SE514527C2 - Method and apparatus for controlling the transmission of EGR gases in a turbocharged internal combustion engine and such diesel engine - Google Patents

Method and apparatus for controlling the transmission of EGR gases in a turbocharged internal combustion engine and such diesel engine

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Publication number
SE514527C2
SE514527C2 SE9904823A SE9904823A SE514527C2 SE 514527 C2 SE514527 C2 SE 514527C2 SE 9904823 A SE9904823 A SE 9904823A SE 9904823 A SE9904823 A SE 9904823A SE 514527 C2 SE514527 C2 SE 514527C2
Authority
SE
Sweden
Prior art keywords
egr
valve
gases
drain valve
control
Prior art date
Application number
SE9904823A
Other languages
Swedish (sv)
Other versions
SE9904823D0 (en
SE9904823L (en
Inventor
Tom Loennqvist
Original Assignee
Scania Cv Ab
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Scania Cv Ab filed Critical Scania Cv Ab
Priority to SE9904823A priority Critical patent/SE9904823L/en
Publication of SE9904823D0 publication Critical patent/SE9904823D0/en
Priority to EP00986168A priority patent/EP1247019A1/en
Priority to PCT/SE2000/002622 priority patent/WO2001050010A1/en
Publication of SE514527C2 publication Critical patent/SE514527C2/en
Publication of SE9904823L publication Critical patent/SE9904823L/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/34—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with compressors, turbines or the like in the recirculation passage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional compressor
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • 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
    • Y02T10/12—Improving ICE efficiencies

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

An arrangement and a method for control of transfer of EGR gases in a turbocharged combustion engine (1), whereby exhaust gases are drawn off in a regulated manner via a draw-off valve (7) to drive an EGR pump (6) for creating an EGR transfer flow which is regulated by an EGR valve (10). Both the draw-off valve (7) and the EGR valve (10) are regulated by means of a single control valve (14), and the draw-off valve (7) responds to a control fluid pressure which is higher than the control fluid pressure to which the EGR valve (10) responds, causing the EGR valve (10) to open before the draw-off valve (7). The invention also relates to a diesel engine equiped with such an arrangement.

Description

lynrl' 514 527 befinna sig så nära inloppsledningen som möjligt för att ett snabbt reglersystern ska erhållas så att oönskad tröghet i systemet undviks. lynrl '514 527 be as close to the inlet line as possible in order to obtain a fast control system so that unwanted inertia in the system is avoided.

Regleringen av dessa båda ventiler sker med hjälp av en till varje ventil tillhörande s. k. styrventil, vilka typiskt utnyttjar fordonets (åtminstone i fall av en tyngre lastbil eller buss) tanktryck, vilket normalt är runt 7 - 9 bar. Detta tryck styrs över de två styrventilema och regleras genom motoms styrsystem för matning av de respektive ventilema med ett styrfluidtryck, vid vilket de regleras för uppnående av EGR- överföringsstyming.The regulation of these two valves takes place by means of a so-called control valve associated with each valve, which typically utilizes the tank pressure of the vehicle (at least in the case of a heavier truck or bus), which is normally around 7-9 bar. This pressure is controlled over the two control valves and is regulated by the motor control system for feeding the respective valves with a control expression, at which they are regulated to achieve EGR transmission control.

Styrventilerna är således styrda i motsvarighet till elektriska signaler och styrsystemet måste noggrant avpassas, bl. a. så att EGR-ventilen säkert öppnar före avtappningsventilen. Skälen för detta är säkerhetsmässiga, eftersom annars skador kan uppkomma på EGR-pumpen.The control valves are thus controlled in accordance with electrical signals and the control system must be carefully adjusted, e.g. a. so that the EGR valve safely opens before the drain valve. The reasons for this are safety, as otherwise damage can occur to the EGR pump.

Genom ytterligare reglering av de olika ventilerna kan olika EGR-mängder överföras beroende på motoms drifttillstånd. Principen för det kända slaget av EGR-styrning är godtagbart fungerande men reglerrnässigt komplicerad och en resulterande anordning relativt kostsam.By further regulating the different valves, different EGR amounts can be transferred depending on the operating condition of the engine. The principle of the known type of EGR control is acceptably functional but regulatorically complicated and a resulting device relatively expensive.

