Heat generation method in an emission control device

Abstract: A fuel vapour purging method controls fuel vapour purging during stratified operation. Several factors influence vapour purge control, including fuel vapour concentration in the cylinder and temperature of the emission control device (70,72). The fuel vapour passes through the cylinder unburned by maintaining the concentration within allowable limits. The unburned fuel vapour reacts exothermically in the emission control device (70,72) thereby generating heat. To guarantee that the fuel vapour reacts in the first emission control device, the fuel vapour purge is restricted to a certain temperature range. To guarantee that the fuel vapour does not burn in the cylinder, the concentration is kept to a restricted value.

Description: The field of the invention relates to fuel vapour purge in direct injection spark ignition engines. In direct injection spark ignition engines, the engine operates at or near wide-open throttle during stratified air/fuel operation in which the combustion chambers contain stratified layers of different air/fuel mixtures. The strata closest to the spark plug contains a stoichiometric mixture or a mixture slightly rich of stoichiometry and subsequent strata contain progressively leaner mixtures. The engine may also operate in a homogeneous mode of operation with a homogeneous mixture of air and fuel generated in the combustion chamber by early injection of fuel into the combustion chamber during its intake stroke. Homogeneous operation may be either lean of stoichiometry, at stoichiometry, or rich of stoichiometry. Direct injection engines are also coupled to conventional three-way catalytic converters to reduce CO, HC, and NOx. When operating at air/fuel mixtures lean of stoichiometry, a NOx trap or catalyst is typically coupled down-stream of the three-way catalytic converter to further reduce NOx. Direct injection engines are also coupled to fuel vapour recovery systems to allow purging of fuel vapours. Conventional systems allow fuel vapour purging in the stratified mode only when the catalyst temperature is high enough to convert the unburned hydrocarbons. In other words, since the fuel vapour is inducted with the fresh charge, it forms a homogenous air/fuel mixture. Then, when the fuel is directly injected during the compression stroke to form a stratified mixture, only the stratified fuel burns since the homogenous fuel vapour mixture is too lean. Therefore, unburned fuel vapour may exit the engine cylinder. In some circumstances, to remove these vapours, the catalytic converter may have to be above a certain temperature, known to those skilled in the art as the light-off temperature. Therefore, fuel vapour purging during the stratified mode is restricted until the catalyst has reached this light-off temperature. Such a method is described in U.S. Patent 5,245,975. The inventor herein has recognised a disadvantage with the above approach. When operating in the stratified mode, less heat is generated to increase or maintain catalyst or NOx trap temperature. Thus, it takes a long time after a cold start before purging is allowed. Also, with some catalyst formulations and catalyst configurations, the catalyst may not maintain this light-off temperature during certain conditions and purging is only possible in the homogeneous mode, thereby reducing fuel economy and allowable purge time. In other words, when operating in the stratified mode, catalyst or NOx trap temperature may fall below the light-off temperature, preventing purge and thereby limiting stratified operation. It is further known from JP10054310-A that when a purge of vaporised fuel is determined to be necessary during stratified operation, a discharge amount of NOx can be calculated and a required amount of HC as a reducing agent for the calculated NOx can be calculated. An actual required purge amount of vaporised fuel is then determined and the determined value of vaporised fuel can be used to control a purge control valve. According to the invention there is provided a method for controlling fuel vapour purge entering an engine having multiple chambers coupled to an emission control device in which the method comprises the steps of operating the engine in a stratified mode where fuel is injected during a compression stroke of the engine and purging fuel vapours into the combustion chambers characterised in that the method further comprises limiting the purged fuel vapours to be less than a maximum value based on cylinder fuel vapour concentration. Said purging step may further comprise purging fuel vapours into the combustion chambers so that an emission control device temperature approaches a desired emission control device temperature. Said purging step may further comprise purging fuel vapours into the combustion chamber when an emission control device temperature is less than a predetermined upper threshold value. Said cylinder fuel vapour concentration may be based on a fuel injection amount, an engine airflow, a total purge flow rate, and an exhaust air/fuel ratio. Said purging step may further comprise purging fuel vapours into the combustion chambers so that they will pass through the chambers unburned, thereby providing unburned hydrocarbons and excess oxygen to react exothermically and generate heat in the emission control device. The method may further comprise the step of determining a desired total purge flow based on said maximum value and a difference between an emission control device temperature and a desired emission control device temperature. A purge flow control valve may be provided and the method may further comprise the step of adjusting the purge flow control valve based on said desired total purge flow. The method may further comprise providing an indication of temperature of