DK142588B

DK142588B - Lubrication system.

Info

Publication number: DK142588B
Application number: DK210776AA
Authority: DK
Inventors: Bo Paul Sigvald Hedlund; John Roland Larsson
Original assignee: Assa Ab
Priority date: 1975-05-13
Filing date: 1976-05-12
Publication date: 1980-11-24
Also published as: DE2620582A1; CH610385A5; DK142588C; SE400347B; DK210776A; SE7505480L; JPS51140073A

Description

(11) FREMLÆGGELSESSKRIFT 142588 \Ray DANMARK is«) in,.ci.3 f 01 u 1/02 «(21) Ansøgning nr. εΐΟγ/Τδ (22) Indleveret den 12. maj 1976 (24) Løbedag 1 2· maj 1 97 6 (44) Ansøgningen fremlagt og fremlseggelsesskriftet offentliggjort den 24. HOV. 1 980 DIREKTORATET FOR ^ PATENT-OG VAREMÆRKEVÆSENET (30) Prioritet begeret fra døn 15. maj 1975a 7505^80, SE (71) AKTIEBOLAGET ÅSSA, S-597 00 Åt vidaber g, SE.(11) PRESENTATION 142588 \ Ray DENMARK ice cream ") in, .ci.3 f 01 u 1/02" (21) Application No εΐΟγ / Τδ (22) Filed on May 12, 1976 (24) Running Day 1 2 · May 1 97 6 (44) The application presented and the writ of petition published on 24th HOV. 1 980 DIRECTORATE OF THE PATENT AND TRADEMARKET (30) Priority Cup from May 15, 1975a 7505 ^ 80, SE (71) SHARE COMPANY ÅSSA, S-597 00 Åt vidaber g, SE.

(72) Opfinder: Bo Paul Sigvald Hedlund, Enbaersvaegen 7, S-597 00 Åtvida= berg, SE: John Roland Larsson* Bostaellsvaegen 6, S-597 00 Åtvida= berg, SE.(72) Inventor: Bo Paul Sigvald Hedlund, Enbaersvaegen 7, S-597 00 Åtvida = berg, SE: John Roland Larsson * Bostaellsvaegen 6, S-597 00 Åtvida = berg, SE.

(74) Fuldmægtig under sagens behandling:(74) Plenipotentiary in the proceedings:

Internationalt Patent-Bureau.________ (64) Smøresystem.International Patent Bureau .________ (64) Lubrication system.

Opfindelsen angår et smøresystem, hvor der intermittent tilføres smøremiddel til et smørested, specielt et sraørested i cylindervæggen af en stempelmotor, og hvor der i smøresystemet indgår en smørepumpe, en trykakkumulator, der fødes ved hjælp af smørepumpen, og en styreventil, der er sluttet til trykakkumulatoren, og som med henblik på at få tilvejebragt smøring på et ønsket tidspunkt er indrettet til intermittent at kunne åbne en forbindelse mellem trykakkumulatoren og smørestedet.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a lubrication system in which lubricant is applied intermittently to a lubrication site, in particular a lubrication point in the cylinder wall of a piston engine, and which includes a lubrication pump, a pressure accumulator fed by the lubrication pump and a control valve connected to the pressure accumulator, and which, in order to provide lubrication at a desired time, is arranged to intermittently open a connection between the pressure accumulator and the lubrication site.

Der kendes smøresysterner, hvor man ved hjælp af en pumpe, en trykakkumulator og en tvangsstyret styreventil kan få tilvejebragt intermittent smøring via et smørested i cylindervæggen af en stempelmotor, hvorved smøretidspunktet er afhængigt af stempelstillingen. Disse kendte smøresystemer har imidlertid forskellige ulemper.Lubrication systems are known in which intermittent lubrication can be provided by means of a pump, a pressure accumulator and a forced control valve via a lubrication point in the cylinder wall of a piston engine, the lubrication time being dependent on the piston position. However, these known lubrication systems have various disadvantages.

2 142588 Sædvanligvis skal f.eks. pumpen udføre et konstant arbejde uafhængigt af den mængde smøremiddel, der skal erstattes. Dette kræver en unødvendig høj effekt til drivning af pumpen, hvortil kommer, at der opstår et uønsket tab af varme i den eller de overstrømningsventiler, som kræves for at gencirkulere det pumpede, men ikke forbrugte smøremiddel.Usually, e.g. the pump does a constant job regardless of the amount of lubricant to be replaced. This requires an unnecessarily high power to operate the pump, in addition to which an undesirable loss of heat occurs in the overflow valve (s) required to recycle the pumped but not consumed lubricant.

Fra svensk patentskrift nr. 71.816 kendes der et smøresystem, hvor man kun kan ændre smøremiddelmængden ved at ændre på indsprøjtningstiden. Dette er imidlertid ikke ønskeligt, når det gælder om at træffe et vel defineret område af det forbipasserende stempel.From Swedish Patent Specification No. 71,816 there is known a lubrication system where you can only change the amount of lubricant by changing the injection time. However, this is not desirable when it comes to hitting a well-defined area of the passing piston.

Fra svensk patentskrift nr. 178.517 kendes der endvidere et smøresystem, hvor smøretidspunktet styres ved hjælp af en styreventil, som påvirkes elektromekanisk. I praksis muliggør magnetventilen dog ikke en tilstrækkelig hurtig åbning. For hvert smørested befinder smøremidlet sig i en akkumulator, som også udgør en doseringsenhed. Akkumulatoren tilføres smøremiddel ved hjælp af en ikke nærmere forklaret pumpe, der skal indstilles til en passende strømning, som svarer til forbruget. Hvorledes dette sker, fremgår imidlertid ikke af nævnte patentskrift.Swedish patent specification 178,517 also discloses a lubrication system, in which the timing of the lubrication is controlled by means of a control valve which is electromechanically actuated. In practice, however, the solenoid valve does not allow a sufficiently rapid opening. For each lubrication site, the lubricant is contained in an accumulator which also forms a dosing unit. The accumulator is supplied with lubricant by means of an unexplained pump to be adjusted to a suitable flow corresponding to the consumption. However, this does not appear in the said patent.

Opfindelsen har til formål at eliminere forannævnte ulemper ved de kendte smøresystemer. Med udgangspunkt i den indledningsvis omhandlede konstruktion tilsigter opfindelsen nærmere bestemt at skabe et smøresystem af enkel og driftssikker opbygning, som muliggør en effektiv smøring med et mindsket smøremiddelforbrug.The invention aims to eliminate the aforementioned disadvantages of the known lubrication systems. More specifically, the invention aims at creating a lubrication system of simple and reliable construction which enables efficient lubrication with a reduced lubricant consumption.

Til opnåelse heraf er smøresystemet ifølge opfindelsen ejendommeligt ved, at der mellem syreventilen og smørestedet er anbragt en doseringsenhed, der kan omstilles til forskellige doseringsmængder smøremiddel, og at smørepumpen og trykakkumulatoren er forbundet med hinanden ved hjælp af et reguleringsorgan, som er indrettet til at kunne afføle smøremiddelforbruget i trykakkumulatoren og begrænse pumpekapaciteten til en til erstatning for forbrugt smøremiddelvolumen nødvendig kapacitet, hvorved der tilvejebringes en automatisk tilpasning af pumpekapaciteten til det ved hjælp af doseringsenheden indstillelige smøremiddelbehov.To achieve this, the lubrication system according to the invention is characterized in that a dosing unit is arranged between the acid valve and the lubrication unit, which can be switched to different amounts of lubricant, and that the lubrication pump and the pressure accumulator are connected to each other by means of a control device which is arranged to be able to sensing the lubricant consumption in the pressure accumulator and limiting the pump capacity to a capacity needed to replace consumed lubricant volume, thereby providing an automatic adjustment of the pump capacity to the lubricant demand adjustable by the metering unit.

Med denne udformning er der skabt et smøresystem, der, som det vil fremgå af det følgende, har væsentlige tekniske fordele i sammenligning med de kendte smøresystemer til lignende formål.With this design, a lubrication system has been created which, as will be apparent from the following, has significant technical advantages in comparison with the known lubrication systems for similar purposes.

