DK154165B - Hydraulic actuation mechanism for a gas shuttle valve in a combustion engine - Google Patents
Hydraulic actuation mechanism for a gas shuttle valve in a combustion engine Download PDFInfo
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- DK154165B DK154165B DK022483A DK22483A DK154165B DK 154165 B DK154165 B DK 154165B DK 022483 A DK022483 A DK 022483A DK 22483 A DK22483 A DK 22483A DK 154165 B DK154165 B DK 154165B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/02—Arrangements or modifications of condensate or air pumps
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Abstract
Description
DK 154165 BDK 154165 B
Opfindelsen angår en hydraulisk aktiveringsmeka-nisme for en gasvekselventil, navnlig en udstødventil/ i en forbrændingsmotor, hvilken mekanisme har dels et på ventilens spindel i åbningsretningen virkende akti-5 veringsstempel, som er aksialt forskydeligt i en cylinder, der har en adgangsport for hydraulikvæskens strømning til og fra to mellem stemplet og cylinderen afgrænsede arbejdskamre, dels en styreventil indrettet til skiftevis at slutte adgangsporten til en til-10 gangsledning for højtryks hydraulikvæske og til en returledning for hydraulikvæsken.The invention relates to a hydraulic actuating mechanism for a gas exchange valve, in particular an exhaust valve / in an internal combustion engine, which mechanism partly has an actuating piston acting on the valve spindle which is axially displaceable in a cylinder having an access port for the hydraulic fluid flow to and from two work chambers delimited between the piston and the cylinder, and a control valve arranged to alternately connect the access port to a supply line for high pressure hydraulic fluid and to a return line for the hydraulic fluid.
Fra dansk patentskrift nr. 104 206 kendes en aktiveringsmekanisme af denne art, hvor de to arbejdskamre tjener henholdsvis til åbning og lukning af udstødsven-15 tilen, idet styreventilen er indrettet således, at den i hver af sine yderstillinger slutter det ene arbejds-kammer til tilgangsledningen for den hydrauliske højtryksvæske og det andet kammer til returledningen. Det arbejdskammer, som er virksomt ved ventilåbningen, in-20 deholder dels et centralt stempel i fast forbindelse med ventilpsindlen, dels et i forhold til det centrale stempel bevægeligt ringformet stempel med en maksimal slaglængde, som er mindre end ventillegemets løftehøjde. Det hydrauliske tryk virker i .den første fase 25 af åbningsbevægelsen på det samlede areal af de to stempler og derefter kun på det centrale stempel, når det ringformede stempel er standset af et anslag i arbejdskammeret.Danish patent specification 104 206 discloses an activating mechanism of this kind, in which the two working chambers respectively serve to open and close the exhaust valve, the control valve being arranged so that in each of its outer positions it closes one working chamber to the the supply line for the hydraulic high pressure fluid and the second chamber for the return line. The working chamber operating at the valve opening contains, in part, a central piston in fixed connection with the valve stem, and a movable annular piston which is movable relative to the central piston with a maximum stroke which is less than the lift height of the valve body. The hydraulic pressure acts in the first phase 25 of the opening movement on the total area of the two pistons and then only on the central piston when the annular piston is stopped by a stop in the working chamber.
En aktiveringsmekanisme ifølge nærværende opfin-30 delse er ejendommelig ved, at de to arbejdskamre er indbyrdes forbundet gennem en ved hjælp af stemplet afspærrelig, i stemplet og/eller cylinderen udformet passage, at de effektive stempelarealer, hvorpå et hydraulisk tryk i de to arbejdskamre virker, er orien-35 teret i samme retning og modsat udstødsventilens åbningsretning, at cylinderen har en afgangsport, som er nprmanpnt sluttet til et område med lavtrvks hvdraulik-An actuating mechanism according to the present invention is characterized in that the two working chambers are interconnected through a piston-shaped and / or cylinder-interconnected passage that the effective piston areas on which a hydraulic pressure in the two working chambers works , oriented in the same direction and opposite to the opening direction of the exhaust valve, the cylinder has a discharge port, which is normally connected to an area of low-power hydraulics.
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2 væske, og som i udstødsventilens lukkede stilling er afspærret fra begge arbejdskamre ved hjælp af stemplet, og at stemplet har en første afskæringskant, som efter en forudbestemt stempelvandring fra udstødsventilens 5 lukkestilling forbinder det ene arbejdskammer med afgangsporten, og en anden afskæringskant, som er anbragt således, at den i det væsentlige .samtidig spærrer strømningsforbindelsen fra adgangsporten til det nævnte ene arbejdskammer.2 fluid, which in the closed position of the exhaust valve is blocked from both working chambers by means of the plunger, and that the plunger has a first cutting edge which, after a predetermined piston walk from the closing position of the exhaust valve 5, connects one working chamber to the discharge port and a second cutting edge which is arranged so as to substantially simultaneously block the flow connection from the access port to said one working chamber.
10 1 mekanismen ifølge opfindelsen afsluttes åb ningsbevægelsens første fase ved, at den anden afskæringskant på stemplet lukker for tilgangen af hydraulikvæske til det nævnte arbejdskammer, som stort set samtidig sluttes til det lave tryk i det hydrauliske 15 system. Den heraf betingede reduktion af det effektive stempelareal i bevægelsens sidste fase opnås således uden nogen slagpåvirkning på mekanismens komponenter svarende til den, som i den før omtalte kendte mekanisme opstår ved standsningen af det ringformede stem-20 pel på et tidspunkt af bevægelsen, hvor accelerationen er høj. Sådanne slagpåvirkninger medfører en stukning af materialet i ans lags fladerne, scan i det lange løb vil føre til rivning mellem de to delstemplers glide-flader. En yderligere fordel ved opfindelsen er, at 25 den eksterne styreventil er enklere og dermed mere driftssikker, fordi den kun skal styre strømningen gennem én til mekanismens cylinder sluttet ledning.10 1 of the mechanism according to the invention, the first phase of the opening movement is terminated by the second cutting edge of the piston closing the supply of hydraulic fluid to said working chamber, which is connected substantially to the low pressure in the hydraulic system. The consequent reduction of the effective piston area in the last phase of the movement is thus achieved without any impact on the components of the mechanism similar to that which occurs in the previously mentioned known mechanism by the stopping of the annular piston at a time of movement where the acceleration is high. Such impact impacts cause the material to crack on the impact surfaces, scanning in the long run will cause tearing between the sliding surfaces of the two pistons. A further advantage of the invention is that the external control valve is simpler and thus more reliable, since it only has to control the flow through one conduit connected to the mechanism cylinder.
