CHARGING AND EMISSION CONTROLLING A TURBOCHARGED

ENGINE SYSTEM:

TECHNICAL HELD

[0001] Embodiments of the present disclosure: relate to turbocharged engine systems. Further embodiments of the present disclosure relate to methods of charging and. emission controlling turbocharged engine systems.

BACKGROUND

[01)02 j One of the most important pollutant of internal combustion engines is the NO _X (nitrogen, oxide). This pollutant forms at high temperature and. when O ₂ is in excess, which goes generally with good, engine efficiency. Thus, reducing NO _x leads generally to efficiency degradation. In other words, the lower the NO _x emissions, the lower the efficiency. Conventional measures to reduce the NO _x after the engine outlet called Exhaust After Treatment ( EAT) are complex, bulky and expensive.

[0003 ] Several solutions already exist for lowering the raw NO _x emissions, e.g. at the engine outlet, and before the optional EAT system. An exemplary solution is Exhaust Gas. Recirculation. (EGR), which consists in recirculating a fraction of the exhaust gases toward the intake. The purpose is to admit inert gases (CO ₂ ) with air into the cylinders, in a way to reduce the maximal cycle temperature during the combustion (slower combustion and thermal capacity effect). This technology leads to aging problems and can strongly reduce the engine efficiency. For lean bum gas engines, EGR can. also reduce the amount of air, and thus the excess of O ₂ , at given load, and therefore reduces the amount of possible NO _x emissions. [0004] Another solution is water injection m the intake or directly m the cylinders (mostly the same idea as for EGR, but with HaO instead of CO ₂ ). This technology requires additional tank, pump(s) and circuit, and often gives a mitigated [NCk ; efficiency] trade-offi

[0005 ] Yet another solution is employing a Miller or Atkinson vahc timing combined with high performance super charging or turbocharging system. Here, the idea is to artificially short down the intake phase by closing the intake valve while the piston is still breathing (Miller), or to artificially short down the compression stroke, by closing the intake valve while the piston has already started moving upwards (Atkinson), and by simultaneously compensating the lack of air mass by further increasing the boost pressure. Thus, thanks to the higher fraction of the global compression built by super or turbocharging with aftercooler (instead of being carried out by the piston), the temperature at the end of the cylinder compression stroke is lower, leading to a decrease of the maximal combustion temperature and consequently, to a reduced NO _X formation.

[0006] Currently, for increasing efficiency with reduced NO _X emissions a part of the internal combustion engines is equipped with systems enabling operation with Miller timings. With such systems the intake valves arc closed quite early during the intake stroke, thus strongly reducing the cylinders air breathing (volumetric efficiency). In order to maintain the required air mass flow of the engine, a turbocharger is employed for compensating the lack of breathing by providing higher pressure ratio (higher intake receiver density). Often, one more compression stage must be added, leading switching from one- stage to two-stage turbocharging architecture.

|0007| However, the compensation of the above-described lack of engine breathing by the turbocharging system can only be effective once the energy within the exhaust gases at the inlet of the turbochargefrs) turbine(s) is sufficient, which is almost always not the case at low engine speed and/or load. In other words, it is quite ne\ cr possible to keep the Miller timing at low engine speed and/or load because the turbocharging system is not able to compensate the lack of volumetric efficiency as it can do at full engine power. Keeping a Miller timing at low engine speed could also be a problem for starting the engine. Exactly the same difficulties can be faced with a constant Atkinson timing, this problem, the current state of art teaches to employ a variable intake valve train configured for switching from a Miller timing at high speed and/or load to a non-Millcr timing at low speed and/or load. However, variable intake valve train systems have the disadvantage that they are rather complex and expensive. This statement is also valid for an Atkinson timing.

[0009] Accordingly, in view of the above, there is a demand for improved turbocharged engine systems and improved methods of charging and emission controlling turbocharged engine systems which at least partially overcome some of the problems of the state of the art .

SUMMARY

[0010] In light of the above, a turbocharged engine system and a method of charging and emission controlling a turbocharged engine system according to the independent claims are provided. Further, a method of controlling operation and a use of a turbocharging assembly according to embodiments described herein are described. Further aspects, advantages, and features are apparent from the dependent claims, the description, and the accompanying drawings.

