Abstract:
A nitrous oxide trap temperature control system for desulfating the trap uses and engine with some cylinders operating with lean combustion and some cylinders operating with rich combustion. The lean and rich combustion gases are combined to form an mixture which is fed to the trap to provide an exothermic reaction. The desired lean and rich air/fuel ratios of the respective lean and rich cylinders are limited depending on trap temperature and incremental heat addition to prevent inadvertently decreasing trap temperature.

Description:
FIELD OF THE INVENTION 
     The invention relates to a system and method for controlling the temperature of an emission control device during sulfur purging. 
     BACKGROUND OF THE INVENTION 
     Engine systems are known which operate the engine with lean combustion, or a lean air/fuel ratio, to improve fuel economy. To accommodate lean burn conditions, emission control devices, such as nitrous oxide (NOx) traps, are used to adsorb nitrous oxide emissions produced during lean operation. Adsorbed nitrous oxide is periodically purged by operating the engine with rich combustion, or a rich air/fuel ratio. 
     During normal lean and rich operation, sulfur contained in the fuel can become trapped in the emission control device. This gradually degrades the emission device capacity for storing nitrous oxide, as well as the device efficiency. To counteract the sulfur effect, various sulfur decontamination methods are available. 
     One method for sulfur decontamination requires elevating the emission control device temperature to a predetermined value. Then, additional fuel is injected while the catalyst is at this elevated temperature to reduce the sulfur stored in the device. The temperature of the device is raised by operating some of the cylinders lean and some of the cylinders rich. When the lean and rich exhaust gasses meet in the device, exothermic reactions takes place, thereby releasing heat to increase the device temperature. The lean and rich exhaust gases are kept at certain desired lean and rich air/fuel ratios to maintain the average air/fuel ratio of the mixed exhaust gases at a desired air/fuel ratio. The desired lean and rich air/fuel ratios are determined in table look-up fashion with various correction factors. An exhaust gas air/fuel ratio sensor is relied upon to correct the desired lean and rich air/fuel ratios for control errors in the correction factors. Such a method is described in U.S. Pat. No. 5,657,625. 
     The inventors herein have recognized a disadvantage with the above approach. When the desired lean and rich air/fuel ratios are adjusted to control trap temperature, poor control is achieved. In particular, when the trap is at a low temperature, a large difference between the rich and lean air/fuel ratios is desired to rapidly increase temperature. However, when the trap is at a low temperature and the air/fuel ratio difference is increased, an initial drop in temperature is experienced because it takes a certain amount of time for the exothermic reaction to begin. Thus, the trap temperature can drop below the light off temperature. At this point, the temperature continues to drop since the exothermic reaction is no longer sustainable due to the trap being below the light off temperature. 
     Another disadvantage encountered when using the above approach is that if the air/fuel ratio difference between the rich and lean cylinders is made too large, the trap temperature can drop even when well above the light off temperature. This is because the additional exothermic heat from the air/fuel ratio difference is not large enough to counteract the lower exhaust temperature caused by operating lean of, or rich of, stoichiometry. 
     SUMMARY OF THE INVENTION 
     An object of the invention claimed herein is to provide a system and method for controlling cylinder air/fuel ratios for desulfating an emission control device, whereby the emission control device is heated by operating some cylinders of an engine lean and some cylinders of an engine rich. 
     The above object is achieved, and disadvantages of prior approaches overcome, by a method for controlling temperature of an emission control device located in an exhaust passage of an internal combustion engine having at least a first and second cylinder, the method comprising the steps of generating a desired lean air/fuel ratio for the first cylinder and a desired rich air/fuel ratio for the second cylinder based on the emission control device temperature, limiting said desired lean and rich air/fuel ratios based on said emission control device temperature, operating the first cylinder at said desired lean air/fuel ratio, and operating the second cylinder at said desired rich air/fuel ratio. 
