DK141379B

DK141379B - Lubricator for piston combustion engines.

Info

Publication number: DK141379B
Application number: DK352776A
Authority: DK
Inventors: Anton Steiger; Herbert Zehnder
Original assignee: Sulzer Ag; Civilingenioer M Gregersen
Priority date: 1975-08-14
Filing date: 1976-08-05
Publication date: 1980-03-03
Also published as: DE2537742B2; IT1065950B; DK141379C; DE2537742C3; JPS5224638A; GB1501526A; DK352776A; JPS5439544B2; CH595548A5; DE2537742A1

Description

(S(S

\P.BLj OD FREMLÆGGELSESSKRIFT 1 41 379 DANMARK «» int ci.3 f oi u 1/02 §(21) Ansøgning nr. 5527/76 (22) Indleveret den 5· 3U£· 1976 (23) Løbedag 5· aug. 1976 (44) Ansøgningen fremlagt og fremlæggelsesskriftet offentliggjort den 5 · maT. 1 980\ P.BLj OD PUBLICATION WRITING 1 41 379 DENMARK «» int ci.3 f oi u 1/02 § (21) Application No 5527/76 (22) Filed on 5 · 3U £ · 1976 (23) Running day 5 · Aug . 1976 (44) The application presented and the petition published on 5 May. 1 980

DIREKTORATET FORDIRECTORATE OF

PATENT-OG VAREMÆRKEVÆSENET (30) Prioritet begæret fra denPATENT AND TRADE MARKET (30) Priority requested from it

14. aug. 1975. 10579/75, CHAug 14 1975. 10579/75, CH

(71) SULZER BROTHERS LIMITED, Zuericherstrasse 9, Winterthur, CH.(71) SULZER BROTHERS LIMITED, 9 Zuericherstrasse, Winterthur, CH.

(72) Opfinder: Anton Steiger, Im Horn, 8508 Illnau, CH: Herbert Zehnder,(72) Inventor: Anton Steiger, Im Horn, 8508 Illnau, CH: Herbert Zehnder,

Rebbergstr., 8555 Ettenhausen, CH.Rebbergstr., 8555 Ettenhausen, CH.

(74) Fuldmaegtig under «agene behandling:(74) Plenipotentiary:

Civilingeniør M.Gregersen._ (54) Smøreapparat til stempelforbrændingsmotorer.Civil engineer M.Gregersen._ (54) Lubricator for piston combustion engines.

Opfindelsen angår et smøreapparat til stempelforbræn-dingsmotorer og af den i krav l's indledning angivne art.BACKGROUND OF THE INVENTION The present invention relates to a lubricator for piston-combustion engines and of the kind specified in the preamble of claim 1.

Et sådant smøreapparat er f. eks. kendt fra beskrivelsen til USA-patent nr. 3 656 582. Ved dette kendte smøreapparat bli-5 ver et stempel i en smøreoliehøjtrykspumpe, der er anbragt ved forbrændingsmotorens krydshoved, mekanisk påvirket af ledrør, der tjener til olietilførsel til højtrykspumpen. Denne udførelsesform har navnlig den ulempe, at en ændring af den i højtryks-pumpen transporterede oliemængde til tilpasning til driftsbetin-10 gelserne ikke er mulig. Endvidere kan anbringelsesstedet for højtrykspumpen på grund af nødvendigheden af en mekanisk drivbevægelse ikke vælges frit.Such a lubricant is known, for example, from the specification of U.S. Patent No. 3,656,582. In this known lubricant, a plunger in a lubricating oil high-pressure pump disposed at the junction of the internal combustion engine is mechanically actuated by a conduit serving. oil supply to the high-pressure pump. In particular, this embodiment has the disadvantage that a change in the amount of oil transported in the high-pressure pump to adapt to the operating conditions is not possible. Furthermore, due to the necessity of a mechanical drive movement, the location of the high-pressure pump cannot be chosen freely.

