CONTROL APPARATUS OF INTERNAL COMBUSTION ENGINE

• US 20120016571A1
• Filed: 04/22/2009
• Published: 01/19/2012
• Est. Priority Date: 04/22/2009
• Status: Active Grant

• Current Assignee: Toyota Jidosha Kabushiki Kaisha (Toyota Motor Corporation)
• Original Assignee: Toyota Jidosha Kabushiki Kaisha (Toyota Motor Corporation)
• Inventors: Nada, Mitsuhiro
• Granted Patent: US 8,904,995 B2
• Time in Patent Office: Days
• US Class Current: 701/104
• CPC Class Codes: F02B 1/12 with compression ignition with fuel-air charge ignited by compression ignition of an additional fuel F02B7/00
• CPC Class Codes: F02B 2275/14 Direct injection into combustion chamber
• CPC Class Codes: F02B 23/0657 the spray interacting with one or more glow plugs
• CPC Class Codes: F02B 23/0672 Omega-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder center axis the surrounding wall being exactly vertical F02B23/0696
• CPC Class Codes: F02B 29/0406 Layout of the intake air cooling or coolant circuit
• CPC Class Codes: F02B 3/06 with compression ignition compression ignition engines using air or gas for blowing fuel into compressed air in cylinder F02B13/02
• CPC Class Codes: F02D 2250/36 Control for minimising NOx emissions
• CPC Class Codes: F02D 41/0057 Specific combustion modes combustion modes per se F02D41/3017
• CPC Class Codes: F02D 41/3035 a mode being the premixed charge compression-ignition mode
• CPC Class Codes: F02D 41/3064 with special control during transition between modes
• CPC Class Codes: F02D 41/365 with means for controlling timing and distribution
• CPC Class Codes: F02D 41/402 Multiple injections
• CPC Class Codes: F02D 41/403 with pilot injections
• CPC Class Codes: F02M 26/05 High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
• CPC Class Codes: F02M 26/10 having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
• CPC Class Codes: F02M 26/23 Layout, e.g. schematics
• CPC Class Codes: Y02T 10/12 Improving ICE efficiencies
• CPC Class Codes: Y02T 10/40 Engine management systems

Abstract

A series of combustion forms including initial low-temperature combustion, premixed combustion, and diffusive combustion are performed when an engine operates under a low load and a medium load. The initial low-temperature combustion is carried out by performing a small-amount injection while performing an operation for lowering the encounter rate between oxygen and a fuel spray in a cylinder, and thereby the heat generation rate is kept low and the amount of NOx generated is suppressed. The premixed combustion is carried out as fuel receives heat in the initial low-temperature combustion, and the amount of smoke generated is suppressed. The diffusive combustion is accomplished as fuel travels through the combustion field of the premixed combustion, and by controlling the fuel injection timing thereof, it is possible to suitably control the timing at which the heat generation rate reaches its maximum in the aforementioned series of combustion. Thereby, it is possible to concurrently suppress the amount of NOx generated, suppress the amount of smoke generated, and secure the required torque.

Claims

1. A control apparatus of a compression self-igniting internal combustion engine that is provided with an exhaust gas recirculation apparatus that recirculates part of exhaust gas discharged by an exhaust system in an intake system, and that performs, during a combustion process of the internal combustion engine, a main injection that is a fuel injection for torque generation from a fuel injection valve, the control apparatus comprising:

a fuel injection control means that sets, as injection periods of the main injection;

a “

fuel injection period for initial combustion”

for initial low-temperature combustion in which fuel is sequentially burnt in a cylinder while performing an encounter rate lowering operation that lowers an encounter rate between oxygen and a fuel spray in the cylinder,

a “

fuel injection period for diffusive combustion”

for performing diffusive combustion by performing, when a temperature in the cylinder is at or greater than a predetermined diffusive combustion starting temperature that leads to diffusive combustion, a fuel injection toward a region where a combustion temperature suppressing effect that is attained by exhaust gas recirculated by the exhaust gas recirculation apparatus can be used, and

a “

fuel injection period for transitional combustion”

that is set between the “

fuel injection period for initial combustion” and

the “

fuel injection period for diffusive combustion”

, and that is for performing transitional combustion composed of premixed combustion that continuously connects the initial low-temperature combustion and the diffusive combustion, as fuel, which was injected when the temperature in the cylinder was lower than the diffusive combustion starting temperature after the initial low-temperature combustion had started, undergoes spray-cooling by an endothermic reaction of fuel injected in the subsequent “

fuel injection period for diffusive combustion”

.

