsatsstempel E er optaget og som afsluttes i en lukket bund F. Indsatsstemplet E er via et gevind G monteret i en åbning H for indføring af hydraulikolien til kammeret A. Indsatsstemplet E har en indre boring igennem hvilken hydraulikolien strømmer for at virke på bunden F i indsatscylinderen. Herved sker der en forskydning af hydraulikstemplet og dermed også 25 fordelerpladen 7, således at doseringsstempleme 21 aktiveres. Hydraulikstemplet 106 har en drænåbning J, således at lækolie kan sive imellem mm mellem ydersiden af indsatscylinderen C og boringen B ud via drænåbningen J. Herved undgås ophobning af olie i kammeret A bag ved hydraulikstemplet 106.Each hydraulic piston 106 is cylindrical and is located in a chamber A which in a conventional lubricator would act as a cylinder in which the piston is displaced. The hydraulic piston 106 has a central bore B in which an insert cylinder C is mounted. This 20 insert cylinder C is hollow and has an inner bore D where an insert piston E is received and terminated in a closed bottom F. The insert piston E is mounted via a thread G in an opening H for introducing the hydraulic oil into the chamber A. The insert piston E has an inner bore through which the hydraulic oil flows to act on the bottom F of the insert cylinder. Hereby, the hydraulic piston is displaced, and thus also the distributor plate 7, so that the dosing pistons 21 are activated. The hydraulic piston 106 has a drainage opening J so that leakage oil can leak between mm between the outside of the insert cylinder C and the bore B via the drainage opening J. This prevents the accumulation of oil in the chamber A behind the hydraulic piston 106.
30 Omkring doseringsstempleme 21 er der en fælles returljeder 109, der returnerer stemplerne 21 efter frakobling af forsyningstrykket på hydraulikstempleme 106. Omkring returfjederen 109 er der et lille smøreoliereservoir 147, der udvendigt er begrænset af DK 176924 B1 13 en baseblock 111. Smøreolien forsynes igennem separat forskruning med pakninger 138 og 139. Apparatet kan valgfrit udstyres med en udluftnings skrue med pakning.30 Around the metering pistons 21 there is a common return conductor 109 which returns the pistons 21 after disconnecting the supply pressure on the hydraulic pistons 106. Around the return spring 109 there is a small lubricating oil reservoir 147 which is externally limited by DK 176924 B1 13 a base block 111. screws with gaskets 138 and 139. The device can optionally be equipped with a vent screw with gasket.
Oven over baseblocken 111 sidder cylinderblokken 112, hvor doseringsstemplerne 21 5 er anbragt for deres reciprokerende bevægelse. Oven over doseringsstempleme 21 er der et pumpekammer 148. I dette kammer er der et udløb med en kontraventilkugle 13, der påvirkes af en fjeder 14. Endvidere er der placeret en forskruning 128, der er forbundet direkte til kontraventiler/SIP-ventiler i cylinder væggen.Above the base block 111 sits the cylinder block 112 where the dosing pistons 215 are arranged for their reciprocating movement. Above the dosing pistons 21 there is a pump chamber 148. In this chamber there is an outlet with a check valve ball 13 which is actuated by a spring 14. Furthermore, a screwdriver 128 is connected directly to check valves / SIP valves in the cylinder wall. .
10 Til justering af slaglængden er der i denne udførelsesform vist et arrangement med en motor 132, der er tilkoblet en snekke 131, der via et snekkehjul 130 justerer slaglængden ved at ændre positionen på setpin/stilleskrue 66.In order to adjust the stroke, an arrangement is shown in this embodiment with a motor 132 connected to a worm 131 which, via a worm wheel 130, adjusts the stroke by changing the position of the set pin / adjusting screw 66.
I denne udførelsesform er det således muligt at justere slaglængden ved at ændre posi-15 tionen på slaglængde-stoppet. Dette er forskelligt fra tidligere udførelsesformer, hvor der blev anvendt et fast nulpunkt og efterfølgende indstilledes slaglængden.Thus, in this embodiment, it is possible to adjust the stroke length by changing the position of the stroke length stop. This is different from previous embodiments where a fixed zero point was used and subsequently the stroke length was adjusted.
For at kontrollere den faktiske slaglængde er der i forlængelse af setpin/stilleskrue 66 monteret en sensor/pickup enhed 114 til registrering af slaglængden, f.eks. i form af 20 en enkoder eller et potentiometer.In order to check the actual stroke, a sensor / pickup unit 114 for recording the stroke, e.g. in the form of an encoder or potentiometer.
Pos. 113 viser et hus for setpin/stilleskrue arrangement.Pos. 113 shows a housing for setpin / adjusting screw arrangement.
Pos. 124 viser en stempelpakning, der tætner mellem de to rum 149 og 147 med hen-25 holdsvis ”læk” olie, der passerer forbi de hydrauliske stempler 6 på drivolie-siden nederst og smøreolien øverst.Pos. 124 shows a piston gasket that seals between the two compartments 149 and 147 with respectively "leaking" oil passing past the hydraulic pistons 6 on the fuel oil side at the bottom and the lubricating oil at the top.
Pos. 127 viser en O-ring, der er tætning mellem baseblocken 111 og cylinderblokken 112.Pos. 127 shows an O-ring which is a seal between the base block 111 and the cylinder block 112.
3030
Pos. 133 viser en fastgøringsskrue for fastgørelse af et lejehus for snekkehjulet 130.Pos. 133 shows a fastening screw for securing a bearing housing for the worm wheel 130.
Pos. 134 viser en O-ring, der er tætning mellem bundpladen 110 og baseblocken 111.Pos. 134 shows an O-ring sealing between the base plate 110 and the base block 111.
