CA1074644A - Diesel engine combustion chambers - Google Patents

Abstract

DIESEL ENGINE COMBUSTION CHAMBERS

Abstract of the Disclosure Combustion chamber arrangements for divided cham-ber (prechamber) type diesel engines characterized by relatively low emissions of HC, CO and NOx, relatively low noise and physical stress and good fuel economy and power output and having:
1. canted valves in the heads and forming therewith lateral wedge-shaped valve recesses, 2. cooperating wedge recesses in the pistons forming disc or pancake-like valve pockets in conjunction with the cylinder head recesses, and 3. in-head prechambers closed by flame cups having wide connecting passages in their floors and side outlets for connection through channels with the edges of the valve pockets.

Description

Specification ....
This invention relates to internal comhustion engines and, more particularly, to dividecl or precombustion type combustion chamber arrangements ~or use in diesel engines, particularly of the automotive type.
The present invention provides an improved precham-ber type combustion chamber arrangement including i,n preferred form overlapping pancake or disc-like valve pockets preferably formed partially in the cylinder heads by wedge-shaped recesses under the heads of canted valves and partially in the pis-t:ons by wedge-shaped valve clearance recesses connecti,ng with the .. ..

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cylinder head recesses. The valve pockets are connected with i.n-head prechambers closed by Elame cups having wide connect-ing or discharge passages in their floors and transversely directed side outlets. These connect through lateral channels in the heads with elevated sides or edges of -the turbulence pockets to discharge hot combustion gases laterally, and at comparatively moderate flow rates, over the associated piston, valve and cylinder head surfaces, thereby spreading the heat transfer effects over the surfaces and dividing the thermal load more or less equally between the cylinder head including the valves and the associated pistons, thus limiting localized heat transfer to the piston heads as compared to other arrange-ments.
The present invention further provides an improved arrangement wherein a portion of the prechamber floor is heated on one side by the alternate passage of compression and combustion gases into and out of the prechamber and the heated portion is contacted on its other side by rich burning gases and fuel droplets, the hot surface aiding in vaporization of the fuel chaxge. Also the invention provides a fuel injection spray tip having at least one pair of angularly disposed ori-fices arranged on axes lying in a plane generally parallel to the associated cylinder axis and oriented to direct fuel in a broad path outwardly and downwardly toward the heated floor portion of the prechamber.
O-ther features are also included in the invention which vary in some arrangements and provide in varying degrees advantageous combinations of operating characteristics including relatively low emissions of HC, CO and NOX, smooth combustion ~074~i4~

with resultant low noise level and component stress, good control of smoke or visible emissions and gooa fuel economy.
Such diverse features of the invention include : variations in the entrance angle and position of the conneCtinY
passages in their respective prechambers to con~rol the rate of swirl therein at the time of ignition. Also, variations in - the locations and orientation of the fuel nozzles, spray ori-fices and glow plugs can vary the balance of exhaust emissions, combustion smoothness, visible smoke and fuel economy with resultant effects on noise levels and component stress. The preferred embodiment is thought to provide *he most favorable combination of such features.
In preferred form the engine includes a piston movable on an axis cooperating with a cylinder head having at least one poppet valve disposed on an a~is canted in relation to the piston axis and defining at the piston top dead center position a shallow pancake-like pocket under the valve head and normal to the valve axis and a precombustion chamber having a discharge passage with a generally straight discharge portion in substantial alignment with the elevated side of the pocket and connected therewith to direct yaseous discharge into the pocket from the prechamber, the discharge passage at its end distal from the pocket having a portion extending sharply upward from the straight portion and open-ing into the precombustion chamber which in turn extends back from the opening toward the canted axis so as to form a wall bounded by the discharge passage and precombustion chamber, and means to inject ruel into the precombustion chamber in a plane generally parallel to the piston axis and towards the wall so that the air discharge into the . .