2. The control apparatus of an internal combustion engine according to claim 1, wherein

the fuel injection control means is configured so as to set a penetration of fuel injected in the “

fuel injection period for diffusive combustion”

to be greater than the penetration of fuel injected in the “

fuel injection period for initial combustion” and

the “

fuel injection period for transitional combustion”

.

3. The control apparatus of an internal combustion engine according to claim 1, wherein

the fuel injection control means is configured so as to substantially synchronize a start timing of the “

fuel injection period for diffusive combustion”

with a combustion start timing of fuel injected in the “

fuel injection period for transitional combustion”

, and to substantially synchronize a finishing timing of the “

fuel injection period for diffusive combustion”

with a timing at which a heat generation rate in combustion of fuel injected in the “

fuel injection period for transitional combustion”

reaches its maximum.

4. The control apparatus of an internal combustion engine according to claim 1, wherein

as for a fuel injection in the “

fuel injection period for initial combustion”

, the “

fuel injection period for transitional combustion”

, and the “

fuel injection period for diffusive combustion”

, the fuel injection control means is configured so as to suspend a fuel injection after termination of a fuel injection in the “

fuel injection period for initial combustion”

, then start a fuel injection in the “

fuel injection period for transitional combustion”

, suspend a fuel injection after termination of a fuel injection in this “

fuel injection period for transitional combustion”

, and then start a fuel injection in the “

fuel injection period for diffusive combustion”

.

5. The control apparatus of an internal combustion engine according to claim 1, wherein

as for a fuel injection in the “

fuel injection period for initial combustion”

, the “

fuel injection period for transitional combustion”

, and the “

fuel injection period for diffusive combustion”

, the fuel injection control means is configured so as to perform a fuel injection in the “

fuel injection period for initial combustion” and

a fuel injection in the “

fuel injection period for transitional combustion”

by a continuous fuel injection without stopping, and, on the other hand, to suspend a fuel injection after termination of a fuel injection in the “

fuel injection period for transitional combustion” and

then start a fuel injection in the “

fuel injection period for diffusive combustion”

.

6. The control apparatus of an internal combustion engine according to any one of claims 1, wherein

at least one operation selected from an exhaust gas recirculation operation by the exhaust gas recirculation apparatus, an intake throttling operation in the intake system, an operation for retarding a timing of a fuel injection from the fuel injection valve, and an operation for lowering the temperature in the cylinder is performed as the encounter rate lowering operation.

7. The control apparatus of an internal combustion engine according to claim 1, wherein

the fuel injection control means is configured so as to set a period in which the temperature in the cylinder is in a range from 750 K to less than 900 K as the “

fuel injection period for initial combustion”

, a period in which the temperature in the cylinder is in a range from 800 K to less than 900 K after the initial low-temperature combustion has started as the “

fuel injection period for transitional combustion”

, and a period after the temperature in the cylinder reaches 900 K after the transitional combustion has started as the “

fuel injection period for diffusive combustion”

.

8. The control apparatus of an internal combustion engine according to claim 1 wherein

fuel injections in the “

fuel injection period for initial combustion”

, the “

fuel injection period for transitional combustion”

, and the “

fuel injection period for diffusive combustion”

are performed when the internal combustion engine operates under a low load and a medium load, and

a proportion of a fuel injection amount in the “

fuel injection period for transitional combustion”

relative to a total injection amount, which is a sum of amounts of fuel injected in the respective injection periods, is set such that the greater the load in a region from the low-load operation to the medium-load operation, the greater the proportion.

9. The control apparatus of an internal combustion engine according to claim 1, wherein

fuel injections in the “

fuel injection period for initial combustion”

, the “

fuel injection period for transitional combustion”

, and the “

fuel injection period for diffusive combustion”

are performed when the internal combustion engine operates under a low load and a medium load, and

the control apparatus is configured such that when the internal combustion engine operates under a high load, initial diffusive combustion is performed in which an average heat generation rate over a predetermined period during an earlier period after combustion has started in the cylinder is substantially identical to an average heat generation rate over a period in which the initial low-temperature combustion is performed.