I en udførelsesform for opfindelsen er passagen mellem de to arbejdskamre udformet i cylinderen og ud-30 munder i en med stemplets anden afskæringskant samvirkende rille i det andet arbejdskammers væg, og en gennem stemplet forløbende kanal forbinder adgangsporten med det andet arbejdskammer.In one embodiment of the invention, the passage between the two working chambers is formed in the cylinder and opens into a groove interacting with the piston's second cut-off edge in the wall of the second work chamber, and a passage extending through the piston connects the access port with the other work chamber.
I denne udførelsesform kan kanalen i stemplet 35 indeholde en i retning mod det andet arbejdskammer åbnende kontraventil, hvorhos stemplet har en tredje 3In this embodiment, the channel in the piston 35 may contain a non-return valve opening in the direction of the second working chamber, the piston having a third
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afskæringskant, som efter en kort indledende vandring af stemplet frigiver en direkte strømningsvej fra adgangsporten til det andet arbejdskammer. Når stemplets tredje afskæringskant lukker den direkte strømningsvej 5 fra den til returledningen sluttede adgangsport kort før afslutningen af ventilens lukkebevægeIse, indespærres den i arbejdskamrene stående væskemængde, idet kontraventilen holder kanalen gennem stemplet lukket, og herved afbremses lukkebevægelsen, således at venti-10 len lander blødt på sit stationære sæde.cutting edge, which, after a brief initial walk of the piston, releases a direct flow path from the access port to the second work chamber. When the third cut-off edge of the piston closes the direct flow path 5 from the access port connected to the return line shortly before the closing of the valve closing movement, the amount of fluid in the working chambers is restricted, the non-return valve holding the channel through the piston closed, thereby slowing the closing movement so that the bleed 10 on his stationary seat.
Samme virkning opnås i en anden udførelsesform for opfindelsen ved, at adgangsporten er i permanent forbindelse med det andet arbejdskammer, at passagen mellem de to arbejdskamre i udstødsventilens lukke-15 stilling er spærret af stemplet og efter en kort indledende vandring af stemplet frigives af en tredje afskæringskant på stemplet, og at en gennem stemplet forløbende kanal, som indeholder en i retning mod det første arbejdskammer åbnende kontraventil, forbinder 20 de to arbejdskamre.The same effect is achieved in another embodiment of the invention in that the access port is in permanent communication with the second working chamber, that the passage between the two working chambers in the closing position of the exhaust valve is blocked by the piston and after a short initial movement of the piston is released by a third a cut-off edge of the plunger, and that a passage extending through the plunger, which includes a non-return valve opening towards the first work chamber, connects the two working chambers.
Udstødsventilens spindel kan være fast forbundet med et aktiveringsstempel for ventilens lukning, hvilket stempel er forskydeligt i et arbejdskammer, der gennem en kanal i cylinderen er sluttet til en port, 25 som er permanent tilsluttet en tilgangsledning for højtryks hydraulikvæske. Herved er udstødsventilen altid, uanset stillingen af styreventilen, påvirket af en lille konstant hydraulisk kraft i lukkeretningen.The spindle of the exhaust valve may be firmly connected to an actuating piston for the valve closure, which piston is displaceable in a working chamber connected through a channel in the cylinder to a port 25 permanently connected to a high pressure hydraulic fluid supply line. In this way, the exhaust valve, regardless of the position of the control valve, is always influenced by a small constant hydraulic force in the closing direction.
Den nævnte kanal kan udmunde i en rille i arbejds-30 kammerets væg, som under denne rille har en anden rille, hvori der udmunder en anden kanal, som gennem en fjederbelastet, i retning mod den anden kanal åbnende kontraventil er sluttet til den første kanal. Når kanten af stemplet passerer underkanten af den første 35 rille, afspærres under stemplet en væskemængde, derSaid channel may open in a groove in the wall of the working chamber, which under this groove has a second groove, in which opens another channel which is connected to the first channel through a spring-loaded check valve towards the second channel. . As the edge of the piston passes through the bottom edge of the first 35 groove, a quantity of liquid is blocked below the piston.
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4 virker sam hydraulisk stødpude til blød afbremsning af ventilens åbningsbevsgelse, hvorved man undgår uheldige traskspændinger i ventilspindlen, hvis nederste del nærmest ventiltallerkenen på en udstødsventil er udsat 5 for høje driftstemperaturer og derfor har nedsat brudstyrke .4 works with a hydraulic cushion for soft braking of the valve opening movement, thereby avoiding undue throttle stresses in the valve stem whose lower part closest to the valve plate of an exhaust valve is exposed to high operating temperatures and therefore has reduced breaking strength.