Med udformningen ifølge opfindelsen opnår man et smøresystem, der arbejder på en sådan måde, at der kun er behov for at frempumpe netop den oliemængde, som forbruges. Fordelen herved er, at man undgår unødvendigt pumpearbejde, idet det ikke er nødvendigt at gencirkulere nogen overskudsolie gennem en overstrømningsventil. En anden fordel er, at man selv ved anvendelse af en enkel pumpe kan opnå en jævn oliestrøm med små trykvariationer under driften, hvor man ved hjælp 3 142588 af styreventilen kan udnytte det i trykakkumulatoren herskende olietryk til hurtigt at skabe smøring ved den rette stempelstilling, og hvor doseringsenheden muliggør en regulering af smøremiddelmængden ved hvert smørested.The design according to the invention achieves a lubrication system which operates in such a way that there is only need to pump precisely the amount of oil consumed. The advantage of this is that unnecessary pump work is avoided, since no excess oil has to be recirculated through an overflow valve. Another advantage is that even with the use of a simple pump, a smooth flow of oil with small pressure variations can be achieved during operation, whereby the oil pressure prevailing in the pressure accumulator can be utilized to quickly create lubrication at the correct piston position. and wherein the metering unit enables a control of the amount of lubricant at each lubrication site.

En udførelsesform for smøresystemet ifølge opfindelsen, som medvirker til at sikre en upåklagelig drift, er ejendommelig ved, at pumpen er en stempelpumpe og har et pumpestempel, der ved hjælp af en returfjeder trykkes i retning mod en til drivning af pumpen bestemt pumpeexcentrik, og at der i trykakkumulatoren indgår et akkumulatorstempel, som er indrettet til ved hjælp af en fjeder, fortrinsvis en forspændt trykfjeder, at kunne presses ind i det akkumulatorkammer, hvori der indpumpes smøremiddel. Med denne udformning opnår man en enkel og funktions-sikker udførelse af såvel smørepumpen som trykakkumulatoren, hvor pumpen drives på en enkel måde, og trykakkumulatorens fjeder muliggør, at smøremidlet kan holdes på et vist tryk.An embodiment of the lubrication system according to the invention which assists in impeccable operation is characterized in that the pump is a piston pump and has a pump piston which is pressed by means of a return spring in the direction of a pump eccentric for driving the pump and that the pressure accumulator includes an accumulator piston which is adapted to be pressed into the accumulating chamber in which the lubricant is pumped into the accumulator chamber by means of a spring, preferably a biased pressure spring. With this design, a simple and function-safe design of both the lubrication pump and the pressure accumulator is achieved, where the pump is operated in a simple manner and the spring of the pressure accumulator allows the lubricant to be kept at a certain pressure.

En udførelsesform for denne udførelse af smøresystemet ifølge opfindelsen er ejendommelig ved, at fjedrene er indrettet til at kunne forskyde pumpestemplet og akkumulatorstemplet i samme retning, at reguleringsorganet udgøres af en medbringer, der er forskydelig synkront med pumpestemplet, og at der på medbringeren og akkumulatorstemplet findes samvirkende organer, ved hjælp af hvilke medbringerens forskydning i pumpestemplets sugeretning begrænses til en stilling afhængig af fyldningsgraden i akkumulatorkammeret, hvorved pumpestemplets bevægelse afpasses efter størrelsen af smøremiddelforbruget. Med denne udformning undgår man en unødvendig pumpning, hvis forbruget har været lille.An embodiment of this embodiment of the lubrication system according to the invention is characterized in that the springs are arranged to be able to displace the pump piston and the accumulator piston in the same direction, that the regulating means is constituted by a carrier which is displaceable synchronously with the pump piston and that the carrier and accumulator piston are present. cooperating means by which the displacement of the carrier in the suction direction of the pump piston is limited to a position depending on the degree of filling in the accumulator chamber, whereby the movement of the pump piston is adjusted to the size of the lubricant consumption. This design avoids unnecessary pumping if consumption is low.

Ifølge opfindelsen kan medbringeren have et parti anbragt således, at det kan befinde sig mellem pumpestemplet og pumpeexcentrikken. Med denne udformning kan pumpestemlet bibringes en vis bevægelsesfrihed, uden at der kræves specielle foranstaltninger, såsom spor eller udskæringer.According to the invention, the carrier may have a portion arranged such that it may be located between the pump piston and the pump eccentric. With this design, the pump body can be given some freedom of movement without requiring special measures such as grooves or cuts.

Volumenet i akkumulatorkammeret kan ifølge opfindelsen være større end det pumpede volumen under et arbejdsslag af pumpen. Med denne udformning sikres der en lav trykvariation i smøremidlet - selv ved anvendelsen af en énstempelpumpe.According to the invention, the volume of the accumulator chamber may be greater than the pumped volume during a working stroke of the pump. This design ensures a low pressure variation in the lubricant - even when using a one-piston pump.

En fordelagtig udførelsesform for smøresystemet ifølge opfindelsen er ejendommelig ved, at der i doseringsenheden indgår mindst én i og for sig kendt doseringsventil, som arbejder med to trykniveauer, dels et højtryksniveau, hvor der sker smøring med en forudbestemt doseringsmængde, og dels et lavtryksniveau, hvor der igen sker tilførsel af doseringsmængden, at der i hver doseringsventil findes et forskydeligt doseringsstempel, og at slaglængden af disse stempler, og dermed doseringsmængden, er fælles indstillelig for flere doseringsventiler. Med denne udformning kan doseringsmængden ændres på en enkel måde. Anvendelsen af to trykniveauer bevirker, at der ikke kan lække smøremiddel tilbage, når der igen sker tilførsel af en doseringsmængde.An advantageous embodiment of the lubrication system according to the invention is characterized in that the dosing unit includes at least one known dosing valve which operates with two pressure levels, partly a high pressure level where there is a lubrication with a predetermined dosage amount and partly a low pressure level where again, the dosing amount is applied, that there is a displaceable dosing piston in each dosing valve, and that the stroke length of these pistons, and thus the dosing amount, is jointly adjustable for multiple dosing valves. With this design, the dosage amount can be changed in a simple way. The use of two pressure levels means that no lubricant can be left when a dosing amount is applied again.

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En udførelsesform for sidstnævnte udførelse af smøresysteraet ifølge opfindelsen, med hvilken der kan opnås en enkel synkronisering af slaglængden for flere doseringsstempler, er ejendommelig ved, at doseringsenheden har en drejelig doseringsaksel med en til hvert doseringsstempel hørende, drejefast monteret dosering s excentrik, hvorved der gennem drejning af doseringsakslen er mulighed for at variere doseringsstemplets slaglængde.An embodiment of the latter embodiment of the lubrication system according to the invention, with which a simple synchronization of the stroke length can be achieved for several dosing pistons, is characterized in that the dosing unit has a pivotable dosing shaft with a pivotally mounted dosing eccentric associated with each dosing piston, rotation of the metering shaft is possible to vary the stroke length of the metering piston.

En fordelagtig udførelsesform for smøresystemet ifølge opfindelsen er ejendommelig ved, at styreventilen udgøres af en skydeventil med et fortrinsvis vertikalt, pasningstætnet og hydraulisk afbalanceret plungestempel, der med sin nedre ende, under indvirkning af en fjeder, hviler mod en på en roterende aksel anbragt knastkurve, som er indrettet til én gang pr. akselomdrejning kortvarigt at kunne forskyde plungestemplet til en øvre stilling, så at smøremiddel fra et akkumulatorkammer i trykakkumulatoren kan passere via styreventilen, og at plungestemplet er indrettet til i sin nedre stilling, hvilestillingen, at kunne blokere strømmen fra akkumulatorkammeret og i stedet forbinde doseringsenheden med en trykaflastningsventil. Med denne udformning opnår man en styreventil, som muliggør en hurtig smøring på det rette tidspunkt, og der opnås en god synkronisering med motoren.An advantageous embodiment of the lubrication system according to the invention is characterized in that the control valve consists of a sliding valve with a preferably vertical, fit-sealed and hydraulically balanced plunger piston, which, with the action of a spring, rests against a cam curve arranged on a rotating shaft. which is arranged once per shaft rotation briefly to be able to displace the plunger piston to an upper position so that lubricant from an accumulator chamber in the pressure accumulator can pass through the control valve, and that the plunger plunger is arranged to be in its lower position, the rest position, to block the current from the accumulator chamber and connect the dosing unit instead pressure relief valve. With this design, a control valve is obtained, which enables rapid lubrication at the right time, and good synchronization with the motor is achieved.

