JP2005233114A - Ignition timing controlling equipment of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an ignition timing control device for an internal combustion engine capable of performing suitable ignition timing control with a few calibration manhours. <P>SOLUTION: This ignition timing control device for the internal combustion engine calculates knocking occurrence index by ∫1/τ×dt performing time integral of an inverse 1/τ of time τ of self ignition of unburnt gas before ignited fire is transmitted and controls ignition timing based on the knocking occurrence index ∫1/τ×dt. Interval of integration can be changed based on operation conditions. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an ignition timing control device for an internal combustion engine that controls ignition timing so as not to cause knocking.

  The ignition timing of the engine affects fuel consumption and output, and if the ignition timing is deviated, there is a risk of knocking or misfiring, so that control is very important. Normally, the ignition timing is controlled so that the cylinder pressure becomes the maximum at 10 to 15 degATDC. However, the minimum torque advance ignition timing (Minimum Spark Advance for Best Torque; hereinafter abbreviated as “MBT”), which is the basis for setting the ignition timing, varies from moment to moment depending on engine speed, load, air-fuel ratio, EGR rate, etc. To do. Therefore, conventionally, a basic ignition timing map set according to the engine speed and load and a correction value map assuming various operating conditions are provided, and control is performed by referring to these maps according to the operating conditions. . However, in such a method, in order to improve accuracy, the number of grids of the map and the map itself must be increased, and enormous preliminary experiments are required to create the map.

Conventionally, when a knock is detected by a sensor, it is fed back to delay the ignition timing. However, this method cannot avoid a control delay because feedback control is performed after a knock that has actually occurred is detected. Therefore, in Patent Document 1, an in-cylinder pressure with respect to a crank angle and an in-cylinder gas temperature at a calculation start crank angle are input, and on the basis of them, the in-cylinder gas temperature is assumed to be adiabatically compressed. Is calculated, and the knock generation time is predicted assuming that the time when the in-cylinder gas temperature reaches 1200 K or more is the knock generation time.
JP-A-7-332149 (pages 3-5, FIGS. 1, 2, 5 etc.)

  However, in Patent Document 1, the ignition timing at which knocking is not performed is basically set, and the “optimal state where knocking does not occur” is appropriately set for other control amounts. The basic “ignition timing without knocking” had to be obtained in advance for each operating condition, and a great deal of man-hours were required.

  The present invention has been made paying attention to such a conventional problem, and it is possible to perform appropriate ignition timing control with a small number of adaptation man-hours by deriving `` ignition timing without knocking '' by calculation. An object of the present invention is to provide an ignition timing control device for an internal combustion engine that achieves both a small calculation load and sufficient calculation accuracy in calculating the “ignition timing without knocking”.

  The present invention solves the above problems by the following means. In addition, in order to make an understanding easy, although the code | symbol corresponding to embodiment of this invention is attached | subjected, it is not limited to this.

  In the present invention, knocking is generated by time-integrating the reciprocal 1 / τ of the self-ignition time τ and self-ignition time calculating means (5323) for calculating the time τ during which the unburned gas self-ignites before the ignited fire is transmitted An ignition timing control device for an internal combustion engine, comprising: a knock generation index calculation means (5324) for calculating an index; and an ignition timing control means (54, 55) for controlling the ignition timing based on the knock generation index, The knock generation index calculation means changes the integration interval based on the driving state.

  According to the present invention, by introducing the knock generation index ∫1 / τ · dt, the “ignition timing without knocking” can be determined with a small number of compatible man-hours. And in calculating the knock occurrence index, it is possible to achieve both a small calculation load and sufficient calculation accuracy by appropriately setting the integration interval according to the operating state. .

  Hereinafter, embodiments of the present invention will be described in more detail with reference to the drawings.

  FIG. 1 is a schematic diagram for explaining the system of the present invention.

  The air is stored in the intake collector 2 and then introduced into the combustion chamber 5 of each cylinder via the intake manifold 3. Fuel is injected and supplied from a fuel injector 21 disposed in the intake port 4 of each cylinder. The fuel injected into the air is vaporized and mixed with the air to form a gas (air mixture) and flows into the combustion chamber 5. This air-fuel mixture is confined in the combustion chamber 5 when the intake valve 15 is closed, and is compressed by the rise of the piston 6.

  In order to ignite this compressed air-fuel mixture with a high-pressure spark, an ignition device 11 of an electronic power distribution system is provided in which an ignition coil with a built-in power transistor is arranged in each cylinder. That is, the ignition device 11 includes an ignition coil 13 that stores electrical energy from the battery, a power transistor that energizes and shuts off the primary side of the ignition coil 13, and a primary current of the ignition coil 13 that is provided on the ceiling of the combustion chamber 5. It includes a spark plug 14 that receives a high voltage generated on the secondary side of the ignition coil 13 due to interruption of the spark coil 13 and performs spark discharge.