the emission control device, determining a fuel vapour concentration in the combustion chambers and controlling the fuel vapours inducted into the combustion chambers (30) based on said temperature and said fuel vapour concentration. A purge control valve may be provided to control the amount of fuel vapours being purged. The method may further comprise the step of adjusting said purge control valve based on said temperature. By limiting fuel vapour purging based on cylinder fuel vapour concentration, it is possible to guarantee that the fuel vapours will pass through the combustion chamber unburned. These unburned fuel vapours, along with oxygen from the unburned portion of the charge inducted, will react exothermically in the emission control device. This exothermic reaction will generate heat that will increase the emission control device to a desired level. In other words, when purging fuel vapours during stratified operation, the fuel vapours are inducted into the cylinder and may form a homogeneous mixture that is too lean to combust, even when the engine is operating in a stratified mode. The point at which the fuel vapours form a combustible mixture is related to the cylinder vapour concentration. Therefore, limiting the fuel vapour purge in this way allows the fuel vapours to form only incombustible mixtures. An advantage of the present invention is increased fuel vapour purging during stratified operation. Another advantage of the present invention is increased stratified operation and therefore increased fuel economy. Yet another advantage of the present invention is decreased emissions. Still another advantage of the present invention is that the addition of fuel vapour purge produces minimal, slowly changing, additional torque, allowing smooth transitions into and out of fuel vapour purge operation. The present invention will now be described further, by way of example, with reference to the accompanying drawings, in which: Figure 1 is a block diagram of an embodiment in which the invention is used to advantage; and Figures 2-10 are high level flowcharts describing a portion of operation of the embodiment shown in Figure 1. Direct injection spark ignited internal combustion engine 10, comprising a plurality of combustion chambers, is controlled by electronic engine controller 12. Combustion chamber 30 of engine 10 is shown in Figure 1 including combustion chamber walls 32 with piston 36 positioned therein and connected to crankshaft 40. In this particular example, piston 30 includes a recess or bowl (not shown) to help in forming stratified charges of air and fuel. Combustion chamber 30 is shown communicating with intake manifold 44 and exhaust manifold 48 via respective intake valves 52a and 52b (not shown), and exhaust valves 54a and 54b (not shown). Fuel injector 66 is shown directly coupled to combustion chamber 30 for delivering liquid fuel directly therein in proportion to the pulse width of signal fpw received from controller 12 via conventional electronic driver 68. Fuel is delivered to fuel injector 66 by a conventional high pressure fuel system (not shown) including a fuel tank, fuel pumps, and a fuel rail. Intake manifold 44 is shown communicating with throttle body 58 via throttle plate 62. In this particular example, throttle plate 62 is coupled to electric motor 94 so that the position of throttle plate 62 is controlled by controller 12 via electric motor 94. This configuration is commonly referred to as electronic throttle control (ETC] which is also utilized during idle speed control. In an alternative embodiment (not shown), which is well known to those skilled in the art, a bypass air passageway is arranged in parallel with throttle plate 62 to control inducted airflow during idle speed control via a throttle control valve positioned within the air passageway. Exhaust gas oxygen sensor 76 is shown coupled to exhaust manifold 48 upstream of catalytic converter 70. In this particular example, sensor 76 provides signal UEGO to controller 12 which converts signal UEGO into a relative air/fuel ratio λ. Signal UEGO is used to advantage during feedback air/fuel control in a conventional manner to maintain average air/fuel at a desired air/fuel ratio. Conventional distributorless ignition system 88 provides ignition spark to combustion chamber 30 via spark plug 92 in response to spark advance signal SA from controller 12. Controller 12 causes combustion chamber 30 to operate in either a homogeneous air/fuel mode or a stratified air/fuel mode by controlling injection timing. In the stratified mode, controller 12 activates fuel injector 66 during the engine compression stroke so that fuel is sprayed directly into the bowl of piston 36. Stratified air/fuel layers are thereby formed. The strata closest to the spark plug contains a stoichiometric mixture or a mixture slightly rich of stoichiometry, and subsequent strata contain progressively leaner mixtures. During the homogeneous mode, controller 12 activates fuel injector 66 during the intake stroke so that a substantially homogeneous air/fuel mixture is formed when ignition power is supplied to spark plug 92 by ignition system 88. Controller 12 controls the amount of fuel delivered by fuel injector 66 so that the homogeneous air/fuel mixture in chamber 30 can be selected to be at stoichiometry, a value rich of stoichiometry, or a value lean of stoichiometry. The stratified air/fuel mixture will always be at a value lean of stoichiometry, the exact air/fuel being a function of the amount of fuel delivered to combustion chamber 30. An additional split mode of operation wherein additional fuel is injected during the exhaust stroke while operating in the stratified mode is available. An additional split mode of operation wherein additional fuel is injected during the intake stroke while