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prechamber during each compression stroke generates a swirl initially curving inwardly towards the piston axis and then traveling downwardly generally parallel to the piston axis towards the wall and the .injected fuel travels with the swirling a.ir into a temporarily locally rich mixture space above the wall wherein combustion occurs under conditions relatively unfavorable to NOx production, the size of the precharnber being roughly equivalent to the volume of the main chamber with the proportions being such that gases discharging from the precombustion chamber fan out against the valve head and cylinder head and the piston so that the piston thermal load is comparable to the thermal load of the valve and cylinder head in the main chamber. Other specific featuxes and alternative embodiments are also dis-closed.
These and other advantages and features of the invention will be more fully understood ~rom the following description of certain preferred and alternative embodiments chosen for purposes of illustration, taken together with the accompanying drawings.
In the drawings:
Figure 1 is a fragmentary transverse cross-sectional view along the axis of a cylinder of an internal combustion engine formed in accordance with a preferred form of the inven-tion with the valve injector and glow plug in side elevation and the valve port sectioned along the valve axis;
Figure 2 is a cross-sectional view throuyh the com-bustion chamber of the preferred embodiment taken generally in the plane indicated by the line 2-2 of Figure l;
: 30 Figure 3 is a fragrnentary cross-sectional view through . ;~ .

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the injection nozzle spray ti~ as viewed from the plane indi-cated by the line 3-3 of Figure 1 with parts in elevation;
Figure 4 is a fragmentary cross-sectional view through the precombustion chamber of the pre:Eerred embodiment as viewed from the plane indicated by the line 4-4 of Figure l;
Figure 5 is a fragmentary cross-sectional view through the main and precombustion chambers as viewed from the transverse plane through their axe~ indicated by the line 5-5 of Figure 2;
Figure 6 is a pictorial view from underneath a portion of a cylinder head of the preferred embodiment and showing portions of the combustion chamber forming surfaces;
Figure 7 is a pictorial view from above of a piston for use in the preerred e~bodiment and showing the piston head con~iguration;
Figure 8 is a pictorial view of a prechamber cup for use in the preferred embodiment;
Figures 9, 10 and 11 are cross-sectional views with parts in elevation similar to Figure 1~ but illustrating various alternative embodiments of combustion chamber arrange-ments formed according to the invention; and Figure 12 is a cross-sectional view through the chamber of the last mentioned embodiment as viewed from the plane indicated by the line 10-10 of Figure 11~
Referring first to the embodiment of Figures 1-8 of the drawings, numeral 10 generally indicates an internal com-bustion engine of the four-stroke automotive diese]. type.
Engine 10 is conventionally provided with a cylinder block 12 defining a plurality of cylinders 14 having axes 15, only one of the cylinders being 5hown. Each of the cylinders opens throu~h an end wall of the cylinder block 12 which is formed as a flat machined surface 16~ Æach cylinder has reciprocably ~4~

disposed therein a piston 18 having the usual piston sealing rinys 20 and having a generally flat upper surface 22 which, - in the upper position of motion of the piston, know~ as the top dead center position, approximates a location of near alignment with the upper surface 16 of the cylinder block.
At leas t one cylinder head 24 is mounted on the cylinder block 12, having a generally flat lower surface 26 opposing and sealingly engaging thxough a gasket 28 the flat upper surface 16 of the cylinder block. The flat head surface 26 also closes the end of each cylind~r 14 and, lying opposite the flat piston surfaces 22, defines together with the piston and cyiinder main combustion chamber portions 30 located at the ends of the cylinders 14.
At each cylinder location the cylinder head 24 is provided with a pair of adjacent ports including an inlet port 32 and an exhaust port 34, These ports respectively connect the main combustion chamber 30 with suitable air inlet and exhausk gas discharge systems, not shown, the movement of gas between the ports and the combus~.ion chamber being con-trolled respectively by inlet and exhaust poppet valves 36, 38 - having heads seatable at the ends of their respective ports to close the ports.
The valves 36, 38 are carried in the head for reci-- procating movement on parallel axes 40 which are can~ed or inclined upwardly ~way from a plane passing through the cylin-der axis 15 and preferably extending longitudinally of the enyin~. The canting of the valves re~uires the valve seats 41 in the cylinder head to be recessed on one side, resulting in the formation of wedge-shaped valve recesses 42, 43 which are defined by the bottoms of the valves and the surroundi.ng wall ' :
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portiorls 44 tapering into the adjoining flat surface ~6 of the cylinder head. These ~alve recesses are complemented by similar wedge-shaped recesses 46, 48 formed in the fla-t upper surface 22 of the piston to provide clearance for the initial opening or final closing mo-tion of the heads of the respective valves. The valve recesses in the head and their related recesses in the piston cooperate to form ad~oining and over-lapping pancake or disc-like air turbulence valve pockets between the ends of the valves and the top of the piston and having elevated ~ides formed largely within the cylinder head.
IJse is made of these valve pockets in the design of the com-bustion chamber as will be subsequently more fully explained.
At each cylinder location, the cylind~r head is provided with a precombustion chamber (prechamber) 50 which is located in the head above one edge of the piston and on t'ne side of the inlet and exhaust ports opposite the direction of upward inclination of their valve axes 40. Each precombustion chamber 50 is formed in the head by a recess 52 that extends upwardly from the cylinder head bc.tom surface ~ and is closed at the bottom by a flame,cup insert S4.
The flame cup insert comprises a unitary body hav~ng a floor (or bottom wall3 portion 56 with upp~r and lower sur-faces 58, 60 and a flanged outer edge 62 interference fitted in a complementary portion of the prechamber recess 52 to retain the insert in the head. A portion of the insert opposes the upper surface 16 of the cylinder block and engages the gasket 28 so as to positively retain the insert 54 in the cylinder head after the engine is assembled. ~rhe xemainder or the insert floor lower su~face 60 eY~tends into th~ cylinder in opposition to the flat upper piston surface 22. It should be noted that the full extent of the lcwer surf~ce 60 is unbroken by any opening.

