Internal combustion engines with exhaust gas recirculation

Abstract: A turbocharger for an engine employing exhaust gas recirculation includes a compressor (3) connected to a turbine, the outlet passage of the compressor including a diffuser (15) defined by two opposed spaced walls (16, 17). An inlet opening for connection to a recirculated exhaust gas passage (8) is provided in one of the walls (16). An annular chamber (18) is also formed in the wall (16). The chamber communicates with the inlet opening and with the diffuser (15) via an opening (19) which is also provided in the wall (16).

Description: The present invention relates to internal combustion engines and is concerned with exhaust gas recirculation systems for recirculating part of the engine's exhaust gas back to the air inlet so as to reduce the content of undesirable pollutants in the exhaust gas. Exhaust gas recirculation is known as one of the ways of purifying the exhaust gas from a vehicle engine. In an exhaust gas recirculation system a proportion of the exhaust gas is fed back from the exhaust system of the engine and is returned to the inlet system where it is added to the air-fuel mixture. This increases the ratio of incombustible gas, such as H₂O, N₂ and CO₂, in the combustion air-fuel mixture and thus decreases the combustion temperature so that the generation of NO x is reduced or suppressed. However, if an excessive quantity of exhaust gas is recirculated, the combustion becomes unstable and both the hydrocarbon level in the exhaust gas and the fuel consumption increase. Therefore, it is necessary to control the amount of exhaust gas which is recirculated within certain limits at which the desired NO x level and engine stability are compatible. Figure 1 is a schematic view of an exhaust gas recirculation system forming part of an engine with a turbocharger which is known from JP-U-1-173445. More specifically, the turbocharger 1 has a turbine 2 and a compressor 3 which are connected together via a bearing casing 4. The turbine 2 is positioned within a duct connected to an exhaust manifold 6 which serves as an exhaust passage of the engine 5. The turbine 2 is driven by exhaust gas from the engine 5 to drive the compressor 3 which compresses the inlet air and supplies it through a suction or inlet passage 7 to the engine 5. A recirculation passage 8 is provided between the exhaust manifold 6 and a portion of the inlet passage 7 situated only shortly upstream of the engine inlet so as to pass a proportion of the exhaust gas G from the engine 5 through the recirculation passage 8 back to the inlet passage 7. Control valves 10 and 11 are provided respectively at the inlet and outlet ends of the recirculation passage 8 and are opened and closed in response to command signals produced by a controller 9. In the above known system, the recirculation passage 8 is connected at its outlet to a point in the inlet passage 7 where the air pressure has been increased by the compressor 3. Therefore, the exhaust gas sometimes flows in the reverse direction, depending upon the pressure conditions, resulting in failure to recirculate the exhaust gas to the engine inlet system. To overcome this problem, one might contemplate the possibility that the recirculation passage 8 be connected to the inlet passage 7 upstream of the compressor 3. However, this would result in the compressor impeller becoming contaminated by the exhaust gases and thus in a reduction in performance of the turbocharger 1. Further, if there are any pressure pulses in the exhaust gas, pressure waves acting on the compressor impeller may cause undesirable resonance thereof. FR-A-2322264, on which the precharacterising portion of claim 1 is based discloses a turbocharger with a diffuser defined by two walls, in one of which there is an inlet opening for recirculated exhaust gas. The inlet opening is connected to the exhaust gas inlet to the turbocharger by a pipe which includes a receiver or compliant volume and a cooler. It is, therefore, the primary object of the present invention to provide an exhaust gas recirculation system in which a proportion of the exhaust gas from an engine having a turbocharger can be recirculated back into the engine inlet system without contaminating the compressor impeller and in such a manner that resonance of the compressor impeller is prevented, even when there are pressure pulses in the exhaust gas. According to the present invention a turbocharger for an engine employing exhaust gas recirculation of a type including a compressor connected to a turbine, the outlet passage of the compressor including a diffuser defined by two opposed spaced walls, in one of which there is an inlet opening for recirculated exhaust gas, is characterised by an annular chamber