operating in the stratified mode is also available, where a combined homogeneous and split mode is available. Nitrogen oxide (NOx) absorbent or trap 72 is shown positioned downstream of catalytic converter 70. NOx trap 72 absorbs NOx when engine 10 is operating lean of stoichiometry. The absorbed NOx is subsequently reacted with HC and catalyzed during a NOx purge cycle when controller 12 causes engine 10 to operate in either a rich homogeneous mode or a stoichiometric homogeneous mode. Controller 12 is shown in Figure 1 as a conventional microcomputer including: microprocessor unit 102, input/output ports 104, an electronic storage medium for executable programs and calibration values, shown as read-only memory chip 106 in this particular example, random access memory 108, keep alive memory 110, and a conventional data bus. Controller 12 is shown receiving various signals from sensors coupled to engine 10, in addition to those signals previously discussed, including: measurement of inducted mass air flow (MAP) from mass air flow sensor 100 coupled to throttle body 58; engine coolant temperature (ECT) from temperature sensor 112 coupled to cooling sleeve 114; a profile ignition pickup signal (PIP) from Hall effect sensor 118 coupled to crankshaft 40; throttle position TP from throttle position sensor 120; and absolute Manifold Pressure Signal MAP from sensor 122. Engine speed signal RPM is generated by controller 12 from signal PIP in a conventional manner and manifold pressure signal MAP provides an indication of engine load. In this particular example, temperature Tcat of catalytic converter 70 and temperature Ttrp of NOx trap 72 are inferred from engine operation as disclosed in U.S. Patent No. 5,414,994, the specification of which is incorporated herein by reference. In an alternate embodiment, temperature Tcat is provided by temperature sensor 124 and temperature Ttrp is provided by temperature sensor 126. Fuel system 130 is coupled to intake manifold 44 via tube 132. Fuel vapors (not shown) generated in fuel system 130 pass through tube 132 and are controlled via purge valve 134. Purge valve 134 receives control signal PRG from controller 12. Generating Heat in an Emission Control Device Heat generated in an emission control device can be used to advantage to, for example, rapidly increase temperature of the device to obtain faster light-off during a cold start, control temperature of the device to obtain optimum conversion efficiency, purge the device to remove sulfur contamination, or many other applications where it is advantageous to generate heat in the device. Heat is generated in the device by providing unburned fuel vapor (HC) from fuel system 130 along with excess oxygen from lean combustion. This is done by operating the engine in a stratified mode and introducing fuel vapors during the induction stroke, thereby forming a homogeneous fuel vapor mixture at a lean air/fuel ratio that will not support burning of the fuel vapor. Therefore, the fuel vapors pass through the cylinder unburned and react exothermically with the excess oxygen since the overall air/fuel ratio is still lean of stoichiometry. According to the present invention, the device can be any emission control device such as a three-way catalytic converter or a NOx trap. In the embodiment described by Figure 1, the upstream device is catalyst 70. In an alternative embodiment (not shown), the upstream device may be trap 72. Limiting Fuel Vapor Purge Based on Emission Control Device Temperature In order to maximize the heat generated from fuel vapor and excess oxygen exothermically reacting, the emission control device should be greater than a lower threshold but less than a upper threshold. The lower threshold represents the temperature above which exothermic reactions are supported. Note that this threshold temperature for supporting exothermic reactions is different than the light-off temperature, since the light-off temperature is the temperature at which the emission control device reaches high efficiency in converting certain compounds into alternate compounds, thereby reducing certain regulated emissions. The upper threshold represents a temperature at which the emission control device reaches high efficiency and no longer needs additional heat. Note that the upper threshold may be equal to the light-off temperature. Also, the upper and lower thresholds are a function of catalyst washcoat chemistry. Calculating Cylinder Fuel Vapor Concentration To calculate cylinder fuel vapor concentration (ρ fc ), fuel vapor concentration (ρ f ) from the fuel vapor system is first calculated according to the following equation: ρ f = m p + m a - λS m f m p (1 + λ S ) Cylinder fuel vapor concentration (ρ fc ) is calculated as: ρ fc = m p ρ f ( m p + m a ) where ( m ˙ p ) is total purge flow rate, ( m ˙ f ) is actual fuel flow rate from the fuel injectors, ( m ˙ a ) is fresh charge measured by the air flow meter, (A) is measured relative air/fuel ratio in the exhaust, and S is the stoichiometric air/fuel ratio. The fuel vapor concentration (ρ f ) is thereby calculated based on total purge flow rate ( m ˙ p ) from the fuel vapor system, fresh charge measured by the air flow meter ( m ˙ a ), the relative air/fuel ratio in the exhaust (λ), the fuel flow rate from the fuel injectors ( m ˙ f ), and the stoichiometric air/fuel ratio S. The cylinder fuel vapor concentration (ρ fc ) is then based on fuel vapor concentration (ρ f ), total purge flow rate ( m ˙ p ), and fresh charge measured by the air flow meter ( m ˙ a ). In this way, and according to the above equations, the cylinder fuel vapor concentration (ρ fc ) is calculated based on available information and can be used to advantage. For example, the calculated cylinder fuel vapor concentration (ρ fc ) can be used to estimate expected emissions