En udførelsesform for sidstnævnte udførelse af smøresystemet ifølge opfindelsen er ejendommelig ved, at piungestemplets nedre ende er forsynet med en i ventilhuset passende gejde til optagelse af sidekræfter forårsaget af knastkurven, og at plungestemplet via gejden og en på denne anbragt løfterulle hviler mod knastkurven. Denne udformning har den fordel, at sidekræfter ikke giver anledning til problemer under de hurtige forløb, som der her er tale om.An embodiment of the latter embodiment of the lubrication system according to the invention is characterized in that the lower end of the sealing plunger is provided with a guide suitable for accommodating side forces caused by the cam curve and the plunger plunger via the guide and a lifting roller placed on the cam curve. This design has the advantage that side forces do not cause problems during the fast processes in question.

Ifølge opfindelsen kan to eller flere styreventiler være sammenbygget, og deres knastkurver kan være anbragt på en fælles aksel, som fortrinsvis også udgør drivaksel for pumpen. Herved opnår man en enkel og kompakt konstruktion, hvori to eller flere styreventiler er sammenbygget til en enhed.According to the invention, two or more control valves may be assembled and their cam curves may be arranged on a common shaft, which preferably also constitutes the drive shaft for the pump. This provides a simple and compact construction in which two or more control valves are assembled into one unit.

En fordelagtig udførelsesform for smøresystemet ifølge opfindelsen, som anvendes til smøring af en fartøjs- eller skibsmotor, er ejendommelig ved, at pumpen og styreventilen er påvirket af en aksel, som er koblet til motorens styreaksel. Med denne udformning kan man opnå en god synkronisering med motoren, uden at der kræves nogen ekstra drivning.An advantageous embodiment of the lubrication system according to the invention used for lubricating a vessel or ship engine is characterized in that the pump and control valve are actuated by a shaft coupled to the engine shaft. With this design you can achieve good synchronization with the engine without requiring any additional drive.

En udførelsesform for sidstnævnte udførelse af smøresystemet ifølge opfindelsen er ejendommelig ved, at styreventilen er indrettet til kun at være åben, medens et af stempelringe afgrænset rum på et stempel passerer smørestedet. Med denne udformning får man mulighed for at træffe et bestemt smøreområde med en vis mængde smøremiddel, og man opnår en reduktion af smøremiddelforbruget.An embodiment of the latter embodiment of the lubrication system according to the invention is characterized in that the control valve is arranged to be open only while a space defined by piston rings on a piston passes through the lubrication site. This design allows you to hit a specific lubrication area with a certain amount of lubricant and a reduction in lubricant consumption is achieved.

En sidste fordelagtig udførelsesform for smøresystemet ifølge opfindelsen er ejendommelig ved, at hver styreventil regulerer smøremiddeltilførsien til 5 1Λ2588 mindst to smøresteder. Med denne udformning kan man reducere antallet af styreventiler, hvis der skal ske smøring samtidigt via flere smøresteder.A last advantageous embodiment of the lubrication system according to the invention is characterized in that each control valve regulates the lubricant supply to at least two lubrication points. With this design, the number of control valves can be reduced if lubrication is to be carried out simultaneously via several lubrication points.

Opfindelsen forklares nærmere i det følgende ved hjælp af et udførelseseksempel under henvisning til tegningen, hvor fig. 1 viser et sidebillede af en ifølge opfindelsen smurt cylinder, fig. 2 et horisontalsnit langs smørekanaler til den i fig.l viste cylinder, fig. 3 skematisk og delvis i snit et smøresystem ifølge opfindelsen, fig. 4 et snit efter linien IV-IV i fig, 3, fig. 5 et snit efter linien V-V i fig. 3, fig. 6 et snit efter linien VI-VI i fig. 3, fig. 7 et snit efter linien VII-VII i fig. 3, fig. 8 et snit efter linien VIII-VIII i fig. 3, fig. 9 et snit efter linien IX-IX i fig. 3, fig. 10 skematisk to sammenkoblede doseringsenheder ifølge opfindelsen, fig. 11 skematisk en ifølge opfindelsen smurt fartøjs- eller skibsmotor, fig. 12 en anden udføreIsesform for den i fig. 3 viste reservepumpe, fig. 13 et snit efter linien XIII-XIII i fig. 12, fig. 14 et snit efter linien XIV-XIV i fig. 12, og fig. 15 et snit efter linien XV-XV i fig. 12*The invention will be explained in more detail below with the aid of an exemplary embodiment with reference to the drawing, in which fig. 1 is a side view of a cylinder lubricated according to the invention; FIG. 2 is a horizontal section along the lubrication channels of the cylinder shown in FIG. 1; 3 is a schematic and partial sectional view of a lubrication system according to the invention; FIG. 4 is a sectional view taken along line IV-IV of FIG. 3; FIG. 5 is a section along the line V-V in FIG. 3, FIG. 6 is a sectional view taken along line VI-VI of FIG. 3, FIG. 7 is a sectional view taken along line VII-VII of FIG. 3, FIG. 8 is a section along line VIII-VIII of FIG. 3, FIG. 9 is a section along line IX-IX of FIG. 3, FIG. 10 schematically shows two interconnected dosing units according to the invention; FIG. 11 schematically illustrates a vessel or ship engine lubricated in accordance with the invention; FIG. 12 shows another embodiment of the embodiment shown in FIG. 3; FIG. 13 is a section along the line XIII-XIII of FIG. 12, FIG. 14 is a section along the line XIV-XIV of FIG. 12, and FIG. 15 is a sectional view taken along line XV-XV of FIG. 12 *

Ifølge fig. 1 er et stempel 1, der drives via en plej Istang 2 og en krumtapaksel 3, bevægeligt frem og tilbage i en cylinder 4. Stemplet 1 har en øvre stempelring 5 og en nedre stempelring 6 anbragt i en vis afstand fra hinanden. I cylindervæggen udmunder mindst ét smøreraiddeludløb 7, der forsynes med smøremiddel via en smøremiddelledning 8. Hensigten er via smøremiddeludløbet 7 at tilføre stemplet l’s glideflade smøremiddel i den korte tid, hvor området mellem stempelringene 5 og 6 passerer smøremiddeludløbet 7 i cylindervæggen, medens stemplet bevæger sig mellem sine vendestillinger. Herved opnår man, at smøremidlet spredes over cylinderfladen, men holdes mellem stempelringene. For at dette skal være muligt, må der trykkes smøremiddel, sædvanligvis olie, ind i det rette øjeblik og med tilstrækkelig høj hastighed for at aflevere en tilstrækkelig oliemængde. Et sådant smørebehov foreligger f.eks. ved store fartøjs- eller skibsmotorer med forholdsvis lavt omløbstal, hvor stempeldiameteren ofte er af størrelsesordenen 1 m.According to FIG. 1 is a piston 1 driven via a groove rod 2 and a crankshaft 3, movable back and forth in a cylinder 4. The piston 1 has an upper piston ring 5 and a lower piston ring 6 spaced apart. At least one lubricant outlet 7 provided with lubricant through a lubricant conduit 8 opens into the cylinder wall. between its turning positions. This results in the spreading of the lubricant over the cylinder surface, but kept between the piston rings. For this to be possible, lubricant, usually oil, must be pressed in at the right moment and at a sufficiently high speed to deliver a sufficient amount of oil. Such a lubrication need exists, e.g. for large vessel or ship engines with a relatively low orbital number, where the piston diameter is often of the order of 1 m.