[0011 ] According to an aspect of the present disclosure, a turbocharged engine system is provided. The turbocharged engine system comprises a combustion engine hav ing at least one cylinder. Further, the turbocharged engine system comprises at least one inlet valve configured to supply the at least one cylinder with intake air or air-foel-mixture and at least one outlet v alve configured to discharge exhaust from the at least one cylinder. The at least one inlet valve is configured to prov ide a constant cyclical c alve timing between an open state and a closed slate of the at least one inlet v alv e. The constant cyclical valve timing is a Miller timing or Atkinson timing. Additionally, the turbocharged engine system comprises at least one turbocharger hav ing a turbine and a compressor for pressurizing the intake air or air-fuel-mixturc. Further, the turbocharged engine system comprises at least one electrical power conv erter coupled with at least one of the compressor and the turbine. Moreov er, the turbocharged engine system comprises a control dec ice configured for controlling the at least one electrical power converter to provide power to or to take off power from at least one of the compressor and the turbine to achiev e a targeted \ aluc of at least one operational parameter of the combustion engine. The turbine has an effective section S _res T being sized such that a generated power by the turbine provides at least a power required by the compressor to reach the targeted v alue of the at least one operational parameter w ithout using the at least one electrical pow er converter as a motor during non-acccleration operation of the combustion engine.

[0012 ] According to a further aspect of the present disclosure, a method of charging and emission controlling a turbocharged engine system is provided. The turbocharged engine system comprises a combustion engine hav ing at least one cylinder, at least one inlet v alve configured to supply the at least one cylinder with intake air or air-fuel-mixlurc. al least one outlet valve configured to discharge exhaust from the at least one cylinder, at least one turbocharger having a turbine and a compressor for pressurizing the intake air or air-fucl- mixture. at least one electrical power converter coupled with at least one of the compressor and the turbine, a control dev ice configured for controlling the electrical power converter. The turbine has an effective section S _res , _T being sized such that a generated power by the turbine provides at least a power required by the compressor to reach the targeted v alue of the at least one operational parameter w ithout using the at least one electrical power converter as a motor during non-acccleration operation of the combustion engine. The method comprises prov iding a constant ex clical valve timing between an open state and a closed state of the at least one inlet valve. The constant cyclical valve timing is a Miller timing or Atkinson timing. Further, the method comprises controlling the at least one electrical power converter by the control device for providing power to at least one of the compressor and the turbine only during acceleration modes of the combustion engine. Alternatively, or additionally, method comprises controlling the at least one electrical power converter by the control device for talcing power off from at least one of the compressor and the turbine only during non-acceleration modes to achieve the targeted value of at least one operational parameter of the combustion engine.

|0() 13 | Accordingly, compared the state of the art, an improved turbocharged engine system and an improved method of charging and emission controlling a turbocharged engine system are provided. In particular, embodiments as described herein beneficially provide for improved efficiency with reduced NO _X emissions at reduced system complexity and less costs. Additionally, the concept of the turbocharged engine system according to the present disclosure beneficially provides for the possibility to easily retrofit existing engine systems, namely by providing a constant Miller or Atkinson timing in combination with a control device - which can easily be external and added-on (for example during an upgrade procedure) - for controlling an electrical power converter coupled with a turbocharger as described herein. Further, the performance, e.g. the acceleration and the load pick-up ability, of the turbocharged engine system can even be improved due the electrical power converter coupled to the turbocharger.

BRIEF DESCRIPTION OF THE DRAWINGS

[0014] So that the manner in which the above recited features of the present disclosure can be understood in detail, a more particular description of the disclosure, briefly summarized above, may be had by reference to embodiments. The accompanying drawings relate to embodiments of the disclosure and arc described in the following: Fig. 1 shows a schematic view of a turbocharged engine system according to embodiments described herein;

Fig. 2 shows a schematic v icw of a turbocharged engine system according to further embodiments described herein; and Figs. 3 to 6 show block diagrams for illustrating embodiments of a method of charging and emission controlling a turbocharged engine system according to embodiments described herein.

DETAILED DESCRIPTION OF EMBODIMENTS

[0015] Reference will now be made in detail to the various embodiments, one or more examples of which arc illustrated in each figure. Each example is provided by way of explanation and is not meant as a limitation. For example, features illustrated or described as part of one embodiment can be used on or in conjunction with any other embodiment to yield yet a further embodiment, ft is intended that the present disclosure includes such modifications and variations.

