DK164293B - Fuel system to a dual-fuel diesel motor - Google Patents
Fuel system to a dual-fuel diesel motor Download PDFInfo
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- DK164293B DK164293B DK082290A DK82290A DK164293B DK 164293 B DK164293 B DK 164293B DK 082290 A DK082290 A DK 082290A DK 82290 A DK82290 A DK 82290A DK 164293 B DK164293 B DK 164293B
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- valve
- pressure
- fuel system
- pilot oil
- piston
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Abstract
Description
iin
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Opfindelsen vedrører et brændstofsystem til en dual-fuel dieselmotor, der normalt opererer med gas som hovedbrændstof og pilotolie som tændhjælp, og hvor der til hver cylinder i det mindste hører en styreolieled-5 ning ledende til en injektorventil til indblæsning af gas og en pilotolietilgangsledning med en injektorventil til indsprøjtning af pilotolie samt en i styre-olieledningen indbygget trykaflastningsventil med et ventillegeme, der er påvirket mod lukket stilling af 10 trykket i pilotolietilgangsledningen og mod åben stilling af en fjeder, og som i løbet af kompressionsslaget af hver motorcyklus står i den åbne stilling og åbner for en første drænkanal i styreolieledningen, når trykket i pilotolieledningen er mindre end pilotolieinjek-15 torventilens åbnetryk.The invention relates to a fuel system for a dual-fuel diesel engine, which normally operates with gas as main fuel and pilot oil as ignition aid, and in which at least one control oil line leads to a gas injector valve and a pilot oil supply line with an injector valve for injecting pilot oil and a pressure relief valve built into the control oil line with a valve body which is actuated against the closed position of the pressure in the pilot oil supply line and towards the open position of a spring and which during the compression stroke of each motor cycle is in the open position and opens for a first drainage channel in the control oil line when the pressure in the pilot oil line is less than the pilot oil valve open pressure.
For ved dual-fuel dieselmotorer at etablere sikker tænding af det i motorcylindrene indblæste brændstof på det for arbejdsprocessens optimering ønskelige tidspunkt af processen er motorens brændstofsystem ind-20 rettet til før og samtidig med hver gasindblæsning i en cylinder at indsprøjte et vist kvantum tændvilligt pilotbrændstof, fx gas- eller dieselolie, som tjener til at indlede forbrændingen i cylinderen.In order to establish, by dual-fuel diesel engines, the safe ignition of the fuel injected into the engine cylinders at the desired time of the process of optimization of the process, the engine's fuel system is adapted to inject a certain quantity of pilot fuel into each cylinder at the same time as each gas injection into a cylinder. eg gas or diesel oil, which serves to initiate combustion in the cylinder.
Dersom indsprøjtningen af pilotolie udebliver, 25 er det så godt som sikkert, at den i cylinderen indblæste gasmængde enten selvantænder sent i motorstemplets arbejdsslag eller efter at være strømmet ud af cylinderen antændes i udstødssystemet, fx af en gnist fra en anden cylinder eller ved blandingen med de varme 30 udstødsgasser fra de andre cylindre. I alle tilfælde forbrænder gassen eksplosionsagtigt med stor risiko for beskadigelse af motoren, inklusive dens udstødssystem og eventuelt tilsluttede turboladere.If the injection of pilot oil fails, it is almost certain that the amount of gas injected into the cylinder either self-ignites late in the working stroke of the engine piston or, after flowing out of the cylinder, ignites in the exhaust system, for example by a spark from another cylinder or by mixing with the hot 30 exhaust gases from the other cylinders. In all cases, the gas burns explosively with a high risk of engine damage, including its exhaust system and possibly connected turbochargers.
Ved ovennævnte brændstofsystem, som kendes fra 35 ansøgerens danske patent nr. 154448, sikrer trykaflastningsventilen, at der normalt kun indblæses gas i en 2By the above fuel system, which is known from the applicant's Danish patent no. 154448, the pressure relief valve ensures that gas is normally only injected into a 2
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cylinder, såfremt der forudgående er indsprøjtet pilotolie .cylinder, if pilot oil has been injected beforehand.
Dersom pilotolietrykket ved normal motordrift skulle udeblive eller ikke nå op på den til åbning af 5 olieventilen i injektoren nødvendige højde, lukker trykaflastningsventilen ikke, og styreolien vil da-undvige gennem denne ventils første drænkanal i stedet for at fortsætte forbi ventilen til injektoren. Som følge heraf forbliver gasventilen i injektoren lukket, og 10 dermed er det sikret, at en eventuel manglende pilot-olieindsprøjtning i en hvilken som helst cylinder omgående detekteres og endnu i samme arbejdscyklus hindrer gasindblæsningen gennem den pågældende injektor. Da motorens øvrige cylindres injektorer ikke berøres af 15 trykaflastningen i styreolieledningen, kan motoren som regel fortsætte med at køre, og dersom årsagen til den manglende pilotolieindsprøjtning i mellemtiden afhjælpes eller bortfalder af sig selv, træder injektoren da automatisk i funktion igen.If, during normal engine operation, the pilot oil pressure fails or does not reach the height required for opening the oil valve in the injector, the pressure relief valve will not close and the control oil will then avoid through this valve's first drainage channel instead of continuing past the valve to the injector. As a result, the gas valve in the injector remains closed and thus it is ensured that any missing pilot oil injection in any cylinder is immediately detected and still prevents the gas supply through that injector during the same duty cycle. Since the injectors of the other cylinders of the engine are not affected by the pressure relief in the steering oil line, the engine can usually continue to run, and if the cause of the missing pilot oil injection in the meantime is rectified or discontinued by itself, the injector will then automatically function again.
20 Pilotolietrykket kan frembringes ved hjælp af en knastaktiveret doseringspumpe og vil umiddelbart før indsprøjtningstidspunktet vokse hastigt fra et lavt forpumpetryk til det til åbning af olieventilen i injektoren nødvendige tryk. Fordi pilotolien kun anvendes 25 som tændhjælp, er indsprøjtning heraf styret til alene at finde sted under den indledende del af motorstemplets arbejdsslag, hvorefter pilotolietrykket falder til et mellemniveau, der er højere end forpumpetrykket men utilstrækkeligt til åbning af olieventilen.The pilot oil pressure can be generated by means of a cam actuated metering pump and will grow rapidly from the low pre-pump pressure to the pressure needed to open the oil valve in the injector immediately before the injection time. Because the pilot oil is only used as an ignition aid, injection thereof is controlled to take place only during the initial part of the engine piston stroke, after which the pilot oil pressure drops to an intermediate level higher than the pre-pump pressure but insufficient to open the oil valve.
