Gasoline vapor purging system of internal combustion engine

Abstract: In an internal combustion engine of gasoline direct injection type, there is arranged a gasoline vapor purging system. The vapor purging system has a vapor purging section which temporarily traps gasoline vapor produced in a fuel supply section of the engine and feeds the gasoline vapor through a vapor purge conduit into an intake section of the engine upon operation of the engine. In the vapor purge conduit, there is installed an electrically actuated valve which controls the flow of the gasoline vapor toward the intake section. The vapor purging system has further a control unit which controls operation of the valve so that a target purging rate of the gasoline vapor toward the intake section is determined based on an amount of gasoline injected to each combustion chamber of the engine through an injector.

Description: The present invention relates to a gasoline vapor purging system according to the preamble portion of claim 1 and to a gasoline vapor purging method according to the preamble portion of claim 9, and in general to evaporation emission controls (EEC) of motor vehicles powered by internal combustion engines, which prevent the escape of gasoline vapors from the fuel tank and fuel supply system, whether or not the engine is running. More specifically, the present invention relates to gasoline vapor purging system for use in an internal combustion engine of gasoline direct injection type. For preventing the escape of gasoline vapors from the fuel supply section such as a fuel tank or the like, most vehicles built during these days use an activated charcoal canister to trap the vapors when the engine is shut off. Upon restarting, a flow of filtered air through the canister purges the vapors from the charcoal. The mixture goes through a vapor purge pipe feeding into an intake section of the engine and it is burnt in the engine. In a gasoline vapor purging system disclosed by Japanese Patent First Provisional Publication 7-42588, a purge control valve is used for controlling the flow of vapors in the vapor purge pipe in accordance with an operation condition of the engine. That is, in the conventional vapor purging system, a target vapor purging rate (viz., target open degree of the purge control valve) is determined in accordance with the flow rate of air (viz., intake air) led into the engine. However, hitherto, the vapor purging system has been given little thought in internal combustion engines of a type which can switch between a so-called "stoichiometric combustion mode" wherein the engine operates on a mixture of stoichiometric air/fuel ratio and a so-called "lean combustion mode" wherein the engine operates on a mixture of higher (or lean) air/fuel ratio. That is, to allow the engine to operate in the lean combustion mode, it is necessary to increase the flow rate of the intake air by increasing the open degree of a throttle valve. Thus, if the target vapor purging rate is determined in accordance with the flow rate of the intake air like in case of the Publication 7-42588, the lean combustion mode is forced to induce excessive vapor purging, which tends to lower combustibility of the mixture in combustion chambers. In internal combustion engines operating on gasoline, there is a so-called "gasoline direct injection type" wherein fuel (viz., gasoline) is directly injected into combustion chambers. The engines of such type disclosed by Japanese Patent First Provisional Publications 62-191622 and 2-169834 have two combustion modes of early and late injection of fuel. That is, injection early in the intake stroke produces a homogenous mixture for high-load conditions, while the late injection delays the event until near the end of the compression stroke to create a stratified mixture for low-load conditions. The stratified mixture generally consists of a first layer of richer mixture which is easily ignited by an ignition plug and a second layer of leaner mixture which is ignited by the burning of the first layer of mixture. Combustion of the stratified mixture realizes ultra-lean combustion and thus brings about improvement in fuel economy due to reduction in pumping loss. However, as is known, combustion of stratified mixture is very sensitive to a change in air/fuel ratio and thus easily affected by the above-mentioned vapor purging and the exhaust gas recirculation (EGR). That is, if the stratified mixture becomes to have an outer layer whose air/fuel ratio is too high (viz., too lean) due to affection by the vapor purging and/or the exhaust gas recirculation (EGR), appropriate combustion of the outer layer is not obtained, which increases a possibility of remaining unburhed substances in the combustion chambers. While, if the stratified mixture has a too low air/fuel ratio (viz., too rich mixture) in total, appropriate combustion of the mixture is not obtained also, which increases a possibility of exhausting marked smoke and thus increasing fuel consumption. For solving the above-mentioned drawbacks, a measure may be thought out wherein during combustion of the stratified mixture, the vapor purging is inhibited or at least turned down. However, in this case, the performance of the gasoline vapor purging system per se is sacrificed. That is, fuel (viz., gasoline vapors) trapped by the charcoal canister can not be completely purged from the charcoal canister