[0016] Within the following description of the drawings, the same reference numbers refer to the same or to similar components. Generally, only the differences with respect to the individual embodiments are described. Unless specified otherwise, the description of a part or aspect in one embodiment can apply to a corresponding part or aspect in another embodiment as well.

[0017] With exemplary reference to Fig. 1, a turbocharged engine system 1 according to the present disclosure is described. According to embodiments, which can be combined with other embodiments described herein, the turbocharged engine system 1 includes a combustion engine 10 having at least one cylinder 11 , at least one inlet valve 12 configured to supply the at least one cylinder 11 with intake air or air-foel-mixture (i.e. an intake gas/ intake gas mixture) , and al least one outlet valve 13 configured to discharge exhaust from the at least one cylinder 11. It is to be understood, the intake gas/ intake gas mixture may include at least one of air. fuel, recirculated exhaust gas, and water. The at least one inlet valve 12 is configured to provide a constant cyclical valve timing between an open state and a closed state of the at least one inlet valve. In particular, the expression “at least one inlet valve” can be understood as “at least one inlet valve system”. The constant cyclical valve timing is a Miller timing or Mkinson timing. Additionally, the turbocharged engine system I includes at least one turbocharger 14 having a turbine 15 and a compressor 16 for pressurizing the intake air or air-foel-niixture. Typically, the turbine 15 is configured for recovering enthalpy from the exhaust gases. Further, the turbocharged engine system 1 includes at least one electrical power converter 17 coupled with at least one of the compressor 16 and the turbine 15. Moreover, the turbocharged engine system 1 includes a control device 18 configured for controlling the at least one electrical power converter 17 to proc ide power to or to take off power from at least one of the compressor 16 and the turbine 15 to achieve a targeted value of at least one operational parameter of the combustion engine 10. The turbine 15 has an effective section S _res ,T being sized such that a generated power by the turbine 15 provides at least a power required by the compressor to reach the targeted value of the at least OIK operational parameter without using the at least OIK electrical power converter 17 as a motor during non-acceleration operation of the combustion engine 10.

|()018 | Accordingly, compared to the prior art. an improved turbocharged engine system is provided. In particular, the turbocharged engine system as described herein beneficially provides for improved efficiency with reduced NO\ emissions at reduced system complexity resulting in an ov erall coast reduction. Additionally, the concept of the turbocharged engine system as described herein beneficially proudcs for the possibility to easily retrofit existing engine systems, namely by providing a constant Miller or Atkinson timing in combination with a control device for controlling an electrical power converter coupled with a turbocharger as described herein. Further, embodiments of the turbocharged engine system as described herein beneficially provide for improved performance, particularly improved acceleration and improved load pick-up ability.

[0019] Before various farther embodiments of the present disclosure are described in more detail, some aspects with respect to some terms used herein are explained,

10020 ] In the present disclosure, “at least one cylinder" can be understood in that one or more cylinders may be provided. For example, the combustion engine as described herein may include a number Nc of cylinders, wherein Nc can be selected from the range of 1 < Nc <30.

[0021] In the present disclosure, “at least one an inlet valve” can be understood in that one or more inlet valves may be provided. For example, the at least one cylinder as described herein may include a number NIv of inlet valves, wherein Niv can be selected from the range of 1 < Niv <4.

[00221 In the present disclosure, “at least one outlet valve" can be understood in that one or more outlet valves may be provided. For example, the at least one cylinder as described herein may include a number Nov of outlet valves,wherein NOv can be selected from the range of 1 < Nov <4.

[0023] In the present disclosure. “Miller timing” can be understood as a timing according to the Miller cycle. In the Miller cycle, the inlet valvc(s) is(are) closed earlier within the cycle than it (they) would be in a conventional Diesel or Beau de Rochas / Otto-cycle engine. In effect, the intake process is shortened, and the volumetric efficiency is reduced, leading to a lower trapped air or fuel-air mixture mass in the cylinder (charge) for a given intake receiver air density. Typically, this loss of charge would result in a loss of power. However, in the Miller cycle, this can be compensated for by the use of a supercharger. The supercharger typically will need to be of the positivedisplacement type due to its ability to produce enough boost already at relatively low engine speeds and/or load. Otherwise, the power at low engine speed and/or load the capability for load pick-up will suffer. In the Miller-cycle engine, when the piston is at its bottom-most position, at the beginning of the compression stroke, the cylinder pressure is lower than the intake receiver pressure. This means that the cylinder pressure will be at the same level as the receiver pressure only long enough after having moved upwards from its bottom most position. Thus, in the Miller cycle engine, the piston actually compresses the air or the fuel-air mixture only during the rest of the compression stroke, once the intake valve(s) is(are) closed. The Miller valve timing can be defined as following: when at least one of the intake valve(s) is already closed 20 crank angle degrees before the piston bottom-most position, end of the intake stoke. The definition of closed valve can be “once the considered valve is at a lift equal or under 10% of its max lift”. As example, if the max lift of a given intake valve is 26 mm, the valve is considered dosed as soon as its lift is equal or under 2.6 mm.