Under krumtapakslen 3*s rotation i retning af pilen 9 må smøremiddel-tilførsien således følge med under en begrænset vinkel « af krumtapakslens omdrejning. Størrelsen af vinklen oc vil variere med slaglængden og stempelringafstanden, men kan ved en større skibsmotor normalt beløbe sig til ca. 6°. Denne lille vinkel stiller store krav til det udstyr, der skal sørge for olieindsprøjtning. Tiden, der er til rådighed for indsprøjtningen, vil variere med omløbstallet.Thus, during rotation of the crankshaft 3 * in the direction of the arrow 9, the lubricant supply must follow at a limited angle 'of the rotation of the crankshaft. The size of the angle and will vary with the stroke length and the piston ring distance, but can usually amount to approx. 6 °. This small angle places great demands on the equipment that will provide oil injection. The time available for injection will vary with the circulation figure.

6 1425886 142588

For at kunne få en effektiv smøring på den beskrevne måde er det nødvendigt at tilføre smøremiddel på mere end ét sted rundt langs cylindervæggen. Fig. 2 viser en cylinder med otte smøresteder 7, men der er selvsagt mulighed for andre antal. Ved en større cylinder kan der være behov for f.eks. tolv smøresteder, medens det ved en mindre cylinder kan være tilstrækkeligt med f.eks. fire smøresteder. Som vist i fig. 2 står hvert andet af smøremiddeludløbene 7 via hver sin ledning 8 i forbindelse med en doseringsenhed 10, der fødes via en trykledning 12, medens de resterende smøremiddeludløb 7 på tilsvarende måde står i forbindelse med en doseringsenhed 11, som fødes via en trykledning 13. Smøring sker hensigtsmæssigt én gang pr. krumtapakselomdrejning, fortrinsvis under stemplets opadgående bevarelse. Ved hjælp af doseringsenhederne 10 og 11 kan der ske smøring ved blot det halve antal smøresteder for hver omdrejning. Oliemængden, der normalt tilføres ved hvert smørested hver gang, beløber sig hensigtsmæssigt til ca. 30 mm (ca. én dråbe). Denne mængde kan naturligvis varieres inden for visse grænser, hvilket f.eks. kan være nødvendigt som følge af varierende driftsbetingelser. Det kan f.eks. være ønskeligt undertiden at kunne tilføre en ca. fire gange større mængde end under normal drift. Det kan også være ønskeligt at kunne anvende samme udstyr til motorer af forskellig størrelse, hvorfor en vis fleksibilitet er ønskelig.In order to achieve effective lubrication in the manner described, it is necessary to apply lubricant in more than one place around the cylinder wall. FIG. 2 shows a cylinder with eight lubrication points 7, but of course other numbers are possible. For a larger cylinder there may be a need for e.g. twelve lubrication points, while for a smaller cylinder it may suffice e.g. four lubrication sites. As shown in FIG. 2, each of the lubricant outlets 7 is connected via a separate conduit 8 to a metering unit 10 which is fed via a pressure line 12, while the remaining lubricant outlets 7 are similarly connected to a dosing unit 11 which is fed via a pressure line 13. Lubrication is conveniently done once per. crankshaft rotation, preferably during the upward conservation of the piston. The metering units 10 and 11 can be lubricated at just half the number of lubrication points per revolution. The amount of oil normally supplied at each lubrication site each time amounts to approx. 30 mm (about one drop). This amount can, of course, be varied within certain limits, e.g. may be necessary due to varying operating conditions. It can for example. be desirable sometimes to be able to add an approx. four times greater than in normal operation. It may also be desirable to be able to use the same equipment for different sized motors, which is why some flexibility is desirable.

Fig. 3 viser en mulig udførelsesform for et smøresystem 14 ifølge opfindelsen. Dette smøresystem er opbygget af et antal separate, kombinerbare enheder, der også kan anvendes i andre kombinationer end vist, eller også hver for sig i andre tilfælde. I systemet indgår der en pumpe 15, der samvirker med en tryk-akkumulator 16. På hver side af pumpen 15 findes der en med pumpen sammenmonteret styreventilenhed henholdsvis 17 og 18, som sørger for smøring på det rette tidspunkt. Pumpen 15 forsynes med olie fra en olietank 19, der fortrinsvis er højt beliggende, så der automatisk opnås det nødvendige tryk for olietilgang til pumpen. Styreventilenhederne 17 og 18 står via en reservepumpe 20 i forbindelse med hver to doseringsenheder, idet styreventilenheden 17 er forbundet med doseringsenhederne 10 og 11. Pumpen 15 drives via en aksel 21, der er forbundet med motorens ikke viste styreaksel, der roterer med et omløbstal, som er nøjagtigt det halve af krumtapakslens omløbstal. Styreakslen svarer til knastakslen i f.eks. en automobilmotor. Akslen 21 påvirker også styreventil-enhederne 17 og 18.FIG. 3 shows a possible embodiment of a lubrication system 14 according to the invention. This lubrication system is made up of a number of separate, combinable units which can also be used in combinations other than shown, or also separately in other cases. The system includes a pump 15 which cooperates with a pressure accumulator 16. On each side of the pump 15 there is a control valve assembly 17 and 18, respectively, which is mounted with the pump, which provides for lubrication at the correct time. The pump 15 is supplied with oil from an oil tank 19, which is preferably high so as to automatically obtain the necessary pressure for oil access to the pump. The control valve units 17 and 18 are connected via a spare pump 20 to each of two metering units, the control valve unit 17 being connected to the metering units 10 and 11. The pump 15 is driven via a shaft 21 which is connected to the control shaft of the motor which does not rotate with a rotary number. which is exactly half of the crankshaft rotational speed. The steering shaft corresponds to the camshaft in e.g. an automobile engine. The shaft 21 also affects the control valve units 17 and 18.

Pumpen 15 er en excentrikdrevet sterapelpumpe med fjedertilbagegang, hvor et pumpestempel 22 drives af en på akslen 21 anbragt pumpeexcentrik 23, mod hvilken den presses ved hjælp af en returfjeder 24. Pumpeexcentrikken 23 går blødt og giver kun anledning til små accelerationskræfter på pumpestemplet 22, som udfører et arbejdsslag for hver styreakselomdrejning. Fra olietanken 19 udgår der en ledning 25, som via en ledning 26 og en kontraventil 27 for 142588 7 syner pumpen 15 med olie. Via en kontraventil 28 trykkes der olie ud i et akkumulatorkammer 29 i trykakkumulatoren 16. Ved hjælp af et akkumulatorstem-pel 30 kan akkumulatorkammeret 29's volumen varieres. En trykfjeder 31 presser akkumulatorstemplet 30 nedad og tilstræber at formindske akkumulator-kammeret 29's volumen og således opretholde et vist tryk deri. Det maksimale akkumulatorkamraervolumen er hensigtsmæssigt større end det maksimale pmipevolumen. Ved at montere trykfjederen 31 med en vis forspænding kan trykket i akkumulatorkammeret 29 holdes i hovedsagen konstant for de volumenvariationer, der kommer på tale som følge af olieudfødning fra akkumulaforkammeret.The pump 15 is an eccentric driven spring return pump, in which a pump piston 22 is driven by a pump eccentric 23 located on the shaft 21 against which it is pressed by a return spring 24. The pump eccentric 23 runs soft and gives rise only to small acceleration forces on the pump piston 22, which performs a work stroke for each steering shaft revolution. From the oil tank 19 there is a conduit 25, which via a conduit 26 and a check valve 27 for pumping the pump 15 with oil. Via a check valve 28, oil is pressed into an accumulator chamber 29 in the pressure accumulator 16. By means of an accumulator piston 30, the volume of the accumulator chamber 29 can be varied. A pressure spring 31 presses the accumulator plunger 30 downwardly and seeks to decrease the volume of the accumulator chamber 29 and thus maintain a certain pressure therein. The maximum accumulator chamber volume is conveniently greater than the maximum pmipe volume. By mounting the compression spring 31 with a certain bias, the pressure in the accumulator chamber 29 can be kept substantially constant for the volume variations due to oil supply from the accumulator chamber.