UPPFINNINGENS ÄNDAMÄL OCH VIKTIGASTE KÄNNETECKEN Det är ett ändamål med uppfinningen att tillhandahålla en utveckling av det tidigare kända systemet och att anvisa en lösning, med vilken ovannämnda problem undanröjs eller åtminstone radikalt rnildras.OBJECTS AND MOST IMPORTANT CHARACTERISTICS OF THE INVENTION It is an object of the invention to provide a development of the prior art system and to provide a solution with which the above-mentioned problems are eliminated or at least radically eliminated.

Detta ändamål uppnås vid ett förfarande och en anordning av inledningsvis nämnt slag genom särdragen i kännetecknande delen av patentkravet 1 respektive 5.This object is achieved in a method and a device of the kind mentioned in the introduction by the features in the characterizing part of claim 1 and 5, respectively.

Härigenom uppnås att båda ventilema kan styras med en och samma styrventil, vilket medför ett flertal fördelar med systemet, nämligen enklare reglering och enklare programmering av styrsystem, färre komponenter och sammantaget ett billigare och likväl tillförlitligt system.In this way it is achieved that both valves can be controlled with one and the same control valve, which entails a number of advantages with the system, namely simpler regulation and simpler programming of control systems, fewer components and overall a cheaper and yet reliable system.

D14 bZ/ Lill-I' Intervallerna, inom vilka ventilema öppnar, kan vara separerade eller överlappa så länge det tillförsälcras att EGR-ventilen öppnar före avtappningsventilen. Båda ventilema kan vara av samma slag och är företrädesvis tjäderbelastade tryckstyrda ventiler av i och för sig förut känt slag, varvid fjädrarna är avpassade så att ventilema avstärns till respektive tiyckområde. Exempel på sådana ventiler är vridbara spjällventiler eller axiellt förskjutbara tallriksventiler. Styrventilen styrs lärnpligen elektroniskt av styrsystemet och detta kan göras på ett mycket enkelt sätt för likväl erhållande av korrekt styrning av EGR- ventilen såväl som av avtappningsventilen.D14 bZ / Lill-I 'The intervals within which the valves open may be separated or overlap as long as it is provided that the EGR valve opens before the drain valve. Both valves can be of the same type and are preferably spring-loaded pressure-controlled valves of a type known per se, the springs being adapted so that the valves are spaced to the respective pressure range. Examples of such valves are rotary damper valves or axially displaceable poppet valves. The control valve is electronically controlled electronically by the control system and this can be done in a very simple manner for nevertheless obtaining correct control of the EGR valve as well as of the drain valve.

Principen för uppfinningen är tillämplig vid olika typer av motorer där EGR-överföring önskas, men är särskilt fördelaktig vid motorer av ovannämnt slag, dvs vid dieselmotorer med två skilda avgassarnlare för betjäning av var sin grupp av cylindrar. Härvid avtappas avgaser från en första avgassamlare genom avtappningsventilen för drivning av EGR- pumpen under det att avgaser från den andra avgassamlaren komprimeras i nämnda EGR- pump och således utgör EGR-gaser.The principle of the invention is applicable to different types of engines where EGR transmission is desired, but is particularly advantageous in engines of the above kind, ie in diesel engines with two different exhaust gases for operating each group of cylinders. In this case, exhaust gases from a first exhaust gas collector are drained through the drain valve for driving the EGR pump, while exhaust gases from the second exhaust gas collector are compressed in said EGR pump and thus constitute EGR gases.

Det är lämpligt att avtappningsventilen styrs med ett tryck av ca 2 - 6 bar för en konventionell dieselmotorer vid ett tungt fordon, varvid föredrages ett styrtryck av ca 3 - 5 bar. EGR-ventilen å sin sida styrs lämpligen under samma förutsättningar med ett tryck av ca 1 - 3 bar och företrädesvis med ett tryck av ca 1,5 - 2,5 bar.It is suitable that the drain valve is controlled with a pressure of about 2 - 6 bar for a conventional diesel engine in a heavy vehicle, whereby a control pressure of about 3 - 5 bar is preferred. The EGR valve, on the other hand, is suitably controlled under the same conditions with a pressure of about 1 - 3 bar and preferably with a pressure of about 1.5 - 2.5 bar.

KORTFATTAD BESKRIVNING AV RITNINGARNA Uppfinningen ska nu närmare förklaras mot bakgrund av ett utföringsexempel och med ledning av ritningarna, på vilka ñg 1 schematiskt visar en anordning för EGR-överföring enligt uppfinningen vid en antydd dieselmotor.BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be explained in more detail in the light of an exemplary embodiment and with reference to the drawings, in which gg 1 schematically shows a device for EGR transmission according to the invention with a indicated diesel engine.