  When a spark is blown off by the spark plug 14 slightly before the compression top dead center and the compressed mixture is ignited, the flame spreads and then explosively burns, and the gas pressure by this combustion works to push down the piston 6. This work is taken out as the rotational force of the crankshaft 7. The combusted gas (exhaust gas) is discharged into the exhaust passage 8 when the exhaust valve 16 is opened.

A three-way catalyst 9 is provided in the exhaust passage 8. When the air-fuel ratio of the exhaust gas is in a narrow range (window) centered on the stoichiometric air-fuel ratio, the three-way catalyst 9 can efficiently remove harmful three components such as HC, CO, and NOx contained in the exhaust gas simultaneously. Since the air-fuel ratio is the ratio of the intake air amount and the fuel amount, the intake air amount introduced into the combustion chamber 5 per one cycle of the engine (crank angle 720 ° section in a four-cycle engine) and the fuel injector 21 The engine controller 50 controls the fuel from the fuel injector 21 based on the intake air flow rate signal from the air flow meter 32 and the signal from the crank angle sensor (33, 34) so that the ratio to the fuel injection amount becomes the stoichiometric air-fuel ratio. The injection amount is determined, and the air-fuel ratio is feedback controlled based on a signal from an O ₂ sensor 35 provided upstream of the three-way catalyst 9.

  A so-called electronically controlled throttle 22 in which a throttle valve 23 is driven by a throttle motor 24 is provided upstream of the intake collector 2. Since the torque requested by the driver appears in the amount of depression of the accelerator pedal 41 (accelerator opening), the engine controller 50 determines a target torque based on a signal from the accelerator sensor 42, and a target air for realizing this target torque. The amount is determined, and the opening degree of the throttle valve 23 is controlled via the throttle motor 24 so as to obtain this target air amount.

  Cam sprockets and crank sprockets are attached to the front portions of the intake valve camshaft 25, the exhaust valve camshaft 26, and the crankshaft 7, respectively, and a timing chain (not shown) is hung around these sprockets so that the camshaft 25 and 26 are driven by the crankshaft 7 of the engine, and are interposed between the cam sprocket and the intake valve camshaft 25 to continuously adjust the phase of the intake valve cam with a constant operating angle. An exhaust valve cam control phase (hereinafter referred to as an “intake VTC mechanism”) 27 that can be controlled, and a cam sprocket and an exhaust valve camshaft 26 are interposed between the camshaft 26 and the exhaust valve cam. Valve timing control mechanism (hereinafter referred to as “exhaust VTC mechanism”) Say.) And a 28. When the opening / closing timing of the intake valve 15 and the opening / closing timing of the exhaust valve 16 are changed, the amount of the inert gas remaining in the combustion chamber 5 changes. As the amount of the inert gas in the combustion chamber 5 increases, the pumping loss decreases and the fuel consumption improves. Therefore, the target intake valve closing timing and the target exhaust gas indicate how much inert gas should remain in the combustion chamber 5 depending on the operating conditions. The valve closing timing is determined in advance, and the engine controller 50 determines the target intake valve closing timing and the target exhaust valve closing timing based on the operating conditions (engine load and rotational speed) at that time, so that these target values can be obtained. The intake valve closing timing and the exhaust valve closing timing are controlled via the actuators of the intake VTC mechanism 27 and the exhaust VTC mechanism 28.

  An intake air temperature signal from the intake air temperature sensor 43, an intake air pressure signal from the intake air pressure sensor 44, an exhaust gas temperature signal from the exhaust air temperature sensor 45, and an exhaust gas pressure signal from the exhaust air pressure sensor 46 are output from the water temperature sensor 37. The engine controller 50 that is input together with the coolant temperature signal controls the ignition timing, which is the primary current cutoff timing of the spark plug 14, via the power transistor 13.

  Next, the basic concept of control that is a feature of the present invention will be described.

  2 and 3 are diagrams for explaining a knock generation mechanism.

