EP0016116A1

EP0016116A1 - Exhaust system

Info

Publication number: EP0016116A1
Application number: EP79900817A
Authority: EP
Inventors: Louis ANDERSSON (deceased)
Original assignee: Andersson Jan; Helger Marie Louise
Current assignee: Andersson Jan; Helger Marie Louise
Priority date: 1978-06-29
Filing date: 1980-02-12
Publication date: 1980-10-01
Also published as: EP0008281A1; JPS55500477A; WO1980000167A1; DE2831376A1

Abstract

Abrege Un systeme d'echappement se caracterise par une faible teneur en impuretes le traversant et un niveau sonore peu eleve, ce systeme d'echappement etant destine a une source de chaleur a impulsions, specialement un moteur a combustion interne. Les gaz d'echappement provenant des differents cylindres d'un tel moteur (1) sont conduits au travers de tuyaux de longueur identique (9) dans un collecteur (10), auquel est rattache tuyau d'echappement (12) ayant une epaisseur de paroi et un diametre uniforme, Ledit tuyau d'echappement se termine par un couvercle annulaire (13). Dans un orifice amenage dans ledit couvercle, un tube interne (14) est introduit de maniere etanche aux gaz dans le tuyau d'echappement (12). La longueur des parties du systeme d'echappement est telle que trois types d'ondes se propagent. Une desdites ondes est une onde de pression negative, commencant au point mort d'un piston (5) dans le moteur (1) et se terminant a l'extremite cote interne (15) du tube interne (14), et est adaptee de maniere a ce que des noeuds apparaissent aux-deux extremites. Une autre onde est une onde de vitesse des gaz commencant aux soupapes d'echappement (4) et se terminant au couvercle annulaire (13) et est adaptee pour que des ventres apparaissent aux deux extremites. Ces deux ondes concernent les gaz d'echappement. Une troisieme onde concerne les niveaux sonores et est adaptee pour se produire entre la soupape d'echappement (4) et ledit couvercle (13), ayant un noeud a l'extremite cote interne (15) du tube interne (14).Bleed An exhaust system is characterized by a low content of impurities passing through it and a low noise level, this exhaust system being intended for a pulsed heat source, especially an internal combustion engine. The exhaust gases from the various cylinders of such an engine (1) are conducted through pipes of identical length (9) in a manifold (10), to which is attached the exhaust pipe (12) having a thickness of wall and a uniform diameter, Said exhaust pipe terminates in an annular cover (13). In a port provided in said cover, an internal tube (14) is introduced in a gas-tight manner into the exhaust pipe (12). The length of the parts of the exhaust system is such that three types of waves propagate. One of said waves is a negative pressure wave, starting at the dead center of a piston (5) in the motor (1) and ending at the inner side (15) end of the inner tube (14), and is adapted to so that knots appear at both ends. Another wave is a gas velocity wave starting at the exhaust valves (4) and ending at the ring cover (13) and is tailored so that bellies appear at both ends. These two waves relate to the exhaust gases. A third wave relates to sound levels and is adapted to occur between the exhaust valve (4) and said cover (13), having a knot at the inner side (15) of the inner tube (14).

Description

EXHAUST SYSTEM

Technical „f.ield

The present invention refers to an exhaust system for a pulsating heat source, especially for an internal combus¬ tion engine, as stated in the preamble of the enclosed main claim. The invention is primarily intended for internal combustion engines for motor vehicles, but may advantageous¬ ly also be used for engines in ships and in aeroplanes or for stationary engines. In the following, however, en ex¬ haust system for an internal combustion engine in a motor vehicle will be described.

The object of an exhaust system is, as is well known, to reduce, where this is desired, the sound level of the exhaust gases coming from a pulsating heat source. More¬ over, it is desirable that the exhaust system shall con- tribute to purifying the exhaust gases and to reducing the discharge of unburned rests and of injurious products.