Den foreliggende opfindelse tager sigte på at angive et 2 141379 smøreapparat af den omhandlede art, ved hvilket de ovennævnte ulemper er undgået, så at man kan vælge anbringelsen af højtrykspumpen så frit som muligt og tillige under drift kan indstille den smøreoliemængde, der transporteres af højtrykspumpen 5 for hvert smøreslag, efter ønske.SUMMARY OF THE INVENTION The present invention aims to provide a lubricator of the kind in which the above-mentioned drawbacks are avoided, so that the application of the high-pressure pump can be selected as freely as possible and also during operation can adjust the amount of lubricating oil transported by the high-pressure pump. 5 for each batter, as desired.

Dette opnås ifølge opfindelsen ved, at smøreapparatet er udformet som angivet i krav l's kendetegnende del.This is achieved according to the invention in that the lubricator is designed as defined in the characterizing part of claim 1.

Idet fremdrivningen af højtrykspumpen ikke mere sker mekanisk, men hydraulisk, kan pumpen, uden at man, som hidtil, er 10 nødt til at tage hensyn til mekaniske drivdele, anbringes i nærheden af de smøresteder, hvortil olien skal føres.Since the propulsion of the high-pressure pump is no longer mechanically but hydraulically, the pump, without having to take into account mechanical drive parts, can be placed near the lubrication points to which the oil is to be fed.

Ved ændring af tilløbstrykket kan endvidere drivstemplets slag og dermed også pumpestemplets slag i højtrykspumpen og altså den transporterede oliemængde ændres efter behag. Thi alt ef-15 ter højden af tilløbstrykket indstiller der sig en ligevægt mellem det på drivstemplet virkende hydrauliske tryk og fjederkraften fra fjederen, og denne ligevægt bestemmer størrelsen af pumpestemplets slag og dermed af det olievolumen, der tilføres til smørestedet.Furthermore, by changing the inlet pressure, the stroke of the drive piston and thus also the stroke of the pump piston in the high-pressure pump and thus the transported oil quantity can be changed at will. Because, depending on the height of the inlet pressure, an equilibrium is established between the hydraulic pressure acting on the drive piston and the spring force from the spring, and this equilibrium determines the magnitude of the stroke of the pump piston and thus of the oil volume supplied to the lubrication site.

20 I denne sammenhæng skal der henvises til, at det fra en bog af F. Sass "Bau und Betrieb von Dieselmaschinen", 2. bind, Springer-Verlag, Berlin 1957, side 161 til 164, kendes cylinder-smøreoliepresser, der har hydraulisk påvirkede stempler, hvorved en anbringelse af smøreoliepresserne efter behov er mulig. Et 25 hydraulisk drevet stempel påvirker herved over en kipvægtstangs-lignende vægtstangsindretning tillige flere pumpestempler, idet en i vægtstangsindretningen angribende tilbagetræksfjeder tjener til tilbageføring af det hydraulisk påvirkede drivstempel til udgangsstillingen. Fjederen har dog i dette tilfælde ikke nogen 30 målende funktion, som det er tilfældet i sammenhæng med bestemmelsen af den oliemængde, der tilføres smørestederne ved smøreapparatet ifølge opfindelsen. løvrigt er det konstruktive opbud ved den kendte smøreindretning forholdsvis stor.20 In this connection, it should be noted that from a book by F. Sass "Bau und Betrieb von Dieselmaschinen", 2nd volume, Springer-Verlag, Berlin 1957, pages 161 to 164, is known cylinder lubricating oil presses which have hydraulic actuated pistons, whereby an application of the lubricating oil presses is possible as required. A hydraulically driven piston thereby acts over a tilting rod-like lever device as well as a plurality of pump pistons, a retracting spring engaging in the lever device serves to return the hydraulically actuated drive piston to the starting position. However, in this case the spring does not have any measuring function, as is the case in the determination of the amount of oil supplied to the lubrication points by the lubricator according to the invention. the constructive supply of the known lubricating device is relatively large.

Ved udformning af smøreapparatet som angivet i krav 2 op-35 når man den fordel, at smøreolie ad en meget kort ledningsvej kan føres til smøring af stemplet, idet stemplets løbeflade og ikke cylinderens løbeflade bliver smurt direkte. Desuden kan højtrykspumpen også anvendes til smøring af en stempeltap i en dykstempelmotor. I denne sammenhæng skal der henvises til, at 3 141379 tilførsel af smøreolie til højtrykspumpen over leddede ledningsafsnit allerede er kendt fra den ovennævnte beskrivelse til USA-patent nr. 3 656 582.By designing the lubricator as set forth in claim 2, one obtains the advantage that lubricating oil can be passed along a very short conduit for lubricating the piston, the piston's running surface and not the cylinder's running surface being lubricated directly. In addition, the high-pressure pump can also be used to lubricate a piston pin in a dive piston engine. In this connection, it should be noted that the supply of lubricating oil to the high-pressure pump over articulated pipe sections is already known from the above description to US Patent No. 3,656,582.