  When the mixed gas is ignited and combustion is started, the heat generation rate rapidly increases (FIG. 2A). Then, the in-cylinder temperature (FIG. 2B) and the in-cylinder pressure (FIG. 2C) also increase. Then, if the unburned gas self-ignites and causes rapid combustion before the ignited fire is transmitted, knocking occurs (FIG. 2C). The reciprocal (1 / τ) of the self-ignition time τ represents the ignition delay. Knock occurs at a crank angle at which the time integral value of 1 / τ becomes 1 (FIG. 2D). That is, ∫1 / τ · dt is a knock occurrence index. In this embodiment, the integration start position is the ignition position. The integration start position should be the intake valve closed position for accurate integration calculation, but the 1 / τ value is very small until ignition is started, so it can be ignored for calculation accuracy, reducing the calculation burden. In this embodiment, the integration start position is set as the ignition position so that the integration is performed after the ignition is started. In FIG. 2, the integration end position is set to a position exceeding た 1 / τ · dt = 1. The black circles in FIG. 2D indicate calculation points for every fixed calculation crank angle interval. As described above, knocking occurs when ∫1 / τ · dt = 1 is established, so it is meaningless to continue the calculation thereafter. Therefore, when the black circle calculation point exceeds 超 え 1 / τ · dt = 1, the integration is terminated to eliminate the unnecessary calculation. The integration end position may be set when the combustion ratio exceeds the combustion end determination value. That is, when the combustion rate reaches 100%, the combustion is completed and no knocking occurs, so the integration end position may be determined based on the combustion rate. However, it is very difficult to determine the position where the mass combustion ratio is 100%. Therefore, the combustion end determination value may be set as 95%, for example. In the present embodiment, as will be described later, it is determined whether or not the combustion ratio X_burn (i) exceeds the combustion end determination value X_burn_end in 53-2 in FIG. 5, and the knock occurrence index idx_kocr in 53-3 in FIG. It is determined whether or not (i) exceeds 1, and if any of them is satisfied, the integral calculation is terminated by terminating the interrupt calculation request.

  This will be described in more detail with reference to FIG. FIG. 3A is a 1 / τ map with the in-cylinder temperature on the horizontal axis and the in-cylinder pressure on the vertical axis. If the in-cylinder temperature and in-cylinder pressure are known, the value of 1 / τ can be obtained from this map. 1 / τ is obtained along the history of in-cylinder pressure and in-cylinder temperature, and time integration is performed to obtain ∫1 / τ · dt. It can be estimated that knocking occurs at a crank angle where ∫1 / τ · dt = 1.

  The result of the estimation is shown in FIG. The actual value of the knocking crank angle is taken on the horizontal axis of FIG. 3B, while the estimated value of the knocking crank angle calculated as described above is taken on the vertical axis. Then, as is clear from FIG. 3B, the estimated value substantially coincided with the actually measured value, and it was proved that the above estimation was correct.

  The present inventor introduced ∫1 / τ · dt as a knock occurrence index. As a result, the knock generation index can be reduced to the in-cylinder pressure and the in-cylinder temperature. Since the in-cylinder pressure and the in-cylinder temperature are the most basic state quantities of the in-cylinder gas, it is possible to have substantially the same characteristics regardless of the engine model, and to the engine warm-up state and environmental conditions. Regardless, it has become possible to accurately estimate the knock occurrence time in real time.

  FIG. 4 is a control block diagram showing the overall control of the ignition timing control apparatus according to the present invention.

  The engine controller 50 sequentially calculates the combustion speed 521, the combustion period 522, and the basic ignition timing 523 based on the operating state 51, and calculates the knock generation index 53 to obtain the advance angle correction / limit (retard width) 54. From these, the knock limit ignition timing 55 is calculated.

  Next, each component block will be described in more detail. In addition, since the specific content of the basic ignition timing calculation part 52 is demonstrated in detail in Unexamined-Japanese-Patent No. 2003-148236, description is abbreviate | omitted in this case.

  FIG. 5 is a diagram illustrating the knock occurrence index block 53 in detail.

  In the knock generation index block 53, the basic ignition timing MBTCAL and the calculated crank angle interval delta_theta are input, and the calculated crank angle CA_calc (i) is sequentially calculated for each calculation counter (i) based on the knock generation index calculation start request JOB_REQ. . Then, the knock generation index 530 is calculated based on the calculated crank angle CA_calc (i), and the knock generation index idx_kocr (i) and the mass combustion ratio X_burn (i) are sequentially calculated for each calculation counter (i). An interrupt operation is requested until the mass combustion ratio X_burn (i) exceeds the combustion ratio X_burn_end at the end of combustion or until the knock generation index idx_kocr (i) exceeds 1.

