• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a method for controlling a heat utilization device (1) in an internal combustion engine (10), in particular of a motor vehicle, wherein the heat utilization device (1) comprises a circuit for a working medium, with an evaporator (2) arranged in an exhaust gas flow path of the internal combustion engine (2). 3), an expansion machine (4), a condenser (5), a surge tank (6), and a feed pump (7), wherein the working temperature of the working medium is controlled by varying the mass flow of the working fluid in response to at least one operating parameter. In order to realize a regulated use of waste heat, it is provided that a desired value (ITI'MASOII / rn'MAGRsoii) of the working medium mass flow of an exhaust gas flow path of an exhaust line and / or an exhaust gas recirculation line is calculated on the basis of a basic setpoint (m'MbAsoii, mVibAGRsoii) for the working medium mass flow, wherein the base target value (m'MbAsoii / m'MbAGRsoii) for the working medium mass flow is at least one function of the exhaust gas temperature (TA i, TAGRI) / preferably before the evaporator (2, 3), and the exhaust gas mass flow (mA, ITI'AGR) in the exhaust gas flow path ,
    公开号:AT511189A4
    申请号:T1034/2011
    申请日:2011-07-14
    公开日:2012-10-15
    发明作者:Klemens Dipl Ing Neunteufl；Helmut Dipl Ing Theissl；Philip Mark Dr Stevenson
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a method for controlling a heat utilization device in an internal combustion engine, in particular of a motor vehicle, wherein the heat utilization device comprises a circuit for a working medium, with a arranged in an exhaust gas flow path of the internal combustion engine evaporator, an expansion machine, a condenser, a surge tank, and a feed pump , wherein the working temperature of the working medium is controlled by changing the mass flow of the working fluid as a function of at least one operating parameter.
    It is known to convert the thermal energy contained in the exhaust system and / or exhaust gas recirculation system (EGR system) of an internal combustion engine into mechanical power.
    DE 10 2009 020 615 A1 describes an exhaust heat utilization device of a motor vehicle with an exhaust heat recovery cycle, in which a working temperature of a working fluid of the exhaust heat recovery circuit is controlled. In this case, by adjusting a flowing through the heat exchanger of the exhaust heat recovery circuit mass flow of the working fluid, the operating temperature is controlled so that a maximum allowable operating temperature of the working fluid is not exceeded.
    From EP 2 249 017 A a similar waste heat utilization device with an evaporator for absorbing waste heat of an internal combustion engine is known, wherein the flow of working fluid is controlled so that the working fluid, which is vaporized in the evaporator, arranged in an overheated state in one in the exhaust stream Heater passes when the working fluid enters the evaporator at or below a predetermined flow rate at which the working fluid can absorb a predetermined maximum amount of heat. The flow rate of the working fluid is controlled so that above the predetermined flow rate, the working fluid flows through the evaporator and is evaporated in the heater and then reaches an overheated state.
    Further waste heat utilization facilities are known from the publications JP 2008 231 980 A and JP 58 023 210 A.
    The object of the invention is to realize a controlled waste heat utilization. 2 • Φ • Φ • · φ • φ φφφφφ φφφφφ Φ # ΦΦ ·
    According to the invention this is achieved in that eih * target value .....
    Working mass flow of an exhaust gas flow path of an exhaust line and / or an exhaust gas recirculation line is calculated based on a base setpoint for the working medium mass flow, the base setpoint for the working medium mass flow is at least one function of the exhaust gas temperature, preferably before the evaporator, and the exhaust gas mass flow in the exhaust gas flow path.
    In order to take into account the effects of the overheating of the working medium, it may be provided that an overheating correction value is added to the basic setpoint of the working medium flow. The overheating correction value can be derived from an exhaust gas temperature difference. As a result, thermal destruction of the evaporator can be prevented by overheating.
    In order to take into account saturation influences, it is advantageous if a saturation correction value is added to the basic setpoint of the working medium mass flow. The saturation correction value can be derived from a saturation temperature dependent on the working medium pressure. The saturation correction prevents the occurrence of wet steam conditions of the working medium at the entrance of the expansion machine. As a result, a mechanical destruction of the expansion machine is prevented.
    The exhaust gas mass flow in the exhaust system can be calculated from the variables exhaust lambda and fuel mass via a model. The EGR mass flow in the exhaust gas recirculation line is preferably calculated from the parameters engine speed, engine torque, fuel mass, air ratio of the exhaust gas, absolute boost pressure, charge air temperature and the filling efficiency via a model.
    Elaborate exhaust gas mass flow sensors can thus be omitted.