Opfindelsen forklares i det følgende næmere under henvisning til tegningen, på hvilken fig. 1 rent skematisk viser en udstødsventil med 10 tilhørende hydraulisk aktiveringsmekanisme ifølge opfindelsen, fig. 2 et længdesnit gennem en udførelsesfom for den i fig. 1 skematisk viste aktiveringsmekanisme, fig. 3 et tilsvarende snit gennem en anden udførel-15 ses for for aktiveringsmekanismen ifølge opfindelsen, og j fig. 4 endnu et tilsvarende aksialsnit gennem en ! tredje udførelsesfom for opfindelsen. i I fig. 1 ses en udstødsventil 1 til en ikke vist | cylinder i en forbrændingsmotor, specielt en marinedie- 1 20 selmotor, og ventilen har et tallerkenformet hoved 2 i med en sædeflade, som samvirker med en modstående sædeflade på et ventilhus 3, der er fastgjort til motorcylinderens ikke viste dæksel. Ventilen l's spindel 4 er forskydelig styret i ventilhuset 3 og strækker sig 25 opefter ind i aktiveringsmekanismens rent skematisk viste cylinder 5, som sammen med et underliggende mellemstyk- | ke 6 er fastgjort til oversiden af ventilhuset 3.The invention will now be explained in more detail with reference to the drawing, in which: 1 is a schematic view of an exhaust valve with 10 associated hydraulic actuation mechanism according to the invention; FIG. 2 is a longitudinal section through an embodiment of the embodiment shown in FIG. 1 schematically illustrates the activation mechanism; FIG. 3 shows a similar section through another embodiment of the activation mechanism according to the invention, and j fig. 4 another corresponding axial section through one! third embodiment of the invention. In FIG. 1 shows an exhaust valve 1 for a not shown | cylinder in an internal combustion engine, in particular a marine diesel engine, and the valve has a plate-shaped head 2 in with a seat surface which cooperates with an opposite seat surface of a valve housing 3 attached to the engine cylinder cover not shown. The spindle 4 of the valve 1 is slidably guided in the valve housing 3 and extends 25 upwards into the purely schematically shown cylinder 5 of the actuating mechanism, which together with an underlying intermediate piece | ke 6 is attached to the upper side of valve body 3.
Den hydrauliske aktiveringsmekanisme omfatter et reservoir 7, f.eks. en pneumatisk-hydraulisk trykak-30 kumulator, der fungerer som kilde for højtryksvæske til aktivering af ventilen 1, og som ved hjælp af en pumpe 8 fødes fra en tank 9. Fra reservoiret 7 fører i en højtryksledning 10 til den ene port af en 3/2 ventil 11, som styrer tilførslen og bortledningen af hy- | 35 draulikvæske til og fra cylinderen 5 gennem en ledning \ 5The hydraulic actuating mechanism comprises a reservoir 7, e.g. a pneumatic-hydraulic pressure accumulator which acts as a source of high pressure fluid for actuation of the valve 1 and which is fed from a tank 9 by means of a pump 8 from the reservoir 7 in a high pressure line 10 to one port of a 3 / 2 valve 11 which controls the supply and discharge of the hy | 35 draulic fluid to and from the cylinder 5 through a conduit \ 5
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12, der forbinder en anden port af ventilen 11 med en port 13 (se også fig. 2-4) i cylinderen 5. Ventilen 11's tredje port er sluttet til tanken 9 gennem en returledning 14.12 connecting another port of valve 11 to port 13 (see also Figures 2-4) of cylinder 5. Valve 11's third port is connected to tank 9 through return line 14.
5 En permanent åben ledning 15 forbinder en anden port 16 i cylinderen 5 med returledningen 14, og en permanent åben grenledning 17 fra højtryksledningen 10 er sluttet til en tredje port 18 i cylinderen 5.5 A permanently open line 15 connects a second port 16 of the cylinder 5 with the return line 14, and a permanently open branch line 17 from the high-pressure line 10 is connected to a third port 18 of the cylinder 5.
Medens reservoiret 7, pumpen 8 og tanken 9 10 normalt vil være fælles for samtlige udstødsventiler i en flercylindret motor, hører der til hver udstødsventil en særskilt styreventil 11, som under påvirkning af udefra tilførte impulser, der kan være af vilkårlig art, såsom mekaniske eller elektriske, omstyres mellem 15 sine to yderstillinger og derved indleder udstødsventilen l's åbning respektive lukning på ønskede tidspunkter af arbejdscyklusen i den tilhørende motorcylinder.While the reservoir 7, pump 8 and tank 9 10 will normally be common to all exhaust valves in a multi-cylinder engine, each exhaust valve has a separate control valve 11 which, under the influence of externally applied impulses which may be of any kind, such as mechanical or electrical, is switched between its two outer positions, thereby opening the exhaust valve 1's opening and closing respectively at desired times of the duty cycle of the associated engine cylinder.
Ved den i fig. 2 mere detaljerede anskueliggjorte udførelsesform omfatter aktiveringsmekanismen et gene-20 relt med 19 betegnet aktiveringsstempel, som fremkalder åbningen af ventilen 1. Stemplet 19 omfatter en øver s te stempeldel 20, som er forskydelig med tæt pasning i en modsvarende øverste del af cylinderen 5, og en nederste stempeldel 21, som har større diameter 25 end delen 20, og som har tilsvarende tæt pasning i en nedre del af cylinderen 5. Et midterafsnit 22 af stemplet 19 har mindre diameter end stempeldelen 20 og afgrænser således sammen med indervæggen af cylinderen 5 et ringformet arbejdskammer 23, hvis volumen 30 ændrer sig under stemplet 19's bevægelser, eftersom de modstående ringarealer af stempeldelene 20 og 21 er ulige store.In the embodiment shown in FIG. In more detailed illustrated embodiment, the actuating mechanism comprises a generic 20 designated actuating piston which induces the opening of valve 1. Piston 19 comprises an upper piston portion 20 which is slidably sealed in a corresponding upper portion of cylinder 5, and a lower piston portion 21 having a larger diameter 25 than the portion 20 and having correspondingly tight fit in a lower portion of the cylinder 5. A central portion 22 of the piston 19 has a smaller diameter than the piston portion 20 and thus defines, together with the inner wall of the cylinder 5, a annular work chamber 23, the volume of which 30 changes during the movement of the piston 19, since the opposing ring areas of the piston parts 20 and 21 are unequally large.