Ved udformning af smøreapparatet som angivet i krav 3 5 kan lækolie, der optræder ved et stempel med forholdsvis stor diameter, med enkle midler udnyttes til smøring.In designing the lubricator as claimed in claim 35, leakage oil occurring at a relatively large diameter plunger can be utilized for lubrication with simple means.

Ved udformning af smøreapparatet som angivet i krav 4 opnår man, at det kan undgås, at smøreolie ustyret kan strømme ud, f.eks. ved en forstyrrelse i høj trykspumpen og stillestående 10 stempelforbrændingsmotor, som det ville være tilfældet, når lavtrykspumpen var fremmeddrevet.By designing the lubricator as set forth in claim 4, it is achieved that it is possible to prevent the lubricating oil from flowing out, e.g. by a disturbance in the high-pressure pump and stationary 10-piston combustion engine, as would be the case when the low-pressure pump was foreign-powered.

Ved udformning af smøreapparatet som angivet i krav 5 opnår man yderligere en af stempelforbrændingsmotorens omløbstal afhængig smøreolietilførsel, da det tryk på oliesøjlen i smøre-15 ledningen, der fremkaldes af accelerationskræfterne, og det véd hjælp af trykreguleringsmekanismen indstillede olietryk adderes.In designing the lubricator as claimed in claim 5, an additional lubricating oil supply dependent on the piston combustion engine is obtained, since the pressure on the oil column in the lubrication line caused by the accelerating forces and the oil pressure adjusted by the pressure control mechanism is added.

Opfindelsen forklares nærmere under henvisning til tegningen, på hvilken fig. la viser et delsnit gennem et stempel i en stempel-20 forbrændingsmotor sammen med et skårne for en ud førelsesform for smøreapparatet, fig. Ib et udsnit af fig. la i større målestok, og fig. 2 et diagram for bevægelserne af arbejdsstemplet i stempelforbrændingsmotoren til forklaring af 25 funktionen af smøreapparatet.The invention is further explained with reference to the drawing, in which: FIG. 1a shows a partial section through a piston in a piston-combustion engine together with a cut for an embodiment of the lubricator; FIG. 1b is a section of FIG. 1a on a larger scale, and fig. 2 is a diagram of the movements of the working piston in the piston combustion engine to explain the operation of the lubricator.

I fig. la og lb på tegningen betegner 1 et arbejdsstempel i en stempelforbrændingsmotor, navnlig en ladet dieselmotor, der med en stempeltap 2 er forbundet med en plej Istang 3. Stemplet 1 er på kendt måde frem- og tilbagebevægelig i en cylinder 4, der 30 kun er antydet i fig. 1. I stemplet 1 er der anbragt en smøreoliehøj trykspumpe 5, der ved hjælp af en smøreledning 6 er forbundet med en smøreolielavtrykspumpe 7. Smøreoliepumpen 7 transporterer smøreolie fra en smøreoliebeholder 8 gennem en trykregulator 10 og en som styreglider udformet styreindretning 11, der 35 er indskudt i smøreolieledningen 6. Styreindretningen 11 indeholder et gliderstempel 12, der er bevægeligt i en cylinder 13 under påvirkning af en knastskive 14. Som antydet med stiplede linier er knastskiven 14 på samme måde som smøreoliepumpen 7 f.eks. ved hjælp af tandhjulsudvekslinger drevet fra stempelforbræn- 4 1A1379 dingsmotorens krumtapaksel 15.In FIG. 1a and 1b in the drawing, 1 denotes a working piston in a piston combustion engine, in particular a charged diesel engine, which is connected with a piston pin 2 to a plunger rod 3. The piston 1 is in a known way reciprocally movable in a cylinder 4 which is only indicated in FIG. 1. In the piston 1, a lubricating oil high pressure pump 5 is connected, which is connected by means of a lubrication line 6 to a lubricating oil impression pump 7. The lubricating oil pump 7 transports lubricating oil from a lubricating oil container 8 through a pressure regulator 10 and a control device 11, which is designed as control device 11, inserted in the lubricating oil line 6. The control device 11 contains a sliding piston 12 which is movable in a cylinder 13 under the influence of a cam disk 14. As indicated by dashed lines, the cam disk 14 is similar to the lubricating oil pump 7, for example. by means of pinion gears driven from the piston combustion 4 1A1379 crankshaft motor 15.