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- Supported on the floor, the uni.tary flame cup fur-ther includes an upstanding cylindrical wall 63, the outer surface of which is spaced from the corresponding cylindrical portion of the recess 52 to provide an insulating barrier that tends to retain heat in the wall portion 63. ~ part cylindrical protrusion 64 cast on the exterior of wall 63 mates with a vertical drilled recess or slot 65 in the wall of head recess 52 to positi~ely locate the flame cup in the desired position. The interior of the wall 63 is curved and smoothly connected with the upper surface 58 of the floor to define a cup-shaped interior chamber portion 66~ Near its upper edge at 67, the wall interior has a part spherical portion. This portion opens to and blends w.ith the upper portion of the recess 52 which is of part spherical configu-ration to form the total volume of the precombustion chamber 50.
The prechamber.50 is connected with the main cha~ber portion 30 by a wide and relatively shallow gas connecting and discharge passage in the floor portion 56. The passage inciudes a first wide mouth generally straiyht passage porti~n 68 that is in substantial alignment with the associated valve pockets and registered with the elevated sides thereoE, passage portion 68 extends laterally in the floor 56 on an axis that preferabl~ lies in a plane approximaiely at right angles to the longitudinal plane defined by the valve axes. Irhus, the passage portion 68 extends at a slight upward angle between the upper and lower suraces 58~ 60 of the flame cup floor, from an opening 70 in the side of the floox that does not break through : the lower surface to a junction point beyond the center of the floor. Here -the first passage portion joins with a second wide passage portion 72 that extends sharply upwardly toward the ' ;i9L4 center of the p.recombustion chamber 50, forming an acute angle with the first passage portion and opening to the cup-shaped portion 66 of the prechambar through an opening 74 in the floor upper surface 58 at a point beyond the center of the floor 5G from the opening 70. From opening 74, the extension of the prechamber primarily back toward the cylinder and valve axes, causes the portion of the floor 56 between its upper surface 58 and the straight passage portion 68 to form a hot wall 75, heated in operation by combustion gases on both sides~
The sharp change in angle and orientation of the second passage portion 72 toward the center of the precombus-tion chamber 50 has the purpose of directing incoming gases into the prechamber with a very low d~gree of swirl ana tur-bulence as compared to most other known prechamber arrange-ments, including the alternative e~hodiments of the present invention to be subsequently described. Both portions of the floor passage 6B, 7~ are relatively wide in relation to their depth (or thickness) in order to provide a relatively large area flow p~th. The dimensions of the first passage portion, as disclosed, involva a passage width about four times its depth, while the upwardly extending second passage portion has a width somewhat more than two and one-half times its thick ness in the narrower lateral direction.
T~e flame cup passage 68, 72 connects with the elevated deeper edges of the valve recesses 42, 44 through a channel 76 cut late]^ally in the surface of the cylinder head and of a width substantially equal to the first passage por-t.ion 68 of the flame cup, of which the channel constitutes an extension.
The arrangement directs hot gases from the precom-bustion chamber laterally into the edges of the valve poc~ets -; 9 , . .. .. .