Et yderligere arbejdskammer 24 afgrænses mellem oversiden af stempeldelen 20 og cylinderen 5's top-35 dæksel 25, og i den viste stilling af aktiveringsstenqp-let 19 og af den mod dette stempels underside anliggende ventilspindel 4, som svarer til den i fig. 1 6A further working chamber 24 is delimited between the upper side of piston portion 20 and the top cover 25 of cylinder 5, and in the position shown, of the actuating pin 19 and of the valve spindle 4 adjacent to this piston, which corresponds to that of FIG. 1 6
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viste lukkede stilling af ventilen er de to arbejdskamre 23 og 24 indbyrdes forbundet gennem en akseparallel passage 26, som i cylinderen 5 forbinder en lomme 27 under dækslet 25 med en rundtgående rille 28 i cy-5 lindervæggen. I denne stilling ligger den rundtgående styre- eller afskæringskant 29 ved den øverste ende af stempeldelen 21 et lille stykke over en rundtgående rille 30 i cylindervæggen, hvori porten 13 udmunder.shown in the closed position of the valve, the two working chambers 23 and 24 are interconnected through an axis parallel passage 26 which in the cylinder 5 connects a pocket 27 under the cover 25 with a circumferential groove 28 in the cylinder 5 wall. In this position, the circumferential guide or cut-off edge 29 at the upper end of the piston portion 21 lies a short distance above an circumferential groove 30 in the cylinder wall, in which the gate 13 opens.
10 Porten 16 udmunder på cylinderen 5's inderside i en rundtgående rille 31, hvis overkant i den viste stilling ligger i samme lodrette afstand fra den Øverste rundtgående styre- eller afskæringskant 32 på stempeldelen 20 som afstanden fra denne stempeldels 15 nederste styre- eller afskæringskant 33 til underkanten af rillen 28. Som det vil fremgå af den senere forklaring af mekanismens virkemåde, kan sidstnævnte afstand eventuelt være lidt større eller mindre end den førstnævnte.The port 16 opens on the inside of the cylinder 5 in a circumferential groove 31, the upper edge of which in the shown position is at the same vertical distance from the upper circumferential guide or cut edge 32 of the piston part 20 as the distance from the lower guide or cut edge 33 of this piston 15 the lower edge of the groove 28. As will be seen from the later explanation of the mechanism's operation, the latter distance may be slightly larger or smaller than the former.
20 Fra en central, i bunden lukket kanal 34 i stemp let 19 udgår to sæt tværgående kanaler 35 og 36, som udmunder henholdsvis i overfladen af stempeldelen 21 og lige under stempeldelen 20. Mellem de to sæt tværboringer er der i den centrale kanal 34 indsat en 25 kontraventil 37, som er fjederbelastet til lukning i retning mod kanalerne 35.20 From a central, bottomly closed channel 34 in piston 19, two sets of transverse channels 35 and 36 emerge, which respectively terminate in the surface of the piston portion 21 and just below the piston portion 20. Between the two sets of transverse bores are inserted in the central channel 34 a non-return valve 37 spring-loaded for closing in the direction of the ducts 35.
Et rørformet aktiveringsstempel 38 for lukning af ventilen 1 er fast forbundet med den øverste ende af ventilspindlen 4 gennem en indvendig konisk ring 39 30 og dermed samvirkende koniske segmenter 40. Stemplet 38 omfatter en øverste del 41, der har tæt pasning i cylinderen 5, og en nederste del 42 med mindre diameter og med tæt pasning i en foring 43 i mellemstyk- 7A tubular actuating piston 38 for closing valve 1 is firmly connected to the upper end of valve spindle 4 through an internal tapered ring 39 30 and thus cooperating tapered segments 40. Piston 38 comprises an upper portion 41 having a tight fit in cylinder 5, and a lower portion 42 of smaller diameter and with a tight fit in a liner 43 of intermediate piece 7
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ket 6. Sammen med cylinderen 5 afgrænser stemplet 38 således et ringformet arbejdskammer 44, hvis volumen varierer under ventilen l's bevægelse. En rundt-gående rille 45 i den nederste del af arbejdskammeret 5 44 er i permanent forbindelse med porten 18 gennem en kanal 46, medens en kortere rundtgående rille 47 i bunden af kammeret 44 har forbindelse til en ved sin yderste ende lukket kanal 48 i cylinderen 5. Kanalerne 46 og 48 er indbyrdes forbundet gennem en tvær-10 gående boring, hvori der er indsat en kontraventil 49, som er fjeder belastet til lukning i retning mod kanalen 46.Thus, together with the cylinder 5, the piston 38 defines an annular working chamber 44, the volume of which varies during the movement of the valve 1. A circular groove 45 in the lower part of the working chamber 5 44 is in permanent communication with the port 18 through a channel 46, while a shorter circumferential groove 47 at the bottom of the chamber 44 communicates with a channel 48 closed at its extreme end in the cylinder. 5. The ducts 46 and 48 are interconnected through a transverse bore in which is inserted a check valve 49 which is spring loaded for closing in the direction towards the duct 46.
Den beskrevne aktiveringsmekanisme virker på følgende måde. I den viste stilling af mekanismens kompo-15 nenter virker det høje hydrauliske tryk gennem grenledningen 17 og porten 18 på den lille ringformede underside af stemplet 38's del 41. Den heraf resulterende, opadrettede kraft på ventilen 1 sikrer, sammen med det i motorcylinderen herskende gastryk, ventilens 20 lukkede stilling. Den eksterne styreventil 11 indtager den i fig. 1 viste stilling.The described activation mechanism works as follows. In the shown position of the components of the mechanism, the high hydraulic pressure through the branch line 17 and the port 18 acts on the small annular underside of the piston 38 part 41, the resulting upward force on the valve 1, together with the gas pressure prevailing in the engine cylinder. , the closed position of the valve 20. The external control valve 11 occupies the position shown in FIG. 1.