     By limiting the desired lean and rich air/fuel ratios, it is possible to prevent inadvertent trap temperature changes in an undesirable direction. In other words, at low trap temperatures, the lean and rich air/fuel ratios are clipped at the point where maximum temperature increase is achieved. Allowing the lean and rich air/fuel ratios to be set beyond this value results in less than optimal temperature control and even temperature changes in an undesirable direction. By changing the limits with temperature, maximum control is always available, resulting in precise and rapid temperature control. 
     An advantage of the present invention is improved nitrous oxide trap temperature control. 
     Another advantage of the present invention is improved nitrous oxide conversion efficiency by improved desulfation. 
     Other objects, features and advantages of the present invention will be readily appreciated by the reader of this specification. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The objects and advantages described herein will be more fully understood by reading an example of an embodiment in which the invention is used to advantage, referred to herein as the Description of Preferred Embodiment, with reference to the drawings, wherein: 
     FIG. 1 is a block diagram of an embodiment wherein the invention is used to advantage; and 
     FIGS. 2-10 are high level flow charts of various operations performed by a portion of the embodiment shown in FIG.  1 . 
    
    
     DESCRIPTION OF PREFERRED EMBODIMENT 
     FIG. 1 shows internal combustion engine  10 , comprising multiple cylinders coupled to intake manifold  11 . The engine cylinders are capable of operating within a range of air/fuel ratio ranging from a lean limit to a rich limit. FIG. 1 shows two cylinders operating at a lean air/fuel ratio and two cylinders operating at a rich air/fuel ratio. The cylinders of engine  10  receive air from intake manifold  11  under control of throttle plate  14 . The rich cylinders receive fuel from injectors  20  and  22 . The rich cylinders receive fuel from injectors  24  and  26 . The rich cylinders produce exhaust gas that has unburned hydrocarbons and carbon monoxide while the lean cylinders produce exhaust flow that has excess oxygen. The rich exhaust gas exits the rich cylinders through rich manifold  30  and pass through first three way catalyst  32 . The lean exhaust gas exits the lean cylinders through lean manifold  34  and pass through second three way catalyst  36 . Rich and lean gases then come together to form an exhaust mixture with a exhaust gas mixture air/fuel ratio before entering lean NOx trap  40 . The catalytic activity of trap  40  promotes an exothermic chemical reaction from the exhaust mixture formed of both lean and rich gases, resulting in catalyzed combustion, the generation of heat, and the increase of temperature of trap  40 . 
     While the preferred embodiment employs two cylinders operating rich and an equal number of cylinders operating lean, various alternative embodiments are possible. For example, any total number of cylinders may be used with the number of lean and rich cylinders also being variable. For example, an 8 cylinder engine may have 5 cylinders operating lean with 3 cylinders operating rich. In either equally or unequally divided systems, the desired lean and rich air/fuel ratios are determined as will be described later herein with particular reference to FIGS. 2-10. 
     Controller  12  is shown in FIG. 1 as a conventional microcomputer including: microprocessor unit  102 , input/output ports  104 , read-only memory  106 , random access memory  108 , and a conventional data bus. Controller  12  is shown receiving various signals from sensors  120  coupled to engine  10 . In addition, controller  12  receives an indication of trap  40  temperature (T) from temperature sensor  42 . Alternatively, temperature (T) may be estimated using various methods known to those skilled in the art. Controller  12  also sends signal fpwr to fuel injectors  20  and  22  and sends signal fpwl to fuel injectors  24  and  26 . 
     FIGS. 2-9 are high level flow charts of various operations performed for desulfating trap  40 . These routines are executed when it has been determined that proper conditions exist for trap desulfation. Various methods are known for determining entry conditions, such as, for example, when vehicle speed is greater than a predetermined value and nitrous oxide trapping efficiency is less than a predetermined value. Other conditions including engine speed, engine load, and gear ratio may be used. In general, trap desulfation is performed when trap  40  is saturated with sulfur and degraded operation has been detected or is suspected. Also, a minimum trap temperature is required to guarantee the that hydrocarbons and carbon monoxide will be oxidized by the excess oxygen as described later herein. 