Background art

Known exhaust systems -do not solve the combination of these problems in a sufficient manner. Thus, they do not, in a dufficiently effective manner, simultaneously succeed in reducing the sound level and in giving a satisfactory purification of the exhaust gases. A step forward, however, to such a solution is the utilization of the principle of standing waves in the exhaust system, giving the possibili- ty of especially improving the sound damping. An example

OMPI of such a solution is given in the inventor's Swiss patent specification No. 478 335.

The invention

The inventor has now, by the present invention, succe ded in essentially improving the results obtained by using the principle of standing waves. It has thereby been pos¬ sible to obtain an improvment both with respect to the sou damping and the gas purification.

. The solution of this problem is, according to the in- vention, obtained by using the measures stated in the cha¬ racterizing portion of the enclosed main claim.

According to the invention the distances through the partial pipes of the manifold of the internal combustion e gine from the exhaust valves to a point where they join each other, a so called junction, or to a connecting flang or the like on said manifold should be made substantially equal in length. From said junction one single exhaustpip of uniform thickness continues and has an inner sectional area .which is four times or somewhat less the sectional ar of an exhaust..channel in the engine. The exhaust pipe is. terminated by an annular gable, in which a short inner pip is inserted. The inner sectional area of the inner pipe i substantially equal to the area of an exhaust channel in t engine, and its length must be substantially equal to the distance from a point in the engine somewhat below the bot tom dead centre of a piston in a cylinder to said junction of the partial pipes in the manifold. It should, thus, be observed that the exhaust system is considered to begin at said point below the bottom dead centre for a piston and that its termination is constituted by the outer end of th inner pipe.

It is important according to the invention that the e haust system is so dimensioned that three distinct standin waves are formed therein. Through the combustion in the cylinders and through the ejector effect at the exhaust valves and at the said junction of the partial pipes in th manifold a low pressure wave will arise which is tuned to form an even number of half-periods of a standing wave be¬ tween said point somewhat below the bottom dead centre for a piston in a cylinder of the engine and the in-side end of the inner pipe. Due to the process of combustion in the en¬ gine a rotating gas wave is generated at the exhaust valves. Said gas wave is tuned to form an even number of periods of a standing wave between the exhaust valves and the inner wall of the terminating gable of the exhaust pipe, whereby loops should be formed at the ends of the standing wave. Said gas wave serves to propel the gas in the exhaust sys¬ tem. Finally, a standing sound wave is generated in the ex¬ haust system between the exhaust valves of the engine and the inner wall of the terminating gable of the exhaust pipe, which wave should have a node at the inside end of the inner pipe.

By means.,of such-an exhaust system the desired advan¬ tages are attained. The arising of said advantages may be explained in the following way: Due to the ejector effect obtained when an exhaust valve is opened and in the transition region from the par¬ tial pipes of the manifold to the exhaust pipe, the exhaust _.gases from each cylinder in the engine will be exhausted very efficiently. Since the exhaust pipe does not produce any resistance to the exhaust gases owing to the tuning per¬ formed, each cylinder will be completely emptied under the influence of a vacuum being generated by said ejector ef¬ fect. Said vacuum will be active during the whole working process of the exhaust valve. Thereby, when the inlet valves open, the subsequent filling of the cylinders will be improved. An increased filling degree will be obtained compared with what is possible in previously known engines. The amount of fuel fed to the cylinders will almost corres¬ pond to the amount of oxygen in the air supplied to the en- gine. An overdosage of fuel for the purpose of cooling the combustion chamber, as has previously been usual, will not be necessary any longer. Since the cylinder has a negative pressure when the exhaust valve is closing (about 0.5 at), a filling will moreover be obtained without the previousl occuring delay caused by the overpressure (about 4 at) in the cylinder. Since no exhaust gas rests remain in the c linder when the subsequent filling occurs, and the fuel mixture supplied will thus be almost ideal, a higher com¬ bustion temperature (1250 °C against previously 890 C) , will be obtained and may also be permitted. A complete combustion will be obtained, and, consequently, no soot, carbon monoxide, no nitric oxides, no nitrous gases and n even any water vapour. This constitutes an advantage, since, for instance, no deposit of soot is obtained in th cylinders and on the ignition plugs, and no water vapour supplied to the exhaust system.