  The knock generation index calculation block 530 will be described with reference to FIG. The knock generation index calculation block 530 includes an in-cylinder average temperature / pressure calculation block 531 and a knock generation index calculation block 532. In the cylinder average temperature / pressure calculation block 531, the crank angle CA, the engine speed NE, the basic ignition timing MBTCAL, the injection pulse width TP, the cylinder volume initial value V_cyl_ini, the cylinder temperature initial value T_cyl_ini, the cylinder pressure initial value P_cyl_ini, The in-cylinder temperature T_cyl, the in-cylinder pressure P_cyl, and the mass combustion ratio X_burn are calculated based on the ignition dead time IGNDEAD, the combustion period BURN, the reference combustion ratio X_ref, and the remaining gas ratio MRESFR. In knock generation index calculation block 532, knock generation index idx_kocr is calculated based on crank angle CA, engine speed NE, basic ignition timing MBTCAL, in-cylinder temperature T_cyl, and in-cylinder pressure P_cyl. The in-cylinder average temperature / pressure calculation block 531 will be described in detail with reference to FIG. 7, and the knock occurrence index calculation block 532 will be described in detail with reference to FIG.

  First, the in-cylinder average temperature / pressure calculation block 531 will be described with reference to FIG.

  The in-cylinder average temperature / pressure calculation block 531 includes a cylinder volume calculation block 5311, a heat generation amount calculation block 5312, a cooling loss calculation block 5313, and an in-cylinder temperature / pressure calculation block 5314.

  In the cylinder volume calculation block 5311, the cylinder volume V_cyl and the piston displacement x_pis are calculated based on the crank angle CA. In the calorific value calculation block 5312, based on the crank angle CA, the injection pulse width TP, the basic ignition timing MBTCAL, the ignition dead time IGNDEAD, the combustion period BURN, the reference combustion rate X_ref, the residual gas rate MRESFR, the heat generation rate Q_burn, the physical property calculation The mass combustion ratio X_burn_r and the mass combustion ratio X_burn are calculated. In the cooling loss calculation block 5313, the cylinder volume V_cyl, piston displacement x_pis, residual gas ratio MRESFR, cylinder temperature initial value T_cyl_ini, cylinder volume initial value V_cyl_ini, cylinder pressure initial value P_cyl_ini, engine speed NE, cylinder pressure previous value P_cyl_z The cooling loss Q_loss is calculated based on the previous in-cylinder temperature value T_cyl_z. In the in-cylinder temperature / pressure calculation block 5314, based on the injection pulse width TP, the cylinder volume V_cyl, the heat generation rate Q_burn, the physical property calculation mass combustion ratio X_burn_r, the cooling loss Q_loss, the in-cylinder pressure previous value P_cyl_z, and the in-cylinder temperature previous value T_cyl_z. Thus, the in-cylinder pressure P_cyl and the in-cylinder temperature T_cyl are calculated.

  Subsequently, each block constituting the in-cylinder average temperature / pressure calculation block 531 shown in FIG. 7 will be described in more detail.

  First, details of the cylinder volume calculation block 5311 will be described with reference to FIG. The cylinder volume calculation block 5311 includes a piston displacement calculation block 53111 and a cylinder volume calculation block 53112. In the piston displacement calculation block 53111, the piston displacement x_pis is calculated from the crank angle CA. In the cylinder volume calculation block 53112, the cylinder volume V_cyl is calculated.

  Next, details of the heat generation amount calculation block 5312 will be described with reference to FIG.

  The calorific value calculation block 5312 includes a Wiebe function constant setting block 53121, a heat generation rate calculation block 53122, a mass combustion ratio calculation block 53123, a calorific value / 1 cylinder / 1 cycle calculation block 53124, and a calorific value / 1 cylinder / And a calculation interval calculation block 53125.

Here, the Wiebe function will be described. In general, X = 1−exp [−a · [(θ−θ _S ) / θ _B ] ^{n +} as a function of the crank angle θ (deg) as a function of the heat release rate ¹ ]… (1)
θ _S : Actual combustion start crank angle (deg)
θ _B : Actual combustion period (deg)
a, n: can be described as constants. The above a and n are determined by the engine model such as the shape of the combustion chamber, the position of the spark plug, and the gas flow characteristics in the combustion chamber. This can be determined in advance by experiments or the like. This equation (1) is the Wiebe function.

Differentiating the above equation (1) by θ gives a function representing the heat generation rate,
dX / dθ
= A (n + 1) / θ _B · [(θ-θ _S ) / θ _B ] ⁿ · exp [-a · [(θ-θ _S ) / θ _B ] ^{n + 1} ] (2)
Solving equation (1) for the actual combustion period θ _B
θ _B = θ / [-log (1-X) / a] ^{1 / (n + 1)} (3)
It becomes.