     Referring now to FIG. 2, a routine for projecting temperature (T) of trap  40  is described. First, in step  210 , the actual temperature is read from sensor  42 . As previously described herein, the actual trap temperature may be estimated using various methods known to those skilled in the art. Then, in step  212 , the projected change in trap temperature (ΔT) is calculated based on the difference between the current temperature value (T) and the previous temperature value (Tpre) divided by the sample time (Δtime). Then, in step  214 , the projected change in trap temperature (ΔT) is clipped between maximum and minimum values, where the maximum and minimum values are predetermined calabratable values. Then, in step  216 , the clipped projected change in trap temperature (ΔT) is added to the current temperature value (T) to form the predicted temperature value (Tp). In step  218 , the previous temperature (Tpre) is set to the current temperature value (T). 
     Referring now to FIG. 3, a routine for determining a feedback amount for controlling trap temperature (T) to a desired temperature (Tdes) is described. In step  310 , the desired desulfation temperature (Tdes) for the trap  40  is determined. In a preferred embodiment, this is a predetermined constant value. However, the desired temperature may be adjusted based on various factors, such as, for example, trap efficiency, trap age, or any other factor known to those skilled in the art to affect optimum temperature for desulfation. Then, in step  312 , the temperature error (e) is calculated from the difference between desired temperature (Tdes) and predicted temperature (Tp). In step  314 , the temperature error (e) is processed by a proportional and integral feedback controller (known to those skilled in the art as a PI controller) to generate a correction (λLFB) to the desired lean air/fuel ratio for the cylinders operating with lean combustion. 
     Referring now to FIG. 4, a routine is described for calculating a feed forward correction value for the desired lean air/fuel ratio that accounts for engine load changes. First in step  410 , the engine load is read. In a preferred embodiment, engine load is represented by the ratio of engine airflow, determined from, for example, a mass air flow meter, to engine speed. Then, in step  412 , the desired lean air/fuel ratio adjustment (λLLA) due to engine load is calculated as the product of load and predetermined gain (Gl). The load correction is necessary because engine load has a strong influence on heat added to trap  40 . For example, if the lean and rich cylinder air/fuel ratios are kept constant, but a large increase in airflow occurs, then substantially more heat is added to trap  40 . 
     Referring now to FIG. 5, a routine for determining a desired rich bias to add to the desired lean air/fuel ratio is determined. The desired rich bias is used for giving a slight rich bias to the mixture air/fuel ratio. This slightly rich mixture releases the stored sulfur oxide in the trap when the trap is at the proper desulfation temperature as described herein. In addition, this rich bias also creates additional exothermic heat which tends to further increase the trap temperature. To account for this in a feed forward fashion, the rich bias is also used to adjust (decrease) the desired difference in lean and rich air/fuel ratios. Thus, the additional heat added from the rich bias is counteracted in a feed forward way by providing less exothermic heat from the lean and rich exhaust gases. In this way, trap temperature can be more accurately controlled to a desired temperature, even when adding the rich bias. 
     First, in step  510 , a determination is made as to whether trap temperature (T) is greater than or equal to the desired temperature (Tdes). If the answer to step  510  is NO, then the parameter (time_at_temp), which tracks the time duration the trap is at or above the desired temperature, is adjusted as shown in step  512 . Otherwise, the parameter time_at_temp is adjusted as shown in step  514 . Then, in step  516 , a determination is made as to whether trap temperature (T) is greater than or equal to the desired temperature (Tdes) and if parameter time_at_temp is greater than predetermined value min_time. The value min_time represents the minimum time for which the trap temperature (T) is above or equal to the desired temperature (Tdes) before desulfation is allowed. If the answer to step  516  is NO, then the rich bias adjustment (λLRB) is set to zero in step  518 . Otherwise, the rich bias adjustment value (λLRB) is calculated based on the desired rich bias (RB) and the parameter time_at_temp in step  520 . In general, the time_at_temp value is used to allow the entire trap material to achieve the desired temperature (Tdes). For example, a rolling average filter may be used to calculated (λLRB). 