Gliderstemplet 1Z indeholder en styrenot 16, der alt efter stillingen af gliderstemplet enten forbinder til styreindretningens cylinder 13 tilsluttede afsnit af smøreolieledningen 5 6 med hinanden eller tilsluttet det til højtrykspumpen 5 føren de afsnit af smøreolieledningen 6 til en aflastningsledning 17, der fører til beholderen 8. Aflastningsledningen 17 er forsynet med et drøvlested 18.The sliding piston 1Z contains a control note 16 which, depending on the position of the sliding piston, either connects parts of the lubricating oil line 5 6 connected to the control unit cylinder 13 or connected to the high pressure pump 5, the sections of the lubricating oil line 6 leading to a relief line 17 leading to the container 8. The relief line 17 is provided with a throttle location 18.

I området mellem motorhuset og stemplet 1 er smørelednin-10 gen 6 udformet som et af ledrør 20, 21, 22 bestående ledningsafsnit.In the area between the motor housing and the piston 1, the lubrication line 6 is formed as a conduit section consisting of articulated pipes 20, 21, 22.

Højtrykspumpen 5 indeholder et pumpehus 23, fig. Ib, i hvilket et differentialstempel 24 er bevægeligt. Differential-stemplet består af et pumpestempel 25 med mindre diameter, hvil-15 ket pumpestempel når ind i et pumpekammer 36, samt et drivstempel 26 med større diameter. Pumpen 5 er over en sugeventil 27 forbundet med et ledningsafsnit 6'” af smøreolieledningen 6.The high-pressure pump 5 contains a pump housing 23, fig. 1b, in which a differential piston 24 is movable. The differential piston consists of a smaller diameter pump piston 25, which pump piston reaches into a pump chamber 36, and a larger diameter drive piston 26. The pump 5 is connected via a suction valve 27 to a conduit section 6 '"of the lubricating oil line 6.

Desuden indeholder pumpen en trykventil 28, gennem hvilken smøreolien fra kammeret 36 kan transporteres til et smørested 30.In addition, the pump includes a pressure valve 28 through which the lubricating oil from the chamber 36 can be transported to a lubrication site 30.

20 I det foreliggende tilfælde befinder smørestedet 30 sig i ydervæggen af stemplet 1 mellem to stempelringe 31. Smørestedet kan dog også være anbragt f.eks. i en stempelringnot.In the present case, the lubrication site 30 is located in the outer wall of the piston 1 between two piston rings 31. However, the lubrication site may also be located e.g. in a piston ring note.

Drivstemplet 26 er bevægeligt i et cylinderrum 32 i huset 23, hvilket rum over et afsnit 32a er tilsluttet til et lednings-25 afsnit 6" i smøreolieledningen 6. Stemplet 26 er belastet af en trykfjeder 33. der er anbragt i et afsnit 32b i cylinderen 32.The drive piston 26 is movable in a cylinder compartment 32 of the housing 23, which compartment over a section 32a is connected to a conduit 25 section 6 "of the lubricating oil line 6. The piston 26 is loaded by a compression spring 33. arranged in a section 32b of the cylinder. 32nd

Til afsnittet 32b i cylinderen 32 slutter sig en ledning 34, der udmunder i væggen på stemplet 1 og tilfører udlækkende smøreolie til et smørested 35.To the section 32b of the cylinder 32 joins a conduit 34 which opens into the wall of the piston 1 and delivers leaking lubricating oil to a lubrication site 35.