    In a further embodiment of the method according to the invention can be provided that an actual working medium mass flow is calculated by the evaporator from the variables actual valve position, pressure before and after the control valve of the evaporator, and the flow coefficient of the control valve via a model. Elaborate mass flow sensors for the working medium can thus be omitted. 3 • · · · · · * * f * * * * t ****** · «# ·· * ···· ***** · · * · ·
    Finally, control deviations of the mass flows in the exhaust gas flow path can be formed from the desired values and actual values * door opening, flow control current flow and fed to a controller, for example a PID controller.
    The invention will be explained in more detail below with reference to FIG.
    1 shows the diagram of the heat utilization device according to the invention, FIG. 2 shows a control system for the working medium through the exhaust gas evaporator, FIG. 3 shows the calculation of the base target value of the working medium flow through the exhaust gas evaporator, FIG. 4 shows the calculation of the overheating correction of the working medium mass flow through the exhaust gas evaporator, 5 the calculation of the saturation correction of the working medium mass flow through the exhaust gas evaporator, FIG. 6 the calculation of the nominal value of the working medium mass flow through the exhaust gas evaporator, FIG. 7 the regulation of the working medium mass flow through the exhaust gas evaporator,
    FIG. 9 shows the calculation of the basic oil value of the working medium mass flow through the EGR evaporator, the calculation of the superheat correction of the working medium mass flow by the EGR evaporator, FIG. 11 shows the calculation of the saturation correction of the EGR evaporator Arbeitsmediummassenstromes through the EGR evaporator, Fig. 12, the calculation of the setpoint of
    13 shows the control of the working medium mass flow through the EGR evaporator, FIG. 14 shows the working medium temperature as a function of the gas side temperature difference, FIG. 15 shows the saturation temperature as a function of the pressure for ethanol as the working medium, FIG Characteristic for the flow coefficients of the control valves and Fig. 17 is a map for the basic setpoint for the working medium mass flow using the example of the exhaust gas evaporator.
    The heat utilization device 1 according to the invention for an internal combustion engine 10 has the main components exhaust gas evaporator 2 and / or EGR evaporator 3, expansion engine 4, condenser 5, expansion tank 6, feed pump 7, control valves 8, 9 with position feedback, and not shown temperature sensors and pressure sensors.
    In at least one evaporator (exhaust gas and / or EGR evaporator 2, 3) is a working medium (for example, water and / or ethanol) using the * in the * ·································· * * «· · · · · · · · · 9 9999 99 ·
    Exhaust gas mass flow iti'a and / or EGR mass flow m'AGR contained thermal energy evaporated. The exhaust gas or EGR evaporator 2, 3 consists of at least two blocks 2a, 2b, 2c, ... and 3a, 3b, 3c, ....
    The generated steam is supplied to an expansion engine 4 (for example, a reciprocating engine) and converted into mechanical power. Subsequently, the working medium is cooled in a condenser 5 and fed to a surge tank 6. About at least one feed pump 7, the working fluid is removed from the surge tank 6 and fed via control valves 8, 9 back to the exhaust gas evaporator 2 and / or EGR evaporator 3 (steam cycle).
    To control the heat utilization device 1, a continuously adjustable control valve 8, 9 (for example, an electrically operated needle valve) is used in front of each evaporator 2, 3. About the valve opening cross section and the pressure of the working fluid before and after the control valve 8, 9, the mass flow through the control valve 8, 9 is changed. Furthermore, certain system states (pressures, temperatures and valve opening as indicated in FIG. 1) are detected metrologically and made available to the controller system as actual values.
    The entire regulator system for the exhaust gas evaporator 2 is shown in FIG. 2 and that for the EGR evaporator 3 in FIG. 8.
    In the method used in step 20 or 30, the calculation of each base setpoint m'MbAsoii, m'MbAGRsoii for the working fluid through the exhaust gas evaporator 2 and EGR evaporator 3. For the exhaust gas evaporator 2, this base setpoint m'MbAsoii as a function of the exhaust gas mass flow m 'A and the exhaust gas temperature TAi calculated at the exhaust gas evaporator inlet. In the illustrated embodiment, a map 20a is used by way of example for this purpose (FIGS. 3 and 17). The used exhaust gas mass flow iti'a is derived in step 21 from the variables Abgaslambda λΑ and fuel mass mK. 1 +
    mA = mK 'Aj For the EGR evaporator 3, the basic setpoint m'MbAGRsoii is calculated as a function of the EGR mass flow itTagr and the gas temperature T ^ ri at the EGR evaporator inlet. In the illustrated embodiment, a map 30a is used for this purpose (FIG. 9). The used EGR mass flow m'AGR is calculated in step 31 from the parameters engine speed n, engine torque M, fuel mass mK, Abgaslambda λΑ, absolute boost pressure pL, and charge air temperature TL, and the filling efficiency ηΡ on a model. The filling efficiency i > is calculated as a function of engine speed n and engine torque M (for example, stored in a map). * * · · · · · · · · «· · · · · t« * * »* · · · i
    • · · «« «· · · · I __ P, Tl 'Rsr
    PsR • M ··· «· * · * · mK · λΑ · fs-2 ^ SR ~ ττ