BESKRIVNING AV UTFÖRINGSFORIVIER Ifig 1 visas en anordning enligt uppfinningen i samband med en schematiskt antydd sexcylindrig, turboöverladdad dieselmotor 1 avsedd som drivmotor i ett tyngre fordon but-l' 514 527 såsom en lastbil eller en buss. Från motorn 1 utgår avgaskanaler till en första avgassarnlare 2a respektive till en andra avgassainlare 2b. Dessa är vidareledda på konventionellt sätt till och för drivning av en turboöverladdare 3, vilket komprimerar friskluft från atmosfären och vidareleder denna via en laddluftkylar 4 till motorns 1 inloppssida via kanalerna 12 och 13.DESCRIPTION OF EMBODIMENT FORIVIVES Fig. 1 shows a device according to the invention in connection with a schematically indicated six-cylinder, turbocharged diesel engine 1 intended as a drive engine in a heavier vehicle but such as a truck or a bus. Exhaust ducts from the engine 1 to a first exhaust collector 2a and to a second exhaust collector 2b, respectively. These are diverted in a conventional manner to drive a turbocharger 3, which compresses fresh air from the atmosphere and diverts it via a charge air cooler 4 to the inlet side of the engine 1 via the ducts 12 and 13.

En EGR-pump är betecknad med 6, och är utformad på samma sätt som en turboöverladdare. Den innefattar en turbin som drivs med hjälp av avgaser avtappade från den första avgassamlaren 2a och är ledda till turbinen via en ledning innefattande en avtappningsventil 7. Till EGR-pumpens kompressor leds EGR-gaser, vilket utgöres av avgaser som är avtappade från motoms andra avgassamlare 2b, via en kanal 8 i vilken även ingår en EGR-kylare 9 för kylning av de återledda avgasema. De komprimerade avgasema leds från EGR-pumpens 6 kompressor via en EGR-ventil 10 till motoms inloppsluftkanal vid en anslutning 11. EGR-ventilen 10 och avtappningsventilen 7 styrs i motsvarighet till ett fluidtryck i de med streckade linjer antydda ledningarna 15, 16 från en styrventil 14, vilken är förbunden med en tryckkälla. I detta exempel utgöres tryckkällan av en tryckluftsbehållare 18 ingående i fordonets ordinarie bromssystem.An EGR pump is denoted by 6, and is designed in the same way as a turbocharger. It comprises a turbine which is driven by means of exhaust gases drained from the first exhaust gas collector 2a and is led to the turbine via a line comprising a drain valve 7. EGR gases are led to the EGR pump compressor, which consists of exhaust gases drained from the engine's second exhaust gas collector 2b, via a duct 8 which also includes an EGR cooler 9 for cooling the returned exhaust gases. The compressed exhaust gases are led from the compressor of the EGR pump 6 via an EGR valve 10 to the engine inlet air duct at a connection 11. The EGR valve 10 and the drain valve 7 are controlled corresponding to a fluid pressure in the lines 15, 16 indicated by dashed lines from a control valve 14, which is connected to a pressure source. In this example, the source of pressure is a compressed air container 18 included in the vehicle's regular braking system.

Styrventil 14 är elektriskt reglerad och styrs i sin tur av motoms styrsystem, antytt med 17. Regleringen av styrventilen 14 är anordnad så att ett styrfluidtryck i ledningama 15 och 16 i ett lägre tryckreglerområde på som exempel 1 - 2,5 bar föranleder öppning av EGR-ventilen 10, under det att ett styrfluidtryck i ett högre område på som exempel 3 - 5 bar föranleder bibehållet öppen ventil 10 samt även öppnad avtappningsventil 7.Control valve 14 is electrically regulated and is in turn controlled by the motor control system, indicated by 17. The control of the control valve 14 is arranged so that a control expression in the lines 15 and 16 in a lower pressure control range of as example 1 - 2.5 bar causes opening of EGR valve 10, while a control expression in a higher range of, for example, 3 - 5 bar causes the open valve 10 to be maintained as well as the opened drain valve 7.

Regleringen är således anordnad så att avtappningsventilen (7) svarar på (öppnar vid) ett styrfluidtryck, som är högre än det styrfluidtryck som EGR-ventilen (10) svarar på, medförande att EGR-ventilen (10) öppnar före avtappningsventilen (7).The control is thus arranged so that the drain valve (7) responds to (opens at) a control fl expression, which is higher than the control fl expression to which the EGR valve (10) responds, causing the EGR valve (10) to open before the drain valve (7).