30 Indblæsningen af gas i motorcylinderen skal for sikring af gassens antændelse begynde førend al den indsprøjtede pilotolie er afbrændt og skal fortsætte, når pilotolietrykket falder til mellemniveauet. Trykaflastningsventilens ventillegeme er derfor i den kend-35 te teknik udformet som en cylindrisk glider, der i hver ende har en koaksial, som nåleventil udformet aksial30 In order to ensure the ignition of the gas, the intake of gas into the engine cylinder must begin before all the injected pilot oil is burnt and must continue as the pilot oil pressure drops to the intermediate level. The valve body of the pressure relief valve is therefore known in the prior art as a cylindrical slider having at each end a coaxial like needle valve formed axially.
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3 ansats til samvirken med et ventilsæde, der omgiver en henholdsvis til pilotolieledningen og til styreolieled-ningen førende kanal. Når pilotolietrykket er tilstrækkelig højt til, at olieindsprøjtning er sikret, vil pi-5 lotolien påvirke den i forbindelse med pilotolieledningen stående ansats med en tilstrækkelig kraft til at ventillegemet under overvindelse af fjederkraften forskubbes til den lukkede stilling, hvor den modstående ansats afspærrer drænkanalen i styreolieledningen. Sam-10 tidig åbner ansatsen for pilotoliens strømning forbi det tilhørende ventilsæde, så at pilotolietrykket forplanter sig ind i rummet omkring ansatsen og påvirker hele gliderens tværsnitsareal. Som følge af at pilotolietrykket i ventillegemets lukkede stilling påvirker 15 et væsentligt større areal end det på den modstående ansats virkende styreolietryk, er pilotolietrykkets mellemniveau tilstrækkeligt højt til i <3et væsentlige at holde ventillegemet i den lukkede stilling.3 is used for cooperation with a valve seat which surrounds a channel leading to the pilot oil line and to the control oil line respectively. When the pilot oil pressure is sufficiently high for oil injection to be secured, the pilot oil will affect the abutment associated with the pilot oil line with a sufficient force to move the valve body over the spring force to the closed position where the opposite abutment blocks the drainage channel in the control oil line. . At the same time, the pilot for the pilot oil flow past the associated valve seat opens, so that the pilot oil pressure propagates into the space around the shoulder and affects the entire cross-sectional area of the glider. Due to the fact that the pilot oil pressure in the closed position of the valve body affects a substantially greater area than the control oil pressure acting on the opposing member, the intermediate level of the pilot oil pressure is sufficiently high to substantially keep the valve body in the closed position.
Den for styreoliens drænkanal spærrende ansats 20 med tilhørende ventilsæde bliver særdeles hårdt belastet i et kort tidsrum af hver motorcyklus, fordi det høje pilotolietryk umiddelbart efter ventilens lukning påvirker hele glidertværsnitsarealet, hvilket kan medføre hurtig nedslidning af ventilen.The steering channel locking drain 20 and associated valve seat 20 are particularly severely stressed for a short period of each engine cycle because the high pilot oil pressure immediately after the valve closure affects the entire sliding cross-sectional area, which can cause rapid valve wear.
25 På mellemniveauet har pilotoliet rykket ikke en konstant størrelse, men det svinger omkring et middeltryk, som mindskes hen mod afslutningen af motorstemplets arbejdsslag. Disse tryksvingninger bevirker, at ventilen vil åbne og lukke flere gange i umiddelbar 30 rækkefølge, inden pilotolietrykket falder tilstrækkeligt til at ventilen vedvarende stiller sig i åben stilling, og dette kan fremkalde uønskede tryksvingninger i styreolieledningen.25 At the intermediate level, the pilot oil has not moved a constant size, but it swings around a mean pressure which decreases towards the end of the working stroke of the engine piston. These pressure fluctuations cause the valve to open and close several times in the immediate succession before the pilot oil pressure drops sufficiently for the valve to remain in the open position and this may cause unwanted pressure fluctuations in the control oil line.
En yderligere ulempe ved det kendte brændstof-35 system ligger i, at ventilelementets lukning medfører en væsentlig volumenforøgelse af den til pilotolietil- 4A further disadvantage of the known fuel system is that the closure of the valve element results in a significant increase in volume for the pilot oil supply.
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gangsledningen ledende kanal, hvilket giver et for en jævn afbrænding af pilotolie uheldigt fald i pilotolietrykket .the passageway conducting channel, which results in an uneven firing of pilot oil in an unfortunate drop in pilot oil pressure.
Fra US-A-2 518 400 kendes en trykaflastnings-5 ventil til en dual-fuel dieselmotor, hvor et ventillegeme i en åben stilling forbinder en styreolietryk-ledning med en drænkanal og i en lukket stilling forbinder ledningen med et hydraulikstempel for åbning af en gastilgangsventil, ventillegemet er via et stempel 10 påvirket mod lukket stilling af det under motorens normale drift stort set konstante forpumpetryk, som hersker i tilgangsledningen til pilotoliepumpen, sålænge der i olietilgangsledningen er et minimalt forpumpetryk vil aflastningsventilen være lukket, hvilket be-15 tyder, at aflastningsventilen holder gastilgangen åben på trods af, at pilotolien ikke indsprøjtes i motorcylinderen.From US-A-2,518,400 a pressure relief valve is known for a dual-fuel diesel engine, in which an valve body in an open position connects a control oil pressure line to a drainage channel and in a closed position the line connects to a hydraulic piston for opening a gas supply valve, the valve body is actuated via a piston 10 against the closed position of the substantially constant pre-pump pressure prevailing in the supply line to the pilot oil pump, as long as there is a minimum pre-pump pressure in the oil supply line, which means that the relief valve is closed. the relief valve keeps the gas inlet open even though the pilot oil is not injected into the engine cylinder.
Et formål for opfindelsen er at undgå ovennævnte ulemper. Med opfindelsen tilstræbes endvidere opnåelse 20 af det jævnest mulige trykforløb i styre- og pilotolie-ledningerne samt en præcis styring af styreolietrykket.An object of the invention is to avoid the above disadvantages. The invention further aims to achieve 20 the smoothest possible pressure flow in the control and pilot oil lines as well as precise control of the control oil pressure.
Et yderligere formål er at anvise en driftssikker og slidbestandig trykaflastningsventil.A further object is to provide a reliable and durable pressure relief valve.