Ventilen l's åbningsbevægelse indledes ved, at ventilen 11 omstyres, hvorved porten 13 sluttes til det høje hydrauliske tryk i reservoiret 7. Fra porten 25 13 strømmer højtryksvæsken ind i kanalerne 35 og 34, løfter kontraventilen 37 og strømmer videre gennem kanalerne 36 ind i arbejdskammeret 23. Gennem rillen 28 og passagen 26 strømmer højtryksvæsken også op i arbejdskammeret 24. Det høje hydrauliske tryk på-30 virker herved stemplet 19 i nedadgående retning på et totalt areal, som er lig med arealet af stempeldelen 20 plus differensen mellem de ringformede flader af stempeldelene 21 og 20. Når den nedadgående kraft på 8The opening movement of valve 1 is initiated by reversing valve 11, thereby connecting port 13 to the high hydraulic pressure in reservoir 7. From port 25 13, high pressure fluid flows into channels 35 and 34, lifting check valve 37 and flowing through channels 36 into work chamber 23 Through the groove 28 and passage 26, the high pressure fluid also flows into the working chamber 24. The high hydraulic pressure thereby impacts the piston 19 downwards on a total area equal to the area of the piston part 20 plus the difference between the annular surfaces of the piston parts. 21 and 20. When the downward force of 8
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stemplet 19 overstiger den ovenfor omtalte opadrettede kraft på stemplet 38 plus gastrykket i motorcylinderen, begynder stemplet 15 og dermed ventilen i at bevæge sig nedad. Efter en kort indledende vandring pas-5 serer afskæringskanten 29 den øverste kant af rillen 30, hvorved højtryksvæsken kan strømme direkte fra porten 30 ind i arbejdskammeret 23 uden om kontraventilen 37.piston 19 exceeds the above-mentioned upward force on piston 38 plus gas pressure in the engine cylinder, piston 15 and thus the valve start to move downward. After a brief initial migration, the cut-off edge 29 passes through the upper edge of the groove 30, whereby the high-pressure liquid can flow directly from the port 30 into the working chamber 23 outside the check valve 37.
Efter en yderligere vandring af stemplet 19 og 10 ventilen 1 passerer afskæringskanten 32 den øverste kant af rillen 31, hvorved arbejdskammeret 24 sættes i forbindelse med porten 16 og gennem denne med returledningen 15, 14. Samtidig passerer den nederste afskæringskant 33 på stempeldelen 20 underkanten af 15 rillen 28, hvorved forbindelsen mellem de to arbejds-kamre 23 og 24 afspærres. Trykket i arbejdskammeret 24 aflastes herved til det i tanken 9 herskende relativt lave tryk, således at det høje tryk nu kun virker på det ovenfor omtalte lille differensareal af 20 stempeldelene 20 og 21.After a further migration of the piston 19 and 10 the valve 1, the cut-off edge 32 passes the upper edge of the groove 31, whereby the working chamber 24 is connected to the port 16 and through it with the return line 15, 14. At the same time, the lower cut-off edge 33 of the piston part 20 passes through the bottom edge of the 15 the groove 28, thereby blocking the connection between the two working chambers 23 and 24. The pressure in the working chamber 24 is hereby relieved to the relatively low pressure prevailing in the tank 9, so that the high pressure now only works on the small difference area mentioned above of the 20 piston parts 20 and 21.
Under påvirkning af den således reducerede kraft og i kraft af sin under den indledende fase opnåede kinetiske energi fortsætter ventilen 1 sin åbningsbevægelse, hvorunder kammeret 24 efterfyldes fra tan-25 ken 9 gennem porten 16. Bevægelsen standser, når den nederste styre- eller afskæringskant 50 på stempeldelen 41 passerer underkanten af rillen 45 i cylinderen 5. Den i bunden af arbejdskammeret 44 stående væskemængde er nu af spærret, idet kontraventilen 49 30 er lukket, og denne væskemængde virker som en stødpude, der afbremser bevægelsen af ventilen 1. Efter at bevægelsen er standset, bliver ventilen stående, så længe det høje hydrauliktryk gennem porten 13 virker på stemplet 19, dvs. indtil ventilen 11 påny omstilles 35 til den i fig. 1 viste stilling.Under the influence of the thus reduced force and by virtue of its kinetic energy obtained during the initial phase, the valve 1 continues its opening movement, during which the chamber 24 is replenished from the tank 9 through the gate 16. The movement stops when the lower guide or cut-off edge 50 on the piston portion 41, the lower edge of the groove 45 passes in the cylinder 5. The amount of liquid at the bottom of the working chamber 44 is now blocked, the check valve 49 30 being closed, and this amount of liquid acting as a buffer which slows the movement of the valve 1. After the movement is stopped, the valve remains standing as long as the high hydraulic pressure through the port 13 acts on the piston 19, ie. until valve 11 is re-adjusted to that of FIG. 1.
Når dette sker, slutter ventilen 11 porten 13 til det lave hydrauliske tryk i tanken 9, hvorved denWhen this occurs, valve 11 joins port 13 to the low hydraulic pressure in tank 9, thereby closing it
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9 nedadrettede kraft på stemplet 19 aftager tilsvarende.9 downward force on the piston 19 decreases accordingly.