using characteristic relationships between cylinder vapor concentration and certain regulated emissions. Further, cylinder fuel vapor concentration (ρ fc ) can be used to control many engine control signals such as, for example, ignition timing or injection timing during stratified operation. For example, when operating in a split mode where fuel vapor purge forms the homogenous mixture and direct fuel injection during forms the stratified mixture, the fuel injection timing during the compression stroke to form the stratified fuel is adjusted based on the cylinder vapor concentration to obtain maximum torque. Limiting Fuel Vapor Purge Based on Cylinder Fuel Vapor Concentration In order to generate heat in the emission control device from the exothermic reaction of fuel vapor and excess oxygen, the fuel vapor must pass through the cylinder unburned. To guarantee fuel vapor passes unburned, cylinder fuel vapor concentration is limited by a maximum allowable purge concentration (ρ fc MAX ) . In other words, the calculated cylinder fuel vapor concentration (ρ fc ) can be compared to the maximum allowable purge concentration (ρ fc MAX ) and used to limit the amount of total purge flow rate ( m ˙ p ). Allowing the calculated cylinder fuel vapor concentration (ρ fc ) to exceed the maximum allowable, or critical, purge concentration (ρ fc MAX ) may also cause a change in engine torque. In a preferred embodiment, the maximum allowable, or critical, total purge flow ( m ˙ Pcrit ) is given as: m Pcrit = ρ fc max m a (1+λ S ) - m a + λ S m f ρ fc max + λΣρ fc max - 1 Therefore, to prevent cylinder fuel vapor concentration (ρ fc ) from exceeding the maximum allowable, or critical, purge concentration (ρ fc MAX ), purge valve 134 is controlled to limit total purge flow ( m ˙ p ) to the maximum allowable, or critical, total purge flow ( m ˙ Pcrit ). In this way, fuel vapor purge will pass through the cylinder unburned, allowing exothermic reaction in an emission control device and preventing a change in engine torque. If cylinder fuel vapor concentration (ρ fc ) exceeds the maximum allowable, or critical, purge concentration (ρ fc MAX ), then addition engine torque will be produced since some fuel vapors will burn during the engine power stroke. Under these conditions, other engine control variables are used to keep engine torque constant such as, for example, fresh air charge, ignition timing, exhaust gas recirculation, fuel injection amount, fuel injection timing, and/or variable cam timing. For example, rapid engine torque control can be achieved by using ignition timing or fuel injection amount. In particular, if using fuel injection amount, the amount of fuel injection amount adjustment can be determined by estimating an amount of fuel vapor purge that is burned, and this amount subtracted from the normal fuel injection amount. The following equation shows the calculation, where fia_c is the adjusted fuel injection amount, fia is the normal fuel injection amount (when fuel vapor purge does not exceed the maximum allowable concentration), and fvp_b is the amount of fuel vapor purge burned (determined using predetermined maps relating how far the actual purge concentration exceeds the maximum allowable concentration): fia _ c = fia - fvp _ b If one of the other engine control variables is used, predetermined characteristic maps relating engine torque to the control variable are used to maintain constant engine torque. Discontinuing Stratified Fuel Vapor Purge In some cases, limiting fuel vapor purge based on a maximum allowable fuel vapor cylinder concentration causes insufficient purging to keep a vapor system from becoming saturated. Thus, is some cases it is necessary to discontinue stratified fuel vapor purging when the actual limited fuel vapor purge is less than a desired value. In this case, either a split mode or homogenous mode is selected to allow maximum fuel vapor purge, where the fuel vapor purge is burned in the cylinder. For example, when actual fuel vapor purge (limited or clipped in any way, or determined through temperature control as described later herein), is less than a minimum required value, operation where fuel vapor purge passes through the cylinder is discontinued. The engine switches to either a purely homogenous mode or a split mode where purge is not limited or clipped and increase fuel vapor purge is possible. In these modes, the fuel vapor purge is burned in the cylinder and does not create an exothermic reaction in the catalyst. Using Cylinder Fuel Vapor to Control Emission Device Temperature As stated previously herein, heat generated by purging fuel vapors during stratified operation can be used to control temperature of the emission control device when the exothermic reaction is taking place. For example, the amount of fuel vapor purge, which is proportional to exothermic heat creating in the emission control device, can be controlled to maintain a desired emission control device temperature. When the emission control device temperature falls below a desired value and the engine is operating stratified, fuel vapor from fuel system 130 can be introduced into the cylinder and pass to the emission control device unburned. The fuel vapor then reacts exothermically in the emission control device, thereby generating heat and increasing temperature of the emission control device. As the temperature of the emission control device approaches the desired value, less fuel vapor purge is introduced, thereby causing temperature of the emission control device to converge to the desired level. Opportunistic Fuel Vapor Purge Based on Emission Control Device Temperature. When the emission control device temperature is in a lower portion of an acceptable range, fuel vapor purge can be allowed to take advantage of a fuel vapor purge opportunity. In