30 Man vil forstå, at der i et stempel 1 kan være anbragt fle re højtrykspumper 5, af hvilke hver enkelt kan forsyne et eller flere smøresteder 30. Ved en flercylindermotor kan der til hver cylinder høre en særskilt styreindretning 11, og alle styreindretningerne 11 kan være tilsluttet til en fælles smørepumpe 7 med 35 en ligeledes fælles trykregulator 10.30 It will be appreciated that a plurality of high-pressure pumps 5 may be arranged in a piston 1, each of which may provide one or more lubrication points 30. A multi-cylinder engine may have a separate control device 11 for each cylinder, and all the control devices 11 may be connected to a common lubrication pump 7 with 35 also a common pressure regulator 10.

‘ Når styreglideren 11 under drift styrer forbindelsen inde i smøreolieledningen 6, bliver drivstemplet 26 i høj trykspumpen 5 mod kraften fra fjederen 33 i fig. la og lb bevæget nedefter.When the control slider 11 during operation controls the connection inside the lubricating oil line 6, the drive piston 26 in the high pressure pump 5 becomes against the force of the spring 33 in FIG. 1a and 1b moved downward.

Derved udfører højtryksstemplet 25 en sugebevægelse, ved hvilken 5Thereby, the high-pressure piston 25 performs a suction movement at which 5

14137S14137S

den tilsuger olie fra smøreolieledningen 6 gennem sugeventilen 27. Størrelsen af sugeslaget er bestemt af tilløbstrykket i ledningen 6, og dette tryk er afhængigt af indstillingen af trykregulatoren 10. Drivstemplet 26 spænder nemlig ved sin bevægelse 5 fjederen 33 så langt, indtil der opstår en ligevægt mellem fjederkraften fra denne fjeder og det hydrauliske tryk, der virker på stemplerne 25, 26. Når forbindelsen i smøreolieledningen 6 bliver afbrudt af gliderstemplet 12 under det videre forløb af arbejdscyklussen i stempelforbrændingsmotoren, forbliver diffe-10 rentialstemplet 24 stående i den stilling, det har indtaget.it sucks oil from the lubricating oil conduit 6 through the suction valve 27. The size of the suction stroke is determined by the inlet pressure in the conduit 6, and this pressure is dependent on the setting of the pressure regulator 10. The drive piston 26, by its movement 5, extends the spring 33 so far until an equilibrium is reached. between the spring force of this spring and the hydraulic pressure acting on the pistons 25, 26. When the connection in the lubricating oil line 6 is interrupted by the sliding piston 12 during the further course of the duty cycle of the piston combustion engine, the differential piston 24 remains in the position it has. consumed.

Så snart gliderstemplet 12 forbinder det afsnit 6 i smøreolieledningen, der fører til højtrykspumpen 5, med aflastningsledningen 17, bevæger fjederen 33 differentialstemplet 24 opefter til den i fig. la og lb viste stilling. Den olie, der 15 findes foran drivstemplet 26, bliver fortrængt gennem aflastningsledningen 17 med drøvlestedet 18. Derved kan bevægelseshastigheden for differentialstemplet 24 bestemmes ved hjælp af drøvlestedet 18. Højtryksstemplet 25 udfører ved denne bevægelse et transportslag og trykker den indsugede smøreolie gennem 20 trykventilen 28 til smørestedet 30.As soon as the sliding piston 12 connects the section 6 of the lubricating oil line leading to the high-pressure pump 5 with the relief line 17, the spring 33 moves the differential piston 24 upwards to the one shown in FIG. 1a and 1b. The oil found in front of the drive piston 26 is displaced through the relief line 17 with the throttle location 18. Thus, the speed of movement of the differential piston 24 can be determined by the throttle location 18. The high pressure piston 25 performs a transport stroke in this movement and presses the suction lubricating oil through the pressure valve 28 to lubrication site 30.

Under den yderligere bevægelse af arbejdsstemplet 1 styrer gliderstemplet 12 forbindelsen inden for smøreolieledningen 6, idet samtidig forbindelsen med ledningen 17 bliver afbrudt, hvorefter det allerede beskrevne forløb gentages.During the further movement of the working piston 1, the sliding piston 12 controls the connection within the lubricating oil conduit 6, at the same time disconnecting the connection with the conduit 17, after which the process already described is repeated.