Med henblik herpå er det indledningsvis nævnte 25 brændstofsystem ifølge opfindelsen ejendommeligt ved, at ventillegemet er påvirket af pilotolietrykket via et stempel, og at ventillegemet er påvirket mod lukket stilling af styreolietrykket, når legemet står i lukket stilling og spærrer den første drænkanal.To this end, the fuel system according to the invention initially mentioned is characterized in that the valve body is actuated by the pilot oil pressure via a piston and that the valve body is actuated against the closed position of the control oil pressure when the body is in the closed position and closes the first drainage channel.
30 Fordi styreolietrykket påvirker det i den lukke de stilling stående ventillegeme mod lukket stilling, kræves pilotolietrykket udelukkende anvendt til den indledende lukning af ventilen, så at styreolietrykket kan opbygges til et trykniveau tilstrækkeligt til, at 35 fjederens i åbneretningen virkende kraft på ventillegemet overvindes, hvorefter ventilen bliver holdt lukketBecause the control oil pressure affects the valve body standing in the closed position against the closed position, the pilot oil pressure is used solely for the initial closing of the valve, so that the control oil pressure can be built up to a pressure level sufficient to overcome the spring force acting on the valve body, after which the valve is kept closed
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5 af styreolietrykket, indtil styreolietilførsien til styreolieledningen bliver afbrudt på et i forhold til motorens belastning passende sted af motorstemplets ar-bejdsslag, hvor gasindblæsningen skal afsluttes. Anven-5 delsen af et stempel til overføring af pilotoliens trykpåvirkning til ventillegemet giver en præcist.virkende ventil og er muliggjort af, at alene det til initiering af gasindblæsningen hørende pilotolietryk er påkrævet for sikring af trykaflastningsventilens funk-10 tion..5 of the control oil pressure until the control oil supply to the control oil line is interrupted at a suitable position relative to the engine load by the working stroke of the engine piston, where the gas supply must be terminated. The use of a plunger for transferring the pressure effect of the pilot oil to the valve body provides a precise acting valve and is made possible that only the pilot oil pressure associated with the initiation of the gas supply is required to ensure the function of the pressure relief valve.
En foretrukken udførelsesform, hvor ventillege-njet er en glider, der i den ene ende har en koaksial, som nåleventil udformet aksial ansats til samvirken med et ventilsæde, der omgiver den første drænkanal, er 15 ejendommelig ved, at glideren har en aksialt bort fra ansatsen vendende første stempelflade, der ligger i et trykkammer, at en i glideren gående mellemkanal forbinder trykkammeret med den første drænkanal, når ansatsen ligger an mod ventilsædet i ventillegemets lukkede 20 stilling, og at stemplet ligger tætsluttende i en boring i aksial forlængelse af glideren og har en aksial bort fra ansatsen vendende anden stempelflade, som er påvirket af pilotolietrykket. Ved passende dimensionering af den første og den anden ventilflades arealer 25 bliver ansatsen og ventilsædet kun lavt belastet i drift, fordi et i åbneretningen virkende stigende tryk på ansatsen modsvarer et tilsvarende i lukkeretningen virkende stigende tryk på den første stempelflade. Udførelsesformen er konstruktivt enkel, og der er fra 30 samtlige oliefyldte kamre i ventilen altid god strømningsforbindelse til enten styreolieledningen eller en eksempelvis sidevendt og under lavt tryk stående drænåbning, hvilket fremmer hurtig indstilling af ventilen i afhængighed af de til enhver tid herskende pilot- og 35 styreolietryk, idet intet kammer skal olietømmes gennem en strømningsbegrænsende spalteåbning, såsom eksempelvis et lukkende ventilsæde.A preferred embodiment, in which the valve bearing is a slider having at one end a coaxial shaped needle-like axial shoulder for cooperation with a valve seat surrounding the first drainage channel, is characterized in that the slider has an axial away from the the first facing piston surface lying in a pressure chamber, that an intermediate channel extending in the slider connects the pressure chamber with the first drainage channel when the impact engages the valve seat in the closed position of the valve body and that the piston seals tightly in a bore in axial extension of the slide and has an axial away from the impactor second piston surface which is affected by the pilot oil pressure. By appropriately dimensioning the areas 25 of the first and second valve faces 25, the impactor and valve seat are only low-loaded in operation, because an increasing pressure on the shoulder acting in the open direction corresponds to a corresponding increasing pressure acting on the first piston surface. The embodiment is structurally simple, and from all 30 oil-filled chambers in the valve, there is always good flow connection to either the control oil line or, for example, a side-facing and low-pressure drainage opening, which promotes rapid adjustment of the valve in dependence on the pilot and 35 control oil pressure, since no chamber should be oil-drained through a flow restricting gap opening, such as, for example, a closing valve seat.
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Ved en videreudvikling af den foretrukne udførelsesf orm, hvor ventilen lukkes, når trykket i pilot-olieledningen når op på et bestemt tryk, er der opnået en minimal belastning af ventilsædet samtidig med op-5 retholdelse af korrekt ventilfunktion, ved at fjederens karakteristik og arealet af den anden stempelflade- fortrinsvis er således indbyrdes afpasset, at den af nævnte bestemte tryk i pilotolieledningen frembragte lukkekraft på den anden stempelflade svarer til fjederens 10 åbnekraft, når glideren står i lukket stilling.In a further development of the preferred embodiment in which the valve closes when the pressure in the pilot oil line reaches a certain pressure, a minimal strain of the valve seat is achieved while maintaining proper valve function, in that the characteristics of the spring and the area of the second piston surface is preferably mutually arranged such that the closing force produced by said particular pressure in the pilot oil line on the second piston surface corresponds to the opening force of the spring 10 when the slider is in the closed position.
Dersom brændstofsystemet er udformet til at etablere styreolietrykket opstrøms for trykaflastningsventilen til hver injektor, inden pilotolietrykket til samme injektor opbygges, for derved at styre tændtids-15 punktet alene gennem indstilling af pilotoliepumperne, kan der ved fjederbrud ske en for tidlig lukning af aflastningsventilen og dermed en for tidlig indblæsning af gas. Por at hindre dette er en udførelsesform ejendommelig ved, at en med glideren og den første dræn-20 kanal koaksial glidebøsning i en yderstilling spærrer for en anden drænkanal, der står i forbindelse med sty-reolieledningen, og at giidebøsningen og glideren mellem sig bærer fjederen, som forbelaster glideren mod åben stilling og glidebøsningen mod lukket stilling.If the fuel system is designed to establish the control oil pressure upstream of the pressure relief valve for each injector, before the pilot oil pressure for the same injector is built up, thereby controlling the ignition point only by adjusting the pilot oil pumps, premature closure of the relief valve can result in a spring failure. premature gas injection. To prevent this, an embodiment is characterized in that a coaxial sliding sleeve with a slider and the first drain channel in an outer position blocks another drain channel which communicates with the steering oil line and that the guide sleeve and the slider between them carry the spring. , which pre-loads the slider toward the open position and the slider to the closed position.