Det høje tryk, som konstant virker i porten 18, åbner nu kontraventilen 49, hvorved der gennem kanalen 48 tilføres højtryksvæske til rillen 47 og dermed til den 5 ringformede flade på undersiden af stempeldelen 41. Herved begynder ventilens opadgående løftebevægelse, og når afskæringskanten 50 igen blotter rillen 45, kan højtryksvæsken fra porten 18 strømme direkte gennem kanalen 46 ind i kammeret 44. Under den opadgående bevæ-10 gelse fortrænges hydraulikvæske fra arbejdskamrene 23 og 24 til tanken 9, først gennem begge porte 16 og 13 og til slut, når afskæringskanten 32 passerer overkanten af rillen 31, alene gennem porten 13. De to arbejdskamre afspærres helt fra returledningen 14, 15 når stemplet 19's afskæringskant 29 passerer overkanten af rillen 30, og den indespærrede væskemængde i de to arbejdskamre virker derefter som stødpude, der afbremser ventilen l's lukkebevægelse og fastlægger den hastighed, hvormed sædefladen på ventiltallerkenen 20 2 lander på det faste sæde i ventilhuset 3.The high pressure which constantly operates in the port 18 now opens the check valve 49, whereby through the channel 48 high pressure liquid is supplied to the groove 47 and thus to the annular surface on the underside of the piston part 41. The upward lifting movement of the valve begins, and when the cutting edge 50 resumes. If the groove 45 blots, the high pressure liquid from the port 18 can flow directly through the channel 46 into the chamber 44. During the upward movement, hydraulic fluid is displaced from the working chambers 23 and 24 to the tank 9, first through both ports 16 and 13 and finally when the cut-off edge 32 passes the upper edge of the groove 31, only through the gate 13. The two working chambers are completely shut off from the return line 14, 15 as the cut-off edge 29 of the piston 19 passes the upper edge of the groove 30, and the confined amount of liquid in the two working chambers then acts as a shock pad which slows down the valve 1's. closing motion and determining the speed at which the seat surface of the valve plate 20 2 lands on the fixed seat in the valve body unseen 3.
Hvis mekanismen dimensioneres således, at kanten 32 først slutter kammeret 24 til porten 16 lidt efter, at kanten 33 har afbrudt forbindelsen fra porten 13 til kammeret, sker der i det korte mellemliggende inter-25 val et gradvis trykfald i kammeret 24, hvorved en brat trykændring ved kammerets tilslutning til tanken 9 undgås. Omvendt vil man ved at vælge de relevante dimensioner således, at kammeret 24 i en kort periode er sluttet til begge porte 13 og 16 sikre sig mod, at 30 der opstår vakuum i kammeret under stemplets nedadgående vandring.If the mechanism is dimensioned such that the edge 32 first connects the chamber 24 to the port 16 slightly after the edge 33 has disconnected from the port 13 to the chamber, in the short intermediate interval a gradual pressure drop occurs in the chamber 24, whereby a pressure change at chamber connection to tank 9 is avoided. Conversely, by selecting the relevant dimensions such that the chamber 24 is connected to both ports 13 and 16 for a short period of time, it is ensured that 30 is created in the chamber during the downward movement of the piston.
I fig. 3 og 4 er de komponenter m.v., der funktionelt svarer til det i fig.2 viste, betegnet med samme henvisningstal forøget med henholdsvis 100 og 200.In FIG. 3 and 4, the components etc. which functionally correspond to the one shown in Fig. 2 are denoted by the same reference numerals increased by 100 and 200 respectively.
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10 I fig. 3 er aktiveringsstemplet 119 for udstødsventilens åbning sammensat af en nedre stempeldel 120, en Øvre stempeldel 121 med mindre diameter og et mellemstykke 122 med endnu mindre diameter. Stempeldelen 5 120 har tæt pasning i cylinderen 105, og dens ringformede overside afgrænser sammen med cylinderen et første arbejdskammer 124. Stempeldelen 121 har radialt spillerum i et andet arbejdskammer 123> men passer tæt i en passage 126, som forbinder kamrene 123 og 124.10 In FIG. 3, the actuating piston 119 for the outlet of the exhaust valve is composed of a lower piston portion 120, an upper piston portion 121 of smaller diameter, and an intermediate piece 122 of even smaller diameter. The piston member 5 120 closely fits into the cylinder 105, and its annular upper side, together with the cylinder, defines a first work chamber 124. The piston member 121 has radial clearance in a second work chamber 123 but fits tightly in a passage 126 connecting the chambers 123 and 124.
10 I stemplets midterdel 122 er der en central kanal 134, hvorfra der udgår tværkanaler 135 og 136, som udmunder henholdsvis i midterdelen 122 og i et overgangsafsnit 151 af stemplet, som har tæt pasning i passagen 126. En kontraventil 137 i kanalen 134 er ^5 fjederbelastet til lukning i retning mod tværkanalerne 135.10 In the central portion 122 of the piston there is a central channel 134 from which is provided cross-channels 135 and 136 which open respectively in the middle portion 122 and in a transition section 151 of the piston which has a tight fit in the passage 126. A check valve 137 in the channel 134 is 5 spring-loaded for closure in the direction of the cross-channels 135.
Når den i fig. 3 ikke viste eksterne styreventil omstilles til at slutte den i kammeret 123 udmundende port 113 til det høje hydrauliske tryk, strømmer hy-20 draulikvæsken fra kammeret 123 igennem passagen 126 og kanalerne 135 ind i kanalen 134, hvorved kon-traventilen 137 åbner, således at væsken fortsætter ind i kammeret 124. Stemplet 119 begynder at bevæge sig nedad og medtager ventilspindlen 104, som lig-25 ger an mod stemplets underside. Efter en kort vandring passerer overkanten 129 af overgangsafsnittet 151 underkanten af passagen 126,'således at væsken nu kan strømme fra porten 113 ind i kammeret 124 uden om kontraventilen 137. På et senere tidspunkt af udstøds-30 ventilens åbningsbevægelse passerer underkanten 133 af stempeldelen 121 den øverste kant af passagen 126, og samtidig eller umiddelbart forinden passerer overkanten 132 af stempeldelen 120 den Øverste kart af en reces 131 i cylindervæggen, hvori returporten 116 35 udmunder.When in FIG. 3, the external control valve (not shown) is adapted to connect the port 113 of the chamber 123 to the high hydraulic pressure, the hydraulic fluid from the chamber 123 flows through the passage 126 and the channels 135 into the channel 134, thereby opening the check valve 137 so that the liquid continues into the chamber 124. The plunger 119 begins to move downwardly and includes the valve stem 104 which abuts the underside of the plunger. After a short passage, the top edge 129 of the transition section 151 passes the bottom edge of the passage 126, so that the liquid can now flow from the port 113 into the chamber 124 outside the check valve 137. At a later point of the ejection valve opening movement, the bottom edge 133 of the piston portion 121 passes. the upper edge of the passage 126, and simultaneously or immediately before, the upper edge 132 of the piston portion 120 passes the upper cart of a recess 131 in the cylinder wall, in which the return port 116 35 opens.