    PsR 'n' ^ H η ,, - = f (n, M)
    rAGR = rip ~ ^ SR '_ rAGR' mK '' fs mAGR ~.
    1 ~ rEGR
    Furthermore, for the working medium mass flow through the exhaust gas evaporator 2 and EGR evaporator 3, respectively, an overheating correction is calculated in steps 22 and 32, respectively, (FIGS. 4 and 10). The overheating correction mk itiküagr takes place to set the working medium temperature at the outlet of the exhaust gas evaporator 2 and EGR evaporator 3 to the respectively desired values.
    For this purpose, the effect is used that the working medium temperature TM / a, TMAgr2 arn output of an evaporator 2, 3 to the gas-side temperature difference ΔΤΑ = ΔΤΑι-ΔΤΑ2, ATAGr = ATAGri- ATagrz on the last evaporator block 2a, 3a (Fig. 1) is coupled , This effect is exemplified in FIG. The calculation of the overheating correction iti'küa, iti'küagr carried out by forming a target value ATasoh, ATagrsoii for the desired gas-side temperature difference at the EGR and exhaust gas evaporator. For the exhaust gas evaporator 2, this desired value ΔΤΑ50ι of the temperature difference is calculated as a function of the exhaust gas mass flow iti'a and the exhaust gas temperature TA1 at the exhaust gas evaporator inlet in step 22a. In the illustrated embodiment, a characteristic diagram is used for this purpose by way of example (FIG. 4). For the EGR evaporator 3, in step 32a, the setpoint value ATAGrsoii of the temperature difference is calculated as a function of the EGR mass flow m agr and the gas temperature TAGri at the EGR evaporator inlet. In the illustrated embodiment, a map is used for this purpose (FIG. 10).
    The current actual value of the temperature differences ΔΤ ^, ATAGRist is calculated in each case from the temperatures TAi, TAGri at the evaporator inputs and the temperatures T ", TAgr2 after the first evaporator block 2c, 3c. Furthermore, a regulator deviation for the exhaust gas evaporator and the EGR evaporator 2, 3 is formed from the target values ΔΤΑ50μ, ATagrsoh and the actual values ATAist (ATAGR | St.) In step 22b or 32b, this controller deviation is in each case assigned to a temperature controller (for example PID controller The output of these temperature controllers is the superheat correction ΓΤΐ'κϋΑ, iti'küagr for the exhaust gas evaporator and the EGR evaporator 2, 3. 6 · t · # * »+ ·· ··· * · ♦ ·· · ** «* · · · · · · · · · · · · · · · · · · · · ·.
    Furthermore, a saturation correction mW, m'KSAGR is calculated for the working medium mass flow through the exhaust gas evaporator 2 and the EGR evaporator 3 in steps 23 and 33, respectively (FIGS. 5 and 11). The saturation correction m'KSA / m'KSAGR is done to the working medium temperature TMA2r TMAgr2 at the output of the exhaust gas evaporator 2 and EGR evaporator 3, safely over the
    To maintain saturated steam temperatures TMSa and TMsagr.
    For this purpose, the respective saturated steam temperature TMsa and TMSAGR is calculated as a function of the working medium pressures pMA2, Pmagr2 at the evaporator outlets, first in step 23a or 33a (for example ethanol in FIG. 15). The differences are formed from the current working medium temperatures TMa2 / TMagr2 at the evaporator outputs and the determined saturated steam temperatures TMsA and Tmsagr and these are supplied to a correction function in step 23b, 33b (for example correction characteristics).
    The result of these correction functions is the saturation correction m'icsA, iti'ksagr of the working medium mass flows for the exhaust gas evaporator 2 and the EGR evaporator 3.
    Furthermore, from the basic setpoint m'MbAsoii / m'MbAGRsoii, the overheating correction iti'küa, m'KüAGR and the saturation correction m '"SA, m, ksagr in step 24 or 34, the final setpoint value for the working medium mass flow m'MAsoii, iti 'magrsoii calculated. This calculation is done by adding base setpoint m'MbAsoii / m'MbAGRsoii / overheat correction ηη'κϋΑ, iti'küagr and saturation correction m'i <sA, mVsAGR (Fig. 6 and Fig. 12). As a result, the desired value of the working medium mass flow mViAsoii, m'MAGRsoii is now available through the exhaust gas evaporator 2 and the EGR evaporator 3.
    From these desired values iti'masoii, m'MAGRsoii and the current actual values m'MAist, m'MAGRist the working medium mass flows, the controller deviations of the mass flows at the exhaust gas evaporator 2 and EGR evaporator 3 are formed and a controller 25a, 35a (for example PID controller) fed. In steps 25a and 35b, the calculation of the target positions VPAson, VPAGrsoii of the control valves 8, 9 (FIGS. 7 and 13) is performed.
    The actual values m'MAist, m'MAGRist of the mass flows are determined in step 25 or 35 as a function of the actual positions VPAist, VPAGRist of the control valves 8, 9, the pressures Pmi; Pmai, Pmagri before and after the control valves 8, 9 and the
    Flow coefficients KVA, Kvagr of the control valves 8, 9 calculated via a model 25b or 35b. The flow coefficients KVA, Kvagr of the control valves 8, 9 are calculated as a function of the actual positions VPAactual, VPAGRist (for example, stored in a characteristic curve FIG. 16). • k · i · * «* · I • · * I ······················································································ * · * ·
    VA nr _ (Λ, ι-ΑβιΗΟΟΟ "J - Ä 'V / ¾
    KyA = f (VPA ") mM AGR
    I (Pmi Pmagri) * 1OOO K,
    pm
    f'AGR K-VAGR ~ f AGRIX)
    The outputs of the two mass flow controllers each provide a desired position for the control valves 8, 9 in front of the respective evaporators 2, 3. 8th