     Referring now to FIG. 6, a routine for clipping the desired lean air/fuel ratio is described. First, in step  610 , a determination is made as to whether the trap temperature (T) is greater than the sum of a lower control limit (TLO) and a safety factor (SF). If the answer to step  610  is NO, then in step  612 , the temporary value (temp) is set to the stoichiometric air/fuel ratio (S). This prevents operation of some cylinders lean and some cylinders rich below the light off temperature of the trap. In other words, operating with lean and rich combustion for temperature control below a light off temperature will actually cause the temperature of trap  40  to reduce. This will give a reversal of controls and cause the controller to become unstable, resulting in degraded performance. 
     Continuing with FIG. 6, if the answer to step  610  is YES, then in step  614 , a determination is made as to whether trap temperature (T) is less than high temperature limit (high_limit), where high_limit is a temperature greater than the sum of lower control limit (TLO) and safety factor (SF). High_limit represents a limit below which closed loop control is not used to prevent poor controlability. If the answer to step  614  is YES, then in step  616 , the temporary value (temp) is set to a predetermined constant value (λLL). This predetermined constant value accomplishes the following advantage. If closed loop temperature control is attempted below a certain temperature, the trap can initially cool below the light off temperature. Thus, unless the control is performed according to the present invention, an infinite cycle is encountered where trap temperature is never controlled to the desired temperature. Constant value (λLL) is determined based on experimental testing to provide a certain acceptable temperature increase rate of trap  40 . 
     Continuing with FIG. 6, if the answer to step  614  is NO, then temporary value (temp) is set to a the desired lean air/fuel ratio (XL) determined in step  710 , described later herein with particular reference to FIG.  7 . Then, in step  619 , the temporary value is clipped to a maximum limit value L 1 . Maximum limit value L 1  represents the lean air/fuel ratio at which maximum incremental heat is added to increase trap temperature described later herein with particular reference to FIG.  10 . If the alternative embodiments are being employed, the maximum limit value can represent the rich air/fuel ratio, or the air/fuel ratio difference, at which maximum incremental heat is added to increase trap temperature. Additional limits may also be used to prevent the engine from experiencing engine misfire or other engine stability limits. For example, the maximum lean air/fuel ratio can be clipped based on engine mapping data so that engine misfire does not occur. In step  1020 , the clipped desired lean air/fuel ratio is set to temporary value (temp). 
     As described herein, if the order of operations are reversed and the desired rich air/fuel ratio is first calculated, then the routine above can be used by simply substituting the desired rich air/fuel ratio for the desired lean air/fuel ratio and appropriate adjustment of the calibration parameters. Similarly, the air/fuel ratio span can be used by simple substitution. 