En styrsekvens kan vara enligt följ ande: med 5 bars styrfluidtrycki ledningarna 15, 16 hålles både EGR-ventilen 10 som avtappningsventilen 7 öppna till 100%. I drift medför detta att i EGR-pumpens turbindel avtappade avgaser tillåts expandera, under det att i EGR-pumpens kompressorsteg EGR- gaser komprimeras för vidare transport till motoms inloppsledning. I detta driftfall kommer maximal EGR-mängd att recirkuleras.A control sequence can be as follows: with 5 bar control fl express the lines 15, 16 both the EGR valve 10 and the drain valve 7 are kept open to 100%. In operation, this means that exhaust gases drained in the turbine part of the EGR pump are allowed to expand, while in the compressor stage of the EGR pump EGR gases are compressed for further transport to the engine inlet line. In this operating case, the maximum EGR amount will be recycled.

Lnpl' 514 527 Vid minskning av styrfluidtrycket till t. ex. 4 bar böljar avtappningsventilen 7 att stänga, vilket minskar expansionen av avtappade avgaser från avgassamlaren 2a över EGR- pumpens 6 turbin. EGR-ventilen 10 är fortfarande öppen till 100%. Denna minskade energitillförsel till EGR-pumpen 6 medför en markant reducering av till motorn tillförd EGR-mängd.Lnpl '514 527 When reducing the control expression to e.g. 4 bar, the drain valve 7 waves to close, which reduces the expansion of drained exhaust gases from the exhaust gas collector 2a over the turbine of the EGR pump 6. The EGR valve 10 is still 100% open. This reduced energy supply to the EGR pump 6 results in a marked reduction in the amount of EGR supplied to the engine.

Vid en minskning av styrfluidtrycket under 2,5 bar är avtappningsventilen 7 helt stängd, och således tillförs inga avgaser pumpens 6 turbin och således utförs inget arbete i EGR- pumpens turbin. Vid de ögonblick då trycket i avgassamlaren är högre än trycket i inloppsröret kommer emellertid en viss del av EGR-gasema av sig själva att transporteras till motoms inloppsrör, vilket i praktiken innebär skapandet av ett s. k. short route system.When the control expression is reduced below 2.5 bar, the drain valve 7 is completely closed, and thus no exhaust gases are supplied to the turbine of the pump 6 and thus no work is performed in the turbine of the EGR pump. At the moments when the pressure in the exhaust gas collector is higher than the pressure in the inlet pipe, however, a certain part of the EGR gases will by themselves be transported to the engine inlet pipe, which in practice means the creation of a so-called short route system.

Med fortsatt reglering av EGR-ventilen 10 kan EGR-flödet styras från 0% upp till vad som är maximalt möjligt med detta aktuella short route system.With continued control of the EGR valve 10, the EGR flow can be controlled from 0% up to what is maximum possible with this current short route system.

Sarnrnantaget medför uppfinningen, med utnyttjande av alla ovan indikerade styrmöjligheter en möjlighet till anpassning av EGR-överföringen inom ett stort reglerområde med avseende på överförd EGR-mängd. genom kan EGR-överföringen anpassas och optimeras till en lång rad olika driftfall.The invention entails, with the utilization of all the control possibilities indicated above, an opportunity for adapting the EGR transmission within a large control area with respect to the amount of EGR transmitted. through, the EGR transmission can be adapted and optimized for a wide range of different operating cases.

Det ska noteras att regleringen av avtappningsventilen 7 respektive EGR-ventilen 10 kan göras grovt i det enklaste fallet, varvid i princip respektive ventil antingen är helt stängd eller helt öppen. Från detta extremläge kan mer sofistikerade stymingar insättas, varvid som svar på avkända driftparametrar såsom varvtal, bränsleförbrukning, uttaget moment, fordonshastighet mm. ventilemas öppningsgrad kan styras känsligt för att emå en möjligast optimerad EGR-recirkulering.It should be noted that the regulation of the drain valve 7 and the EGR valve 10, respectively, can be done roughly in the simplest case, whereby in principle the respective valve is either completely closed or completely open. From this extreme position, more sophisticated controls can be inserted, whereby in response to sensed operating parameters such as speed, fuel consumption, torque taken out, vehicle speed etc. the degree of opening of the valves can be sensitively controlled to ensure the most optimized EGR recirculation possible.