The vacuum developed during the exhaust phase will c tribute to a rapid cooling of the walls of the combustion chamber (to about 700 °C) , which is one of the explanatio why a higher combustion temperature may be permitted. The negative pressure will also, as has been mentioned above, cause a better filling, and the lower temperature obtaine in the cylinder after the combustion process will cause a better compression of the subsequently supplied fuel mixt

Said negative pressure is caused by the tuned exhaus gas .system. By means thereof the negative pressure wave will be forced to operate already from a point below the bottom dead centre of the piston. The exhaust system wil due to the better emptying, the better filling by a corre ly adapted fuel-air mixture and the more complete combust process only obtain pure exhaust gases, which do not have any measurable quantities of inconvenient gases, such as carbon monoxide and nitrous gases and water vapour. Only the lead compounds existing in the fuel, such as tetraeth lead, will be propelled through the exhaust system, but w be deposited on the inner envelope surface of the exhaust pipe due to the turbulence of the exhaust gases. An engine provided with the new exhaust system will give the engine increased power, due to the co-operating causes stated above. The more complete, hotter combustio combustion process in the cylinders contributes thereto a

^ permits a higher piston pressure. The combustion will be completely finished before the piston has reached its lower piston position. Moreover, the fuel will be better utili¬ zed. No exhaust gas rests will appear which could carry off heat, neither in the cylinders nor in the exhaust pipe. An important reason is that the exhaust system works with a sucking negative pressure, making the favourable temperature conditions in the cylinder possible. Said negative pressure also contributes to a rapid cooling of the exhaust gases and this is the reason why no power consuming overcoming of a - counter pressure in the exhaust system occurs. Altogether, said improving effects allow an increased engine power of about 30 per cent.

The very good sound, damping is obtained due to the fact that the negative pressure in the exhaust system is a bad conductor of sound, and that no unburnt sound conducting gas rests can occur, and that the standing sound wave has a node at the in-side end of the inner pipe, where the exhaust ga¬ ses leave the exhaust system. Simultaneously, the velocity of the driving gas wave has a maximum point just before said in-side end of the inner pipe.

Detailed description

In the following description a nearer explanation of the in¬ vention will be given in connection with the Figures on the .attached drawings. On said drawings Fig. 1 diagrammatically illustrates an internal combustion engine having a manifold from the exhaust valves, and an exhaust pipe connected to the manifold according to the invention. Fig. 2 shows the exhaust system still more skeletonized. Figs. 3, 4 and' 5 illustrate the standing waves typical for the exhaust sys¬ tem according to the invention. Thus, Fig. 3 shows a stan¬ ding negative pressure wave for the exhaust gases in the system, Fig. 4 shows a standing turbulent gas wave for pro¬ pelling the exhaust gases in the system, and Fig. 5 shows a standing sound wave in the- system. Figs. 6, 7 and 8 il¬ lustrate, in a very diagrammatical way, the exhaust system

O PI Λ WIPO with the three standing waves.