     Referring now to FIG. 7, the desired lean air/fuel ratio (λL) is calculated for controlling fuel injection to the lean cylinders, where the parameter λ indicates a relative air/fuel ratio, as is known to those skilled in the art. In step  710 , the desired lean air/fuel ratio (λL) is calculated, where GRB is a predetermined gain. In a preferred embodiment, the desired lean air/fuel ratio (λL) is calculated as shown below: 
     
       
         λ L =(λ LRB*GRB−λLLA+λLFB )  
       
     
     Referring now to FIG. 8, the desired rich air/fuel ratio (λR) is calculated based on the desired lean air/fuel ratio. The desired rich air/fuel ratio is used for controlling fuel injection to the rich cylinders. First, in step  810 , the clipped desired lean air/fuel ratio (λLd) is read from step  620  described previously herein with respect to FIG.  6 . Then, in step  812 , the desired exhaust gas mixture air/fuel ratio (λdes) is determined, where again the parameter (λ) refers to a relative air/fuel ratio. In step  814 , the ratio (R) of the number of lean cylinders to the number of rich cylinders is calculated. Then, in step  816 , the desired rich air/fuel ratio (λR) is calculated according to the equation below:          λ                 R     =       λ                 des   *   λ                 Ld         λ                   Ld        (     1   +   R     )         -     λ                 des   *   R                                
     This equation can be simplified when the desired air/fuel ratio is stoichiometric and the ratio (R) is unity to the following equation:          λ                 R     =       λ                 Ld         2   *   λ                 Ld     -   1                              
     In an alternative embodiment, the order of calculation can be reversed with respect the desired lean and rich air/fuel ratios. In other words, the desired rich air/fuel ratio can be calculated based on the feedback correction (λLFB), rich bias adjustment (λRB), and lean air/fuel ratio adjustment (λLLA) and clipped in a similar fashion to the desired lean air/fuel ratio. Then, the desired lean air/fuel ratio is calculated according to the following equation:          λ                 L     =       λ                 des   *   λ                 Rd   *   R         λ                   Rd        (     1   +   R     )         -     λ                 des                                
     In another alternative embodiment, the air/fuel ratio span, the difference between the lean air/fuel ratio and the rich air/fuel ratio, can be used to control trap temperature (T). In this case, the desired air/fuel ratio span (Δλ) is determined based on temperature error and the feed forward load correction and feed forward rich bias correction. The desired air/fuel ratio span (Δλ) can then be clipped in a similar fashion to the clipping of the desired lean air/fuel ratio. Then, the desired lean and rich air/fuel ratios can be determined as shown by the equations below:          λ                 L     =       1   2          (       Δ                 λ                 d     +     λ                 des     +             R        (       Δ                 λ                 d     -     λ                 des       )       2     +       (       Δ                 λ                 d     +     λ                 des       )     2             R   +   1           )                              
     For the simple case where the desired exhaust gas mixture air/fuel ratio (λdes) is stoichiometric and the ratio (R) is unity then the following simpler equation can be used:          λ                 L     =       1   2     +       Δ                 λ                 d     2     +         1   +       (     Δ                 λ                 d     )     2         2                              
     Then, the desired rich air/fuel ratio is calculated simply from the following equation: 
     
       
         λ R=λL−Δλd    
       
     
     Referring now to FIG. 9, a routine for calculating fuel pulse width signals (fpwL and fpwR) is described. In step  910 , the lean fuel pulse width is calculated based on engine airflow from the mass air flow sensor (MAF), the number of lean and rich cylinders, the stoichiometric air/fuel ratio (S), and the desired lean air/fuel ratio (λL). Then, in step  912 , the rich fuel pulse width is calculated based on engine airflow from the mass air flow sensor (MAF), the number of lean and rich cylinders, the stoichiometric air/fuel ratio (S), and the desired rich air/fuel ratio (λR) and the rich bias correction (λLRB). 
     Referring now to FIG. 10, a graph is shown representing an approximate relationship between incremental heat added to the trap versus lean air/fuel ratio (λL), air/fuel ratio difference (Δλ), or inverted rich air/fuel ratio (λR) −1 . The graph shows that a certain value represents a maximum heat addition. Increasing beyond this point results in less, or even negative, heat addition to the trap. Thus, the control should be limited to the value L 1 , to prevent control instabilities and less than optimal control. The incremental heat addition to the trap may be determined relative to stiochiometry. The incremental heat addition takes into account both the cooling off of engine out exhaust gas temperature due to operation away from stoichiometry as well as the heat addition from the exothermic reaction proportional to the difference in the lean and rich air/fuel ratios. 
     Although several examples of embodiments which practice the invention have been described herein, there are numerous other examples which could also be described. For example, the invention may be used to advantage with both direct injection engines in which nitrous oxide traps may be used. The invention is therefore to be defined only in accordance with the following claims.