[0024] In the present disclosure. “Atkinson timing" can be understood as timing according to the Atkinson cycle. In the Atkinson cycle the inlet valve is held open longer than normal, allowing a reverse flow of intake air or fuel-air mixture toward the intake manifold. The effectis c compression ratio is reduced - for the time the intake air or fuel-air mixture is escaping the cylinder freely rather than being compressed - but the expansion ratio is unchanged (i.e., the compression ratio is smaller than the expansion ratio). The Atkinson valve timing can be defined as following: when at least one of the intake valve(s) is still opened 20 crank angle degrees after the piston botom-most position, end of the intake stroke. The definition of opened valve can be when the considered valve is at a lift superior or equal to 10% of its max lift. As example, if the max lift of a given intake valve is 41 mm, the valve is considered opened if its lift is superior or equal to 4.1 mm.

[00251 It is to be understood that originally, the goal of both Miller and Atkinson cycles was to have an expansion stroke longer than the compression stroke (or equivalent), leading to beter cycle efficiency. Implicitly, and as already explained, especially through combustion maximal temperature reduction, these two cycles finally allow a better compromise [ NOx. efficiency ] on supercharged or turbocharged engines.

[0026] In the present disclosure, “at least one turbocharger” can be understood in that one or more turbochargers may be provided. According toan example, a single turbocharger may provide a one-stage charging system, two turbochargers may provide a two-stage charging system, three turbochargers may provide a three-stage charging system etc. Accordingly, the turbocharged engine system may be provided with number Nrc of turbochargers, wherein Nn can be selected from the range of 1 ≤ N H 14. In case two or more turbochargers are provided, the two or more turbochargers can be arranged in parallel.

10027 ] In the present disclosure, the expression “at least one electrical power converter coupled with at least one of the compressor and the turbine” can be understood in that one or more electrical power com ertcrs can be provided which can be coupled with the compressor and/or the turbine. For example, the at least one electrical power converter can be coupled to the shaft connecting the compressor and the turbine. Accordingly, the at least one electrical power converter may be arranged between the compressor and the turbine of the turbocharger. Such a configuration may also be referred to as e-turbo. Alternativ ely, the at least one electrical power converter may be only coupled to the compressor, e.g. via a shaft, w hich may also be referred to as e- compressor.

[0028] According fc) another example, the at least one electrical power converter may be only coupled to the turbine, c.g. via a shaft, which may also be referred to as c-turbinc. Typically, the at least one electrical power converter is configured for converting electrical power into mechanical power and vice versa. In other words, the at least one electrical power converter can be understood as an electric device configured for recox ering energy by converting mechanical power into electrical power, particularly by electrically braking down the turbine, when the turbine power is larger than the required compressor power, or providing mechanical power when the compressor requires more power than the turbine is able to provide, e.g. from or to the turbocharger, particularly from or to the compressor/turbine,

[0029] In the present disclosure, the expression “a control device configured for controlling the at least one electrical power converter” can be understood as an electronic device capable of controlling the at least one electrical power converter, e.g. by means of a control signal.

|00301 In the present disclosure, “at least one operational parameter of the combustion engine” can be understood as any parameter of the combustion engine during operation which allows for characterizing the operational state of the combustion engine.

[0031] According to embodiments, which can be combined with other embodiments described herein, the cffecthc section S« _s j is S _res = (SR _S ^X S _St )/I ² +• Sst ² ) ^w , wherein Sst is the throat area of a stator of the turbine in cm ² , particularly the throat area of a nozzle ring of the turbine in cm ² , and wherein Siu is the throat area of a rotor of the turbine in cm ² . It is to be understood that the throat area of the stator is the minimum cross-scctional area in the stator. The throat area of the rotor is the minimum cross-sectional area in the rotor.