A part of a combustion engine 1 is illustrated diagra matically in perspective by a sectional view through a cyr linder 2. The engine may have a random number of cylinder and there is no limitation to the two cylinders indicated by solid lines and the third cylinder indicated by dashed lines. Normally, the engine has four or six cylinders. Ea cylinder has an inlet valve 3, an exhaust valve 4 and a pi ton 5, the latter being in a conventional manner connected to a crankshaft 6 via a piston rod 7. The exhaust channel 8 of each cylinder is connected to a partial pipe 9 in a manifold 10 for the engine. An exhaust pipe 12 is connec¬ ted to a flange 11 or the like on the manifold 10. The ex haust pipe 12 can be comparatively thin-walled .and can, if so is desired, be bent. Its length shall be adapted in accordance with the requirements stated by the invention. The exhaust pipe 12 is. terminated by an annular gable 13, in which a comparatively short inner pipe 14 is inserted. The exhaust pipe 12, the gable 13 and one end of the inner pipe are gas-tight joined to each other, for instance by welding. Gas escape from the exhaust pipe 12 is thus made possible sol-ely through the inner pipe 14. If necessary, appropriate supports may be arranged between the in-side end 15 of the inner pipe and the inner envelop surface of the enclosing exhaust pipe. To the outer envelop sur¬ face of the last mentioned pipe one or more fastening mean can be attached for mounting the exhaust system under the motor vehicle. The dimensioning of the inner pipe should also meet the requirements by the invention. In Fig. 2 the exhaust system is further skeletonized in order to facilitate the explanation of the mode of ope¬ ration of the invention. From the left-hand side one re¬ cognizes the piston 5 of the engine, the exhaust valve 4, the partial pipes 9 of the manifold 10, the junction 11 (th flange) between the manifold and the exhaust pipe, the ex¬ haust pipe 12, the inner pipe 14 and the gable 13 at the terminating end of the exhaust pipe.

The designations below Fig. 2 indicate reference poin for the description of the oscillation waves in the exhaust system. Thus, number 16 indicates the point which is said to be situated somewhat below the bottom dead centre of the piston 5. Number 17 indicates the valve seat 17 for one of the exhaust valves 4. Number 18 indicates the junction be¬ tween the partial pipes 9 in the manifold 10, i.e. substan¬ tially the connecting flange 11. Number 15 indicates the free in-side end of the inner pipe 14, and number 13 indi¬ cates, as mentioned above, the free gable end of the exhaust pipe.

In Fig. 3 a diagram is shown of the gas pressure in the exhaust system as a function of its length. The curve indi¬ cates a negative pressure curve and shows its course from an initial point 16 with principally atmospheric pressure at said point below the bottom dead centre of the piston 5, to an illustrated end point 15, positioned at the in-side end of the inner pipe 14. The distance between the initial point 16 and the end point 15 is so selected that a standing wave arises which must have nodes at the terminal points. According to gas flow laws the curve will mainly obtain the course illustrated, having a so-called dead zone along the central portion. At the beginning and at the end of the curve a marked negative pressure is obtained, caused by the ejector effect at the exhaust valves 4 and at the junction at the flange 11 and being periodically repeated after said dead zone.

For propelling the gas along the exhaust pipe 12 a standing gas wave is arranged according to Fig. 4. The ve¬ locity of said wave, as a function of the length of the ex- haust system, is shown by the illustrated periodic curve. Said curve shall have a loop at the initial point 17, cor¬ responding to the wave generating exhaust valves 4, and a loop at the end point, i.e. at the gable 13 of the exhaust pipe. By tuning the standing wave course one can achieve that the exhaust gases obtain a required escape velocity, especially at the in-side end 15 of the inner pipe 14. This explains the importance of the inserted inner pipe, which must have a length substantially corresponding to the tance between the points 16 and 18, defined according to Fig. 2, and an inner cross-section which is substantially equal to the cross-section of an exhaust channel in the en gine block. The combined effect of the curves according t Figs. 3 and 4 gives the favourable course of the gas flow described above.

A very low sound level is obtained by the new exhaust system, and the curve according to Fig. 5 shows the loudne level as a function of the length of the exhaust system. Even this curve represents a standing wave which is tuned be formed between the point 17, i.e. the sound generating exhaust valves 4, and the point 13, i.e. the gable 13 of t exhaust pipe, and so that a node is obtained at the point 15, i.e. at the in-side end 15 of the inner pipe. The wav is reflected at the gable 13 of the exhaust pipe and passe the same point 15, where the gas escaping from the inner pipe has the lowest loudness level