Pumpestemplet 22 og akkumulatorstemplet 30 er sammenkoblet via en medbringer 32, der kan begrænse pumpestemplet 22’s nedadgående bevægelse som en funktion af akkuraulatorstemplet 30's stilling. Pumpestemplet 22 vil standses under sin nedadgående bevægelse, når et fremspring 33 på medbringeren 32 støder mod et tilsvarende fremspring 34 på akkumulatorstemplet 30. Hvis der ikke forbruges olie eller forbruges mindre olie end et fuldt pumpeslag pr. pumpeomdrejning, vil medbringeren hindre pumpestemplet i at gå tilbage til fuldt tilbageført stilling. Tilbagegangen er udført således, at den svarer til det forbrugte olievolumen. Herved opnår man, at blot den oliemængde, som forbruges, kommer til at pumpes frem under det næste pumpes lag. Fordelen ved dette er, at man undgår et unødvendigt pumpearbejde, idet ingen overskudsolie behøver at gencirkuleres gennem en overstrømningsventil. En yderligere fordel er, at man kan opnå en jævn oliestrøm med små trykvariationer til trods for, at det drejer sig om en énstempelpumpe. Pumpen 15 er hensigtsmæssigt dimensioneret til at kunne forsyne en stor motorcylinder, men det er muligt at anvende samme pumpe til betydeligt mindre motorer med mindre smøremiddelbehov. Pumpekapaciteten kan f.eks. , som i det viste tilfælde, være tilstrækkelig til to cylindre, hvor smøremiddeludløbene i hver cylinder er delt i to forskellige grupper, fig. 2, der sammen kontrolleres af hver sin styreventi lenhed.The pump piston 22 and the accumulator piston 30 are interconnected via a carrier 32 which can limit the downward movement of the pump piston 22 as a function of the position of the accumulator piston 30. The pump piston 22 will stop during its downward movement when a projection 33 on the carrier 32 bumps on a corresponding projection 34 on the accumulator piston 30. If no oil is consumed or less oil than a full pump stroke per pump rotation, the driver will prevent the pump piston from returning to full return position. The decline is made to correspond to the oil volume consumed. This results in the fact that only the amount of oil consumed will be pumped out under the layer of the next pump. The advantage of this is that you avoid unnecessary pump work, since no excess oil has to be recirculated through an overflow valve. A further advantage is that a smooth oil flow with small pressure variations can be achieved, despite the fact that it is a single-piston pump. The pump 15 is suitably sized to supply a large motor cylinder, but it is possible to use the same pump for significantly smaller motors with less lubricant requirements. The pump capacity can e.g. , as in the case shown, be sufficient for two cylinders in which the lubricant outlets in each cylinder are divided into two different groups; 2, which together are controlled by each control valve unit.

De to styreventilenheder 17 og 18 er opbygget ens og regulerer snøring af hver sin cylinder til en motor, som i det viste tilfælde har seks cylindre. Heraf følger, at styreventilenhederne 17 og 18 arbejder med en vis indbyrdes faseforskydning bestemt af cylinderantallet og den indbyrdes cylinderplacering. For ,.; enkelhedens skyld skal kun styreventilenheden 17 forklares nærmere i det følgende.The two control valve units 17 and 18 are constructed in the same way and regulate the lacing of each cylinder to a motor which in the case shown has six cylinders. It follows that the control valve units 17 and 18 operate with some mutual phase shift determined by the cylinder number and the cylinder position. For ,.; for the sake of simplicity, only the control valve assembly 17 will be explained in more detail below.

I styreventilenheden 17 indgår der to indbyrdes ens styreventiler 35 og 36, der påvirkes af hver sin knastkurve henholdsvis 37 og 38 på akslen 21. Styreventilerne 35, 36 er udført som skydeventiler med pasningstætnede plunge-stempler 39, A0. Opgaven for hver styreventil er ved en præcis stempelstilling i motoren at åbne en forbindelse fra en trykoliekilde, i det foreliggende tilfælde akkumulatorkammeret 29. Derefter skal denne forbindelse lukkes og i 8 142588 stedet en anden forbindelse åbnes, hvilket forklares i det følgende. For at opnå de hurtige åbningsforløb, der kræves, må knastkurverne 37 og 38 gøres meget stejle. Dette giver anledning til bl.a. store sidekræfter på plungestemplerne 39 og AO. For at optage disse sidekræfter er plungestemplerne 39 og AO forsynet med hver sin gejde 41, som løber i et tilsvarende spor i ventilhuset. For at opnå en friktionsformindskelse findes der på hver gejde en løfterulle 42, som ligger an mod den respektive knastkurve 37, 38 under påvirkning af en trykfjeder 43 i hver styreventil.The control valve unit 17 includes two mutually identical control valves 35 and 36 which are actuated by each cam curve 37 and 38 respectively on the shaft 21. The control valves 35, 36 are designed as sliding valves with sealed plunger pistons 39, A0. The task of each control valve is to open, at a precise piston position in the engine, a connection from a pressure oil source, in the present case the accumulator chamber 29. Then this connection must be closed and in another place the connection is opened, which is explained below. In order to achieve the fast opening required, the cam curves 37 and 38 must be made very steep. This gives rise to, among other things, large side forces on the plunger pistons 39 and AO. To absorb these lateral forces, the plunger pistons 39 and AO are each provided with guide 41, which runs in a corresponding groove in the valve housing. To achieve a friction reduction, on each guide there is a lifting roller 42 which abuts the respective cam curve 37, 38 under the influence of a compression spring 43 in each control valve.

Styreventilen 35 er via en ledning 44 og et kammer 45 i reservepumpen 20 forbundet med en trykledning 12 til en doseringsenhed 10, og på tilsvarende måde er styreventilen 36 via en ledning 46 og et kammer 47 forbundet med en trykledning 13 til en doseringsenhed 11, fig. 2. De to styreventiler 35, 36 er desuden via en ledning 48 og en kontraventil 49 forbundet med olietanken 19.The control valve 35 is connected via a conduit 44 and a chamber 45 in the reserve pump 20 to a pressure line 12 for a metering unit 10, and similarly, the control valve 36 is connected via a conduit 46 and a chamber 47 to a pressure line 13 for a metering unit 11. . 2. The two control valves 35, 36 are additionally connected to the oil tank 19 via a conduit 48 and a check valve 49.

Akslen 21 løber gennæn et akselkammer 50, der hensigtsmæssigt er oliefyldt. Via en kanal 51 er akselkammeret 50 forbundet med hvert af de kamre 52 og 53, hvori de øvre ender af plungestemplerne 39, AO når ind. Herved virker i hovedsagen samme hydrauliske tryk på hvert plungestempels to ender. Som vist i fig. 3, 7 og 8 er piungestemplerne udformet således, at der altid hersker en hydraulisk trykbalance på plungestemplerne i forskellige stillinger. Herved behøves der ved forskydningsbevægelser hovedsagelig kun at overvindes masse- og inertikræfter, hvilket medfører, at bevægelsen lettes. Også kammeret 54, hvori akkumulatorstemplet 30’s øvre del og trykfjederen 31 befinder sig, er via en kanal 55 forbundet med akselkammeret 50. Kanalerne 51 og 55 skaber sikkerhed for dels en trykudjævning og dels en smøring af de bevægelige dele.The shaft 21 passes through a shaft chamber 50 which is suitably oil filled. Via a channel 51, the shaft chamber 50 is connected to each of the chambers 52 and 53 into which the upper ends of the plunger pistons 39, AO reach. Hereby essentially the same hydraulic pressure acts on the two ends of each plunger piston. As shown in FIG. 3, 7 and 8, the scallop pistons are designed such that a hydraulic pressure balance always exists on the plunger pistons in different positions. This means that only shear and inertia forces need to be overcome in shear movements, which facilitates the movement. Also, the chamber 54, in which the upper part of the accumulator piston 30 and the compression spring 31 is located, is connected via a duct 55 to the shaft chamber 50. The ducts 51 and 55 provide security for both a pressure equalization and partly a lubrication of the moving parts.