1111
DK 154165 BDK 154165 B
De to kamre 123 09 124 er nu a£spsrret fra hinanden, og trykket i kammeret 124 aflastes gennem porten 116. Medens det hydrauliske tryk i den indledende del af åbningsbevægelsen virkede på et areal lig med 5 arealet af en cirkel med stempeldelen 120’s diameter, virker trykket nu kun på det væsentlig mindre areal af stempeldélen 121's overside. Den reducerede kraftpåvirkning på udstødsventilen er imidlertid tilstrækkelig til i forbindelse med ventilens kinetiske energi at sik-10 re den fortsatte åbningsbevægelse mod det tilsvarende reducerede gastryk i motorcylinderen og den modsat rettede kraft på aktiveringsstemplet 138 for ventillukningen.The two chambers 123 09 124 are now spaced apart and the pressure in the chamber 124 is relieved through the port 116. While the hydraulic pressure in the initial portion of the opening movement acted on an area equal to the area of a circle of piston portion 120 diameter, the pressure now acts only on the substantially smaller area of the piston portion 121 upper side. However, the reduced force effect on the exhaust valve is sufficient to ensure, in conjunction with the kinetic energy of the valve, the continued opening movement against the correspondingly reduced gas pressure in the engine cylinder and the opposite directed force on the actuating piston 138 for the valve closure.
Stemplet 138 og de tilhørende dele af cylinderen 15 105 er identiske med det i fig.2 viste, hvilket bl.a. in debærer , at opbremsningen af udstødsventilens åbning foregår på samme måde,når den underste afskæringskant 150 på stempeldelen 141 passerer underkanten af rillen 145, hvortil kanalen 146 fra tilgangsporten 118 er slut-20 tet. Også udstødsventilens lukningsbevægelse foregår på samme måde, når porten 113 gennem den eksterne styreventil sluttes til det lave hydrauliske tryk i systemet. Lukningsbevægelsen afbremses til slut ved, at afskæringskanten 129 passerer underkanten af passaqen 126, 25 hvorved den i kammeret 124 stående væskemængde afspærre s og virker som stødpude, idet kontraventilen 137 holdes lukket af sin fjederbelastning mod det lave hydrauliske tryk i kammeret 123 og passagen 126.The piston 138 and the associated parts of the cylinder 15 105 are identical to the one shown in FIG. in that the opening of the outlet valve opening is similarly effected when the lower cut-off edge 150 of the piston portion 141 passes through the bottom edge of the groove 145, to which the channel 146 from the inlet port 118 is closed. Also, the closing movement of the exhaust valve takes place in the same way when the port 113 through the external control valve is connected to the low hydraulic pressure in the system. Finally, the closing movement is slowed down by the cut-off edge 129 passing the lower edge of the passage 126, 25 whereby the amount of liquid contained in the chamber 124 seals and acts as a bump, keeping the check valve 137 closed by its spring load against the low hydraulic pressure in the chamber 123 and the passage 126.
Ved udførelsesformen i fig. 4 er aktiveringsmeka-30 nismens cylinder 205 med arbejdskamrene 223 og 224, forbindelsespassagen 2.26 samt portene 213 og 216 identiske med det i fig. 3 viste. Aktiveringsstemplet for udstødsventilens åbning afviger derimod ved, at det består af to dele 220 og 252, som har en lille ind-35 byrdes forskydelighed i aksialretningen. StempeldelenIn the embodiment of FIG. 4, the cylinder 205 of the actuating mechanism with the working chambers 223 and 224, the connecting passage 2.26 and the ports 213 and 216 are identical to that of FIG. 3. By contrast, the actuating piston for the outlet of the exhaust valve differs in that it consists of two parts 220 and 252 which have a small intersection in the axial direction. The piston part
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12 252 har en øvre del 221 og en midterdel 222, som svarer fuldstændig til delene 121 og 122. Dens nedre afsnit 253 har, ligesom afsnittet 151 af stemplet 119, tæt pasning i passagen 226, og det er endvidere 5 styret med tæt pasning i en central boring i den nedre stempeldel 220 og påvirket i retning opefter af en fjeder 254. Stempeldelen 252's relative opadgående bevægelse kan være begrænset af et ikke vist stop.12 252 has an upper portion 221 and a middle portion 222 which corresponds completely to portions 121 and 122. Its lower portion 253, like section 151 of piston 119, has a tight fit in the passage 226, and it is further controlled with tight fit in a central bore in the lower piston portion 220 and influenced upwardly by a spring 254. The relative upward movement of the piston portion 252 may be limited by a stop not shown.
Funktionen af den i fig. 4 viste aktiveringsmeka-10 nisme er i alt væsentligt den samme som for den i fig. 3 viste. Forskellen er i det væsentlige den, at den forskydelige stempeldel 252 har overtaget funktionen af kontraventilen 137, idet tilslutningen af det høje hydrauliske tryk til porten 213 og kammeret 223 først be-15 væger stempeldelen 252 nedad under sammentrykning af fjederen 254, medens stempeldelen 220 bliver stående. Når overkanten 229 af stempelafsnittet 253 passerer overkanten af kammeret 224, har højtryksvæsken adgang til dette kammer gennem passagen 226, og den re-20 sterende del af udstødsventilens åbningsbevægelse foregår herefter på samme måde som beskrevet i forbindelse med fig. 3. Dette gælder også afbremsningen af udstødsventilen ved åbningsbevægelsens afslutning og den følgende fastholdelse af ventilen i åben stilling, idet 25 stemplet 238 og de tilhørende komponenter er identiske med det i fig. 2 og 3 viste.The function of the device shown in FIG. 4, the activation mechanism shown in FIG. 4 is substantially the same as that of FIG. 3. The difference is essentially that the displaceable piston part 252 has taken over the function of the check valve 137, the connection of the high hydraulic pressure to the port 213 and the chamber 223 first moving the piston part 252 downwardly during compression of the spring 254, while the piston part 220 becomes standing up. As the upper edge 229 of the piston section 253 passes the upper edge of the chamber 224, the high pressure fluid has access to this chamber through the passage 226, and the remaining portion of the opening movement of the exhaust valve then proceeds in the same manner as described in connection with FIG. 3. This also applies to the braking of the exhaust valve at the end of the opening movement and the subsequent holding of the valve in the open position, the piston 238 and its components being identical to that of FIG. 2 and 3.