under operation of the engine, so that it tends to occur that when the engine is stopped, the canister shows its saturation condition in adsorbing vapors. In this case, gasoline vapor generated thereafter can not be trapped by the canister any longer, which permits escape of the vapor into the atmosphere. US 4,867,162 discloses a gasoline vapor purging control system comprising an electromagnetic proportion control valve arranged between a charcoal canister connected to a fuel tank and an inlet port opening into an intake pipe of the surge tank of the engine, said engine comprising fuel injection valves injecting fuel to the intake port. The amount of the evaporated fuel gas introduced into the intake passage is varied depending upon the injected fuel amount, said fuel injection amount being calculated based on amount of air drawn into the engine and the rotational speed of the engine and being corrected with respect to the stoichiometric air/fuel ratio, the temperature of the cooling water, the temperature of air drawn in the engine, and the variation of the voltage of the battery. It is, therefore, an object of the present invention to provide an improved gasoline vapor purging system and method as indicated above having a performance in vapor purging unaffected by a change in a combustion mode of the internal combustion engine. For the apparatus aspect, this objective is solved by a gasoline vapor purging system having the features of claim 1. Preferred embodiments of the invented gasoline vapor purging system are laid down in the respective dependent claims. For the method aspect, this objective is solved by a gasoline vapor purging method having the features of claim 9. Preferred embodiments are laid down in the respective dependent claims. In the following, the present invention is explained in greater detail with respect to several embodiments thereof in conjunction with the accompanying drawings, wherein: Fig. 1 is a schematic view of a gasoline vapor purging system according to an embodiment; Fig. 2 is a flowchart showing programmed operation steps executed by a control unit for deriving a target purging rate; Fig. 3 is one of data maps used for determining the target purging rate, which shows a relationship between an engine speed, an amount of injected fuel, and a target purging rate; Fig. 4 is a flowchart similar to Fig. 2, but showing the other method for deriving the target purging rate; and Fig. 5 is a flow table showing work steps executed by a control unit for determining various target purging rates. Referring to Fig. 1 of the drawings, there is shown but schematically a gasoline vapor purging control system of an embodiment which is incorporated with an internal combustion engine 11 of gasoline direct injection type. In an upstream single conduit part of an air intake section 12 of the engine 11, there are installed an air flow meter 13 and a throttle valve 14 which is positioned downstream of the air flow meter 13 as shown. Although not shown in the drawing, an air cleaner is connected to an upstream end of the single conduit part of the intake section 12, by which air introduced into the intake section 12 is cleaned. The intake section 12 has an intake manifold which comprises a united part constituting the upstream single conduit part and a plurality of branches extending from the united part to intake ports of respective combustion chambers. The air flow meter 13 measures the flow rate "Qa" of the intake air, that is, the amount of intake air per unit time. The throttle valve 14 thus controls the flow rate "Qa" of the intake air. Electromagnetic fuel injectors 16 are arranged to directly inject metered fuel into respective combustion chambers of the engine 11. Each fuel injector 16 is controlled by a control unit 17 which has a microcomputer installed therein. That is, by processing various information signals applied thereto from various sensors, the control unit 17 issues an instruction pulse signal to each of the fuel injectors 16 to control the amount of fuel injected into the corresponding combustion chamber. A throttle valve control device 15 is provided, which can electronically control the open degree of the throttle valve 14 in accordance with an instruction signal applied thereto from the control unit 17. For this control, an information signal from an accelerator sensor 26 is also fed to the control unit 17. That is, through the throttle valve control device 15, the open degree of the throttle valve 14 is controlled in accordance with the engine operation condition determined based on the information signals from the sensors. For detecting the open degree of the throttle valve 14, a throttle sensor 14A is provided which feeds the control unit 17 with an information signal representing the open degree of the throttle valve 14. In place of the throttle sensor 14A, an idling sensor may be used. In an exhaust passage 18 of the engine 11, there is installed an oxygen sensor 19 of which information signal is fed to the control unit 17. More specifically, the oxygen sensor 19 is installed in an united part of branches of the exhaust manifold 18A. As is known, by measuring oxygen concentration in the exhaust gas by the oxygen sensor 19, an air/fuel ratio of the mixture fed to the engine 11 is detected. Thus, the oxygen sensor 19 is also known as an air/fuel ratio sensor. A crank angle sensor 20 is installed in a distributor (not shown), which issues a crank angle signal in synchronization with the engine speed. By counting peaks of the signal in a unit time, or by detecting the period of the base crank angle, the engine speed "Ne" is detected. A temperature sensor 21 is further provided which detects the temperature "TW" of cooling water of the engine 11. The information signal from the accelerator sensor 26 represents a depression degree "APS" by which an accelerator pedal (not shown) is depressed by a driver. It is to be noted that the depression degree "APS" corresponds to an engine output torque needed by the driver. Gasoline vapors from a fuel tank 30 are led to an activated charcoal canister 23 through a vapor pipe 22, so that the vapors are contemporarily trapped by the canister 23. An upper space in the canister 23 is connected through a vapor purge pipe 24 to a purge port 12A which is formed in the united upstream part of the intake manifold of the intake section 12 downstream of the throttle valve 14. To the purge pipe 24, there is connected a purge control valve 25 which is controlled by the control unit 17. That is, open timing and open period of the valve 25 are controlled by the control unit 17 in a duty-ratio control manner. A stepping motor may be used as the control valve 25. In the computer of the control unit 17, the following programmed operation steps are executed for controlling the purging of gasoline vapors. Fig. 2 is a flowchart showing operation steps for deriving a target purging rate "EVPTR" based on an amount "Tib" of injected fuel. For ease of description, the amount "Tib" will be referred to as "fuel injection amount" in the following. That is, at step S1, the engine speed "Ne" is derived from the signal issued from the crank angle sensor 20. At step S2, the flow rate "Qa" of intake air is derived from the signal issued from the air flow meter 13. At step S3, a basic amount "Tp" of injected fuel for each combustion chamber is derived from the following equation: Tp = k x Qa/Ne wherein: k : constant In fact, the basic amount "Tp" is the amount of injection fuel which brings about a stoichiometric air/fuel ratio. At step S4, a target equivalent ratio "TFBYA" is looked up from a data map which shows a relationship between various operation conditions of the engine and equivalent ratios. The operation conditions of the engine are a stoichiometric combustion condition wherein the engine operates on a mixture of stoichiometric air/fuel ratio, a lean combustion condition wherein the engine operates on a lean mixture, a stratified charge combustion condition wherein the engine operates on a stratified charge of mixture, a homogenous charge combustion condition wherein the engine operates on a homogenous charge of mixture, high/low load combustion condition wherein the engine operates on a mixture under high/low load, etc.,. At step S5, a fuel injection amount "Tib" is derived from the following equation: Tib = Tp x TFBYA Then, at step S6, a target purging rate "EVPTR" is looked up from a data map which, as is seen from Fig. 3, shows a relationship between the fuel injection amount "Tib", engine speed "Ne" and target purging rate "EVPTR". As is understood from the above, in the present embodiment, the target purging rate "EVPTR" is determined based on the amount "Tib" of fuel actually injected into the combustion chamber, that is, based on a target torque of the engine. In other words, in the present embodiment the target purging rate "EVPTR" is not determined on the basic amount "Tp" of injected fuel which brings about a stoichiometric air/fuel ratio. Accordingly, even when, under operation of lean combustion mode, the open degree of the throttle valve 14 is further increased for achieving a target lean mode combustion and thus the flow rate of intake air fed to each combustion chamber is increased, it is possible to fit the vapor purging rate to a combustion condition of the engine, that is, to the mount of fuel actually injected to each combustion chamber. Accordingly, according to the present embodiment,undesired excessive vapor purging, which would occur in the above-mentioned conventional vapor purging control system in such condition, is suppressed or at least minimized. If desired, the fuel injection amount "Tib" may be derived from other method. That is, the fuel injection amount "Tib" can be derived from a pulse duration "Ti" of a fuel injection pulse signal which is issued from a control unit under normal fuel injection operation of the engine. As is known, the fuel injection pulse signal issued under such normal operation of the engine is provided in accordance with the existing condition of the engine, that is, with respect to a target equivalent ratio, various correction factors, etc.,. Fig. 4 is a flowchart showing programmed operation steps executed for deriving the target purging rate "EVPTR" from the pulse duration "Ti". At step S11, the pulse duration "Ti" of a fuel injection pulse signal is read. Usually, the pulse duration "Ti" is determined from the following equation: Ti = Tp x COEF x TFBYA + TS wherein: Tp: basic amount of injected fuel for achieving stoichiometric air/fuel ratio; COEF: coefficient; TFBYA: target equivalent ratio; TS: invalid fuel injection pulse. At step S12, a fuel injection amount "Tib' " is derived from the following equation: Tib' = Ti - Ts wherein: Ts: invalid pulse duration. At step S13, a