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formed between the cylinder head and piston so that the gas is directed in a wide path, fanning out across the width of the opposing cylinder head and piston surfaces rathe.r than down upon the piston as is common practice in prechamber diesel engines. our improved arrangement reduces localized heat txansfer to the pi.ston surEace and spreads heat ~low to the piston over a greater surface area while also permitting the cylinder head and valves to provide an increased propo.rtion of heat dissipation. As a result, the piston head can accept the heat load imposed thereon without an increase in thicXness sufficient to require an increase in height oE the cylinder blocX over the height of a comparable gasoline engine of the same cylinder dimensions, thereby permitting the use of common tooling for machining both diesel and gasoline engine cylinder blocks.
In order to provide a combustible mixture of air and fuel in the precombustion chamber 50, the cylinder head mounts at each cylinder location a pencil type fuel injection noz~le 78 which i3 located in a bore 80 having an axis preferably parallel to the cylinder axis and opening through the upper wall of the precham~er almost tangential to the inner wall surfa~e 82 of the prechamber at the point closest to the cylinder axis. The fuel injection noz le is provided with a spray tip 84, best shown in Figure 3, having a needle valve 85 and at least two angularly disposed orifices 86, 88 which lie in a plane parallel to the cylinder axis and direct injected fuel downwardly, generally parallel to the cylinder and piston a~is 15, in a wide, fan-like, relativel~ soft spray pattern toward the sides and bottom hot wall ~5 o-E the flame 0 cup inser-t. If desired, additional orifices may be disposed ,7~64L~

in the injection no~zle spray tip to direct the fuel in an even softer pattern towa.rd additional areas of the flame cup sides and bottom wal.l.
The fuel spray is pxeferably directed generally tangentially to and in the direction of the swirling airflow in the prechambar. It is thought this forms a locally fuel rich-zone in the prechamber which during combustion helps limit or control formation of nitrogen oxides~ Subsequent mixing oE the burning rich gases and air in the rnain combus-tion chamber provides for completion of combustion reactionsand holds emissions of hydrocarbons and carhon monoxide to normal~y low diesel engine levels.
The cylinder head also mounts a glow plug 90 at each cylinder location. ~ach plug 90 is secured in an opening 92 having an axis that lies in a co~non plane with the axis of the fuel injection nozzla bore 80 and, preferably, the pre-chamb~r connecting passage 680 72, the plane lying parallel with and preferably encompassing the axis of the cylinder.
Each glow plug 90 has an elongated end 94 that extends into the pre~hamber in or near the path of fuel spray from the injectox noz~le orifices, thus providing a hot spot to aid the prompt ignition of fuel delivered to the prechamber by the injector during engine starting and warm-up, The variQus features o~ the above described embod.i-: ment of the invention wh~n incorporated in an automotive type our-stroke diesel engine have been shown to provide an advan-tageous combination of high cornbustion efficiency, low smoke ` and emission levels and relatively low combustion noise.
Through analy.sis of the result of tests, it is considered that the various features obtain the following specific advantages when combined in the manner illustrated~

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The provision of inclined or canted valves combined with the side prec'namber outlet throug'n a thin wide passage avoids excessive localized piston head temperatures and also results in good utilization of air in the main chamber, making possihle adequate power output with low smoke while utilizing a bore stroke ra-tio generally considered too high to be favor-able for diesel engines and permitting a relatively low ratio of engine weigh~ to power output. Another result is good mixing in the main chamber, giving relatively complete com-bustion and 1QW emi3sions of hydrocarbons and carbon monoxide~
The abrupt bend in the flame cup connecting passageand the radial entry into the precombustion chamber cavity ; gives a low rate o air swirl in the prechamber compared to most swirl cham~er engines. This contributes to smooth com-bustion with resulting low noise and stress levels.
Placement o~ the fuel injector nozzle centerline close to the prechamber wall and the use of a nozzle configu-ration giving a wide and thin spray with low penetration and in the direction of air swirl in tha prechamber forms a fuel-rich region near the pxechamber;wall but without excessive collection oE fuel on the wall. Combustion, thus occurs under locally rich conditions and in a locally low temperature zone, which aids in giving smooth combustion and low formation o~
nitrogen oxides.
Division o~ the prechamber connecting passage into two distinct flow portions permits the flow area and orienta-tion of these portions to be optimized separately for the control OI mi~ing in the main chamber and air motion in the - prechamber.
The use of a wide thin floGr in the precham~er pro-vides a local high temperature wall area 75 which reduce~
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ignition delay and prevents fuel from accumulatiny on the wall.
This aids in providing ~mooth combustion and low hyclrocarbon emissions.
In addition to the Eoregoing features, the associated fuel pump is preferably provided with relatively low injection pre~sura and slower than normal injection rates, which, when combined with precise control of injection timing, provide for combustion to begin at controlled optimum points over the speed and load range, thus contributing to the smooth combustion and low emission performance of the engine.
ReEerence will now be made to Figures 9-12 of the drawings in ~hich various alternative emboaiments of the invention are illustrated. In the main, the constructions of the various embodiments are identical. The features of differ-ence reside in the placement and configuration oE the pre-combustion chamber, as well as with the location and orientation of the fuel injection nozzle and glow plug for each cylinder.
Thus, description of the alternative embodiments will be limited to these differing features, it b~ing understood that the remainder of the construction in each case is identical to the first described embodiment. Similar or identical com-ponents in the various embodiments are identified by reference numerals di~fering by multiples of one hundred.
Referring now to the embodiment of Figure 9 in which reference numerals in the 100 series are utilized, the arrange-ment shown is identical to that of the firs-t described embodi-ment, with the exception of the location and orientation of the fuel injection nozzle 178 and the glow plug 190. In t'nis embodiment, glow plug 190 is located near the prechamber inner wall surface 182, being mounted in an opening 192 inwaxdly of, but having an axis coplanax with, the fuel injection nozzle 6~