25 Såfremt fjederen knækker vil glidebøsningen forskydes bort fra yderstillingen og derved blotte den anden drænkanal, så at trykopbygning i styreolieledningen hindres, og gasventilen forbliver lukket. Som følge af den manglende gasindblæsning i motorcylinderen vil 30 fejltilstanden hurtigt detekteres af motorens overvågningssystem, hvorefter betjeningspersonalet kan udskifte fjederen.25 If the spring breaks, the sliding sleeve will be moved away from the outer position, thereby exposing the second drainage channel so that pressure build-up in the control oil line is prevented and the gas valve remains closed. Due to the lack of gas supply in the engine cylinder, the failure condition will be quickly detected by the engine monitoring system, after which the operating personnel can replace the spring.
Overbelastning af ventilelementet og det tilhørende sæde er på enkel vis ved en foretrukket ud-35 førelsesform, hvor der i giidebøsningens inderside er udformet et i bøsningens åbneretning virkende, effek- 7Overloading of the valve member and associated seat is in a simple manner in a preferred embodiment, in which an effective effect acting in the opening direction of the bushing is formed in the inner side of the guide sleeve.
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tivt stempelareal, som er påvirket af styreolietrykket i den anden drænkanal, hindret ved, at bøsningen har en bort fra fjederen vendende inderrand, der er udformet som ventil til samvirken med et ventilsæde, som ligger 5 koaksialt med bøsningen på den modsat fjederen liggende side af den anden drænkanal, fordi bøsningen vil-forskydes bort fra ventilsædet og derved åbne for bortdræning af styreolie, når det på glidebøsningens effektive areal virkende styreolietryk overskrider en forud-10 bestemt trykhøjde, som afhænger af fjederforspændingen.The piston area affected by the control oil pressure in the second drainage channel is obstructed by the bushing having an inner edge away from the spring, which is designed as a valve for cooperation with a valve seat located coaxially with the bushing on the opposite side of the spring. the second drainage channel, because the bushing will be displaced away from the valve seat and thereby open to draining control oil when the control oil pressure acting on the effective area of the sliding sleeve exceeds a predetermined pressure height which depends on the spring bias.
En foretrukken udførelsesform for opfindelsen beskrives herefter nærmere med henvisning til den skematiske tegning, hvor fig. 1 rent skematisk viser hovedkomponenterne i 15 et brændstofsystem ifølge opfindelsen til et enkelt par af dual-fuel injektorer, fig. 2 et længdesnit gennem systemets trykaflastningsventil med et ventilhus og et ventilelement, fig. 3 i større skala et fra ventilelementsiden 20 set endebillede af ventilhuset i fig. 2, fig. 4 et sidebillede af et aktiveringsstempel, fig. 5 og 6 i større skala ventilelementet i fig. 2 i henholdsvis sidebillede og endebillede, fig. 7 i større skala et tværsnit gennem ventil-25 sædet for ventilen i fig. 2, fig. 8 et snit gennem en til ventilsædet hørende glidebøsning, og fig. 9 en grafisk illustration af et muligt trykforløb i de til ventilelementet sluttede olieled-30 ninger.A preferred embodiment of the invention will now be described in more detail with reference to the schematic drawing, in which fig. 1 is a schematic representation of the main components of a fuel system according to the invention for a single pair of dual-fuel injectors; 2 is a longitudinal section through the pressure relief valve of the system with a valve housing and a valve element; FIG. 3 is an enlarged end view of the valve body of FIG. 2, FIG. 4 is a side view of an activation plunger; FIG. 5 and 6 on a larger scale the valve element of FIG. 2 in the side view and end view, respectively; 7 is an enlarged cross-section through the valve seat of the valve of FIG. 2, FIG. 8 is a section through a valve sleeve associated with the valve seat; and FIG. 9 is a graphical illustration of a possible pressure loss in the oil lines connected to the valve element.
Fig. 1 antyder en brændgasinjektor 1 og en pilotolieinjektor 2, som er indrettet til fælles montering i en motorcylinders ikke viste cylinderdæksel, og som i deres forreste, i cylinderens forbrændings-35 kammer indragende ender har en forstøver henholdsvis 3 og 4 med ikke viste dysehuller til henholdsvis ind-FIG. 1 indicates a fuel injector 1 and a pilot oil injector 2, which are arranged for common mounting in a cylinder cover of a motor cylinder, and which have at their front end projecting into the cylinder's combustion chamber an atomizer 3 and 4 with nozzle holes not shown respectively. Check
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8 blæsning af gas og indsprøjtning af pilotolie i motorcylinderen. Foroven på injektoren 1 er markeret en tilgangsledning 5 for gas fra en egnet kilde samt en tilgangsledning 6 for styreolie, som tjener til at 5 åbne en i injektoren indbygget ventil, der styrer ind-blæsning af gas i cylinderen, og som er påvirket mod lukket stilling af en forspændt fjeder. Foroven på pi-lotolieinj ektoren 2 er markeret en tilgangsledning 7 for pilotolie, som via en fjederbelastet ventil 10 kan -ledes til de tilhørende dysehuller i - forstøveren 4. Dersom motoren skal drives på gas med høj brændværdi kan det nødvendige gasforstøverareal i visse tilfælde blive så lille, at gas- og pilotolieinjektorerne kan kombineres i en enkelt injektor. Et eksempel på en 15 sådan injektor er beskrevet mere udførligt i ansøgerens danske patent nr. 155 757.8 blowing gas and injecting pilot oil into the engine cylinder. At the top of the injector 1 is marked a supply line 5 for gas from a suitable source and an access line 6 for control oil, which serves to open a valve built into the injector which controls the supply of gas into the cylinder and which is actuated against the closed position of a biased spring. At the top of the pilot oil injector 2 is marked an inlet pipe 7 for pilot oil, which can be fed via a spring-loaded valve 10 to the associated nozzle holes in the nebulizer 4. If the engine is to be operated on high calorific gas, the necessary gas atomizer area can in some cases be so small that the gas and pilot oil injectors can be combined into a single injector. An example of such an injector is described in more detail in the applicant's Danish Patent No. 155,757.