Based on the above, the Wiebe function constant setting block 53121 will be described with reference to FIG. FIG. 10 is a control block diagram describing the above equation (3). That is, in the equation (3), the actual combustion period θ _B (BURN_r) can be calculated by substituting θ = BURN and X = X_ref. The Wiebe function constant setting block 53121 calculates the heat generation start timing BURN_ini based on the basic ignition timing MBTCAL and the ignition dead time IGNDEAD, and calculates the actual combustion duration BURN_r based on the combustion duration BURN and the reference combustion ratio X_ref. .

The heat generation rate calculation block 53122 will be described with reference to FIG. FIG. 11 is a control block diagram describing the above equation (2). That is, in equation (2), if θ = CA, θ _S = BURN_ini, and θ _B = BURN_r are substituted, the heat generation rate dX / dθ can be calculated. The heat generation rate calculation block 53122 calculates the heat generation rate based on the crank angle CA, the heat generation start timing BURN_ini, and the actual combustion period BURN_r.

The mass combustion ratio calculation block 53123 will be described with reference to FIG. FIG. 12 is a control block diagram describing the above equation (1). In other words, the mass combustion ratio X (X_burn) can be calculated by substituting θ = CA, θ _S = BURN_ini, and θ _B = BURN_r in equation (1). The mass combustion ratio calculation block 53123 calculates a mass combustion ratio X_burn and a physical property calculation mass combustion ratio X_burn_r based on the crank angle CA, the heat generation start timing BURN_ini, the actual combustion period BURN_r, and the residual gas ratio MRESFR.

  The calorific value / 1 cylinder / 1 cycle calculation block 53124 will be described with reference to FIG. The calorific value / 1 cylinder / cycle calculation block 53124 calculates the calorific value per cylinder per cycle based on the injection pulse width TP, the constant KCONST, the target air-fuel ratio TABYF, and the low calorific value Heat_Lower.

  The heating value / 1 cylinder / calculation interval calculation block 53125 will be described with reference to FIG. The heat generation amount / 1 cylinder / calculation interval calculation block 53125 calculates a heat generation amount Q_burn based on the heat generation rate and the heat generation amount for each cylinder per cycle.

  The above is the description of the heat generation amount calculation block 5312. Next, details of the cooling loss calculation block 5313 of FIG. 7 will be described with reference to FIG.

  The cooling loss calculation block 5313 includes a combustion chamber surface area calculation block 53131, an average piston speed calculation block 53132, a motoring-gas property value calculation block 53133, a motoring-cylinder pressure calculation block 53134, and a motoring-cylinder temperature. It has a calculation block 53135, a heat transfer coefficient calculation block 53136, and a cooling loss calculation block 53137.

  The combustion chamber surface area calculation block 53131 calculates the combustion chamber surface area based on the piston displacement x_pis. The average piston speed calculation block 53132 calculates an average piston speed based on the engine speed.

  The motoring-gas property value calculation block 53133 calculates the specific heat ratio κ based on the mass combustion ratio obtained from the residual gas rate MRESFR and the in-cylinder temperature. Since the specific calculation method is the same as that of the gas property value calculation block 53141 (FIG. 19), the description is omitted here.

  The motoring-cylinder pressure calculation block 53134 calculates a cylinder pressure P_cyl based on the cylinder pressure previous value, the cylinder volume previous value, the cylinder volume current value, and the specific heat ratio κ. In this calculation, it is calculated as an adiabatic change. The motoring-in-cylinder temperature calculation block 53135 calculates the in-cylinder temperature T_cyl based on the previous in-cylinder temperature value, the previous cylinder volume value, the current cylinder volume value, and the specific heat ratio κ. In this calculation, it is calculated as an adiabatic change.

  Next, before describing the heat transfer coefficient calculation block 53136, the equation of the cooling loss Woschni will be described.

The cooling loss Q _L is calculated by:
Q _L = ∫ _t1 ^t2 h ・ A ・ (T-T _W ) ・ dt… (4)
h = 110 ・ d ^-0.2・ P ^0.8・ T ^-0.53・ [C ₁・ c _m + C ₂・ (V _S・ T _I ) / (P _I・ V _I ) ・ (P-P _M )] ^0.8 … (Five)
h: Heat transfer coefficient [kcal / (m ²・ h ・ K)]
d: Cylinder bore diameter [m]
V _S : Cylinder volume [m ³ ]
c _m : Average piston speed [m / s]
P _I : In-cylinder pressure when the intake valve is closed [kgf / cm ² ]
V _I : In-cylinder volume when intake valve is closed [m ³ ]
T _I : In-cylinder temperature when intake valve is closed [K]
P _M : Motoring cylinder pressure [kgf / cm ² ]
P: In-cylinder pressure [kgf / cm ² ]
T: In-cylinder temperature [K]
C ₁ : 6.18 (exhaust), 2.28 (compression and expansion) [-]
C ₂ : 3.24 × 10 ^-3 [m / (s · K)]
In the above, C ₁ and C ₂ are commonly used constants.