Claims (11)
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA200701104A DK176924B1 (en) | 2007-07-30 | 2007-07-30 | Hydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubrication |
| PCT/DK2008/000281 WO2009015666A1 (en) | 2007-07-30 | 2008-07-29 | Lubricating apparatus and hydraulic piston for engine cylinder lubrication |
| KR1020107004266A KR20100051087A (en) | 2007-07-30 | 2008-07-29 | Lubricating apparatus and hydraulic piston for engine cylinder lubrication |
| JP2010518497A JP2010534788A (en) | 2007-07-30 | 2008-07-29 | Lubricator and hydraulic piston for engine cylinder lubrication |
| CN200880100903XA CN101842560B (en) | 2007-07-30 | 2008-07-29 | Lubricating apparatus and hydraulic piston for engine cylinder lubrication |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK200701104 | 2007-07-30 | ||
| DKPA200701104A DK176924B1 (en) | 2007-07-30 | 2007-07-30 | Hydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubrication |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| DK200701104A DK200701104A (en) | 2009-01-31 |
| DK176924B1 true DK176924B1 (en) | 2010-05-17 |
Family
ID=39884758
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DKPA200701104A DK176924B1 (en) | 2007-07-30 | 2007-07-30 | Hydraulic lubricator for a dosing system for cylinder lubricating oil and hydraulic piston for use in such lubrication |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP2010534788A (en) |
| KR (1) | KR20100051087A (en) |
| CN (1) | CN101842560B (en) |
| DK (1) | DK176924B1 (en) |
| WO (1) | WO2009015666A1 (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008013235B4 (en) * | 2008-03-07 | 2010-06-17 | Ab Skf | Device for the metered dispensing of a lubricating fluid |
| JP6109485B2 (en) * | 2012-03-16 | 2017-04-05 | 三菱重工業株式会社 | Cylinder lubrication device |
| CN105673125B (en) * | 2012-05-15 | 2018-06-22 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Cylinder lubrication device and the method for operating the cylinder lubricating system |
| CN102966408A (en) * | 2012-11-05 | 2013-03-13 | 浙江新柴股份有限公司 | Piston-type engine oil pressure-limiting valve device |
| CN103016092A (en) * | 2012-12-12 | 2013-04-03 | 优华劳斯汽车系统（上海）有限公司 | Lubricating system and method of engine |
| FR3054004B1 (en) * | 2016-07-13 | 2018-08-24 | Dosatron International | MECHANISM FOR DETERMINING A PROPORTIONAL DOSING PUMP, PUMP AND METHOD FOR IMPLEMENTING THE SAME |
| EP3483403B1 (en) * | 2017-11-09 | 2022-11-30 | Winterthur Gas & Diesel AG | Lubrication arrangement for a large diesel engine |
| DK179482B1 (en) * | 2017-12-13 | 2018-12-14 | Hans Jensen Lubricators A/S | A large slow-running two-stroke engine, a method of lubricating it, and an injector with a hydraulic-driven pumping system for such engine and method |
| DK179946B1 (en) * | 2018-07-06 | 2019-10-21 | Hans Jensen Lubricators A/S | A method for optimizing lubrication in a large slow-running two-stroke engine |
| DK179952B1 (en) * | 2018-07-06 | 2019-10-25 | Hans Jensen Lubricators A/S | A method for upgrading a lubrication system in a large slow-running two-stroke engine |
| DK180054B1 (en) * | 2018-10-02 | 2020-02-11 | Hans Jensen Lubricators A/S | Substitution of a valve seat for improving a lubricator pump unit and lubrication system of a large slow-running two-stroke engine, and an improved lubricator pump unit |
| EP4139564A4 (en) * | 2020-04-22 | 2024-05-22 | Hans Jensen Lubricators A/S | METHOD FOR LUBRICATING LARGE SLOW-RUNNING MARINE DIESEL ENGINES |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1068406C (en) * | 1992-11-24 | 2001-07-11 | 汉斯·詹森斯·玛斯金菲布里克有限公司 | A lubrication system for spot lubrication of working cylinders in large piston machines, primarily naval diesel motors |
| EP0639696B1 (en) * | 1993-04-02 | 1998-01-21 | Yamaha Hatsudoki Kabushiki Kaisha | Method and system for lubricating an internal combustion engine |
| 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 |
| DE20107681U1 (en) * | 2001-05-07 | 2001-09-20 | Vogel Fluidtec GmbH, 68766 Hockenheim | Lubrication pump unit |
| DK200100841A (en) * | 2001-05-25 | 2002-11-26 | Hans Jensen Lubricators As | Central lubricators |
| DK177024B1 (en) * | 2005-02-25 | 2011-01-31 | Hans Jensen Lubricators As | Method and apparatus for lubricating the cylinder surfaces of large diesel engines |
-
2007
- 2007-07-30 DK DKPA200701104A patent/DK176924B1/en not_active IP Right Cessation
-
2008
- 2008-07-29 WO PCT/DK2008/000281 patent/WO2009015666A1/en active Application Filing
- 2008-07-29 KR KR1020107004266A patent/KR20100051087A/en not_active Application Discontinuation
- 2008-07-29 CN CN200880100903XA patent/CN101842560B/en not_active Expired - Fee Related
- 2008-07-29 JP JP2010518497A patent/JP2010534788A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DK200701104A (en) | 2009-01-31 |
| WO2009015666A1 (en) | 2009-02-05 |
| CN101842560A (en) | 2010-09-22 |
| CN101842560B (en) | 2012-08-22 |
| JP2010534788A (en) | 2010-11-11 |
| KR20100051087A (en) | 2010-05-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |
Effective date: 20210730 |