Claims (9)

10 15 20 25 30 n,,»;.1' 514 527 PATENTKRAV10 15 20 25 30 n ,, »;. 1 '514 527 PATENTKRAV 1. Förfarande för styrning av överföring av EGR-gaser i en turboöverladdad förbränningsmotor (1), varvid genom en avtappningsventil (7) avgaser reglerat avtappas för drivning av en EGR-pump (6), vilken komprimerar EGR-gaser till ett EGR- överföringsflöde, varvid EGR-överföringsflödet mellan pumpen (6) och en inloppsledning (13) till motorn (1) regleras genom en EGR-ventil (10), och varvid regleringen av ventilema (7,lO) sker genom styrfluidtillförsel till de respektive ventilema (7,lO), kännetecknat av att både avtappningsventilen (7) och EGR-ventilen (10) regleras med hjälp av en och samma styrventil (14), varvid avtappningsventilen (7) svarar på ett styrfluidtryck, som är högre än det styrfluidtryck som EGR-ventilen (10) svarar på, medförande att EGR-ventilen (10) öppnar före avtappningsventilen (7).A method for controlling the transmission of EGR gases in a turbocharged internal combustion engine (1), wherein through a drain valve (7) exhaust gases are regulated in a controlled manner to drive an EGR pump (6), which compresses EGR gases to the fate of an EGR transmission , wherein the EGR transfer flow between the pump (6) and an inlet line (13) to the motor (1) is regulated by an EGR valve (10), and wherein the regulation of the valves (7, 10) takes place by control supply to the respective valves (7). , 10), characterized in that both the drain valve (7) and the EGR valve (10) are regulated by means of one and the same control valve (14), the drain valve (7) responding to a control expression which is higher than the control expression expressed by the EGR valve. the valve (10) responds, causing the EGR valve (10) to open before the drain valve (7). 2. Förfarande enligt krav l, varvid motorn (1) är av det slag, som uppvisar två skilda avgassamlare (2a,2b) för betjäning av varsin grupp av cylindrar, kännetecknat av att avgaser från den ena avgassamlaren (2a) avtappas genom avtappningsventilen (7) och utnyttjas för drivning av EGR-pumpen, och att avgaser från den andra avgassamlaren ( 10) avtappas för att utgöra EGR-gaser att återledas till motorns inlopp.Method according to claim 1, wherein the engine (1) is of the type having two different exhaust gas collectors (2a, 2b) for operating each group of cylinders, characterized in that exhaust gases from one exhaust gas collector (2a) are drained through the drain valve ( 7) and is used to drive the EGR pump, and that exhaust gases from the second exhaust gas collector (10) are drained to constitute EGR gases to be returned to the engine inlet. 3. Förfarande enligt krav 1 eller 2, kännetecknat av att avtappningsventilen (7) styrs att öppna vid ett styrfluidtryck av c:a 2 - 6 bar och mer föredraget c:a 3 - 5 bar.Method according to claim 1 or 2, characterized in that the drain valve (7) is controlled to open at a control expression of about 2 - 6 bar and more preferably about 3 - 5 bar. 4. Förfarande enligt krav 1, 2 eller 3, kännetecknat av att EGR-ventilen (10) styrs att öppna vid ett styrfluidtryck av c:a 1 - 3 bar och mer föredraget c:a 1,5 - 2,5 bar.Method according to claim 1, 2 or 3, characterized in that the EGR valve (10) is controlled to open at a control expression of about 1 - 3 bar and more preferably about 1.5 - 2.5 bar. 5. Anordning för styrning av överföring av EGR-gaser i en turboöverladdad förbränningsmotor (1), inkluderande en avtappningsventil (7) för reglering av avtappning av avgaser för drivning av en EGR-pump (6), vilken är inrättad att komprimera EGR- gaser till ett EGR-överföringsflöde, varvid en EGR-ventil (10) är inrättad för reglering avDevice for controlling the transmission of EGR gases in a turbocharged internal combustion engine (1), including a drain valve (7) for regulating the discharge of exhaust gases for driving an EGR pump (6), which is arranged to compress EGR gases to the fate of an EGR transmission fl, an EGR valve (10) being provided for regulating 6. EGR-överföringsflödet mellan pumpen (6) och en inloppsledning (13) till motom (1), och varvid organ är anordnade för regleringen av ventilema genom styrfluidtillförsel till de respektive ventilema, kännetecknad av att en enda styrventil (14) är anordnad för reglering av både avtappningsventilen (7) och EGR-ventilen (10), varvid q,.,¿.v' 514 527 7 avtappningsventilen (7) är anordnad att svara på ett styrfluidtryck, som är högre än det styrfluidtryck som EGR-ventilen (10) är anordnad att svara på, medfórande att EGR- ventilen (10) öppnar före avtappningsventilen (7). i 5 6. Anordning enligt krav 5, varvid motorn (1) är av det slag, som uppvisar två skilda avgassamlare (2a,2b) för betjäning av varsin grupp av cylindrar, kännetecknad av att en kanal är anordnad för avtappning av avgaser från den ena avgassarnlaren (2a) genom avtappningsventilen (7) till EGR-pumpen (6) för drivning av densamma, och att en andra kanal är anordnad för avtappning av avgaser från den andra avgassarnlaren (2b) vilka 10 avgaser är inrättade att utgöra EGR-gaser att återledas till motorns inlopp.The EGR transfer fl between the pump (6) and an inlet line (13) to the motor (1), and wherein means are provided for regulating the valves by control supply to the respective valves, characterized in that a single control valve (14) is provided for regulating both the drain valve (7) and the EGR valve (10), wherein the drain valve (7) is arranged to respond to a control expression which is higher than the control expression of the EGR valve (10). 10) is arranged to respond, causing the EGR valve (10) to open before the drain valve (7). Device according to claim 5, wherein the engine (1) is of the type having two different exhaust gas collectors (2a, 2b) for operating each group of cylinders, characterized in that a duct is arranged for draining exhaust gases from the one exhaust manifold (2a) through the drain valve (7) to the EGR pump (6) for driving the same, and that a second channel is arranged for draining exhaust gases from the second exhaust manifold (2b) which exhaust gases are arranged to constitute EGR gases to be returned to the engine inlet. 7. Anordning enligt krav 5 eller 6, kännetecknad av att avtappningsventilen (7) är anordnad att öppna vid ett styrtluidtryck av cza 2 - 6 bar och mest föredraget c:a 3 - 5 bar. 15Device according to claim 5 or 6, characterized in that the drain valve (7) is arranged to open at a control sound pressure of about 2 - 6 bar and most preferably about 3 - 5 bar. 15 8. Anordning enligt krav 5, 6 eller 7, kännetecknad av att EGR-ventilen (10) är anordnad att öppna vid ett styrfluidtryck av cza 1 - 3 bar och mest föredraget cza 1,5 - 2,5 bar. 20Device according to Claim 5, 6 or 7, characterized in that the EGR valve (10) is arranged to open at a control expression of approximately 1 - 3 bar and most preferably approximately 1.5 - 2.5 bar. 20 9. Dieselmotor inkluderande en anordning enligt något av kraven 5 - 8.Diesel engine including a device according to any one of claims 5 - 8.
SE9904823A 1999-12-29 1999-12-29 Method and apparatus for controlling the transmission of EGR gases in a turbocharged internal combustion engine and such diesel engine SE9904823L (en)