    List of abbreviations and reference numbers: 1 heat utilization device 2 exhaust gas evaporator 3 EGR evaporator 4 expansion machine 5 condenser 6 expansion tank 7 feed pump 8 control valve for working medium upstream of exhaust gas evaporator 9 control valve for working fluid upstream of EGR evaporator 10 internal combustion engine 20, 20a, 21, 22, 22a, 22b, 23, 23a, 23b, 24, 25 steps 30, 30a, 31, 32, 32a, 32b, 33, 33a, 33b, 34, 35 steps 22b, 32b ΔΤ - controller 25a, 35a mass flow controller 21, 25b, 31, 35b Model n Engine speed M Engine torque mK Fuel mass pL Absolute boost pressure TL Charging temperature
    Tai exhaust gas temperature before exhaust gas evaporator TAz exhaust gas temperature in the exhaust gas evaporator ATasoi. Setpoint of the temperature difference in the exhaust gas evaporator ÄTAis Actual value of the temperature difference in the exhaust gas evaporator 9
    Exhaust gas temperature before EGR evaporator ... TaGR.2 Exhaust gas temperature in EGR evaporator ATagRsoII Setpoint of the temperature difference in EGR -Verdampfer ATAGRiSt actual value of the temperature difference in the EGR evaporator Tmsa saturation temperature of the working medium after the exhaust gas evaporator TMSAGR saturation temperature of the working medium after EGR evaporator Tma2 temperature of the working medium after exhaust gas evaporator T MAGR2 temperature of the working medium after EGR evaporator pMl pressure of the working medium upstream of the control valves Pmai pressure of the working medium to control valve of exhaust gas evaporator PMA2 Pressure of working fluid to exhaust gas evaporator Pmagri Pressure of working fluid to control valve of EGR evaporator PMAGR2 Pressure of working fluid to EGR evaporator VP Aist Actual position of control valve of exhaust gas evaporator VPasoII Target position of control valve of exhaust gas evaporator VP AGRIst Actual position the control valve of the EGR evaporator VPagRsoII Target position of the control valve of the EGR evaporator Kva Flow coefficient of the control valve of the exhaust gas evaporator KvAGR Flow coefficient of the control valve of the EGR evaporator pM Density of the working fluid upstream of the control valves Aa Air ratio of the exhaust gas of the internal combustion engine Rsr Gas constant in the intake manifold of the internal combustion engine fs Stoichiometric air requirement of the engine Hf Filling efficiency the internal combustion engine PSR density in the intake manifold of the internal combustion engine
    Lsr Degree of delivery related to * the 'iüständ &quot; in the intake manifold of the internal combustion engine Vh Stroke volume of the internal combustion engine ma Exhaust mass flow of the internal combustion engine ΓΠ MASOII Setpoint of the working medium mass flow through the exhaust gas evaporator m'MAIst Actual value of the working medium mass flow through the exhaust gas evaporator ΠΓ1 MbAsoll Basic setpoint of the working medium mass flow through the exhaust gas evaporator m'KüA Overheating correction for exhaust gas evaporator m'KSA Saturation correction for exhaust gas evaporator m'AGR EGR mass flow m'MAGRsoll Setpoint of working fluid mass flow through the EGR evaporator m'MAGRist Actual value of the working fluid Mass flow through the EGR evaporator m'MbAGRsoll Basic setpoint of the working fluid Mass flow through the EGR evaporator m'KüAGR Overheating correction for EGR evaporator hi 'ksagr saturation correction for EGR evaporator
    权利要求:
    Claims (10)
    [1]
    A method for controlling a heat utilization device (1) in an internal combustion engine (10), in particular of a motor vehicle, wherein the heat utilization device (1) comprises a circuit for a working medium with an evaporator (2, 3) arranged in an exhaust gas flow path of the internal combustion engine (10) ), an expansion machine (4), a condenser (5), a surge tank (6), and a feed pump (7), wherein the working temperature of the working fluid is controlled by varying the mass flow of the working fluid in response to at least one operating parameter, characterized in that a setpoint value (iti'masoii, iti'magrsoii) of the working medium mass flow of an exhaust gas flow path of an exhaust line and / or an exhaust gas recirculation line is calculated on the basis of a basic target value (m'MbAsoii, m'MbAGRsoii) for the working medium mass flow, the base target value (m'MbAsoii / m'MbAGRsoii) for the working medium mass flow at least one function of the exhaust gas temperature (TAi, TAgri), preferably before the evaporator (2, 3), and the exhaust gas mass flow (m'A, m agr) in the exhaust gas flow path.
    [2]
    2. The method according to claim 1, characterized in that the base setpoint (m'MbAsoii, m'MbAGRsoii) of the working medium mass flow, an overheating correction value (mW, iti'küagr) is added.
    [3]
    3. The method according to claim 2, characterized in that the superheat correction value (mW, m'koagr) from an exhaust gas temperature difference (ATa, ATagr), preferably between an exhaust gas temperature (TAi, TAGRi) before the evaporator (2, 3) and an exhaust gas temperature (TA2, daytime) in the evaporator (2, 3) is derived.
    [4]
    4. The method according to any one of claims 1 to 3, characterized in that a saturation correction value (iti'ksa, iti'ksagr) is added to the basic setpoint value (m'MbAsoii, m'MbAGRsoii) of the working medium mass flow.