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bore 180. In this embodiment, the spray pattern of the fuel injection nozzle is aimed in the direction of air swirl and toward the inner portion of the prechamber walls and floor very close to the area toward which the spray pattern of the injector o the first described embodiment is also aimed, Referxing now to the embodiment of ~igure 10 in which reference numerals in the 200 series are utilized, the arrangement of the fuel injector 278 and glow plug 290 is physically similar to the arrangement of these components in the embodiment of Figure 9. However, the pattern of fuel spray from the fuel injector nozzle may be modified to be directe~ gener-ally across the center of the precombustion chamber 250 towara locations near the end of the second portion 272 of the flame cup connecting passage. However, the orientation of this second passage portion 272 is also altered so that it is direc-ted sharply upwardly at nearly right angles to the first passage portion 268, aiming at a location between the center of the prechamber and its outer side wall. The result is that ~- this embod ment provides a greater amount of swirl in the ~ e-chamber than the first two embodiments described~ resulting in : ~omewhat faster combustion and various other differences in operating characteristics.
Referring now to the embodiment of Figures 11 and 12 ` in which reference numerals of the 300 series are utilized, it - should be noted that placement of the fuel injector nozzle 378 is essentially the same as in the emboaiments of Figures 9 and lOo The location and orientation of the glow plug 390 differs, - however, since it is placed on an axis that does not lie on a transverse plane through the fuel injection nozzle and flame cup connecting passage~ Also, the shape of the flame cup 1~

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interior 366 is altered somewhat with a much sharper junction of the inner portion o~ the wall surface 382 with the upper surface 358 of the flame cup floor~ rrhe connecting passage is also altered in that the second passage portion 372 intersects the first portion 368 in a sharp but obtuse angle and the second portion is directed almost tangentially along the adja-c~nt outer portion of the inner wall surface 382. This arrange-ment provides a relatively high degree of swirl.
One other diffe~ence is that the prechamber 350 is relocated with respect to the cylinder axis so that the cen-tral plane of the connecting passage 368, 372 does not extend through the cylinder axis. To accommodate this, an alteration is made in the shape of the connecting channel 376 which carries gas flow between the side outlet opening 370 of the Elame cup first passage portion and the wedge-shaped valve pockets 342, 3~3 of the cylinder head.
While various alternative embo~iments have been illustrated which include many of the major features of the invention as disclosed in the first described embodiment, it should be und?rstood that numerous other variations could be made within the scope of the inventive concepts taught herein.
Accordingly, it is intended that the invention not be limited by the specific embodiments disclosed but that it have th~
full scope permitted by -the language of the following claims.

Claims (7)

Claims The embodiments of the invention in which an exclu-sive property or privilege is claimed are defined as follows:

1. In combination in a diesel engine, means defining a cylinder having an axis, a piston recipro-cably carried in the cylinder and a cylinder head having a generally flat lower surface closing the end of the cylinder and defining in cooperation with the piston a main combustion chamber at the end of the cylinder, said cylinder head having adjacent inlet and exhaust ports opening to the combustion chamber and closed by poppet valves having heads and movable on axes inclined upwardly away from a plane passing through the cylinder axis such that the valve heads are canted with respect to the lower surface of the cylinder head so as to form, in closed position, wedge-shaped valve recesses in the cylinder head surface, a precombustion chamber formed in the cylinder head on the side of the inlet and exhaust ports opposite the inclination of the valve axes and defined by a recess in the cylinder head closed by a flame cup having a bottom wall with an unbroken lower surface flush with the lower surface of the cylinder head, said valve recesses being connected with said precombustion chamber by a channel extending outwardly from the edges or the deeper portions of the wedge-shaped valve recesses to the flame cup and a passage in the bottom wall of the flame cup, opening to said channel through the side of the flame cup bottom wall and extending to the precombustion chamber.