På motorens styreaksel, som i fig. 1 skematisk er antydet ved 8, er fastgjort en knast 9 til aktivering af en pilotoliepumpe 10 samt en knast 11, 20 der aktiverer en styreoliepumpe 12 for levering af styreolie til injektoren 1. Pumperne 10 og 12 kan være af den såkaldte Bosch-type, der på kendt måde er udstyret med organer til variation af pumpens leveringsmængde ved en relativ drejning af dens stempel og 25 foring samt eventuelt også midler til ændring af begyndelsestidspunktet for det effektive pumpeslag (leveringsfasen) . Pumpen 10 har foruden sin til ledningen 7 sluttede afgang en tilgang 13, gennem hvilken pumpen fødes med pilotolie fra en forpumpe, og en re-30 turledning 14 til forpumpens sugeside. På tilsvarende vis er pumpen 12 tilsluttet en tilgang 15 for sty-reolie og en returledning 16 til styreoliekilden, som kan være den med pilotoliepumpen forbundne forpumpe.On the steering shaft of the motor, as in FIG. 1 is schematically indicated at 8, is attached a cam 9 for activating a pilot oil pump 10 and a cam 11, 20 which activates a control oil pump 12 for supplying control oil to the injector 1. The pumps 10 and 12 may be of the so-called Bosch type. in a known manner, are provided with means for varying the delivery quantity of the pump by a relative rotation of its piston and liner as well as possibly also means for changing the starting time of the effective pump stroke (the delivery phase). The pump 10, in addition to its outlet connected to the conduit 7, has an inlet 13 through which the pump is fed with pilot oil from a pre-pump and a return line 14 to the suction side of the pre-pump. Similarly, pump 12 is connected to a control oil inlet 15 and a return line 16 to the control oil source, which may be the pre-pump connected to the pilot oil pump.
I stedet for pumpen 12 kan der alternativt an-35 vendes en af knasten 11 aktiveret styreventil, som fødes fra en kilde for styreolie ved et passende højtAlternatively, instead of the pump 12, a control valve actuated by the cam 11 may be used, which is fed from a source of control oil at a suitably high
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9 tryk, dvs. et tryk som ved påvirkning af det dertil bestemte areal af injektoren l's gasventil kan åbne denne ventil og holde den åben mod kraften fra den tilhørende lukkefjeder.9 pressure, i.e. a pressure which, upon actuating the designated area of the gas valve of the injector 1, can open this valve and keep it open against the force of the corresponding closing spring.
5 En ventilblok 17 er opstrøms for injektorerne således indskudt i tilgangsledningerne 6 og 7,. at disse i afstand fra hinanden forløber gennem blokken.5, a valve block 17 is upstream of the injectors thus inserted into the supply lines 6 and 7. that these are spaced apart through the block.
En i blokken indsat trykaflastningsventil 18 kan holde styreolietilgangsledningen 6 i åben forbindelse 10 med en drænledning 19, der leder til en under tilnærmelsesvis atmosfæretryk stående opsamlebeholder 20 for styreolie, fra hvilken styreolietilgangen 15 eksempelvis kan fødes. Ved motorer med høj ydelse pr. cylinder kan der i hvert cylinderdæksel være flere par af 15 injektorer 1 og 2, der alle parallelt forsynes med pilotolie og styreolie fra samme ventilblok 17, der hensigtsmæssigt er monteret på siden af motorcylinderens dæksel.A pressure relief valve 18 inserted in the block can hold the control oil supply line 6 in open connection 10 with a drain line 19 which leads to a control oil collecting container 20 located under approximate atmospheric pressure, from which the control oil supply 15 can, for example, be fed. For high-performance engines per per cylinder, there may be in each cylinder cover several pairs of 15 injectors 1 and 2, all provided in parallel with pilot oil and control oil from the same valve block 17 suitably mounted on the side of the engine cylinder cover.
I fig. 2 ses trykaflastningsventilen 18, der 20 omfatter en ventilkrop 21, som ved sin ene ende bærer et ventilhus 22 og ved sin anden ende er fastgjort af en bolt 23 til en monteringsflange 24, som kan fastspændes til ventilblokken 17. En rundtgående reces 25 i ventilkroppen står gennem ikke viste tvær-25 boringer i ventilblokken 17 i forbindelse med tilgangsledningen 6 for styreolie og leder via flere, fortrinsvis fire radiale boringer til en central tilgangskanal 27 for styreolie.In FIG. 2, the pressure relief valve 18, which comprises a valve body 21, which at one end carries a valve housing 22 and at its other end is secured by a bolt 23 to a mounting flange 24, which can be clamped to the valve block 17. An annular recess 25 in the valve body stands through transverse-25 bores in valve block 17 in connection with control oil inlet line 6 and conducts via several, preferably four radial bores to a central control oil inlet channel 27.
En fra pilotolietilgangsledningen 7 afgrenet 30 og ikke vist tværboring udmunder i bunden af den ventiloptagende udboring i ventilblokken, så at det øjeblikkelige pilotolietryk i ledningen 7 påvirker yderenden af ventilhuset 22 i området omkring en reces 28 til sikring af god trykkommunikation med tværborin-35 gen.A branch 30 branched from the pilot oil supply conduit 7 and not shown in the bore leads to the bottom of the valve receiving bore in the valve block, so that the instant pilot oil pressure in the conduit 7 affects the outer end of the valve housing 22 in the region of a recess 28 to ensure good pressure communication with the cross bore.
Det indre af ventilhuset 22 er gennem flere radialvendte drænåbninger 29 forbundet med drænled-The interior of the valve housing 22 is connected through a plurality of radial-facing drain openings 29
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10 ningen 19, så at der i husets indre normalt hersker et tryk på under 10 bar.10, so that a pressure of less than 10 bar normally exists in the interior of the housing.
Med henblik på positionering af boringerne 26 og åbningerne 29 umiddelbart ud for de tilhørende bo-5 ringer i ventilblokken er ventilhuset 22, ventilkroppen 21 og flangen 24 indbyrdes drejningsfikse-ret ved hjælp af to i boringer placerede styrestifter 30 og 31.In order to position the bores 26 and the openings 29 immediately adjacent to the corresponding bores in the valve block, the valve housing 22, the valve body 21 and the flange 24 are mutually rotated by two guide pins 30 and 31 located in the bores.
En i en not i ventilhusets yderperiferi indlagt 10 tætning 32 hindrer, at pilotolietrykket tabes ved omløb af pilotolie til drænledningen 19. På tilsvarende vis tætner to aksialt på hver sin side af recessen 25 beliggende og i hver sin not i ventilkroppens yderperiferi indlagte tætninger 33 mod utilsigtet tab af sty-15 reolie.A seal 32 inserted in a groove in the outer periphery of the valve body prevents the pilot oil pressure from being lost by circulating pilot oil to the drain line 19. Similarly, two seals located axially on each side of the recess 25 and in each groove in the outer periphery of the valve body 33 accidental loss of steering oil.