25 Smøreapparatet ifølge opfindelsen tillader en påvirkning udefra, af den smøreoliemængde, der for hvert af motorens slag tilføres til smørestedet 30, idet man kan vælge tilløbstrykket ved hjælp af trykregulatoren 10. Alt efter dimensioneringen af differentialstemplet 24 er det muligt at opnå meget høje tryk 30 på smørestedet 30, så at højtrykspumpen 5 f.eks. også kan anvendes til smøring af en lejring af en stempeltap 2 eller et krydshoved i en krydshovedmaskine.The lubricator according to the invention permits an external influence of the amount of lubricating oil supplied to each lubrication point 30 for each stroke of the engine, by selecting the inlet pressure by means of the pressure regulator 10. Depending on the dimension of the differential piston 24, very high pressures 30 can be obtained. at the lubrication site 30 so that the high pressure pump 5 e.g. can also be used for lubricating a bearing of a piston pin 2 or a crosshead in a crosshead machine.

Fig. 2 viser et muligt forløb af arbejdsmåden af smøreapparatet ifølge opfindelsen under en omdrejning af en totaktsmo-35 tor. I diagrammet viser en linie A slagbevægelsen og massekraften i stemplet 1 under en hel omdrejning fra et øverste dødpunkt 0 til et nederste dødpunkt U og tilbage til det øverste dødpunkt 0. I diagrammet betegner I et ekspansionsslag og II et kompressionsslag i motoren. I et område X sker der en gasudveksling, 40 nemlig udstødning og skylning med ladning.FIG. 2 shows a possible course of operation of the lubricator according to the invention during the rotation of a two-stroke engine. In the diagram, a line A shows the stroke and mass force in the piston 1 during a full revolution from a top dead center 0 to a lower dead center U and back to the top dead center 0. In the diagram, I denotes an expansion stroke and II a compression stroke in the motor. In an area X there is a gas exchange, namely exhaust and flushing with charge.

6 1A13 7 96 1A13 7 9

Styreindretningen 11 i smøreapparatet er dimensioneret således, at forbindelsen i smøreolieledningen ved hjælp af gliderstemplet 12 og dermed fyldningen af højtrykspumpen 5 sker i et område F. Forbindelsen af det afsnit i smøreolieledningen, 5 der ligger nærmest ved højtrykspumpen, med aflastningsledningen 17 og dermed aflastningen af højtrykspumpen 5, i hvilken tid der tilføres olie til smørestedet 30, sker i et område E.The control device 11 of the lubricator is dimensioned such that the connection in the lubricating oil line by means of the sliding piston 12 and thus the filling of the high-pressure pump 5 takes place in an area F. The connection of the section of the lubricating oil line 5 which is closest to the high-pressure pump, with the relief line 17 the high-pressure pump 5, during which time oil is applied to the lubrication site 30, occurs in an area E.

Af diagrammet i fig. 2 fremgår det, at fyldningen af højtrykspumpen 5 sker i et område F, i hvilket den på stemplet 10 virkende resulterende massekraft M+ er rettet opefter, d. v. s. hen mod det øverste dødpunkt. Derved får man den virkning, at massekraften, der virker på den i det afsnit i smøreolieledningen, der ligger nærmest ved højtrykspumpen, værende oliesøjle overlejres på trykket fra trykregulatoren 10 og derfor medfører 15 en forøgelse af smøreoliemængden. Derved får man en gunstig afhængighed af den pr. slag til smørestedet 30 tilførte oliemængde af motorens omløbstal.From the diagram of FIG. 2, it is seen that the filling of the high-pressure pump 5 takes place in an area F, in which the resulting mass force M + acting on the piston 10 is directed upwards, i.e., towards the top dead center. This results in the effect that the mass force acting on the oil column closest to the high-pressure pump is superimposed on the pressure from the pressure regulator 10 and therefore 15 increases the amount of lubricating oil. This gives you a favorable dependence on it per. blows to the lubrication point 30 added to the engine oil flow rate.