other words, if it is necessary to purge fuel vapor because fuel vapor storage has become saturated, fuel vapor purge can be enabled as long as the emission control device can tolerate increased temperature. In this way, increased fuel vapor purge time is obtained while keeping the emission control device within acceptable temperature limits. Using Cylinder Fuel Vapor Concentration to Control A Second Emission Device Temperature Downstream of A First Emission Control Device In addition, heat generated by purging fuel vapors during stratified operation can also be used to control temperature of a second emission control device downstream of the emission control device where the exothermic reaction is taking place. In other words, the heat generated in the upstream device also affects the downstream emission control device temperature and thus can be used to control the temperature of the downstream emission control device. While controlling downstream device temperature, limits on control authority for limiting exothermic reaction in the upstream device are necessary to prevent upstream device temperature from becoming greater than a maximum allowable device temperature. In this configuration, fuel vapor purge is controlled according to a difference between a desired minimum temperature for the downstream emission control device and actual temperature of the downstream emission control device. Also, combined temperature control is possible where fuel vapor purge is controlled to maintain both temperature of the upstream and downstream emission control device. In this configuration, fuel vapor is controlled according to both the difference between a desired minimum temperature for the downstream emission control device and actual temperature of the downstream emission control device and the difference between a desired minimum temperature for the upstream emission control device and actual temperature of the upstream emission control device. Discontinuing Stratified Fuel Vapor Purge Based on Total Fuel Used to Produce the Current Desired Torque. By injecting fuel vapors into the engine during stratified operation and allowing them to pass through unburned to maintain emission control device temperature, stratified operation is extended, thus giving a fuel economy benefit. However, if the total amount of fuel used in this operation mode, including fuel vapor and fuel injected to the form strata that are burning, is greater than the amount of fuel that would be used during homogeneous operation to produce equal engine torque, then fuel economy is degraded by continuing stratified operation. Stated another way, when the stratified mode no longer provides a fuel savings because of the additional fuel vapor injected to maintain temperature of the emission control device, the engine air/fuel operating mode is switched to the homogeneous mode thereby maximizing fuel economy. In addition, fuel vapor purge during the homogenous mode is still allowed since the additional fuel vapor will burn and produce engine torque. To determine the mode, the following criteria is used: ρ f m p + m f > m f stoich where, ( m ˙ f stoich ) is the amount of fuel necessary during homogenous operation to produce equal engine torque to that produced by actual fuel flow rate from the fuel injectors m ˙ f during stratified mode. As the engine switches to the homogeneous mode, the new fuel flow rate from the fuel injectors ( m ˙ f h ) is found as: m f h = m f stoich - ρ f m p when fuel vapor purge is continued in the homogenous mode. Referring now to Figure 2, a routine for controlling temperature (Tcat) of catalyst 70 is described. First, in step 210 a determination is made as to whether engine 10 is operating in a stratified mode where fuel is injected directly into cylinder 30 during a compression stroke. When the answer to step 210 is YES, a determination is made as to whether temperature Tcat of catalyst 70 is between threshold values T1 and T2. Threshold value T2 represents an upper level above which catalyst 70 is operating a peak efficiency and thus control of temperature (Tcat) is not required. Temperature threshold T1 represents a lower level below which catalyst 70 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. When catalyst temperature Tcat is within this range, the routine continues to step 214, where the fuel vapor concentration (ρ fc ) in the cylinder is calculated, as will be described later herein with particular reference to Figure 3. Continuing with Figure 2, a temperature error (e) is calculated in step 216 based on a desired temperature (Td) of catalyst 70 and the actual temperature (Tcat) of catalyst 70. Then, in step 218, an initial control value (PRG_temp) is calculated based on a function (f) of error (e). In a preferred embodiment, function (f) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Then, in step 220, the initial control value (PRG_temp) is clipped based on the calculated fuel vapor concentration (ρ fc ) in the cylinder, as described later herein with particular reference to Figure 4. This operation prevents the temperature controller from adding too much fuel vapor from fuel system 130 and creating a combustible fuel vapor concentration in the cylinder. Finally, in step 222, control signal PRG is calculated based on the clipped value (PRG_c). Referring now to Figure 3, a routine for calculating the concentration of fuel vapors from fuel system 130 (ρ f ) and cylinder fuel vapor concentration (ρ fc ) is described. First, in step 310, the concentration of fuel vapors from fuel system 130 is calculated as: ρ f = m p + m a - λ S m f m p (1+λ S ) Then, in step 312, the cylinder fuel vapor concentration (ρ fc ) is calculated as: ρ fc = m p ρ f ( m p + m a ) where m ˙ p is the total purge flow rate, m ˙ f is the fuel flow rate from the fuel injectors, m ˙ a is fresh charge measured by the air flow meter, λ is the measured relative air/fuel ratio from the UEGO sensor, and S is the stoichiometric air/fuel ratio. Total purge flow rate, m ˙ p is determined based on the previous control signal PRG where: m p = g ( PRG ) where (g) is a predetermine function relating command signal PRG to total flow rate, m ˙ p . Thus, it is possible to estimate the actual fuel vapor concentration from fuel system 130 and cylinder fuel vapor concentration from available measurements. Referring now to Figure 4, in step 410 a determination is made as to whether purge concentration is greater than the maximum allowable purge concentration (ρ fc MAX ) to guarantee that the fuel vapors pass the cylinder unburned and react exothermically in catalyst 70. Also, a safety factor, SF is also included. When the answer to step 410 is NO, the clipped control value (PRG_c) is set to initial control value (PRG_temp) in step 412. Thus, when the concentration is less than that which will burn in the cylinder, the temperature controller according to Figure 2 is allowed full authority to change fuel vapor flow through valve 134. Continuing with Figure 4, when the answer to step 410 is YES, a critical purge flow ( m ˙ P crit ) is calculated according to the following equation: m P crit = ρ fc max m a (1+λ S )- m a + λ S m f ρ fc max + λ S ρ fc max - 1 This value represents the maximum allowable total purge flow that gives an unburnable fuel vapor concentration in the cylinder. Next, in step 416, the maximum allowable command signal (PRG_MAX) is calculated based on the critical purge flow ( m ˙ P crit ) and the inverse of function (g) . Finally, in step 418, the clipped value (PRG_c) is set equal to the maximum allowable command signal (PRG_MAX). This prevents the temperature control described by Figure 2 from allowing fuel vapor purge concentration to enter the cylinder that will burn and produce torque. Thus, the system is able to control catalyst temperature while remaining in a stratified mode and keeping combustion torque constant. Referring now to Figure 5, an alternative embodiment is described where purge vapors are controlled during stratified operation to maintain temperature (Ttrp) of a NOx trap 72 downstream of catalyst 70. First, in step 510 a determination is made as to whether engine 10 is operating in a stratified mode where fuel is injected directly into cylinder 30 during a compression stroke. When the answer to step 510 is YES, a determination is made in step 512 as to whether temperature Tcat of catalyst 70 is between threshold values T1 and T2. Threshold value T2 represents an upper level above which catalyst 70 is operating a peak efficiency. Temperature threshold T1 represents a lower level below which catalyst 70 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. In an alternative embodiment, threshold values T1 and T2 can represent threshold temperature of NOx trap 72. In this alternative embodiment, temperature of catalyst 70 Tcat may be too low to support exothermic reaction due to, for example, washout chemistry. However, NOx trap 72 may be within a temperature range to support exothermic reaction because of it different washcoat formulation. Therefore, in this alternative embodiment the temperature range for allowing purge during stratified operation can is based on temperature of both Tcat and Ttrp. When catalyst temperature Tcat is within this range, or in the alternative embodiment, when trap temperature Ttrp is within the range, the routine continues to step 513, where a determination is made as to whether trap temperature Ttrp is less than control threshold temperature Tt1. If the answer to step 512 is YES, the routine continues to step 513 where the fuel vapor concentration (ρ fc ) in the cylinder is calculated as described previously herein with particular reference to Figure 3. Continuing with Figure 5, a temperature error (e) is calculated in step 516 based on a desired temperature (Td) of NOx trap 72 and the actual temperature (Ttrp) of NOx trap 72. Then, in step 518, an initial control value (PRG_temp) is calculated based on a function (f) of error (e). In a preferred embodiment, function (f) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Then, in step 520, the initial control value (PRG_temp) is clipped based on the calculated fuel vapor concentration (ρ fc ) in the cylinder, as described previously herein with particular reference to Figure 4. This operation prevents the temperature controller from adding too much fuel vapor from fuel system 130 and creating a combustible fuel vapor concentration in the cylinder. Finally, in step 522, clipped control signal (PRG_c) is limited based on temperature (Tcat) of catalyst 70, as described later herein with particular reference to Figure 6 or Figure 8. Referring now to Figure 6, a routine for limiting clipped control signal (PRG_c) is described so that temperature (Ttrp) of NOx trap 72 can be controlled to the desired level while preventing temperature (Tcat) from becoming too high. First in step 610, a determination is made as to whether temperature (Tcat) of catalyst 70 is less than a maximum allowable temperature (TuMAX). When the answer to step 610 is YES, control signal PRG is calculated based on the clipped value (PRG_c). Otherwise, control signal PRG is calculated based on the clipped value (PRG_c) and a function (f2) of maximum allowable temperature (TuMAX) and temperature (Tcat) of catalyst 70. In a preferred embodiment, function (f2) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Referring now to Figure 7, another alternative embodiment is described where purge vapors are controlled during stratified operation to maintain both temperature (Ttrp) of a NOx trap 72 downstream and temperature (Tcat) of catalyst 70. First, in step 710 a determination