Som vist i fig. 4, 5, 7 og 8 er for en og samme cylinder de to knastkurver (f.eks. 37 og 38) indbyrdes forskudt en vinkel på 180°. De kan derfor fremstilles parvis med indbyrdes fast indstilling, og kan ligesom pumpeexcentrikken 23 være udført i ét stykke med akslen 21. I det foreliggende tilfælde udgør knastkurverne 37 og 38 imidlertid en del af en knastbøsning 56, som er påført akslen 21 til højre for pumpeexcentrikken 23. Via en medbringerstift 57 er knastbøsningen 56 forbundet drejefast med en indexskive 58, som på kendt måde via f.eks. kile og kiléspor er forbundet drejefast med akslen 21 i en vis stilling i forhold til denne. En møtrik 59 holder knastbøsningen 56 og indexskiven 58 på plads på akslen 21«As shown in FIG. 4, 5, 7 and 8, for one and the same cylinder, the two cam curves (eg 37 and 38) are offset at an angle of 180 °. Therefore, they can be made in pairs with mutually fixed adjustment and, like the pump eccentric 23, can be made integrally with the shaft 21. In the present case, however, the cam curves 37 and 38 form part of a cam sleeve 56 which is applied to the shaft 21 to the right of the pump eccentric. 23. Via a carrier pin 57, the cam bush 56 is pivotally connected to an index disk 58 which, in known manner via e.g. wedge and wedge grooves are pivotally connected to shaft 21 in a certain position relative thereto. A nut 59 holds the cam sleeve 56 and index disc 58 in place on shaft 21 «

Som vist i fig. 9 er indexskiven 58 forsynet med et antal med ens deling fordelte huller 60, hvor medbringerstiften 57 griber ind i det øverste. Delingen mellem hullerne 60 varierer med motorens cylinderantal. Ved f.eks. en sekscylindret motor er antallet af huller seks og delingen 60°, men ved en fircylindret motor er antallet af huller fire og delingen 90°. Den til styreven- 142583 9 tilunheden 18 hørende knastbøsning er identisk med knastbøsningen 56, men er drejet 60° i forhold til denne ved, at en tilsvarende medbringerstift i stedet griber ind i et hul op til det øverste hul i den tilsvarende indexskive, som i rotationsretning har samme orientering som indexskiven 58 i forhold til akslen 21. Mellem knastkurven 38 og akselkammeret 50's v^ 60 findes der en understøtning 61, ved hjælp af hvilken akslen 21 med påførte knastbøsninger holdes i en korrekt eksial stilling.As shown in FIG. 9, the index disc 58 is provided with a plurality of equally spaced holes 60, with the carrier pin 57 engaging the upper. The pitch between the holes 60 varies with the engine cylinder number. For example, a six-cylinder engine is the number of holes six and the pitch 60 °, but for a four-cylinder engine the number of holes four and the pitch is 90 °. The cam bushing of the control unit 18 is identical to the cam bushing 56, but is rotated 60 ° relative to it by a corresponding driver pin engaging in a hole up to the top hole of the corresponding index disk as in direction of rotation has the same orientation as the index disc 58 relative to shaft 21. Between the cam curve 38 and the shaft of the shaft chamber 50 there is a support 61 by means of which the shaft 21 with applied cam bushes is held in a proper axial position.

Arrangementet med løse knastbøsninger 56 gør det således muligt, at man ved udskiftning af indexskiven 58 på en enkel måde kan tilpasse styreventilfunk« tionen til motorer oed andre cylindertal.Thus, the arrangement of loose cam bushes 56 makes it possible to simply change the control valve function to engines and other cylinder numbers when replacing the index disc 58.

Reservepumpen 20 tjener til at forenkle påfyldning af olien ved start af smøresystemet og udgør en vis reservemulighed for hånddreven smøring. Den er udført således, at den frakobler den ordinære pumpe, men går ind på samme ledninger til doseringsenhederne. Samtlige tilsluttede doseringsenheder fødes samtidig af reservepumpen. Reservepumpen muliggør endvidere tømning af trykakkumulatoren 16, når den ordinære pumpe 15 er standset. I reservepumpen 20 indgår der et pumpestempel 62, som af en trykfjeder 63 trykkes til venstre i fig. 3 til den viste hvilestilling. Pumpestemplet 62 kan forskydes i aksial retning mod kraften fra fjederen 63, ved hjælp af en drivanordning 64, der som i det viste tilfælde kan være udført for manuel drift. Pumpestemplet 62 er forlænget og udgør også et; ventilplungestempel til omstyring af oliestrøwnen mellem den ordinære pumpe 15 og reservepumpen 20. I hvilestillingen står ledningerne 12 og 44 .1 forbindelse med hinanden via kammeret 45, ligesom ledningerne 13 og 46 står i forbindelse med hinanden via kammeret 47. Når reservepumpen 20 sættes i funktion, og pumpestemplet 62 via drivanordningen 64 føres til højre, kommer ledningerne 44 og 46 til at lukkes af stempelpar-tierne henholdsvis 65 og 66 og vil ved hjælp af disse forblive lukket under den frem- og tilbagegående pumpebevægelse. Ved indsugningsbevægelse vil der via en ledning 67 og en kontreventil 68 strømme olie ind i kammeret 69. Derfra trykkes olien via en kontraventil 70 og ledningen 71 ind i kamrene 45 og 47 og videre til ledningerne 12 og 13. Den herved opnåede smøring sker uden hensyn til stempelstillingen i motoren. Reservepumpen kan være indrettet til at smøre samtlige motorcylindre på én gang. Når reservepumpen standses, aflastes trykket i kammeret 69 og ledningen 71 via kontraventilen 49.The spare pump 20 serves to simplify the filling of the oil at the start of the lubrication system and provides a certain reserve option for hand-driven lubrication. It is designed so that it disconnects the ordinary pump but enters the same wiring to the dosing units. All connected dosing units are simultaneously fed by the backup pump. The spare pump further permits emptying of the pressure accumulator 16 when the ordinary pump 15 is stopped. The spare pump 20 includes a pump piston 62, which is pressed to the left by a compression spring 63 in FIG. 3 to the rest position shown. The pump piston 62 can be displaced axially against the force of the spring 63 by means of a drive device 64 which, as in the case shown, may be designed for manual operation. Pump piston 62 is extended and also constitutes one; valve plunger piston for routing the oil flow between the ordinary pump 15 and the backup pump 20. In the resting position, the wires 12 and 44 are connected to each other via the chamber 45, as well as the wires 13 and 46 are connected to each other via the chamber 47. When the spare pump 20 is activated and the pump piston 62 is driven to the right via the drive 64, the conduits 44 and 46 will be closed by the piston portions 65 and 66, respectively, and will remain closed during the reciprocating pump movement. Upon suction movement, oil will flow into chamber 69 via a conduit 67 and a check valve 68. From there, the oil is pressurized via a check valve 70 and the conduit 71 into the chambers 45 and 47 and on to the conduits 12 and 13. to the piston position in the engine. The spare pump can be arranged to lubricate all the engine cylinders at once. When the auxiliary pump is stopped, the pressure in the chamber 69 and the conduit 71 is relieved via the check valve 49.