  FIG. 16 illustrates the equation (5) as a control block. As shown in FIG. 16, the heat transfer coefficient calculation block 53136 is based on the cylinder pressure, cylinder temperature, average piston speed, motoring cylinder pressure, cylinder temperature initial value, cylinder volume initial value, cylinder pressure initial value. Calculate the heat transfer coefficient.

  FIG. 17 illustrates the equation (4) as a control block. As shown in FIG. 17, the cooling loss calculation block 53137 calculates the cooling loss Q_loss based on the in-cylinder temperature, the combustion chamber wall temperature, the combustion chamber surface area, the heat transfer coefficient, the calculation interval, and the engine speed.

  The above is the description of the cooling loss calculation block 5313. Next, the cylinder temperature / pressure calculation block 5314 in FIG. 7 will be described with reference to FIG.

  The in-cylinder temperature / pressure calculation block 5314 includes a gas property value calculation block 53141, a total gas amount calculation block 53142, an adiabatic change in-cylinder pressure calculation block 53143, an adiabatic change in-cylinder temperature calculation block 53144, and an in-cylinder temperature calculation block. 53145 and an in-cylinder pressure calculation block 53146.

The gas property value calculation block 53141 calculates a gas property value (specific heat ratio, constant volume specific heat) based on the mass combustion ratio and the in-cylinder temperature. Here, when calculating gas properties based on the ratio of burnt gas (applying “mass combustion ratio for physical property calculation”),
(Gas property value) = (Burn gas property value) * (Burn gas ratio) + (Burn gas property value) * (1-Burned gas ratio)… (6)
Therefore, it is shown in the block diagram of FIG. As shown in FIG. 19, the motoring-gas physical property value calculation block 53133 obtains the constant volume specific heat and specific heat ratio of burned based on the in-cylinder temperature T_cyl (initial value is T_cyl_ini), and also the in-cylinder temperature. Based on T_cyl (initial value is T_cyl_ini), the constant volume specific heat and specific heat ratio of the unburned portion are obtained, and the physical property value of the in-cylinder gas is calculated by multiplying the burned portion and the ratio of the unburned portion.

  As shown in FIG. 20, the total gas amount calculation block 53142 calculates the total gas amount based on the injection pulse widths TP, KCONST, and the air-fuel ratio ABYF.

  The adiabatic change in-cylinder pressure calculation block 53143 calculates the adiabatic change in-cylinder pressure based on the previous cylinder pressure value, the previous cylinder volume value, the current cylinder volume value, and the specific heat ratio κ. The adiabatic change in-cylinder temperature calculation block 53144 calculates the adiabatic change in-cylinder temperature based on the previous cylinder temperature value, the previous cylinder volume value, the current cylinder volume value, and the specific heat ratio κ. The in-cylinder temperature calculation block 53145 calculates the in-cylinder temperature T_cyl based on the adiabatic change in-cylinder temperature, the heat generation amount, the cooling loss, the total gas amount, and the constant volume specific heat. The in-cylinder pressure calculation block 53146 calculates the in-cylinder pressure P_cyl based on the adiabatic change in-cylinder pressure, the in-cylinder temperature, and the adiabatic change in-cylinder temperature.

  The above is the description of the in-cylinder temperature / pressure calculation block 5314, and all of the in-cylinder average temperature / pressure calculation block 531 in FIG. 6 has been described. Next, the knock occurrence index calculation block 532 of FIG. 6 will be described in detail with reference to FIG.

  Knock generation index calculation block 532 includes a reset flag calculation block 5321, an unburned gas temperature calculation block 5322, an instantaneous ignition delay reciprocal calculation block 5323, and a knock generation index calculation block 5324.

  Details of the reset flag calculation block 5321 are shown in FIG. The reset flag calculation block 5321 sets a reset flag when the crank angle CA exceeds the basic ignition timing MBTCAL. The unburned gas temperature calculation block 5322 has an unburned gas property value calculation block 53221 and an unburned gas temperature calculation block 53222 as shown in FIG. Since the unburned gas property value calculation block 53221 is the same as the gas property value calculation block 53141 (FIG. 19), the description thereof is omitted. The physical property value of only unburned gas is calculated by inputting zero as the mass combustion ratio. The unburned gas temperature calculation block 53222 calculates the unburned gas temperature T_ub based on the unburned gas temperature previous value, the in-cylinder pressure current value, the in-cylinder pressure previous value, and the specific heat ratio κ.

