EP0369461A1 - Internal-combustion engine with at least one rotary valve per cylinder - Google Patents

Abstract

An internal-combustion engine (1) having cylinders arranged individually or in series, having an injection apparatus (26) comprising an injection pump (27), preferably a high-pressure injection pump, and an injection nozzle (29), and having at least one rotating control element (3) per cylinder for the exhaust and refill operations, which is arranged between cylinder block (4) and cylinder cover (2) or in the latter with an axis (32) of rotation preferably lying perpendicular to the cylinder axis and, between two spigots (14a, 14b) extending along the axis of rotation, has a control element firmly connected to the spigots, and countersurfaces uniformly surrounding the control body and the spigots (14a, 14b) being provided in the cylinder head and each spigot (14a, 14b) being traversed by an axially extending gas channel (16, 17) which in each case merges into an elbow shaped gas channel which is arranged in the control body and emerges at the surface of the control body with an opening (18), means for transmitting a rotary movement from the crankshaft to the control element (3) being provided, the control body being designed as a body (15) having the shape of a sphere, in particular of a hollow sphere, and the injection nozzle (29) being mounted in the spherical body (15), is to be designed in such a way that, while a small and compact construction is guaranteed, the supply of the injection medium to the injection nozzle (29) is facilitated. This is achieved by the fact that the injection pump (27, 327) is also mounted in the spherical body (15) of the spherical rotary slide valve (3). <IMAGE>

Description

The invention relates to an internal combustion engine according to the preamble of claim 1.

An internal combustion engine of this type is the subject of the applicant's earlier patent application PCT / EP 88/00411. In this diesel engine, the injection nozzle is mounted in the ball of the rotary valve, the injection pump being attached to the upper part of the cylinder cover. This results in a relatively large and bulky design for the internal combustion engine. The supply of the injection medium to the injection nozzle is also not easy.

The invention has for its object to design an internal combustion engine of the type mentioned in such a way that the supply of the injection medium to the injection nozzle is facilitated while ensuring a small and compact design.

This object is achieved by the characterizing features of claim 1. In the embodiment according to the invention, the injection pump is mounted in the spherical control body or is integrated therein. This gives the internal combustion engine the desired smaller, compact design, the supply of the injection medium being facilitated because, on the one hand, the supply path can be shortened considerably and, on the other hand, the supply path is neither unintentionally interrupted, nor is it separated by the parting line during operation of the internal combustion engine extends only temporarily corresponding components, as is the case with the subject of the earlier patent application. The configuration according to the invention thus also leads to a significant simplification of the construction, as a result of which the production costs can be significantly reduced. Because of the small and compact design, the internal combustion engine can also be more easily integrated into vehicles and machines driven by it, so that there is also an enlarged area of application for the internal combustion engine according to the invention.

Advantageous developments of the invention, which also contribute to the present solution to the problem, and also improve the function, the seal and / or the stability or resilience and wear resistance of certain components are described in the subclaims.

It should be emphasized below that the function and the advantages which can be achieved by the developments of claims 42 to 53 can also be viewed independently of the function of the embodiment according to claim 1 and its advantages. These claims are therefore to be assigned independent inventive significance. These configurations enable, on the one hand, an advantageous cooling of the rotary valve and, on the other hand, a reduction in the distance between the cylinders or, given predetermined distances, an increase in the rotary valve and thus a stable, small and compact design.

• Fig. 1 einen Axialschnitt durch den Zylinderkopf einer erfin­dungsgemäß ausgestalteten Brennkraftmaschine mit einer in den Kugeldrehschieber der Brennkraftmaschine integrierten Einspritzvorrichtung;
• Fig. 2 eine perspektivische Funktionsdarstellung einer Ver­stellvorrichtung für die Einspritzvorrichtung als Einzelheit;
• Fig. 3 den Kugeldrehschieber in perspektivischer Darstellung, teilweise geschnitten;
• Fig. 4 eine zwischen dem Zylinderdeckel und dem Kugeldreh­schieber der Brennkraftmaschine wirksame Dichtungsan­ordnung für den Kraftstoff in perspektivischer Schnittdarstellung;
• Fig. 5 einen der Fig. 1 entsprechenden Schnitt mit einer Ein­spritzvorrichtung als zweites Ausführungsbeispiel;
• Fig. 6 eine Einzelheit der Fig. 5 in vergrößerter Darstellung;
• Fig. 7 einen der Fig. 1 entsprechenden Schnitt mit einer Ein­spritzvorrichtung als drittes Ausführungsbeispiel;
• Fig. 8 eine perspektivische Funktionsdarstellung einer Ver­stellvorrichtung für die Einspritzvorrichtung nach Fig. 7;
• Fig. 9 den Schnitt A-A in Fig. 7;
• Fig. 10 einen Zylinderkopf einer Brennkraftmaschine im Schnitt als weiteres Ausführungsbeispiel;
• Fig. 11 das Zylinderdeckel-Unterteil nach Fig. 10 in der Drauf­sicht.