target purging rate "EVPTR" is looked up from a data map which, as is understood from Fig. 3, shows a relationship between the fuel injection amount "Tib' ", engine speed Ne and target purging rate "EVPTR". Fig. 5 is a flow table showing work steps executed by the control unit 17 for deriving the target purging rate. As will become apparent as the description proceeds, the target purging rate changes depending on the operation condition of the engine, that is, whether the engine operates under stoichiometric combustion mode, lean combustion mode, stratified mixture combustion mode, homogenous combustion mode or so. At block B1, judgment is carried out as to whether the engine is operating under stoichiometric combustion mode or lean combustion mode. That is, for example, by looking up a data map "FMAPCH" which represents a relationship between the engine operation condition (engine speed, torque produced, etc.,) and combustion mode, such judgment is achieved. When it is judged that the engine is operating under stoichiometric combustion mode, block B2 is selected, while, when it is judged that the engine is operating under lean combustion mode, block B3 is selected. At block B2, a target purging rate "EVPTR-1" for the stoichiometric combustion mode is looked up from a corresponding data map, such as that shown in Fig. 3. While, at block B3, judgment is carried out as to whether the lean combustion is a stratified combustion or a non-stratified combustion. That is, for example, by looking up a data map "FMAPCH" which represents a relationship between the engine operation condition (engine speed, torque produced, etc.,) and combustion type, such judgment is achieved. When it is judged that the lean combustion is the stratified combustion, block B4 is selected, while, when it is judged that the lean combustion is the non-stratified combustion, block B7 is selected. At block B7, that is, when the engine is operating on a non-stratified lean air/fuel mixture, a target purging rate "EVPTR-0" is looked up from a corresponding data map, such as that shown in Fig. 3. At block B4, judgment is carried out as to whether the engine is idling or not. That is, when the throttle sensor 14A issues a signal representing O (zero) open degree of the throttle valve 14, block B5 is selected judging that the engine is under idling. While, when the throttle sensor 14A issues a signal representing the throttle valve 14 being open, block B6 is selected judging that the engine is not under idling. At block B5, that is, when the engine is idling on a stratified lean mixture, the target purging rate "EVPTR-0" is set to 0 (zero) having regard to a fact that under such condition the combustibility of the mixture is easily affected by the vapor purging. While, at block B6, that is, when the engine is normally operating on a stratified lean mixture, a target purging rate "EVPTR-0" is looked up from a corresponding data map, such as that shown in Fig. 3. For deriving the rate "EVPTR-0", the above-mentioned operation steps of Fig. 2 or Fig. 4 are executed. As is known, the influence of vapor purging to the combustion of stratified lean mixture under normal operation of the engine is very low as compared with that to the combustion of the same under idling operation of the engine, but high as compared with that to the combustion of homogenous lean mixture under normal operation of the engine. Thus, as is seen from the map illustrated in block B6, when the target equivalent ratio "TFBYA" exceeds a predetermined level, that is, when a target air/fuel ratio under the stratified combustion of lean mixture becomes higher (viz., leaner) than a predetermined level, a certain limitation is applied to the target purging rate "EVPTR-0". That is, the target purging rate "EVPTR-0" is saturated at the level of "EVPTR-S". More specifically, because, with increase of the target air/fuel ratio (viz., with decrease of the target equivalent ratio "TFBYA", or as the mixture becomes leaner), the influence of the vapor purging to the combustion becomes higher, the target purging rate "EVPTR-0" has the upper limitation of "EVPTR-S". As is known, in the homogenous charge combustion, fuel is entirely spread in the combustion chamber to produce a homogenous air/fuel mixture, while, in the stratified charge combustion, fuel is partially spread in the combustion chamber to produce an easily combustible air/fuel mixture at only a given portion of the chamber. Accordingly, in the stratified charge combustion, fuel in the purged vapor from the charcoal canister affects the combustion of the mixture relatively hard. This phenomenon becomes much severe when the mixture becomes leaner, that is, when the fuel injection amount becomes less. Thus, if the target purging rate "EVPTR-0" is determined simply based on the fuel injection amount "Tib", such undesired phenomenon can not be eliminated or lowered. However, if the target purging rate "EVPTR-0" is processed to have the upper limitation of "EVPTR-S" in such a manner as is described hereinabove, such undesired phenomenon can be eliminated or at least minimized. In the control unit 17, an open degree of the purge control valve 25, more specifically, a duty ratio of an instruction pulse signal applied thereto which achieves the target purging rate "EVPTR" (viz., EVPTR-0 or EVPTR-1) is looked up from a corresponding data map. When receiving such instruction pulse signal