De to doseringsenheder 10 og 11 er indbyrdes ens, hvorfor blot doseringsenheden 10, fig. 10, skal forklares nærmere. Fra trykledningen 12 udgår der et antal, i det foreliggende tilfælde fire, fordelingsledninger 72, der hver for sig fører til en i og for sig kendt doseringsventil 73 for hvert smørested. Disse doseringsventiler kan også være sammenbygget for fælles fødning. For enkelhedens skyld erder blot vist én doseringsventil 73, hvori der indgår et dose ίο 142588 ringsstempel 74, som af en trykfjeder 75 presses i retning mod en doseringsexcentrik 77 anbragt på en doseringsaksel 76. Ved doseringsstemplet 74's bort fra doseringsexcentrikken 77 vendende ende findes der en kanal 78, som via en kontraventil 79 udmunder i en ledning 8 til et smørested. Ved hjælp af en skematisk vist doseringsmekanisme 80, her i form af et på doseringsakslen drejefast tandsegment 81 og en indstillingsskrue 82, kan stillingen af doseringsexcentrikken 77 ændres, hvilket medfører, at doseringsstemplet 74’s slaglængde og dermed doseringsmængden af olie kan ændres. Doseringsakslen 76 påvirker hensigtsmæssigt samtlige doseringsventiler 73 til en og samme cylinder og kan også påvirke doseringsventilerne til flere cylindre. Doseringsmekanismen 80 kan påvirkes manuelt eller ad automatisk vej via et styresystem.The two dosing units 10 and 11 are mutually identical, so only the dosing unit 10, fig. 10, must be explained in more detail. From the pressure line 12, there are a plurality of, in the present case four, distribution lines 72, each of which leads to a known metering valve 73 for each lubrication site. These metering valves may also be built-in for joint feeding. For the sake of simplicity, only one metering valve 73 includes a dose of ring piston 74 which is pressed by a compression spring 75 towards a metering eccentric 77 disposed on a metering shaft 76. At the end of the metering piston 74 away from the metering eccentric channel 78, which via a check valve 79 opens into a conduit 8 to a lubrication site. By means of a schematically illustrated dosing mechanism 80, here in the form of a tooth segment 81 rotatable on the dosing shaft and an adjusting screw 82, the position of the dosing eccentric 77 can be changed, which means that the stroke length of the dosing piston 74 and thus the dosing amount of oil can be changed. The metering shaft 76 conveniently affects all metering valves 73 for one and the same cylinder and may also affect the metering valves for multiple cylinders. The dosing mechanism 80 can be actuated manually or automatically via a control system.

De beskrevne dele virker på følgende måde.The described parts work as follows.

Når motoren er i gang, roterer akslen 21 og driver derved pumpen 15, som pumper olie ind i akkumulatorkammeret 29, hvor trykket kan gå op til ca.When the engine is running, the shaft 21 rotates, thereby driving the pump 15, which pumps oil into the accumulator chamber 29, where the pressure can go up to approx.

15 å 20 MPa eller mere. Under størstedelen af akslen 21's omdrejning blokerer plungestemp lerne 39 og 40 forbindelsen mellem akkumulafcorkammeret 29 og ledningerne 44 og 46 (jf. stillingen af piungestemplet 39). Når et plungestem-pel trykkes hastigt opad af en knastkurve, se plungestemplet 40, kan der imidlertid strømme olie fra akkumulatorkammeret 29 ud i ledningen 46 og derfra videre til den tilhørende gruppe doseringsventiler i doseringsenheden 10. Som følge af det trykstød, der opstår, når styreventilen 36 åbner, kommer doseringsstemplet 74, som vist til højre i fig. 10, til at presses ud og tætne kanalen 78. På grund af, at doseringsstemplet 74 har en vel afvejet pasning i sit løb, hindres ingen olie i at presses forbi doseringsstemplet. Det er blot den olie, der findes foran doseringsstemplet, som presses ud via kanalen 78, indtil doseringsstemplet tætner kanalen 78.15 to 20 MPa or more. During most of the rotation of shaft 21, plunger pistons 39 and 40 block the connection between accumulator chamber 29 and conduits 44 and 46 (cf. the position of the piston 39). However, when a plunger plunger is urgently pushed upward by a cam curve, see plunger plunger 40, oil may flow from the accumulator chamber 29 into the conduit 46 and thereafter to the associated group of metering valves in the metering unit 10. As a result of the pressure shock that occurs when the control valve 36 opens, the metering plunger 74, as shown to the right in FIG. 10, for pressing out and sealing the duct 78. Because the dosing plunger 74 has a well-balanced fit in its course, no oil is prevented from being pressed past the dosing plunger. Only the oil present in front of the metering plunger is extruded through the canal 78 until the metering plunger seals the canal 78.

Når styreventilen 36 efter en kort tid lukker, ophører højtryksperioden, og der kan nu ske trykaflastning via ledningen 46, styreventilen 36, ledningen 48 og kontraventilen 49. Størrelsen af det trykniveau, hvortil der sker aflastning, bestemmes af kontraventilen 49. Dette lave trykniveau er valgt således, at trykfjederen 75 formår at overvinde den på doseringsstemplet 74 i dettes lukkeretning virkende trykkraft fra olien. Den af olien udøvede lukkekraft er herved lig med produktet af olietrykket og tværsnitsarealet i kanalen 78. Trykfjederen 75 er derimod ikke stærk nok til at tilbagepresse den olie, som findes mellem doseringsstemplet 74 og aflastningsventilen 49. For at opnå dette skulle der kræves, at trykfjederen 75 overvinder aflastningstrykket med doseringsstemplets betydeligt større hele tværsnitsareal. Resultatet bliver, at die langsomt, i det mindste i forhold til udfødningshastigheden, lækker forbi doseringsstemplet 74 til dettes udfødningsside og bliver det volumen, som fødes ud ved næste smøretilfælde. Aflastningsperioden er mere end ti gange længere end 11 142583 trykperioden. Kontraventilen 79 hindrer olie fra smørestedet i at vende tilbage til doseringsrummet i doseringsventilen. Doseringsventilen arbejder således med to trykniveauer, et højtryksniveau, hvor der sker smøring, og et lavtryks-niveau, hvor der igen sker tilførsel af doseringsmængden.When the control valve 36 closes after a short time, the high-pressure period ceases, and pressure relief can now be effected via the conduit 46, the control valve 36, the conduit 48 and the check valve 49. The size of the pressure level to which relief takes place is determined by the check valve 49. This low pressure level is selected so that the compression spring 75 is able to overcome the compressive force acting on the metering piston 74 in its closing direction from the oil. The closing force exerted by the oil is thereby equal to the product of the oil pressure and the cross-sectional area of the duct 78. The compression spring 75, on the other hand, is not strong enough to compress the oil found between the metering plunger 74 and the relief valve 49. 75 overcomes the relief pressure with the considerably larger cross-sectional area of the metering piston. The result is that the die slowly, at least in relation to the feeding rate, leaks past the dosing plunger 74 to its feeding side and becomes the volume that is delivered at the next lubrication event. The relief period is more than ten times longer than the pressure period. The check valve 79 prevents oil from the lubrication site from returning to the metering chamber in the metering valve. The metering valve thus operates with two pressure levels, a high-pressure level where lubrication occurs, and a low-pressure level, where the dosage amount is again supplied.

Hurtigheden i smøreforløbet gør det muligt at smøre via såvel korte som lange ledninger fra doseringsenheden inden for den nødvendige tid. Herved kan doseringsenhederne placeres på et ud fra f.eks. et servicesynspunkt fordelagtigt sted på en og samme side af en motorcylinder» Ved at smøreanlægget er tæt og helt fyldt med olie, bliver det selvsmørende og derved funktionssikkert. Anvendelsen af slidbestandige tætninger bevirker, at der opnås lang levetid.The speed of the lubrication process allows lubrication via both short and long wires from the dosing unit within the required time. Hereby, the dosage units can be placed on one from e.g. a service point advantageously located on one and the same side of an engine cylinder »By lubricating the lubricant and completely filled with oil, it becomes self-lubricating and thus functional safe. The use of abrasion resistant seals results in long life.

De i det foregående forklarede dele kan kombineres på et antal forskellige måder for at passe til aktuelle behov. Fig. 11 viser skematisk et arrangement til en sekscylindret motor» hvor tre smøresystemer 14 har deres aksler 21 sammenkoblet med hinanden og samtlige drives via motorens sfyreaksel. Hvert smøresystem 14 er opbygget ifølge fig. 3 og betjener to cylindre.The parts explained above can be combined in a number of different ways to suit current needs. FIG. 11 schematically shows an arrangement for a six-cylinder engine, wherein three lubrication systems 14 have their shafts 21 interconnected with each other and all are driven via the motor shaft of the motor. Each lubrication system 14 is constructed according to FIG. 3 and operates two cylinders.