2. In combination in a diesel engine, means defining a cylinder having an axis, a piston recipro-cably carried in the cylinder and a cylinder head having a generally flat lower surface closing the end of the cylinder and defining in cooperation with the piston a main combustion chamber at the end of the cylinder, said cylinder head having adjacent inlet and exhaust ports opening to the combustion chamber and closed by poppet valves having heads and movable on axes inclined upwardly away from a plane passing through the cylinder axis such that the valve heads are canted with respect to the lower surface of the cylinder head so as to form, in closed position, wedge-shaped valve recesses in the cylinder head surface, a precombustion chamber formed in the cylinder head on the side of the inlet and exhaust ports opposite the inclination of the valve axes and defined by a recess in the cylinder head closed by a flame cup having a bottom wall with an unbroken lower surface flush with the lower surface of the cylinder head, said valve recesses being connected with said precombustion chamber by a channel extending outwardly from the edges of the deeper portions of the wedge-shaped valve recesses to the flame cup and a passage in the bottom wall of the flame cup, opening to said channel through the side of the flame cup bottom wall and extending to the precombustion chamber, said piston having a generally flat upper surface opposing the cylinder head lower surface, and having shallow wedge-shaped recesses in its upper surface and opposite the near portions of said valve heads to provide clearance for partial valve movement, said piston recesses cooperating with the valve recesses in the head to provide disc-like valve pockets in the main combustion chamber and connected with the precombustion chamber.

3. The combination of claim 2 wherein the flame cup bottom wall has an upper surface and the flame cup passage extends at least half way across said bottom wall, opening to the precombustion chamber through an opening in said upper surface.

4. The combination of claim 3 wherein said flame cup passage includes a first wide portion extending trans-versely in the bottom wall from said side opening to a junction point beyond the center of said bottom wall and a second wide portion extending from said junction point upwardly toward said precombustion chamber at a sharp angle with said first passage portion to direct gas flow into said precombustion chamber with a limited amount of swirl and turbulence.

5. The combination of claim 3 wherein said flame cup passage includes a first wide portion extending trans-versely in the bottom wall from said side opening to a junction point beyond the center of said bottom wall and a second wide portion extending from said junction point upwardly toward the center of said precombustion chamber at an acute angle with said first passage portion to direct gas flow into said precombustion chamber with a minimum of swirl and turbulence.

6. In combination in a diesel engine, means defining a cylinder having an axis, a piston recipro-cably carried in the cylinder and a cylinder head having a generally flat lower surface closing the end of the cylinder and defining in cooperation with the piston a main combustion chamber at the end of the cylinder, said cylinder head having adjacent inlet and exhaust ports opening to the combustion chamber and closed by poppet valves having heads and movable on axes inclined upwardly away from a plane passing through the cylinder axis such that the valve heads are canted with respect to the lower surface of the cylinder head so as to form, in closed position, wedge-shaped valve recesses in the cylinder head surface, a precombustion chamber formed in the cylinder head on the side of the inlet and exhaust ports opposite the inclination of the valve axes and defined by a recess in the cylinder head closed by a flame cup having a bottom wall with an unbroken lower surface flush with the lower surface of the cylinder head, said valve recesses being connected with said precombustion chamber by a channel extending outwardly from the edges of the deeper portions of the wedge-shaped valve recesses to the flame cup and a passage in the bottom wall of the flame cup, opening to said channel through the side of the flame cup bottom wall and extending to the precombustion chamber, a fuel injection nozzle extending into said precombustion chamber to supply fuel thereto and a glow plug having an elongated end extending into said precombustion chamber to aid ignition of fuel therein, said injection nozzle and said glow plug end having axes coplanar with the axis of said flame cup passage.

7. The combination of claim 6 wherein the axis of said fuel injection nozzle lies parallel to said cylinder axis and the nozzle is arranged to spray the complete fuel charge into the portion of the prechamber lying closest to the cylinder axis.