  In the instantaneous ignition delay reciprocal calculation block 5323, the instantaneous ignition delay reciprocal tauinv is obtained based on the unburned gas temperature T_ub and the in-cylinder pressure P_cyl. This map is obtained in advance by experiments. As shown in FIG. 24, knock generation index calculation block 5324 calculates time from engine speed NE, and integrates instantaneous ignition delay inverse tauinv according to the time to calculate knock generation index idx_kocr. If the reset flag is set, the initial value zero is set as the knock occurrence index idx_kocr.

  The above is the description of the knock occurrence index calculation block 532 in FIG. 6, and all of the knock occurrence indices 53 in FIG. 4 have been described. Next, the retard width calculation block 54 of FIG. 4 will be described in detail with reference to FIG. FIG. 25 is a diagram showing a detailed control block of the retard width calculation block 54.

  The retard width calculation block 54 includes a crank angle calculation block 541, a mass combustion ratio calculation block 542, a knock strength calculation block 543, and a retard width calculation block 544.

  The crank angle calculation block 541 calculates the knock generation crank angle CA_knk from the knock generation index idx_kocr (i) and the calculated crank angle CA_calc (i) based on a diagram previously obtained through experiments.

  The mass combustion ratio calculation block 542 calculates a knock generation mass combustion ratio X_bknk from the calculated crank angle CA_calc (i), the mass combustion ratio X_burn (i), and the knock generation crank angle CA_knk based on a diagram obtained in advance by experiments. Ask.

  Knock strength calculation block 543 determines knock strength I_knk from knock generation crank angle CA_knk and knock generation mass combustion ratio X_bknk based on a diagram previously obtained through experiments. In the diagram in the figure, the arrow direction (downward) is the retard side.

  The retard width calculation block 544 calculates a retard width (advance correction limit) CA_rtd from the knock intensity I_knk based on a diagram previously obtained through experiments.

  Next, the knock limit ignition timing calculation block 55 of FIG. 4 will be described in detail with reference to FIG. FIG. 26 shows a detailed control block of the knock limit ignition timing calculation block 55. The ignition timing ADV is obtained by retarding the retard width CA_rtd from the basic ignition timing MBTCAL.

  The control of the engine controller 50 shown in FIG. 4 has been described above.

  As described above in detail, according to the first aspect of the invention, the integration interval is appropriately set according to the operating state, so that both the calculation accuracy and the calculation load can be achieved. It is.

  According to the invention described in claim 2, the integral calculation is started from the ignition position (53-1). The integral start position should be the intake valve closed position to perform the integral calculation strictly, but actually, the integral value of the ignition delay hardly increases as compared with the subsequent period until the combustion starts. For this reason, even if the ignition position is set as the integration start position, the calculation accuracy can be ensured sufficiently and sufficiently, and since unnecessary sections are not integrated, the calculation load can be reduced.

  According to the invention described in claim 3, the integral calculation is terminated based on the combustion speed at the time of normal combustion in which knock does not occur. Knock is generated by explosive combustion of unburned gas at a time earlier than the end of combustion in the case of normal combustion. Therefore, it is sufficient to integrate for the combustion period assuming normal combustion. Since the combustion period is a function of the combustion speed, the integration interval can be determined based on the combustion speed.

  According to the fourth aspect of the present invention, the integral calculation is terminated when the combustion ratio calculated based on the combustion speed at the time of normal combustion becomes equal to or greater than the combustion end determination value (53-2). The combustion period (or the combustion end position) can be determined more appropriately by judging based on the combustion ratio. Actually, it is difficult to determine the position at which the combustion ratio becomes 100%, so there is no problem in terms of accuracy even if the combustion end is the time when the combustion ratio is equal to or higher than the combustion end determination value. In this way, the integration interval can be set appropriately.

  According to the fifth aspect of the present invention, the integral calculation is terminated when the knock occurrence index becomes equal to or greater than the knock index determination value (53-3). Since knock occurs when the knock occurrence index becomes equal to or greater than the knock index determination value, it is meaningless to continue the integration calculation thereafter. Therefore, the extra calculation can be omitted by terminating the integral calculation when the knock occurrence index becomes equal to or greater than the knock index determination value.

  According to the invention described in claim 6, when the combustion ratio is equal to or higher than the combustion end determination value (53-2), or when the knock occurrence index is equal to or higher than the knock index determination value (53-3), The integral calculation is ended when any of the conditions is met. By doing so, the integration interval can be appropriately and sufficiently set according to the operation state regardless of the occurrence of knocking.