Reservepumpen 20 er ikke nødvendig for smøresystemet 14's funktion. Ledningerne 44 og 46 kan i stedet være tilsluttet direkte til ledningerne 12 og 13, og start- og reservesmøring af motoren kan da ske ved, at reservepumpen 20 eller andet smøreapparat er sluttet separat til motoren.The spare pump 20 is not necessary for the operation of the lubrication system 14. The wires 44 and 46 may instead be connected directly to the wires 12 and 13, and the starting and reserve lubrication of the motor can then be done by the spare pump 20 or other lubricant being connected separately to the motor.

Akslen 21 behøver ikke nødvendigvis, som i det foreliggende tilfælde, at påvirke fire forskellige styreventiler, idet der også er mulighed for andre antal. Styreventilerne kan bygges sammen med hinanden på ønsket måde, alt efter behov. Det beskrevne smøresystem er som nævnt først og fremmest bestemt til langsomt gående fartøjs- eller skibsmotorer, men der er naturligvis mulighed for andre anvendelser inden for opfindelsens ramme.The shaft 21 need not, as in the present case, necessarily affect four different control valves, as other numbers are also possible. The control valves can be constructed with each other in the desired way, as needed. As mentioned, the lubrication system described is primarily intended for slow-moving vessel or ship engines, but of course other applications are possible within the scope of the invention.

Smøresystemet kan også anvendes til at smøre andre bestemt afgrænsede rum end området mellem to stempelringe på et stempel. En mulighed er f.eks. at smøre et oliespor på et stempel, eller en vis tandlomme på et roterende tandhjul, etc.The lubrication system can also be used to lubricate other defined spaces other than the area between two piston rings on a piston. One possibility is e.g. lubricating an oil groove on a piston, or some tooth pocket on a rotating gear, etc.

Fig. 12-15 viser en anden udførelsesform for den i fig. 3 viste reservepumpe 2), hvor pumpen er indkoblet på tilsvarende måde som i fig. 3. Hvor det drejer sig om samme dele som i fig. 3, er delene i fig. 12-15 betegnet med samme henvisningstal som de tilsvarende dele i fig. 3. Scan ved udførelsen ifølge fig. 3 trykkes pumpestemplet til venstre ved hjælp af fjederen 63 til dén viste hvilestilling, hvor doseringsenhederne via tangentielle spor 90, i det foreliggende tilfælde fire spor, i pumpestemplet 62 står i forbindelse med styreventilerne, fig. 14. I sin bort fra fjederen 63 vendende ende er pumpestemplet 62 forsynet med en excentrisk beliggende tap 91, der griber ind i et periferispor 92 i et i drivanordningen 64 indgående drejelegeme 93, som med akseltappe 94 og 95 er lejret drejeligt i pumpehuset 96. Periferisporet 92 begrænses radialt indad af et excentriklegeme 97, som regulerer pumpestempletFIG. 12-15 show another embodiment of the embodiment shown in FIG. 3, wherein the pump is connected in a similar manner as in FIG. 3. In the case of the same parts as in fig. 3, the parts of FIG. 12-15 denoted by the same reference numerals as the corresponding parts of FIG. 3. Scan in the embodiment according to FIG. 3, the pump piston is pressed to the left by means of the spring 63 to the rest position shown, where the metering units via tangential grooves 90, in this case four grooves, in the pump piston 62 are connected to the control valves. 14. At the end facing away from the spring 63, the pump piston 62 is provided with an eccentrically located pin 91 which engages a circumferential groove 92 of a pivot member 93 included in the drive device 64 which is pivotally mounted with the shaft 94 and 95 in the pump housing 96. The circumferential groove 92 is radially inwardly restricted by an eccentric body 97 which regulates the pump piston

Claims

142588 12 62. axial position. The piston surface of the pump piston 62T is provided with an axial groove 98. The chamber 69 communicates via a conduit 99 with a chamber 100, in which a valve body 101 is axially displaceable and is loaded in the direction to the left by a spring 102. The chamber 10 is via a conduit 103 in conjunction with conduit 48, and standing via conduit 104 and check valve 70 in conjunction with chamber 69. When starting pump 20 is turned by rotating body 93 in the direction of arrow 105, pump plunger 62 will initially rotate without axial displacement. the direction of the arrow 106, depending on the configuration and location of the pin 91 and the circumferential groove 92; 12. This causes the track 90 to change position, fig. 14 so that the connection between lines 12 and 44 is disconnected. Instead, the conduit 12, like the other corresponding conduits, is connected to the groove 98 which is connected to the conduit 71. 15. By continuing to rotate the rotary body 93, the position of the pump piston 62 * is maintained in the circumferential direction, but by the eccentric body 97 an axial displacement is obtained to the right in FIG. 12. In this way, oil in chamber 69 via conduit 99 will be pressed into chamber 100 and displace valve body 101 so that conduit 104 is connected to conduit 71. From there, the oil proceeds via groove 98 to the various dosing units. Return movement, ie suction movement, of the plunger 62 is obtained by the spring 63 and by rotating the rotary body in the opposite direction of the former. Thereby, the valve body 101 changes position so that the conduit 71 is again connected to conduit 103. This creates safety for relieving the metering units via the valve 49. This design of the spare pump also ensures that the conduits 103 and 104 cannot be open at the same time. . The pump piston 62 is thus intended to be switchable between two pivot positions, first a pivot position where the spare pump is at rest, and partly a pivot position where the spare pump is operating.

A lubrication system in which a lubricant is applied intermittently to a lubrication point (7), in particular a lubrication point in the cylinder wall of a piston engine, and wherein the lubrication system includes a lubrication pump (15), a pressure accumulator (16) fed by the lubrication pump ( 15) and a control valve (35) connected to the pressure accumulator (16), which, for the purpose of obtaining lubrication, is arranged at a desired time to intermittently open a connection between the pressure accumulator (16) and the lubrication point (7). ), characterized in that a dosing unit (10) is arranged between the control valve (35) and the lubrication point (7), which can be adjusted to different dosing amounts of lubricant, and that the lubrication pump (15) and the pressure accumulator (16) are connected with one another by means of a regulating means (32) arranged to be able to sense the lubricant consumption in the pressure accumulator (16) and to limit the pump capacity to a capacity needed to replace the lubricant volume consumed, For example, an automatic adjustment of the pump capacity is provided to the lubricant requirements adjustable by the metering unit (10).

Lubrication system according to claim 1, characterized in that the pump (15) is a piston pump and has a pump pile (22) which is pressed by means of a return spring (24) in the direction of a pump eccentric (23), which is intended to drive the pump. and that the pressure accumulator (16) includes an accumulator piston (30) which is arranged to be pressed into the accumulator chamber (29) in which the lubricant is pumped into the accumulator chamber (29) by means of a spring (31), preferably a biased pressure spring.

Lubrication system according to claim 2, characterized in that the springs (24, 31) are arranged to be able to displace the pump piston (22) and the accumulator piston (30) in the same direction that the regulating means (32) is constituted by a carrier which is displaceable synchronously. with the pump piston (22) and that on the carrier (32) and the accumulator piston (30) there are cooperating means (33, 34), by which the displacement of the carrier (32) in the suction direction of the pump piston (22) is limited to a position depending on the degree of filling. in the accumulator chamber (29), whereby the movement of the pump piston (22) is adjusted to the amount of lubricant consumption.

Lubrication system according to claim 3, characterized in that the carrier (32) has a portion arranged such that it can be located between the pump piston (22) and the pump eccentric (23).

Lubrication system according to claim 2, 3 or 4, characterized in that the volume in the accumulator chamber (29) is greater than the pumped volume during a working stroke of the pump.

Lubrication system according to one or more of claims 1-5, characterized in that the dosing unit (10) includes at least one dosing valve (73) known per se which operates with two pressure levels and a high pressure level where lubrication takes place. with a predetermined dosing amount, and partly a low pressure level, where again the dosing amount is applied, that in each dosing valve there is a displaceable dosing piston (74) and that the stroke length of these pistons, and thus the dosing amount, is jointly adjustable for several dosing valves.

Lubrication system according to claim 6, characterized in that the metering unit (10, 11) has a rotatable metering shaft (76) with a dosing eccentric (77) associated with each metering piston (74), whereby by rotating the metering shaft (76) is possible to vary dosage