Ventilhuset 22 og -kroppen 21 er i retning bort fra husets yderende udformet med trinvis voksende diameter for at undgå unødig slid på og belastning af tætningerne 32 og 33 ved aflastningsventilens sam-20 ling og af- samt påmontering i ventilblokken ved dels at tætningen kun skal indføres over et kort ventilstykke med den til tætningen hørende fulde diameter, førend den kan lægges ned i noten, dels at notens yderside ved montering kun skal forskydes en kort 25 distance for at frigøres fra den tilhørende pakflade i ventilblokken.The valve housing 22 and body 21 are designed in a direction away from the outer edge of the housing with incremental diameter to avoid unnecessary wear and strain of the seals 32 and 33 during the relief valve assembly and removal and mounting in the valve block, partly because the seal only has to is inserted over a short valve piece with the full diameter of the seal before it can be inserted into the groove, and partly that the outside of the groove when mounted must only be moved a short distance to be released from the corresponding sealing surface in the valve block.
I ventilhuset 22's endeafsnit er udformet en første central boring 34 (fig. 3), der fra den tværgående reces 28 i aksial retning hen mod ventilkrop-30 pen udmunder i et trykkammer 35, der fortsætter over i en anden central boring med større diameter end den første. Et i fig. 4 vist stempel 36 ligger med en tætsluttende og aksialt forskydelig cirkulærcylindrisk kropsdel 37 i den første boring. Kropsdelen går via et 35 halsparti 38 over i en cylindrisk hoveddel 39 med større diameter, der gennem anlæg mod trykkammerets en-In the end portion of the valve housing 22, a first central bore 34 (Fig. 3) is formed which, from the transverse recess 28, axially towards the valve body 30, opens into a pressure chamber 35 which proceeds into a second central bore of larger diameter than the first. One in FIG. 4 shows piston 36 with a tightly sloping and axially displaceable circular cylindrical body portion 37 in the first bore. The body portion passes through a neck portion 38 into a larger diameter cylindrical body portion 39 which through contact with the pressure chamber end.
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11 debund begrænser stempelvandringen hen mod recessen 28.11 debund restricts the piston walk towards the recess 28.
Et ventillegeme 40 er aksialt forskydeligt under styring af et som stempel 41 udformet endeparti, 5 der ligger tætsluttende i den anden boring og har en første aksialvendt stempelflade 42, som ligger i ±ryk-kammeret 35. Ventillegemets modstående endeparti er optaget i en med den første og anden boring koaksial udsparing i ventilhuset 22 og er udformet som en ko-10 aksial, keglestubformet ansats 43, der. virker som nåleventil. Mellem ansatsen og stemplet har legemet 40 en udragende, rundtgående flange 44, som danner styr for en trykfjeder 45.A valve body 40 is axially displaceable under the control of an end portion 5 formed as a piston 41 which seals tightly in the second bore and has a first axially facing piston surface 42 which is in the ± jerk chamber 35. The opposite end portion of the valve body is accommodated in a first and second bores are coaxial recesses in the valve housing 22 and are formed as a coaxial conical stub-shaped shoulder 43 which. acts as a needle valve. Between the abutment and the plunger, the body 40 has a protruding, circumferential flange 44 which provides a guide for a compression spring 45.
Et centralt, cylindrisk fremspring 46 (fig. 7) 15 på ventilkroppen har en med ventilhusets anden boring koaksial, første drænkanal 47, som forlænger tilgangskanalen 27 frem til et i ventilhusets udsparing udmundende, keglestubformet sæde 48 for ventillegemets ansats 43.A central cylindrical projection 46 (Fig. 7) 15 of the valve body has a coaxial, first drainage channel 47 with the valve bore second, which extends the inlet channel 27 to a cone-shaped stub-shaped seat 48 for valve body abutment 43.
20 En i fig. 8 vist glidebøsning 49 ligger tæt sluttende omkring en glideflade 50 på det som glide-styr virkende fremspring 46 og har i enden bort fra ventillegemet en udragende, rundtgående flange 51, der bl.a. danner styr for fjederen 45.20 An embodiment of FIG. 8, the sleeve 49 shown seals closely around a sliding surface 50 on the sliding guide 46 and has at the end away from the valve body a protruding, circumferential flange 51 which includes forming guide for the spring 45.
25 Fra tilgangskanalen 27 udgår mindst én radial anden drænkanal 52, som udmunder mellem glidefladen 50 og et keglestubformet ventilsæde 53, som ligger omkring roden af fremspringet 46. Sædet 53 samvirker med inderranden 54 af den som ventillegeme virkende 30 bøsning 49. Trykfjederen 45 forbelaster bøsningen mod lukket stilling og ventillegemet 40 mod åben stilling. Glidebøsningens inderside er udformet i tre forskellige afsnit med hver sin diameter. Ud for glidefladen 50 har bøsningen en inderdiameter Dg, som er 35 en anelse mindre end diameteren Dv af afsnittet op til sædet 53, og det mellemliggende afsnit har størstAt least one radially second drainage channel 52 exits from the inlet duct 27, which opens between the sliding surface 50 and a cone-shaped valve seat 53, which lies around the root of the projection 46. The seat 53 interacts with the inner rim 54 of the valve body acting as a valve body 49. The compression spring 45 baffles the bushing toward closed position and valve body 40 toward open position. The inside of the sliding sleeve is formed in three different sections with different diameters. Next to the sliding surface 50, the sleeve has an inner diameter Dg, which is slightly smaller than the diameter Dv of the section up to the seat 53, and the intermediate section has the largest
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12 diameter Dk for ud for drænkanalen 52 at skabe et trykkammerlignende hulrum med en aksial udstrækning, der muliggør olietilstrømning til hulrummet, selv når bøsningen bevæges bort fra sit ventilsæde.12 diameter Dk to create, for the drainage duct 52, a pressure chamber-like cavity with an axial extension which allows oil flow into the cavity even as the sleeve is moved away from its valve seat.