    Saturation correction value; (iti'ksa, m'xsAGR) is derived from a saturation temperature (TMsa, Tmsagr) which depends on the working medium pressure (Pma2 / Pmagr2) downstream of the evaporator (2, 3).
    [5]
    6. The method according to any one of claims 1 to 5, characterized in that the exhaust gas mass flow (m a) in the exhaust system from the variables air ratio of the exhaust gas (λΑ) and fuel mass (mK) via a model (21) is calculated.
    [6]
    7. The method according to any one of claims 1 to 6, characterized in that the EGR mass flow (m agr) in the exhaust gas recirculation line from the variables engine speed (n), engine torque (M), fuel mass (mK), air ratio of the exhaust gas (λΑ) , absolute boost pressure (pL), charge air temperature (TL) and the filling efficiency (r>) are calculated by model (31).
    [7]
    8. The method according to any one of claims 1 to 7, characterized in that an actual working medium mass flow (mWist, rn'MAGRist) through the evaporator (2, 3) from the variables actual valve position (VPAist, VPagrisi) and pressure (pMi pMAi, Pmagri) before and after the control valve (8, 9) of the evaporator (2, 3) and the flow coefficient (KVA, Kvagr) of the control valve (8, 9) via a model (25b, 35b) is calculated.

    A-11SG Vienna, Mariahilfer Gürtel 39 / v ~) r * l: MJ 1) £ 92 39 33-0 Fax: t) ft} 333 ι ** ιβΐ | »
    [8]
    9. Method according to one of claims 1 to 7, characterized in that from the desired values (m'MAsoil · rnViAGRsoii) and actual values (m MAist, rn is Rist) for the working medium flow controller deviations of the mass flows in the exhaust gas flow path formed and a Redler (25a, 35a) are supplied. 2011 07 14 Fu γ ^ ιϊ3 ι