[0032] According to embodiments, which can be combined with other embodiments described herein, the power from the turbine that should be or is supplied to the compressor is determined by the formula: foe, infer: Mass flow at compressor inlet (kg . s ^-1 ) ^c p, mixture : Specific heat capacity at constant pressure of mixture flowing through compressor (J • kg~ ^f • K ^-1 )

T _Cii „ _let : Total temperature at compressor inlet (K)

Pc, outlet- Total pressure at compressor outlet (bar)

Pc, Met- Total pressure at compressor inlet (bar)

Kniixture- Heat capacity ratio of mixture f lowing through compressor

(specif ic to the mixture) (— )

K„~1.4 n _c : Compressor isentropic efficiency (— )

Pmech- Mechanical losses (IV)

[0033] According to embodiments, which can be combined with other embodiments described herein, the control device 18 is configured to compare an actual value of the at least one operational parameter wi th the targeted value of the at least one operational parameter. Further, the control device 18 is configured to control the at least one electrical power converter 17 when there is a deviation between the actual x aluc and the targeted value. For instance, the actual value of the at least one operational parameter can be a measured value of the at least one operational parameter. According to another example, the actual value can be a calculated v alue from a measured value of the at least one operational parameter.

[0034] With exemplary reference to Fig. 2, according to embodiments, which can be combined with other embodiments described herein, the turbocharged engine system I includes at least one sensor 19 to measure the at least one operational parameter. Typically, the at least one operational parameter is selected from the group including an air mass flow rate Q _in , an air fuel ratio X, an intake pressure p _m . particularly an intake air pressure or an intake air-fuel- mixture pressure, an exhaust temperature Tex. and a NO _X emission rate Q _ou . /Vccordingly. it is to be understood that one or more sensors may be provided configured for measuring the at least one operational parameter. For example, the at least one sensor 19 may include a flow-meter and/or a X-sensor and/or a pressure sensor and/or a temperature sensor and/or a NO _X sensor. [0035] According to embodiments, ’which can be combined with other embodiments described herein, the at least one electrical power converter 17 is configured to be used as motor and/or generator. As exemplarily shown in Fig. 2, according to embodiments, which can be combined with other embodiments described herein, the electrical power converter 17 may include a rotor 171 and a stator 1 72. Typically, the rotor 171 is connected to a shaft 141 connecting the compressor 16 with the turbine 15.

100361 With exemplary reference to Figs. 3 to 6, embodiments of a method 20 of charging and emission controlling a turbocharged engine system 1 according to the present disclosure are described. The turbocharged engine system I includes a combustion engine 10 having at least one cylinder 1 1, at least one inlet valve 12 configured to supply the at least one cylinder 11 with intake air or fuel-air mixture, and at least one outlet valve 13 configured to discharge exhaust from the at least one cylinder 1 1 . Further, the turbocharged engine system 1 includes at least one turbocharger 14 having a turbine 15 and a compressor 16 for pressurizing the intake air or fuel-air mixture. Additionally, the turbocharged engine system 1 includes at least one electrical power converter 17 coupled with at least one of the compressor 16 and the turbine 15. Moreover, the turbocharged engine system 1 includes a control device IS configured for controlling the electrical power converter 17. The turbine 15 has an effective section Snsj being sized such that a generated power by the turbine 15 provides at least a power required by the compressor to reach a targeted value of the at least one operational parameter without using the at least OIK electrical power converter 17 as a motor during non-acceleration operation of the combustion engine 10; According to embodiments, which can be combined with any other embodiments described herein, the effective section Sns,T is mall enough, such that it is not required to have an electric power supply at low loads to reach the targeted value of the at least one operational parameter . This allows to run the engine in case of electrical failure of the at least one electrical power converter (recovery mode). [0037] According to embodiments, ’which can be combined with other embodiments described herein, the method 20 includes providing (represented by block 21 in Figs. 3 to 6) a constant cyclical valve timing between an open state and a closed state of the at least one inlet valve: The constant cyclical valve timing is a Miller timing or Atkinson timing. Further, the method includes controlling (represented by block 22 in Figs. 3 to 6) the at least one electrical power converter 17 by the control device 18 for providing power (represented by block 23 in Figs. 3 to 6) to at least one of the compressor 16 and the turbine 15 only during acceleration modes of the combustion engine 10. Additionally or alternatively, the method includes controlling (represented by block 22 in Figs. 3 to 6) the at least one electrical power converter 17 by the control device 18 fbr taking power off (represented by block 24 in Figs. 3 to 6) from at least one of the compressor 16 and the turbine 15 only during nonacceleration modes to achieve the targeted value of at least one operational parameter of the combustion engine 10. The at least one operational parameter can be an air mass flow rate Qi _n , an air fuel ratio X, an intake pressure pj _n , particularly an intake air pressure or an intake air-fiiel-mixture pressure, an exhaust temperature T _& and a NO _X emission rate Qout. Typically, providing power (represented by block 23 in Figs. 3 to 6) to at least one of the compressor 16 and the turbine 15 includes com crting electrical power into mechanical power. Accordingly, typically taking power off (represented by block 24 in Figs. 3 to 6) from at least one of the compressor 16 and the turbine 15 includes converting mechanical power into electrical power.