The above mentioned is, in principle, valid for the fundamental tone, for which a good sound damping is obtain Since the sound wave, however, contains harmonics, it migh be necessary, for certain applications, to attain a furthe damping of said harmonics. This can ^"be achieved thereby, that the exhaust pipe 12 is extended beyond the gable 13 a is terminated by a further gable, in which an inner pipe corresponding to the inner pipe 14 and having substantiall the same length is inserted in the same way as the inner pipe 14. The further gable should preferably be situated about a quarter sound wave length from the in-side end 15 of the inner pipe 14. The standing waves thus described: the negative pres¬ sure wave of the gas and its propelling wave and the sound wave, are illustrated once more separately in the new ex¬ haust system according to Figs. 6 to 8. In said Figures an exhaust system is diagrammatically shown- having the pis ton 5, the exhaust valve 4, the partial pipe 9 of the mani fold, the exhaust pipe 12, the inner pipe 14 and the end gable 13. Below each Figure the previously mentioned de¬ signation numbers are given. The junction between

r WIP fold and the exhaust pipe is represented by a flange 18. In Fig. 6 the negative pressure wave is shown with its initial point somewhat below the piston 5, which is shown in its bottom dead centre position. In Fig. 7 the propelling gas wave between the exhaust valve 4 and the end gable 13 is shown. In Fig. 8 the sound wave between the exhaust valve 4 and the end gable, with the node at the in-side end 15 of the inner pipe 14, is presented.

The new exhaust system has been experimentally tested and its good properties stated above have been fully con¬ firmed. It has then been apparent that the. appearing waves substantially have the illustrated and described courses. The ,theory lying behind the courses of the curves is very complicated, and therefore the experimental results obtained are presented here.

OMH

Claims

1. An exhaust system for a pulsating heat sourc especially an internal combustion engine, said system uti¬ lizing standing waves, c h a r a c t e r i z e d in that

A. the partial pipes (9) that are parts of the manifold (10) of the engine (1) are given substantially equal lengt and equal inner sectional area from the exhaust- alve (4) each cylinder (5) in the engine to a junction (11) of the partial pipes of all cylinders;

B. an exhaust pipe (12) , having an inner sectional area which is substantially equal to the sectional area of an e haust channel (8)^" in the block of the engine (1) multiplie by approximately 4, is attached at the junction (11) of sa partial pipes (9) ;

C. the exhaust pipe (12) is terminated by an annular gab (13), in a hole of which a substantially concentric inner pipe (14) with a smaller diameter than said exhaust pipe i inserted in the exhaust pipe;

D. the length of the inner pipe (14) in said exhaust pip (12) is substantially equal to the distance from a point somewhat below the bottom dead centre for a piston (5) in the engine (1) to the junction (11) for the partial pipes (9) in the manifold (10);

E. the length of the exhaust system is equal to the dis¬ tance from the point somewhat below the bottom dead centre for a piston in the engine to the in-side end (15) of the inner pipe (14) plus the length of said inner pipe;

F. a standing negative pressure wave, being generated by the combustion in the cylinders and by the ejector effect at the exhaust valves (4) and at the junction (11) for the partial pipes in the manifold (10) , is adapted to operate between the end points of said distance by selecting it to correspond to an integer multiple of the half period lengt of the negative pressure wave, and is arranged to have nod at said end points;

G. a standin g_taround a central axis of the exhaust pipe (12) rotating gas wave,, serving to propel the exhaust gas in said standing negative pressure wave through the exhaust system, is generated by the combustion process in the engine_, and is formed between the exhaust valves (4) and the inner surface of the annular gable (13) of the exhaust pipe (12) by adapting it to have an even number of oscillation waves and to have loops at the exhaust valves (4) and at the gable (13);

H. a standing sound wave is generated in the exhaust sys¬ tem between the exhaust valves (4) of the engine (1) and the inner surface of the annular gable (13) of the exhaust pipe (12) , and is adapted to have a node at the in-side end (15) of the inner pipe (14).

2. An exhaust system according to claim 1 , c h a r a c t e r i z e d in that the inner sectional area of the inner pipe- (14) is substantially equal to the sectio¬ nal area of an exhaust channel (8) in the block of the en¬ gine (1) .

OMPI t_*. WIPO