is made as to whether engine 10 is operating in a stratified mode where fuel is injected directly into cylinder 30 during a compression stroke. When the answer to step 710 is YES, the routine continues to step 514, where the fuel vapor concentration (ρ fc ) in the cylinder is calculated, as described previously herein with particular reference to Figure 3. Then, in step 712, a determination is made as to whether temperature Tcat of catalyst 70 is between threshold values T1 and T2. Threshold value T2 represents an upper level above which catalyst 70 is operating a peak efficiency. Temperature threshold T1 represents a lower level below which catalyst 70 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. When the answer to step 712 is YES, a catalyst temperature error (e) is calculated in step 714 based on a desired catalyst temperature (Tdcat) of catalyst 70 and the actual temperature (Tcat) of catalyst 70. Continuing with Figure 7, in step 716 a determination is made as to whether temperature Ttrp of NOx trap 72 is between threshold values T1' and T2'. Threshold value T2' represents an upper level above which NOx trap 72 is operating a peak efficiency. Temperature threshold T1' represents a lower level below which NOx trap 72 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. When the answer to step 716 is YES, a trap temperature error (e') is calculated in step 718 based on a desired trap temperature (Tdtrp) of NOx trap 72 and the actual temperature (Ttrp) of NOx trap 72. Otherwise, trap temperature error (e') is set to zero in step 720. Then, in step 722, from either step 718 or 720, a total error (etot) is calculated from both trap temperature error (e') and catalyst temperature error (e). Then, in step 724 an initial control value (PRG_temp) is calculated based on a function (f) of total error (etot). In a preferred embodiment, function (f) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Then, in step 726, the initial control value (PRG_temp) is clipped based on the calculated fuel vapor concentration ρ fc ) in the cylinder, as described previously herein with particular reference to Figure 4. This operation prevents the temperature controller from adding too much fuel vapor from fuel system 130 and creating a combustible fuel vapor concentration in the cylinder. Finally, in step 728, clipped control signal (PRG_c) is limited based on temperature (Tcat) of catalyst 70, as described previously herein with particular reference to Figure 6. If the answer to step 712 is NO, then a determination is made in step 740 as to whether temperature Ttrp of NOx trap 72 is between threshold values T1' and T2'. When the answer to step 740 is YES, trap temperature error (e') is calculated in step 742 based on a desired trap temperature (Tdtrp) of NOx trap 72 and the actual temperature (Ttrp) of NOx trap 72. Then, in step 744, catalyst temperature error (e) is set to zero. Otherwise, trap temperature error (e') is set to zero and catalyst temperature error (e) is set to zero in step 746. Accordingly, both emission control device temperatures are maintained above a value representing peak catalyst efficiency using unburned fuel vapor purge. Referring now to Figure 8, a routine for limiting clipped control signal (PRG_c) is described so that temperature (Ttrp) of NOx trap 72 can be controlled to the desired level while preventing temperature (Tcat) from becoming too high or stratified operation is discontinued if purge flow is too low. First, in step 810, a determination is made as to whether temperature (Tcat) of catalyst 70 is less than a maximum allowable temperature (TuMAX). When the answer to step 810 is YES, intermediate control signal PRG_S is calculated based on the clipped value (PRG_c). Otherwise, intermediate control signal PRG_S is calculated in step 814 based on the clipped value (PRG_c) and a function (f2) of maximum allowable temperature (TuMAX) and temperature (Tcat) of catalyst 70. In a preferred embodiment, function (f2) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Then, in step 820, a determination is made as to whether intermediate control signal PRG_S is grater than required fuel vapor purge REQ_PRG. Required fuel vapor purge REQ_PRG is determined so that fuel system 130 does not become oversaturated with fuel vapors. When the answer to step 820 is NO, then additional fuel vapor purge is required. Since fuel vapor purge cannot be increased in the current mode without increasing engine torque or emission control device temperature, engine 10 is switched to homogenous operation in step 822. In an alternative embodiment, engine 10 is switched a split mode where both a homogeneous mixture and stratified mixture, both of which burn in the engine cylinders, are formed. Referring now to Figure 9, a routine for controlling temperature (Tcat) of catalyst 70 is described. First, in step 910, a determination is made as to whether engine 10 is operating in a stratified mode where fuel is injected directly into cylinder 30 during a compression stroke. When the answer to step 910 is YES, a determination is made as to whether temperature Tcat of catalyst 70 is between threshold values T1 and T2. Threshold value T2 represents an upper level above which catalyst 70 is operating a peak efficiency and thus control of temperature (Tcat) is not required. Temperature threshold T1 represents a lower level below which catalyst 70 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. When catalyst temperature Tcat is within this range, the routine continues to step 914, where the fuel vapor concentration (ρ fc ) in the cylinder is calculated, as will be described later herein with particular reference to Figure 3. Continuing with Figure 9, a temperature error (e) is calculated in step 916 based on a desired temperature (Td) of catalyst 70 and the actual