Når udstødsventilens lukkebevægelse indledes ved tilslutning af porten 213 til det lave tryk i det hydrauliske system, hvorved trykket i kammeret 223 af-30 lastes, bevæger den forskydelige stempeldel 252 sig under indvirkning af fjederen 254 igen opad til sin i fig. 4 viste relative topstilling, og derefter bevæger hele aktiveringsstemplet 220, 252 sig opad under påvirkning af det høje tryk i kammeret 244, suppleret 35 med gastrykket i motorcy linderen. Af bremsningen af lukkebevægelsens slutfase indtrasder, når afskæringskanten 229 passerer underkanten af passagen 226 og derved afspærrer den i kammeret 224 stående væskemængde.When the closing movement of the exhaust valve is initiated by connecting the port 213 to the low pressure of the hydraulic system, whereby the pressure in the chamber 223 is relieved, the displaceable piston part 252, again under the action of the spring 254, moves upwards to its position in FIG. 4, and then the entire actuator piston 220, 252 moves upward under the high pressure of chamber 244, supplemented by gas pressure in the motor cylinder. The braking of the closing phase of the closing movement occurs as the cut-off edge 229 passes the lower edge of the passage 226, thereby blocking the amount of liquid contained in the chamber 224.
Claims (7)
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK022483A DK154165C (en) | 1983-01-20 | 1983-01-20 | HYDRAULIC ACTIVATION MECHANISM FOR A GAS EXCHANGE VALVE IN A COMBUSTION ENGINE |
| IN1580/CAL/83A IN159382B (en) | 1983-01-20 | 1983-12-23 | |
| KR1019830006236A KR910000670B1 (en) | 1983-01-20 | 1983-12-28 | Hydraulic actuating mechanism for a gas exchange valve of an internal combustion engine |
| JP59006235A JPS59192813A (en) | 1983-01-20 | 1984-01-17 | Hydraulic operation mechanism for gas exchange valve of internal combustion engine |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK22483 | 1983-01-20 | ||
| DK022483A DK154165C (en) | 1983-01-20 | 1983-01-20 | HYDRAULIC ACTIVATION MECHANISM FOR A GAS EXCHANGE VALVE IN A COMBUSTION ENGINE |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK22483D0 DK22483D0 (en) | 1983-01-20 |
| DK22483A DK22483A (en) | 1984-07-21 |
| DK154165B true DK154165B (en) | 1988-10-17 |
| DK154165C DK154165C (en) | 1989-04-03 |
Family
ID=8091128
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK022483A DK154165C (en) | 1983-01-20 | 1983-01-20 | HYDRAULIC ACTIVATION MECHANISM FOR A GAS EXCHANGE VALVE IN A COMBUSTION ENGINE |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPS59192813A (en) |
| KR (1) | KR910000670B1 (en) |
| DK (1) | DK154165C (en) |
| IN (1) | IN159382B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998057048A1 (en) * | 1997-05-29 | 1998-12-17 | Man B & W Diesel A/S | A hydraulically actuated exhaust valve for an internal combustion engine |
| WO2012166035A1 (en) * | 2011-06-03 | 2012-12-06 | Alternative Solar Energy Engine Ab | Pressure pulse generator |
| WO2013058704A1 (en) * | 2011-10-21 | 2013-04-25 | Cargine Engineering Ab | Actuator |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0661696U (en) * | 1993-02-16 | 1994-08-30 | 川崎重工業株式会社 | Ship control device |
| JP2011196278A (en) * | 2010-03-19 | 2011-10-06 | Honda Motor Co Ltd | Variable valve gear of internal combustion engine |
-
1983
- 1983-01-20 DK DK022483A patent/DK154165C/en not_active IP Right Cessation
- 1983-12-23 IN IN1580/CAL/83A patent/IN159382B/en unknown
- 1983-12-28 KR KR1019830006236A patent/KR910000670B1/en not_active IP Right Cessation
-
1984
- 1984-01-17 JP JP59006235A patent/JPS59192813A/en active Granted
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998057048A1 (en) * | 1997-05-29 | 1998-12-17 | Man B & W Diesel A/S | A hydraulically actuated exhaust valve for an internal combustion engine |
| WO2012166035A1 (en) * | 2011-06-03 | 2012-12-06 | Alternative Solar Energy Engine Ab | Pressure pulse generator |
| US8973541B2 (en) | 2011-06-03 | 2015-03-10 | Perfecter Ab | Pressure pulse generator |
| WO2013058704A1 (en) * | 2011-10-21 | 2013-04-25 | Cargine Engineering Ab | Actuator |
| SE544218C2 (en) * | 2011-10-21 | 2022-03-08 | Freevalve Ab | Pressure fluid controlled actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| KR840007266A (en) | 1984-12-06 |
| KR910000670B1 (en) | 1991-01-31 |
| JPH02524B2 (en) | 1990-01-08 |
| DK154165C (en) | 1989-04-03 |
| DK22483D0 (en) | 1983-01-20 |
| IN159382B (en) | 1987-05-09 |
| DK22483A (en) | 1984-07-21 |
| JPS59192813A (en) | 1984-11-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUP | Patent expired |