Denne virkning kan yderligere forstærkes ved, at højtrykspumpen 5 med sin akse i forhold til den i fig. la og lb vi-20 ste stilling er vendt om, d.v.s., at stemplet 26 er anbragt foroven og stemplet 17 forneden. I det område, hvor massekraften er rettet mod det øverste dødpunkt, virker nemlig massekraften fra stemplet 24 yderligere mod kraften fra fjederen 33, hvad der medfører en yderligere forskydning af differentialstemplet 24 25 mod fjederen 33 og dermed en yderligere forstærkning af indsugningsvolumenet .This effect can be further enhanced by the fact that the high-pressure pump 5 with its axis with respect to that of FIG. 1a and lb-20 position are reversed, i.e., the plunger 26 is positioned at the top and the plunger 17 at the bottom. Namely, in the region where the mass force is directed to the top dead center, the mass force of the piston 24 acts further against the force of the spring 33, which results in a further displacement of the differential piston 24 25 against the spring 33 and thus a further increase in the intake volume.

Af fig. 2 fremgår det også, at udladningen af højtrykspumpen 5 sker i et område E, i hvilket der sker en vending af accelerationen af stemplet 1 og således af kraftretningen for 30 massekræfterne. Derved bliver indflydelsen af massekræfterne på bevægelsen af differentialstemplet 24 holdt så lille som muligt. Desuden sker smøringen i en optimal stilling af stemplet i cylinderen. Stemplet befinder sig uden for området for slidserne i en totaktsmotor og i nogen afstand fra forbrændingsrummet, så 35 at olien kan fordeles jævnt på cylindervæggen.In FIG. 2, it is also apparent that the discharge of the high-pressure pump 5 takes place in an area E in which the acceleration of the piston 1 is reversed and thus of the direction of force of the mass forces. Thereby, the influence of the mass forces on the movement of the differential piston 24 is kept as small as possible. In addition, the lubrication takes place in an optimal position of the piston in the cylinder. The piston is outside the area of the slots in a two-stroke engine and at some distance from the combustion chamber so that the oil can be evenly distributed on the cylinder wall.

I stedet for den i fig. 2 viste fremstilling er det også muligt at vælge andre områder E og F, i hvilke højtrykspumpen udfører sin sugebevægelse og sin transportbevægelse. Desuden behøver der ikke at ske et smøreslag ved hjælp af pumpestemplet 24 for hvert slag af arbejdsstemplet 1. Man kan også tænke sig en .. _____Instead of the one shown in FIG. 2, it is also possible to select other areas E and F in which the high-pressure pump performs its suction movement and its transport movement. Furthermore, there is no need to make a lubrication by means of the pump piston 24 for each stroke of the working piston 1. One can also think of a .. _____

Claims

An embodiment in which a lubrication stroke occurs sufficiently in step with the piston movement, but only after several strokes of the working piston 1. The dead space of the high-pressure pump 5, i.e. the remaining cylinder space when the piston 25 is in its upper end position in FIG. 1a and 1b, should be as small as possible. When the working space in piston 25 at the beginning of operation, e.g. after a longer standstill or after a mounting, is filled with air, this air can be compressed by the piston and removed through the pressure line of the pump 10 5. Special measures for venting, e.g. ventilation valves are therefore superfluous. The pressure valve 28, which is loaded by a spring 28 ', must be designed such that the opening pressure of the valve is higher than the highest oil pressure present in the lubricating oil line 6.

15 This prevents oil without pumping action from the piston 25 from the oil line 6 to flow to the lubrication site 30. A height container 8 ', which is connected by means of an overflow line 9 to the lubricating oil container 8, is designed to prevent an outflow of oil from the high pressure pump. 5 and wire 20.

1. Lubricating apparatus - for piston combustion engines, in particular for lubricating a cylindrical moving piston, consisting of a lubricating oil impression pump which communicates over a lubricating oil line with a working space in a lubricating oil high pressure piston pump, from which lubricating oil over a further lubricating oil. the movement of the piston is applied to at least one lubrication point, characterized in that lubricating oil from the low pressure pump (7) over a pressure control device (10) and over a control device (11) inserted after the pressure control device (10), calculated in the flow direction of the oil, and controlled in step with the piston movements, is supplied to the high-pressure pump (5) consisting of a differential piston (24) inserted in a pump housing (23), the piston of the smaller diameter serves as a high-pressure piston (25) and whose piston with the larger diameter 35 serves as a drive piston, one in a transition area between the