5 Fordi diameterforholdet Dv/Dg >1 vil bøsningens inderside udvise et i åbneretningen effektivt stempelareal 55, som vil påvirke bøsningen til bevægelse bort fra ventilsædet, når styreolietrykket bliver tilstrækkeligt højt til, at den på arealet 55 virkende 10 åbnekraft overstiger fjederen 45's lukkekraft. Styreolien undviger derefter forbi ventilsædet 53 og via ventilhusets udsparing og åbningerne 29 ud i drænledningen 19. Flangen 51's yderdiameter kan afpasses således efter udsparingens inderdiameter, at der 15 mellem disse er en smal drøvlespalte, som styreolien skal passere på vej ind i udsparingen. Drøvlespalten begrænser trykfaldet over ventilsædet og. hindrer pludselige trykfald i styreolieledningen 6, når bøsningsventilen åbner. Det vil indses, at glidebøsningen 20 virker som overtryksventil, når ventilelementet står i lukket stilling og afspærrer den første drænkanal. Dersom pumpen 12 er indrettet til levering af en rigelig oliemængde, og udsparingen er udført med større diameter eller endog en jævnt voksende diameter i et om-25 råde 56 (fig. 1) umiddelbart på fjedersiden af flangen 51, vil den egentlige regulering af styreolietrykket ske over drøvlespalten, idet styreolien umiddelbart efter bøsningens indledende bevægelse bort fra sædet vil trænge ud i det ringformede rum 57 mellem ventil-30 kroppen 21 og flangen 51 og dér påvirke hele flangens endeflade 58 med et tryk, der påvirker bøsningen til yderligere bevægelse bort fra sædet, hvilket på sin side fører til stigende fjederlukkekraft og på grund af den større diameter i området 56 til faldende drøvle-35 modstand, så at der indstiller sig en ligevægt med stort set konstant olietryk ved gasinjektorventilen,Because the diameter ratio Dv / Dg> 1, the inside of the sleeve will exhibit a piston area 55 effective in the opening direction which will affect the sleeve for movement away from the valve seat when the control oil pressure becomes sufficiently high that the open force exerted on the area 55 exceeds the closing force of the spring 45. The guide oil then escapes past the valve seat 53 and via the valve body recess and the openings 29 into the drain line 19. The outer diameter of the flange 51 can be adjusted to the inner diameter of the recess such that there is a narrow throttle gap between which the steering oil must pass on the way into the recess. The throttle gap limits the pressure drop across the valve seat and. prevents sudden pressure drop in the control oil line 6 when the sleeve valve opens. It will be appreciated that the sliding sleeve 20 acts as an overpressure valve when the valve member is in the closed position and closes the first drainage channel. If the pump 12 is arranged to deliver a plentiful amount of oil and the recess is made with a larger diameter or even an evenly increasing diameter in a region 56 (Fig. 1) immediately on the spring side of the flange 51, the actual control of the control oil pressure will immediately after the initial movement of the sleeve away from the seat, the steering oil will penetrate into the annular space 57 between the valve body 21 and the flange 51 and thereupon affect the entire flange end surface 58 with a pressure affecting the sleeve for further movement away from the sleeve. the seat, which in turn leads to increasing spring closing power and, due to the larger diameter in the region 56, to decreasing throttle resistance, so that an equilibrium with substantially constant oil pressure is established at the gas injector valve,
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13 indtil kammen 11 mindsker eller afbryder styreolie-tilførsien.13 until the cam 11 decreases or interrupts the control oil supply.
Dersom fjederen 45 knækker er det klart, at selv et ringe styreolietryk vil forskyde bøsningen 49 5 bort fra sædet 53.If the spring 45 breaks, it is clear that even a low control oil pressure will displace the bushing 49 5 away from the seat 53.
Lukning af den første drænkanal 47 sker under stigende pilotolietryk i ledningen 7 ved, at trykket på en anden stempelflade 59, der består af stemplet 37's ud mod recessen 28 åbne endeflade, bliver af en 10 sådan størrelse, at stemplet 36 påvirker, ventillegemet 40 med en lukkekraft, der overstiger fjederkraften, hvorefter stemplet og legemet bevæges hen mod fremspringet 46, indtil ansatsen 43's ventilflade ligger an mod sædet 48. Ventillukningen frembringer 15 minimal forstyrrelse i pilotoliesystemet, fordi den medfølgende volumenændring i systemet er ringe, idet den anden stempelflade har lille areal og stemplet har kort vandringsvej.The closing of the first drainage channel 47 occurs under increasing pilot oil pressure in the conduit 7 by the pressure of a second piston surface 59 consisting of the piston 37 open to the recess 28 towards the recess 28 being of a size such that the piston 36 affects, the valve body 40 with a closing force exceeding the spring force, after which the plunger and body move toward the projection 46 until the valve face of the shoulder 43 abuts the seat 48. The valve closure causes minimal disruption to the pilot oil system because the accompanying volume change in the system is low. area and stamp have short walking path.
Styreolietilførslen kan uden risiko for tidlig 20 gasindsprøjtning påbegyndes førend pilotolietrykket er opbygget til indsprøjtningstryk, fordi styreolien blot vil undvige gennem den første drænkanal 47 og drænledningen 19, når ventillegemet står i åben stilling. Såsnart ansatsen 43 afspærrer den første 25 drænkanal 47, sættes trykkammeret 35 i forbindelse med styreolietilgangskanalen 27 gennem en central, gennemgående mellemkanal 60 i ventillegemet. Af hensyn til ansatsens mekaniske styrke kan mellemkanalen i det gennem ansatsen gående afsnit have reduceret dia-30 meter. En tværgående not 61 i den første stempelflade skærer mellemkanalen og giver denne forbindelse med kammeret 35 uafhængig af, om stempelhovedet 39 ligger tæt an mod ventilelementet.The control oil supply can be started without the risk of early gas injection before the pilot oil pressure is built up to injection pressure, because the control oil will only escape through the first drain channel 47 and the drain line 19 when the valve body is in the open position. As soon as the bracket 43 locks the first drainage channel 47, the pressure chamber 35 is connected to the control oil supply channel 27 through a central, through-flow passage 60 in the valve body. Due to the mechanical strength of the strut, the intermediate channel in the section passing through the strut may have reduced the diameter by 30 meters. A transverse groove 61 in the first piston surface cuts the intermediate channel and provides this connection with the chamber 35 regardless of whether the piston head 39 is adjacent to the valve member.
Ved opbygning af styreolietryk i tilgangskana-35 len 27 vil styreolien strømme ind i kammeret 35 og her opbygge et tilsvarende tryk, der på den førsteWhen the control oil pressure is built up in the inlet channel 27, the control oil will flow into the chamber 35 and here build up a corresponding pressure which on the first
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14 stempelflade 42 frembringer en lukkekraft, som ved vedvarende styreolietilførsel er tilstrækkelig til fastholdelse af ventilelementet i den lukkede stilling.14 piston surface 42 produces a closing force which, by continuous control oil supply, is sufficient to hold the valve element in the closed position.
Når først styreolietrykket er opbygget, er aflastnings-5 ventilens funktion uafhængig af pilotolietrykket.Once the control oil pressure is built up, the function of the relief valve is independent of the pilot oil pressure.