    Flg. 1 REPLACED

    Λα Τα, πν Τα, Τμα * ΡΜΑ2 VP * «μμ PUA1 T«,

    Flg.2 Τα, ΓΠ'α * &gt; rn'wbÄK «2ÜB ► F / g. 3 REPLACED

    Tai Tae2

    Fig.4 Pm «23a Tmsa Ψ ►Θ-»

    ηΥκ £ Α Fig.5> 1

    m'wuoi ► ΓΠ'κοα ΓΤΐ'κΒΑ Fig.6 REPLACED

    Figure 7

    Flg. 8 REPLACED T * at the "3R

    rn'uMeR "&lt; | * ►Ag.9 Taooi m'AGB - h. ATagrh «'* Ψ 22fl 32h KJ ► W i AT / tanat t Tagfq Fig. 10

    Fig. 11 REPLACED

    Flg. 12

    Fig. 13 Tn | A2 TmAQH2

    SUBSEQUENT

    Fig. 15

    Fig. 16 REPLACED ^ uumi

    ^ v v m a Fig. 17 SUGGESTED z 1 .. .. * · ·· * · · * * * *! 56215vlp: ::: * * ···: Akterjz .: 2BA 1034/2011 F02G (new) PATENT CLAIMS 1. Method for controlling a heat utilization device (1) in an internal combustion engine (10), in particular of a motor vehicle, wherein the heat utilization device (1) a circuit for a working medium, comprising an evaporator (2, 3) arranged in an exhaust gas flow path H of the internal combustion engine (10), an expansion engine (4), a condenser (5), a surge tank (6), and a feed pump (7) wherein the working temperature of the working medium is controlled by varying the mass flow of the working fluid as a function of at least one operating parameter, wherein a desired value (mWoii, itTmagrsoii) of the working medium mass flow of an exhaust gas flow path of an exhaust line and / or an exhaust gas recirculation line on the basis of a base target value (m'MbAsoii, m ' MbAGRsoii) for the working medium mass flow, the base setpoint (m'MbAsoii, m'MbAGRsoii) being calculated for the working medium mass flow is at least one function of the exhaust gas temperature (Tai, TAgri), preferably upstream of the evaporator (2, 3), and of the exhaust gas mass flow (iti'a, iti'agr) in the exhaust gas flow path, characterized in that the basic setpoint (m'MbAsoii, m'MbAGRsoii) of the working medium mass flow at least one correction value is added. 2. The method according to claim 1, characterized in that the base setpoint (m'MbAsoii, m'MbAGRsoii) of the working medium mass flow, an overheating correction value (iti'küa, m'küagr) is added. 3. The method according to claim 2, characterized in that the overheating correction value (iti'küa, iti'küagr) from an exhaust gas temperature difference (ATa, ATAGr), preferably between an exhaust gas temperature (TA1, TAGRi) before the evaporator (2, 3) and an exhaust gas temperature (TA2, TAGR2) in the evaporator (2, 3) is derived. 4. The method according to any one of claims 1 to 3, characterized in that a saturation correction value (iti'ksa, hi'ksagr) is added to the base target value (m'MbAsoii, m'MbAGRsoii) of the working medium mass flow. SUBSEQUENT

