SUPERCHARGED INTERNAL COMBUSTION ENGINE

Abstract: Turbocharged internal combustion engine with exhaust return via a valve (7) on the intake side (5) of the turbocompressor unit (2) to the engine intake side. The turbine (3) and the compressor (4) of the turbocompressor unit are adapted to each other and to the engine in such a way that the pressure on the inlet side (5) of the turbine is always higher than the pressure on the pressure side (14) of the compressor. The rotary shaft (17) of the unit is coupled via a drive chain (18, 19, 20) containing a continuously variable transmission (19) to the crank shaft (21) of the engine. An electronic control unit (22) controls the transmission ratio and the degree of opening of the valve.

Description: Supercharged internal combustion engine The present invention relates to a supercharged internal combustion engine compris¬ ing firstly a turbocompressor unit with an exhaust driven turbo unit, which has an inlet conimunicating with the exhaust side of the engine, and a compressor unit, which has a suction side communicating with the surrounding atmosphere and a pressure side communicating with the engine intake side, and secondly an exhaust recirculation valve coupled between the exhaust side ofthe engine and the inlet of the turbo unit, said valve being settable for recirculation of a certain portion of the exhaust to the engine intake side. Exhaust can be returned to the intake side of a supercharged engine in essentially two different ways, each having different advantages and disadvantages, namely be¬ fore or after the compressor. The simplest method technically would be to connect the recirculation line to the suction side ofthe compressor, but in that case the ex¬ haust must pass through the compressor and then through the charge air cooler which is usually present. A significant disadvantage of tiiis is however, that all the components would in time become coated with haπnful soot from the exhaust. This disadvantage can be avoided by introducing the exhaust downstream of said compo- nents but if a turbo unit is used with the desired high efficiency, the charge air pres¬ sure will be higher than the exhaust pressure within the normal operating rpm range of the engine, which means that some form of pump device is desired which increa¬ ses the exhaust pressure to a level above the charge air pressure. A supercharged engine with an exhaust pump in the form of an ejector pump is known by SE-A- 9301093-2. The purpose of the present invention is in general to achieve a supercharged internal combustion engine of the type described by way of introduction which permits re¬ turn of exhaust to the intake side downstream of the compressor wihtout requiring an exhaust pump. This is achieved according to othe invention by virtue of the fact that the turbo unit and the compressor unit are so adapted to each other and to the engine that, within the normal operating speed range of the engine, the exhaust pres¬ sure on the inlet side of the turbo unit is higher than the charge air pressure on the pressure side of the compressor unit. As regards design, this can be achieved with a turbocompressor which is dimensio¬ ned so that the pressure fall over the turbine will be greater than normal. A certain loss of efficiency in the turbo unit is in this case unavoidable. In a preferred further development ofthe engine according to the invention, the turbo unit is coupled to the engine crank shaft via a reduction gearing and a conti¬ nuously variable transmission. The loss which arises when redistributing the pressures can thus be recovered so that final result will be a net gain despite the in¬ crease in the exhaust pressure on the intake side ofthe turbo unit. An engine with these characteristic features thus fulfills three important conditions. By combining the setting ofthe degree of opening ofthe valve towards the engine intake side with a suitable setting of the rpm ofthe compressor with the aid of the continuously vari¬ able transmission, both the exhaust percent and the amount of air on the intake side can be freely controlled at each point on the operational curve ofthe engine at the same time as the compound arrangement permits exhaust return without any loss of efficiency. The invention will be described in more detail below with reference to examples shown in the accompanying drawing where the Figure shows schematically one embodiment of an engine installation with a six cylinder internal combustion engine. The engine 1 in the Figure can be a four stroke diesel engine. It shows a turbocomp¬ ressor unit, generally designated 2, which comprises a turbo unit 3 and a compressor unit 4. The turbo unit 3 is connected on its suction side 5 to an exhaust conduit 6 including an adjustable three way exhaust return valve 7, to which an exhaust conduit 8 is also connected. The conduit 8 is connected via an exhaust cooler 9 to the engine intake manifold (not shown). The outlet 10 from the turbo unit is connected to an exhaust pipe 11. The compressor 4 is connected on its inlet side 12 via a conduit 13 to an intake filter (not shown) and on its outlet side 14 via a conduit 15 to a charge air cooler 16 to the engine intake manifold. As can be seen from the Figure the conduit 8 is connected to the engine charge air side downstream of the charge air cooler 16 which, in addition to avoiding soot deposit in the cooler, is advantageous as regards function due to the fact that there is a pressure drop over the cooler. The turbocompressor unit 2 has a rotary shaft 17, which is coupled, via a high speed gearing 18, a continuously variable transmission (CVT) 19 and a low speed gearing 20. to the engine crank shaft 21. In the component chain from the rotary shaft 17 to the crank shaft 21 there can be included a clutch and/or torsion damper, by means of which the driving connection between the rotary shaft 17 and the crank shaft 21 can be broken. In the high speed gearing 18 a first rpm reduction is provided from the operating rpm ofthe turbo unit of approximately 100,000 φm down to the CVT operating rpm of about 10,000 rpm. In the low speed gearing 20, the φm is reduced further to the operating φm of the crank shaft of about 2,000 φm. The transmission ratio in the CVT 19 and the degree of opening of the valve 7 towards the conduit 8 is controlled by an electronic control unit 22, which contains a microprocessor, in which the amount of returned exhaust and the amount of air is programmed for each operational point within the normal operational speed range of the engine, which can be expressed simply as being the φm range from maximum engine torque to maximum engine power. The turbo unit 3 and the compressor unit 4 are furthermore dimensioned relative to each other and to the engine so that the pressure in the exhaust conduit 6 is always higher than the pressure in the charge air conduit 15 within the normal engine operating range. The smaller the pressure diffe¬ rence is, the more the valve 7 must be open towards the conduit 8 to provide a given amount of exhaust. The amount of air is controlled by the compressor φm, which is regulated by the CVT. The control unit 22, which controls this, can be the electronic control unit which is present in most modem engines and which controls all engine functions as a function of vehicle engine data fed into the control unit from sensors known per se and not shown in more detail here. The invention has been described above with reference to a preferred embodiment which has a transmission with a continuously variable transmission ratio, i.e. of the type which is usually called CVT. Wilihin the scope of the invention there can be also be used fixed gear transmissions in which the transmission ratio can be varied in steps, or hydraulic transmissions, electrical transmissions or other types of transmissions with variable transmission ratios.