from the control unit 17, the purge control valve 25 controls its open timing and open period. As is described hereinabove, in the present embodiment, target purging rate is determined based on the fuel injection mount "Tib" or Tib' " irrespective of whether the combustion is a stratified lean mixture combustion or a homogeneous lean mixture combustion. Accordingly, even when, under a lean mixture combustion mode, for achieving a target air/fuel ratio in the mode, the open degree of the throttle valve 14 is increased by a degree greater than that in case of a stoichiometric combustion mode to achieve a target lean air/fuel ratio and thus the amount of air fed into each combustion chamber is increased, the gasoline vapor purging is appropriately carried out in accordance with the combustion condition in the combustion chamber without being affected by the increased air amout. In other words, under such condition, the vapor purging rate is determined in accordance with the fuel injection amount "Tib" or "Tib' ". That is, undesired excessive vapor purging, which would lower combustibility of the lean mixture, is eliminated or at least minimized. Under a stratified lean mixture combustion mode, the target purging rate "EVPTR" is determined in accordance with the target equivalent ratio "TFBYA" (or target air/fuel ratio). Thus, even under such mode wherein the combustion of lean mixture would be easily affected by the vapor purging, satisfied combustibility of the mixture is kept while assuring optimal gasoline vapor purging. Thus, as compared with the above-mentioned conventional technique wherein under stratified lean mixture combustion the vapor purging is inhibited or at least turned down, the embodimentcan exhibit a marked performance in the vapor purging. In other words, in the embodiment,the vapor purging and the combustibility of the stratified lean mixture are both improved at the same time. That is, even under the stratified lean mixture combustion mode, the vapor purging is sufficiently carried out. If desired, the target purging rate "EVPTR" (viz., EVPTR-0, EVPTR-1, EVPTR-S) may be corrected in accordance with the concentration of the purged vapor. For example, the correction is so made that the target purging rate reduces with increase of the concentration of the vapor. For measuring the concentration of the vapor, a hydrocarbon concentration sensor is mounted in the vapor purge pipe 24 (see Fig. 1). Furthermore, the concentration of the vapor may be derived from a difference between an air/fuel ratio correction factor "α" set for a feedback control of the engine under a mode wherein the vapor purging is not carried out and another air/fuel ratio correction factor β" set for the feedback control of the engine under a mode wherein the vapor purging is carried out. As is known, in the feedback control of the engine, by processing an information signal issued from an oxygen sensor 19 (or air/fuel ratio sensor), the existing air/fuel ratio of mixture is controlled to a stoichiometric value. Furthermore, if desired, the target purging rate "EVPTR" may be corrected in accordance with the rate of exhaust gas recirculation (EGR). That is, for example, the correction is so made that the target purging rate reduces with increase of the rate of EGR. Furthermore, if desired, the target purging rate "EVPTR" may be corrected in accordance with the amount "OGA" of operation gas which is represented by the following equation: OGA = (Qa + Q EGR + Q PURGE )/F R wherein: Qa : amount of air measured by air flow meter 13, Q EGR : amount of exhaust gas fed back to combustion chamber, Q PURGE : amount of air in gasoline vapor, F R : rate of amount of fuel. The description above discloses (amongst others) a gasoline vapor purging system for an internal combustion engine of gasoline direct injection type, which optimally carries out the vapor purging in accordance with the combustion of the engine. Said system comprises a vapor purging section which temporarily traps gasoline vapor produced in a fuel supply section of the engine and feeds the gasoline vapor through a vapor purge conduit to an intake section of the engine upon operation of the engine; an electrically actuated valve installed in the vapor purge conduit to control flow of the gasoline vapor toward the intake section; and a control unit which controls operation of the valve so that a target purging rate of the gasoline vapor directed toward the intake section is determined based on an amount of gasoline injected to each combustion chamber of the engine through an injector. There is further disclosed a gasoline vapor purging control system for use with an internal combustion engine which has a vapor purging section which temporarily traps gasoline vapor produced in a fuel supply system of the engine and feeds the same to an intake section of the engine upon operation of the engine. Said control system comprises first means for determining a target vapor purging rate based on an amount of fuel fed to each combustion chamber of the engine; second means which, when the engine operates on a stratified lean mixture, corrects the target vapor purging rate in accordance with a target air/fuel ratio of the mixture; and third means for selectively controlling the vapor purging effected by the vapor purging section in accordance with the target vapor purging rate and the corrected target vapor purging rate.