Ved det i fig. 9 viste, stærkt forenklede kurveforløb angiver ordinataksen olietryk i bar, og abscisseaksen viser krumtapakslens drejningsvinkel med en afstand mellem markeringerne på 10° krumtapvinkel. Den 10 med .kortstreglinie illustrerede kurve viser pilotolietrykket før olieinjektorventilen, og det ses af det viste udsnit af en komplet arbejdscyklus, at pilotolietrykket opbygges umiddelbart førend arbejdsstemplet passerer øverste dødpunktstilling som indledning til 15 arbejdsslaget. Ved et pilotolietryk på omtrent 250 bar ses et fald i trykstigningstakten, hvilket indikerer at pilotolieindsprøjtningen initieres, og umiddelbart derefter forskydes ventilelementet til lukket stilling. Pilotolieindsprøjtningen vedvarer indtil arbejdsstem-20 plet har påbegyndt arbejdsslaget.In the embodiment shown in FIG. 9, the highly simplified waveforms show the ordinate axis oil pressure in bar, and the abscissa axis shows the axis of rotation of the crankshaft with a distance between the markings of 10 ° crank angle. The 10-dashed curve illustrates the pilot oil pressure before the oil injector valve, and it is seen from the shown section of a complete duty cycle that the pilot oil pressure builds up immediately before the work piston passes the top dead center position as an introduction to the 15 stroke. At a pilot oil pressure of about 250 bar, a decrease in the pressure rise rate is observed, indicating that the pilot oil injection is initiated and immediately thereafter the valve member is shifted to the closed position. The pilot oil injection continues until the work piston has started the work stroke.
Den fuldtoptrukne kurve angiver trykforløbet i styreolieledningen 6, når motoren er lavt belastet, og den stiplede kurve trykforløbet, når motoren arbejder nær fuldlast. Det fremgår, at styreolietrykket før 25 ventilelementets lukning ligger på lavt niveau svarende til bortledningstrykket i drænåbningen 29. Få graders krumtapdrejning efter aflastningsventilens lukning stiger styreolietrykket jævnt op mod gasinjektorventilens åbnetryk ved omkring 400 bar, og allerede fra et tryk 30 på ca. 90 bar overtager styreolietrykket pilotolietrykkets lukkefunktion i ventilen. Styreolietrykket vedbliver at stige indtil bøsningen åbner ved et tryk på ca. 600 bar, og derefter holdes dette tryk stort set konstant, indtil knasten 11 eller pumpen 12 af-35 bryder pilotolietilførsien ved en krumtapstilling, der afhænger af motorbelastningen.The fully drawn curve indicates the pressure flow in the control oil line 6 when the engine is low loaded and the dotted curve the pressure flow when the engine is operating near full load. It can be seen that the control oil pressure before the valve element closure is at a low level corresponding to the drainage pressure in the drain opening 29. A few degrees of crank rotation after the closing of the relief valve increases the control oil pressure evenly against the opening pressure of the gas injector valve at about 400 bar, and already from a pressure of about 30 bar. At 90 bar, the control oil pressure takes over the pilot oil pressure closing function in the valve. The control oil pressure continues to rise until the bush opens at a pressure of approx. 600 bar, and then this pressure is kept substantially constant until the cam 11 or pump 12 interrupts the pilot oil supply at a crank position which depends on the engine load.
Claims (9)
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK082290A DK164293C (en) | 1990-04-02 | 1990-04-02 | FUEL SYSTEM FOR A DUAL-FUEL DIESEL ENGINE |
| FI911553A FI103601B1 (en) | 1990-04-02 | 1991-03-28 | Fuel system for dual fuel diesel engine |
| KR1019910005220A KR0180545B1 (en) | 1990-04-02 | 1991-04-01 | Fuel system for double engine fuel diesel engine |
| JP3096324A JP2529034B2 (en) | 1990-04-02 | 1991-04-02 | Fuel system for dual fuel diesel engine |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK082290A DK164293C (en) | 1990-04-02 | 1990-04-02 | FUEL SYSTEM FOR A DUAL-FUEL DIESEL ENGINE |
| DK82290 | 1990-04-02 |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK82290D0 DK82290D0 (en) | 1990-04-02 |
| DK82290A DK82290A (en) | 1991-10-03 |
| DK164293B true DK164293B (en) | 1992-06-01 |
| DK164293C DK164293C (en) | 1992-10-26 |
Family
ID=8097948
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK082290A DK164293C (en) | 1990-04-02 | 1990-04-02 | FUEL SYSTEM FOR A DUAL-FUEL DIESEL ENGINE |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2529034B2 (en) |
| KR (1) | KR0180545B1 (en) |
| DK (1) | DK164293C (en) |
| FI (1) | FI103601B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014037068A1 (en) | 2012-09-04 | 2014-03-13 | Gvh Gesellschaft Für Verbrennungsmotoren Und Hybridantriebe Mbh | Valve device, system and use thereof for injecting gaseous fuel |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101129887B1 (en) * | 2010-08-11 | 2012-03-28 | 현대중공업 주식회사 | Dual fuel injection valve |
| KR101493819B1 (en) * | 2013-11-29 | 2015-02-16 | 대우조선해양 주식회사 | Pilot Fuel Oil Supply System |
| CN109555620B (en) * | 2018-10-22 | 2023-09-22 | 中船动力研究院有限公司 | Gas injection valve with automatic protection device and working method thereof |
-
1990
- 1990-04-02 DK DK082290A patent/DK164293C/en not_active IP Right Cessation
-
1991
- 1991-03-28 FI FI911553A patent/FI103601B1/en not_active IP Right Cessation
- 1991-04-01 KR KR1019910005220A patent/KR0180545B1/en not_active IP Right Cessation
- 1991-04-02 JP JP3096324A patent/JP2529034B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014037068A1 (en) | 2012-09-04 | 2014-03-13 | Gvh Gesellschaft Für Verbrennungsmotoren Und Hybridantriebe Mbh | Valve device, system and use thereof for injecting gaseous fuel |
Also Published As
| Publication number | Publication date |
|---|---|
| FI911553A0 (en) | 1991-03-28 |
| JPH0626404A (en) | 1994-02-01 |
| KR910018665A (en) | 1991-11-30 |
| FI103601B (en) | 1999-07-30 |
| FI911553A (en) | 1991-10-03 |
| FI103601B1 (en) | 1999-07-30 |
| DK164293C (en) | 1992-10-26 |
| DK82290D0 (en) | 1990-04-02 |
| JP2529034B2 (en) | 1996-08-28 |
| KR0180545B1 (en) | 1999-03-20 |
| DK82290A (en) | 1991-10-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |
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