temperature (Tcat) of catalyst 70. Then, in step 918, an initial control value (PRG_temp) is calculated based on a function (f) of error (e). In a preferred embodiment, function (f) represents a proportional, integral, and derivative controller, known to those skilled in the art as a PID controller. Then, in step 920, the initial control value (PRG_temp) is clipped based on the calculated fuel vapor concentration (ρ fc ) in the cylinder, as described previously herein with particular reference to Figure 4. This operation prevents the temperature controller from adding too much fuel vapor from fuel system 130 and creating a combustible fuel vapor concentration in the cylinder. Then, in step 922, a determination is made as to whether clipped value (PRG_c) is less than a required purge value to prevent saturation of fuel system 130. If the answer is YES, then in step 924, stratified operation is discontinues. Thus, engine 10 is operated in homogenous mode and purging is allowed at the required rate. Otherwise, in step 930, control signal PRG is calculated based on the clipped value (PRG_c). Referring now to Figure 10, a routine for enabling fuel vapor purging is described. First, in step 1010, a determination is made as to whether engine 10 is operating in a stratified mode where fuel is injected directly into cylinder 30 during a compression stroke. When the answer to step 1010 is YES, a determination is made in step 1012 as to whether temperature Tcat of catalyst 70 is between threshold values T11 and T22. Threshold value T22 represents an upper level above which efficiency of catalyst 70 degrades. Temperature threshold T11 represents a lower level below which catalyst 70 cannot support an exothermic reaction between unburned fuel vapors and excess oxygen. Continuing with Figure 10, when the answer to step 1012 is YES, a determination is made in step 1014 as to whether catalyst temperature Tcat is in a lower portion of an allowable purge temperature range defined by T11 and T22, where parameter X represents a predetermined percentage of the allowable purge temperature range. Parameter X is based on engine operating conditions such as, for example, engine fresh air flow. When the answer to step 1010 is NO or step 1014 is YES, fuel vapour purging is enabled in step 1016. Otherwise, in step 1018, fuel vapour purging is disabled. This concludes a description of an example in which the invention is used to advantage. Those skilled in the art will recognise that many modifications may be practised without departing from the spirit and scope of the invention. For example, the invention can be carried out when operating in a purely stratified mode or when in a split mode, where both a stratified and homogenous mixture are formed. In addition, various emission control devices can be substituted for either catalyst 70 or trap 72. For example, a second trap could be used in place of catalyst 70. In this example, the routines using temperature of catalyst 70 would now use temperature of the second trap.

Claims: A method for controlling fuel vapour purge entering an engine (10) having multiple chambers (30) coupled to an emission control device (70, 72), in which the method comprises the steps of operating the engine(10) in a stratified mode where fuel is injected during a compression stroke of the engine and purging fuel vapours into the combustion chambers (30) characterised in that the method further comprises limiting the purged fuel vapours to be less than a maximum value based on cylinder fuel vapour concentration. A method as claimed in Claim 1, wherein said purging step further comprises purging fuel vapours into the combustion chambers (30) so that an emission control device temperature approaches a desired emission control device temperature. A method as claimed in Claim 1 or in Claim 2 wherein said purging step further comprises purging fuel vapours into the combustion chamber when an emission control device temperature is less than a predetermined upper threshold value. A method as claimed in any of Claims 1 to 3 wherein said cylinder fuel vapour concentration is based on a fuel injection amount, an engine airflow, a total purge flow rate, and an exhaust air/fuel ratio. A method as claimed in any of Claims 1 to 4 wherein said purging step further comprises purging fuel vapours into the combustion chambers so that they will pass through the chambers unburned, thereby providing unburned hydrocarbons and excess oxygen to react exothermically and generate heat in the emission control device. A method as claimed in Claims 1 to 5 further comprising the step of determining a desired total purge flow based on said maximum value and a difference between an emission control device temperature and a desired emission control device temperature. A method as claimed in Claim 6 wherein a purge flow control valve (134) is provided and the method further comprises the step of adjusting the purge flow control valve (134) based on said desired total purge flow. A control method as claimed in any of claims 1 to 7 wherein the method further comprises providing an indication of temperature of the emission control device, determining a fuel vapour concentration in the combustion chambers and controlling the fuel vapours inducted into the combustion chambers (30) based on said temperature and said fuel vapour concentration. A method as claimed in claim 8 wherein a purge control valve (134) is provided to control the amount of fuel vapours being purged. A method as claimed in claim 9 wherein the method further comprises the step of adjusting said purge control valve (134) based on said temperature.

Inventors: KERNS JAMES MICHAEL, KERNS, JAMES MICHAEL
Applicants: FORD GLOBAL TECH INC, FORD GLOBAL TECHNOLOGIES, INC.
Application year: 2000
Main classification: F02D41
IPC codes: F02D41