Priority Applications (3)

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SE9904823A SE9904823L (en) 1999-12-29 1999-12-29 Method and apparatus for controlling the transmission of EGR gases in a turbocharged internal combustion engine and such diesel engine
EP00986168A EP1247019A1 (en) 1999-12-29 2000-12-21 Method and apparatus to control egr-recirculation for a combustion engine
PCT/SE2000/002622 WO2001050010A1 (en) 1999-12-29 2000-12-21 Method and apparatus to control egr-recirculation for a combustion engine

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US6422219B1 (en) * 2000-11-28 2002-07-23 Detroit Diesel Corporation Electronic controlled engine exhaust treatment system to reduce NOx emissions
DE102009044913A1 (en) * 2009-09-23 2011-04-07 Robert Bosch Gmbh Internal combustion engine

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DE4312462A1 (en) * 1993-04-16 1994-10-20 Mak Maschinenbau Krupp Internal combustion engine with exhaust gas recirculation
SE9700474L (en) * 1997-02-10 1997-12-22 Scania Cv Ab Supercharged internal combustion engine, preferably diesel type, equipped with an exhaust gas recirculation device
US5771867A (en) * 1997-07-03 1998-06-30 Caterpillar Inc. Control system for exhaust gas recovery system in an internal combustion engine
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