Claims: Gasoline vapor purging system of an internal combustion engine (11) which has a vapor purging section (22,23) which temporarily traps gasoline vapor produced in a fuel supply system (30) of the engine (11) and feeds the same to an intake section (12) of the engine (11) upon operation of the engine (11), characterized by a control unit comprising: first means for determining a target vapor purging rate (EVPTR) based on an amount of fuel (Tib,Tib') fed to each combustion chamber of the engine; second means which, when said engine (11) operates on a stratified lean mixture, corrects said target vapor purging rate (EVPTR) in accordance with a target air/fuel ratio of the mixture; and third means for selectively controlling the vapor purging effected by said vapor purging section (22,23) in accordance with the target vapor purging rate (EVPTR) and the corrected target vapor purging rate. Gasoline vapor purging system according to claim 1, characterized by an electrically actuated purge control valve (25) installed in said vapor purge conduit (24) to control the flow of the gasoline vapor toward said intake section (12), wherein said control unit controls operation of said valve (25) so that said target vapor purging rate (EVPTR) of the gasoline vapor directed toward the intake section (12) is determined based on the amount (Tib,Tib') of gasoline injected to each combustion chamber of the engine (11) through an injector, and wherein said control unit when said engine (11) operates on said stratified lean mixture corrects said target vapor purging rate (EVPTR) determined based on the amount (Tib,Tib') of the injected gasoline in accordance with a target air/fuel ratio of the mixture. Gasoline vapor purging system according to claim 2, characterized in that said target vapor purging rate (EVPTR) and the corrected target vapor purging rate are each corrected in accordance with a concentration of the gasoline vapor in said vapor purge conduit (24). Gasoline vapor purging system according to claim 2 or 3, characterized in that said target vapor purging rate (EVPTR) and the corrected target vapor purging rate are each corrected in accordance with an amount of exhaust gas which is fed back from an exhaust section of the engine (11) to said intake section (12). Gasoline vapor purging system according to one of the claims 2 to 4, characterized in that said target purging rate (EVPTR) and the corrected target purging rate are each corrected in accordance with an amount "OGR" of operation gas, said amount "OGR" being represented by the following equation: OGA = (Qa + Q EGR + Q PURGE )/F R wherein: Qa : is an amount of air measured by air flow meter 13, Q EGR : is an amount of exhaust gas fed back to combustion chamber, Q PURGE : is an amount of air in gasoline vapor, and F R : is a rate of amount of fuel. Gasoline vapor purging system according to any of the preceding claims, characterized in that said engine is of a type which can switch between a stratified charge combustion mode in which the engine operates on a stratified charge of lean mixture and a homogenous charge combustion mode in which the engine operates on a homogenous charge of lean mixture. Gasoline vapor purging system according to any of the preceding claims 2 to 6, characterized by a canister (23) connected to the fuel supply system (30), the canister (23) trapping the gasoline vapor, wherein said vapor purge conduit (24) connects the canister (23) and the intake section (12), and wherein the purge control valve (25) installed in the vapor purge conduit (24) controls the flow of gasoline vapor from the canister (23) to the intake air passage. Gasoline vapor purging system according to any of the preceding claims, characterized in that the control unit further comprises a combustion controlling section selectively controlling one of stratified combustion and homogeneous combustion. Gasoline vapor purging method for an internal combustion engine of the gasoline direct injection type, comprising the steps of: calculating an amount of fuel delivered to the engine; calculating an amount of gasoline vapor purged from a canister to an intake air passage of the engine as a function of the calculated amount of the fuel; and controlling a purge control valve based on the calculated amount of the gasoline vapor, the purge control valve being installed in a conduit connecting the canister and the intake air passage, characterized in that a target purging rate is changed depending on whether the engine operates under stoichiometric combustion mode, lean combustion mode, stratified mixture combustion mode or homogenous combustion mode, wherein under a stratified lean mixture combustion mode the target purging rate (EVPTR) determined based on the amount (Tib,Tib') of the injected gasoline is corrected in accordance with the target air/fuel ratio of the mixture.

Inventors: FURUSHOU MASAYA, KAKIZAKI SHIGEAKI, MATSUMOTO MIKIO, OOBA HIRAKU, FURUSHOU, MASAYA, KAKIZAKI, SHIGEAKI, MATSUMOTO, MIKIO, OOBA, HIRAKU
Applicants: NISSAN MOTOR, NISSAN MOTOR COMPANY, LIMITED
Application year: 1998
Main classification: F02B17
IPC codes: F02D41, F02M25, F02B17