which is formed in the said one of the opposed walls and communicates with the inlet opening and by an opening in the said one of the opposed walls which connects the chamber to the diffuser. Thus all the essential features of the exhaust gas recirculation system in accordance with the invention are embodied in a turbocharger. In use, the exhaust gas from the exhaust gas passage of the engine is introduced into the air inlet passage of the engine not at a position downstream of the turbocharger but into the diffuser of the turbocharger compressor in which, in use, a relatively low pressure prevails. This means that the exhaust gas may be fed back into the inlet of the engine without being impeded by the high pressure produced by the turbocharger compressor. This results in the impeller of the compressor not being contaminated by the exhaust gases since the diffuser is located downstream of the impeller. Furthermore, any possible pressure pulses in the exhaust gases are not permitted to act on the impeller since they are inherently attenuated in the chamber and this means that the impeller is prevented from being induced to resonate by pressure pulses. The inlet opening, the annular chamber and the opening which connects the chamber to the diffuser may be formed in either of the two opposed walls which define the diffuser but it is preferred that they are provided in that wall which is closest to the turbine. The opening in the wall may be one of a number of openings or there may be only a single opening and in the latter case it is preferred that the opening is annular, e.g. in the form of a slit. The opening is preferably partly defined by a plate which is removably connected to the compressor casing, to permit it to be replaced or its position adjusted, and forms part of the wall. In a preferred embodiment of the invention a water cooling jacket is attached to the outer surface of the said one of the opposed walls. This results in cooling of the chamber and thus of the recirculated exhaust gas. This contributes to the reduction in the amount of nitrogen oxides in the exhaust gas. The present invention also embraces an internal combustion engine including an inlet passage, an exhaust gas passage, a turbocharger and an exhaust gas recirculation passage arranged to pass a proportion of the exhaust gas flowing through the exhaust gas passage into the air inlet passage and this engine is characterised in that the turbocharger is of the type referred to above and that the exhaust gas recirculation passage is connected to the inlet opening in the said one of the opposed walls. Further features and details of the invention will be apparent from the following description of two specific embodiments which is given by way of example with reference to Figures 2 and 3 of the accompanying drawings which are schematic scrap sectional views of first and second embodiments, respectively, of the invention which is embodied in a turbocharger, only a portion of the turbocharger compressor being shown in each case. The embodiment shown in Figure 2 is functionally similar to the system shown in Figure 1 in that a turbocharger 1, which includes a turbine 2 and a compressor 3 connected together by means of a bearing casing 4, is mounted on an engine 5 and a proportion of the exhaust gas G from the engine 5 is returned through a recirculation passage 8 to the engine inlet system by which air is supplied to the engine 5. The distinction from the system of Figure 1 is that the exhaust gas G from the recirculation passage 8 is introduced into the diffuser 15 which is defined between the compressor impeller 12 of the compressor 3 and the compressor scroll 14 in the compressor housing 13 at the outer periphery of the compressor impeller 12. More specifically, opposed annular portions of the compressor housing 13 constitute walls 16 and 17 which define the diffuser 15, which is of annular shape. An annular chamber 18 is provided in the diffuser defining wall 16 adjacent to the bearing casing 4. The recirculation passage 8 is connected at its outlet to the outer surface of the diffuser defining wall 16 and communicates with the chamber 18 through an inlet in the wall 16. An opening, such as an annular slit 19, is provided in the inner surface of the diffuser defining wall 16, namely an inner plate 16a, and thus connects the inner portion of the chamber 18 to the diffuser 15 so that exhaust gas G fed from the recirculation passage 8 into the chamber 18 is introduced through the slit 19 into the diffuser 15. The diffuser defining wall 16 is a separate component from the bearing casing 4 and the inner plate 16a directly defining the diffuser 15 is replaceably mounted by means of a bolt 20 to permit the adjustment of the size of the slit 19. Reference