Claims: Claims 1. Supercharged internal combustion engine, comprising firstly a turbocompressor unit with an exhaust driven turbo unit, which has an inlet communicating with the exhaust side of the engine, and a compressor unit which has a suction side communicating with the surrounding atmosphere and a pressure side communicating with the engine intake side, and secondly an exhaust recirculation valve coupled between the exhaust side of the engine and the inlet of the turbo unit, said valve being settable for recirculation of a certain portion of the exhaust to the engine in- take side, characterised in that the turbo unit (3) and the compressor unit (4) are so adapted to each other and to the engine that, within the normal operating speed range of the engine, the exhaust pressure on the inlet side (5) of the turbo unit is higher than the charge air pressure on the pressure side (14) of the compressor unit. 2. Internal combustion engine according to claim 1. characterised in that the turbo unit (3) is coupled via a transmission (18,19,20) to the crank shaft (21) ofthe engine. 3. Internal combustion engine according to claim 2, characterised in that the turbo unit (3) is coupled to the crank shaft (21) of the engine via a reduction gearing (18) and a transmission (19) with a variable transmission ratio. 4. Internal combustion engine according to claim 3, characterised in that the transmission (19) has a continuously variable transmission ratio. 5. Internal combustion engine according to one of claims 1-4, characterised in that the compressor unit (4) communicates with the intake side ofthe engine via a charge air cooler (16) and that the valve (7) communicates with the engine intake side downstream of the charge air cooler. 6. Internal combustion engine according to one of claims 1-5, characteπsed in that the valve (7) communicates with the engine intake side via an exhaust gas cooler (9). 7. Internal combustion engine according to one of claims 3-6, characterised in that the valve (7) and the transmission (18) with variable transmission ratio are control¬ led relative to each other by an electronic control unit (22).

Inventors: DAHLGREN MAGNUS, UDD SOEREN, DAHLGREN, MAGNUS, UDD, SOEREN
Applicants: DAHLGREN MAGNUS, UDD SOEREN, VOLVO AB, AB VOLVO, DAHLGREN, MAGNUS, UDD, SOEREN
Application year: 1997
Main classification: F02M25
IPC codes: F02B3, F02B29, F02B37, F02B39, F02B41, F02B75, F02D23, F02M25