|00381 In the present disclosure, acceleration mode can be understood as a mode at which engine power changes at constant or variable engine speed. In other words, an acceleration mode is a mode at which variation of engine power occurs in a given time slot. For example, in the case of a constant engine speed of 1500 rpm, a power increase from 80-100% in 5 seconds. Another example fbr an acceleration inode is in the case of a variable speed engine, a power increase from 20-40% in I minute. [0039] In the present disclosure, non-acceleration mode can be understood as constant engine load and speed operation, i,e. no variation of engine load and speed in a given time slot. For example, in the case of a constant engine speed: of 1000 rpm, a constant engine load of 85®4 during 30 seconds. Another example for a non-acceleration mode is in the case of a variable speed engine, a constant engine load of 40" o and speed during 4 hours.

[0040] With exemplary reference to Figs. 4 to 6, according to embodiments, which can be combined with other embodiments described herein, the method 20 further includes comparing (represented by block 25 in Figs. 4 to 6) an actual value of the at least one operational parameter with the targeted value of the at least one operational parameter and controlling (represented by block 22 in Figs. 4 to 6) the at least one electrical power converter 17 by the control device 18 when there is a deviation between the actual value and the targeted value. In particular, the at least one electrical power converter 17 may be controlled by the control device 18 to minimize the deviation between the actual value and the targeted value in order to achicv c the targeted value of the at least one operational parameter of the combustion engine.

[0041] According to embodiments, which can be combined with other embodiments described herein, the actual value of the at least one operational parameter can be a measured value of the at least one operational parameter. Accordingly, with exemplary reference to Figs. 5 and 6, the method 20 may include measuring (represented by block 26 in Figs. 5 and 6) the actual value of the at least one operational parameter by a sensor 19.

|00421 According to another example, the actual value can be a calculated value which is calculated from a measured value of the at least one operational parameter. Accordingly, with exemplary reference to Fig. 6, the method 20 may include calculating (represented by block 27 in Fig. 6) the actual value of the at least one operational parameter from a measured value of the at least one operational parameter. [0043] Accordingly, in view of the embodiments described herein, it is to be understood that the turbocharged engine system as well as the method of charging and emission controlling a turbocharged engine system arc improxed compared to the state of the art, particularly with respect to system efficiency and NO _x emissions reduction while at the same time providing for a reduced system complexity and thus better costs efficiency. Further it is to be noted, that according to embodiments, which can be combined with any other embodiments described herein, the effective section Sres,T is small enough, such that it is not required to have an electric power supply at low loads to reach the targeted value of the at least one operational parameter. This allows to run the engine in case of electrical failure of the at least one electrical power converter (recovery mode).

[0044] While the foregoing is directed to embodiments, other and further embodiments may be devised without departing from the basic scope, and the scope is determined by the claims that follow.

REFERENCE NUMBERS

1 turbocharged engine system

10 combustion engine

11 cylinder

12 inlet valve

13 outlet valve

14 turbocharger

141 shaft

15 turbine

16 compressor

17 electrical power converter

171 rotor

172 stator

18 control device

19 sensor

20 method of charging and emission controlling a combustion engine

21, 22, 23, 24, 25, 26, 27 blocks of block diagrams for illustrating embodiments of the method of charging and emission controlling a combustion engine

P _in intake: pressure

Q _in air mass flow rate

Q _out NO _x emission rate λ air fuel ratio

T _ex exhaust temperature