  The present invention is not limited to the embodiment described above, and various modifications and changes can be made within the scope of the technical idea, and it is obvious that these are equivalent to the present invention.

It is the schematic for demonstrating the system of this invention. It is a figure explaining a knock generation mechanism. It is a figure explaining a knock generation mechanism. It is a control block diagram which shows the whole control of the ignition timing control apparatus by this invention. It is a figure explaining the knock generation index block 53 in detail. It is a figure which shows the knock generation parameter | index calculation block 530. FIG. 11 is a diagram showing an in-cylinder average temperature / pressure calculation block 531. It is a figure which shows the cylinder volume calculation block 5311. It is a figure which shows the emitted-heat amount calculation block 5312. FIG. It is a figure which shows the Wiebe function constant setting block 53121. It is a figure which shows the heat release rate calculation block 53122. It is a figure which shows the mass combustion ratio calculation block 53123. It is a figure showing calorific value / 1 cylinder / 1 cycle calculation block 53124. It is a figure showing calorific value / 1 cylinder / calculation interval calculation block 53125. FIG. 11 is a diagram showing details of a cooling loss calculation block 5313. It is a figure which shows the heat transfer coefficient calculation block 53136. It is a figure which shows the cooling loss calculation block 53137. FIG. 10 is a diagram showing an in-cylinder temperature / pressure calculation block 5314. It is a figure which shows the motoring-gas physical property value calculation block 53133. It is a figure which shows the total gas amount calculation block 53142. FIG. It is a figure which shows the knock generation parameter | index calculation block 532. FIG. 12 is a diagram showing a reset flag calculation block 5321. It is a figure which shows the unburned gas temperature calculation block 5322. FIG. 11 shows a knock occurrence index calculation block 5324. It is a figure which shows the detailed control block of the retard width calculation block. It is a figure which shows the knock limit ignition timing calculation block 55. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine 50 Engine controller 51 Operating condition detection means 523 Basic ignition timing calculation means 53 Knock generation index block 530 Knock generation index calculation block 531 In-cylinder average temperature / pressure calculation block 53121 Wiebe function constant setting block (combustion speed calculation means)
53123 Mass combustion ratio calculation block (combustion ratio calculation means)
532 Knock occurrence index calculation block (knock occurrence index calculation means)
5323 Instantaneous ignition delay reciprocal calculation block (self-ignition time calculation means)
5324 Knock occurrence index calculation block (knock occurrence index calculation means)
54 retard width calculation block (ignition timing control means (ignition timing correction amount calculation means))
55 Knock limit ignition timing calculation block (ignition timing control means)

Claims (6)

A self-ignition time calculating means for calculating a time τ during which the unburned gas self-ignites before the ignited fire is transmitted;
A knock occurrence index calculating means for calculating a knock occurrence index by time integrating the reciprocal 1 / τ of the self-ignition time τ;
Ignition timing control means for controlling the ignition timing based on the knock occurrence index;
An ignition timing control device for an internal combustion engine comprising:
The knock occurrence index calculating means changes the integration interval based on the driving state.
An ignition timing control device for an internal combustion engine. A basic ignition timing calculating means for calculating a basic ignition timing based on the operating state;
The knock occurrence index calculating means starts integral calculation from the basic ignition timing;
The ignition timing control device for an internal combustion engine according to claim 1, wherein the ignition timing control device is an internal combustion engine. Combustion rate calculation means for calculating the combustion rate during normal combustion without knocking,
The knock generation index calculating means ends the integral calculation based on the combustion speed during the normal combustion.
The ignition timing control device for an internal combustion engine according to claim 1 or 2, characterized by the above. Combustion rate calculation means for calculating a combustion rate based on the combustion speed during normal combustion,
The knock generation index calculating means ends the integral calculation when the combustion ratio is equal to or higher than a combustion end determination value.
The ignition timing control device for an internal combustion engine according to claim 3, wherein The knock occurrence index calculation means ends the integration calculation when the knock occurrence index is equal to or greater than the knock index determination value.
The ignition timing control device for an internal combustion engine according to claim 1 or 2, characterized by the above. A combustion rate calculating means for calculating a combustion rate at the time of normal combustion in which knock does not occur;
A combustion rate calculation means for calculating a combustion rate based on the combustion speed during normal combustion;
With
The knock generation index calculating means ends the integration calculation when either of the conditions is satisfied when the combustion ratio is equal to or higher than the combustion end determination value or when the knock generation index is equal to or higher than the knock index determination value. To
The ignition timing control device for an internal combustion engine according to claim 1 or 2, characterized by the above.

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