numeral 21 represents a seal plate integrally mounted on the inner periphery of the diffuser defining wall 16. In use, a proportion of the exhaust gas G in the exhaust manifold 6 (see Figure 1) of the engine 5 flows to the compressor 3 through the recirculation passage 8, enters into the chamber 18 in the diffuser defining wall 16 and is then introduced into the diffuser 15 through the slit 19 in the plate 16a. If it is supposed that the pressure at the discharge opening of the compressor 3 is 1, then the pressure in the diffuser 15 is about 0.6, that is to say relatively low, so that the exhaust gas can flow freely from the exhaust manifold 6 of the engine 5 into the engine inlet system without being hindered by the pressure generated by the compressor 3. The compressor impeller 12 is not contaminated by the exhaust gas since the diffuser 15 is positioned downstream of it. Even when the exhaust gas discharged from the engine 5 has pressure pulses, no pressure waves are transmitted to the compressor impeller 12 and resonance is thus prevented due to the fact that the exhaust gas is passed firstly into the chamber 18, which acts as a compliant volume, before being introduced into the diffuser 15 and is converted into uniform flow throughout the chamber 18. The diffuser defining wall 16 is a separate component from the bearing casing 4 and the inner plate 16a is designed to be replaceable so that it is possible to select its mounting angle or the exhaust gas flow rate by changing the diffuser defining wall 16 itself or the inner plate portion 16a thereof. This increases the flexibility of the system to comply with different requirements. Figure 3 shows a modified embodiment which is similar to the embodiment shown in Figure 2 except that a water-cooling jacket 22 is mounted on the outer surface of the diffuser defining wall 16 adjacent to the bearing casing 4. The chamber 18 in the diffuser defining wall 16 is cooled down by the water-cooling jacket 22. Exhaust gas flowing into the chamber 18 is thus cooled before it is introduced into the diffuser 15. It is thus possible to reduce the temperature of the air-fuel combustion mixture in the engine 5 and thus to reduce the NO x content of the exhaust gases. It will be understood that the invention is not limited to the embodiments described above and that various modifications may be made. For example, the chamber 18 is formed in the diffuser defining wall 16 adjacent to the bearing casing 4 in the embodiments of Figures 2 and 3; however, the chamber 18 may be arranged in the diffuser defining wall 17 which is remote from the bearing casing 4 and is opposed to the diffuser defining wall 16, the recirculation passage 8 being connected to the wall 17 and the slit 19 being provided in the wall 17.

Claims: A turbocharger for an engine employing exhaust gas recirculation including a compressor (3) connected to a turbine (2), the outlet passage of the compressor including a diffuser (15) defined by two opposed spaced walls (16,17), in one (16) of which there is an inlet opening for recirculated exhaust gas (G) characterised by an annular chamber (18) which is formed in the said one (16) of the opposed walls (16, 17) and communicates with the said inlet opening and by an opening (19) in the said one (16) of the opposed walls (16, 17) which connects the chamber (18) to the diffuser (15). A turbocharger as claimed in Claim 1, characterised in that the inlet opening, the annular chamber (18) and the opening (19) are formed in that one (16) of the two opposed walls (16, 17) which is closest to the turbine. A turbocharger as claimed in Claim 1, characterised in that the opening (19) is an annular opening. A turbocharger as claimed in Claim 2 or 3, characterised in that the opening (19) is partly defined by a plate (16a) which is removably connected to the compressor casing (13) and forms part of the wall (16). A turbocharger as claimed in any one of the preceding claims, characterised by a water-cooling jacket attached to the outer surface of the said one (16) of the opposed walls (16, 17). An internal combustion engine including an air inlet passage, an exhaust gas passage, a turbocharger and an exhaust gas recirculation passage arranged to pass a proportion of the exhaust gas flowing through the exhaust gas passage into the air inlet passage, characterised in that the turbocharger is as claimed in any one of the preceding claims and that the exhaust gas recirculation passage (8) is connected to the inlet opening in the said one (16) of the opposed walls (16, 17).

Inventors: MITSUBORI KEN, MITSUBORI, KEN
Applicants: ISHIKAWAJIMA HARIMA HEAVY IND, ISHIKAWAJIMA-HARIMA JUKOGYO KABUSHIKI KAISHA
Application year: 1993
Main classification: F02M25
IPC codes: F02B37, F04D25, F02B39, F02M25