    Saturation correction value (iti'ksa, iti'ksagr) is derived from a working fluid pressure (Pma2 / Pmagr2) after the evaporator (2, 3) dependent saturation temperature Omsa, TMsagr). 6. The method according to any one of claims 1 to 5, characterized in that the exhaust gas mass flow (m a) in the exhaust system from the variables air ratio of the exhaust gas (λΑ) and fuel mass (mK) via a model (21) is calculated. 7. The method according to any one of claims 1 to 6, characterized in that the EGR mass flow (m agr) in the exhaust gas recirculation line from the variables engine speed (n), engine torque (M), fuel mass (mK), air ratio of the exhaust gas (λΑ) , absolute boost pressure (pL), charge air temperature (TL) and fill efficiency (nF) are calculated via a model (31).
    [9]
    8. The method according to any one of claims 1 to 7, characterized in that an actual working medium mass flow (m'MAist, rn'magRist) through the evaporator (2, 3) from the variables actual valve position (VPAist, VPAGRist) and pressure ( pHi, pMAi, Pmagri) before and after the control valve (8, 9) of the evaporator (2, 3) and the flow coefficient (KVA, KVAGr) of the control valve (8, 9) is calculated via a model (25b, 35b).
    [10]
    9. The method according to any one of claims 1 to 7, characterized in that from the setpoint values (mW-oii, hiVagrsoii) and actual values (m'MAist, rn'm agrisO) formed for the working medium flow controller deviations of the mass flows in the exhaust gas flow path and a controller (25a , 35a) are supplied.

    2012 03 08 Fu / Bt FOLLOW-UP
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    AT518976B1|2018-03-15|METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE
    EP1826378A2|2007-08-29|Method for operating a combustion engine, in particular of a motor vehicle
    DE102011003068B4|2019-02-07|Device and method for waste heat utilization of an internal combustion engine
    DE102007053778B4|2017-12-07|Exhaust gas recirculation in an internal combustion engine with two turbochargers
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    同族专利:
    公开号 | 公开日
    EP2732140B1|2021-08-11|
    WO2013007530A1|2013-01-17|
    AT511189B1|2012-10-15|
    US20140202134A1|2014-07-24|
    CN103781997A|2014-05-07|
    CN103781997B|2015-12-09|
    US9482150B2|2016-11-01|
    EP2732140A1|2014-05-21|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1034/2011A|AT511189B1|2011-07-14|2011-07-14|METHOD FOR CONTROLLING A HEAT UTILIZATION DEVICE IN AN INTERNAL COMBUSTION ENGINE|ATA1034/2011A| AT511189B1|2011-07-14|2011-07-14|METHOD FOR CONTROLLING A HEAT UTILIZATION DEVICE IN AN INTERNAL COMBUSTION ENGINE|
    PCT/EP2012/062574| WO2013007530A1|2011-07-14|2012-06-28|Method for controlling a heat recovery device in an internal combustion engine|
    US14/232,745| US9482150B2|2011-07-14|2012-06-28|Method for controlling a heat recovery device in an internal combustion engine|
    EP12730952.4A| EP2732140B1|2011-07-14|2012-06-28|Method for controlling a heat recovery device in an internal combustion engine|
    CN201280034715.8A| CN103781997B|2011-07-14|2012-06-28|For regulating the method for heat-energy utilizing device in internal-combustion engine|
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