The invention is explained in more detail below on the basis of a preferred exemplary embodiment illustrated in a drawing. It shows:

• 1 shows an axial section through the cylinder head of an internal combustion engine designed according to the invention with an injection device integrated in the rotary valve of the internal combustion engine;
• 2 shows a perspective functional illustration of an adjusting device for the injection device as a detail;
• Figure 3 shows the rotary valve in perspective, partially cut.
• 4 shows a sealing arrangement for the fuel, which is effective between the cylinder cover and the rotary valve of the internal combustion engine, in a perspective sectional view;
• 5 shows a section corresponding to FIG. 1 with an injection device as a second exemplary embodiment;
• 6 shows a detail of FIG. 5 in an enlarged representation;
• 7 shows a section corresponding to FIG. 1 with an injection device as a third exemplary embodiment;
• FIG. 8 shows a perspective functional illustration of an adjusting device for the injection device according to FIG. 7;
• 9 shows section AA in FIG. 7;
• 10 shows a cylinder head of an internal combustion engine in section as a further exemplary embodiment;
• Fig. 11, the cylinder cover lower part of FIG. 10 in plan view.

The internal combustion engine shown only partially in FIG. 1 and designated 1 has a cylinder head cover 2 with an upper part 2.1 and a lower part 2.2. Between the top 2.1 and the lower part 2.2 rotatably supports the rotary ball valve 3. In the cylinder block 4 lying below the lower part 2.2, a piston 6 is displaceably guided in a bushing 5. The upper part 2.1 is detachably connected to the lower part 2.2 and the underlying cylinder block 4 by means of clamping screws.

The upper part 2.1 has a dome-shaped counter surface 10.1 on the inside and in the lower part 2.2 a spherical ring-shaped counter surface 10.2 is arranged at the upper end of the combustion chamber. Cooling channels are provided in the cover 2, which are connected to the cooling channels 9 of the cylinder block 4 on its cylinder head surface. The piston 6 has a preferably rotationally symmetrical end face 7, which, however, can also be designed differently depending on the aspects of combustion technology. In an annular groove 11 of the counter surface 10.2 of the lower part 2.2, an annular sealing strip 12 is inserted, which is supported against the bottom of the groove 11 and against the spherical surface 13.

The one-piece rotary valve 3 consists of two gas-tight welded spherical half-shell parts, to each of which a tubular bearing pin 14a and 14b is welded centrally on opposite sides or can be connected in some other way to the spherical half-shell parts. The parts which complement one another to form a hollow ball in the equatorial seam 15.1 are penetrated by two elbow-shaped control channels 16 and 17, the ends of which open in a form-fitting manner in control openings 18 of the ball body 15, the end of one or both of the tubular bearing journals 14a and 14b being coaxial in this way enforce that at least on one side, here on the output side (output control channel 17), each of the outer circumferential surface of the control channel and an inner circumferential surface of the journal 14a, 14b delimited quarter-circular cooling channels 8.1, 8.2 are formed, which are connected to the cavity 8 of the spherical body 15 are.

The bearing pin 14b also has one on its outer surface che flange ring-like radially outwardly extending annular projection with an attached ring gear 19 with radially extending teeth, which is arranged outside the bearing opening and is driven by the rotary valve 3, not shown, uniformly by the drive shaft, also not shown.

The outer circumferential surface of the other bearing pin 14a also has a flange-like, radially extending, annular projection. The projection is arranged outside of the opening in the bearing and lies against the end face of the cover 2 with a slide ring or the like. Both journals 14a, 14b can communicate with the cooling channels of the cylinder block 4.

The rotary ball valve 3 is supported by means of its journals 14a and 14b in cylindrical bearing openings 21a, 21b, which are each half in the upper part 2.1 and half in the lower part 2.2, in order to enable the mounting of the rotary ball valve 3.

The rotary ball valve 3 is rotatably supported in the bearing openings 21a, 21b with the interposition of rotary bearings 22. Shaft seals arranged on both sides ensure a secure seal between the gas, coolant and lubricant-carrying channels.

The axial rotation of the rotary slide valve 3 takes place via the ring gear 19, which is axially fixed on the bearing journal 14b between a shoulder of the bearing journal 14b and an outer retaining ring and with axial bearing elements 24 on both sides - here axial bearings with compensating disks - with little running play between opposing sliding surfaces of the cover 2 and a cap 25 fastened to it on the end face, wherein here a flange half of the cover and a flange half of the cap 25 form a cavity for the gearwheel 19.

In operation, the rotary valve 3 is not shown th drive shaft via transmission members, also not shown, which are in engagement with the ring gear 19, driven uniformly in such a way that only the gas inlet and, after compression and ignition of the mixture, the gas outlet communicates with the combustion chamber, that is to say with the cylinder, via the control channels 16, 17 . The flow directions in the control channels 16, 17 are indicated by arrows.

The rotary ball valve 3 can be used both in connection with four-stroke as well as in connection with two-stroke internal combustion engines with an appropriate arrangement of the gas channels.

The rotary ball valve 3 can be made in one or more parts and can consist of metallic or ceramic or composite materials, depending on the requirements of the respective field of application.

The rotary ball valve 3 can also be part of a single-cylinder or multi-cylinder engine. Its field of application is therefore not limited to the type described. Other designs of the piston 6 and the cylinder cover 2 are also possible in accordance with the respective requirements of the configuration of the combustion chamber to be selected. It is particularly noteworthy that it can also be used for in-line engines without having to change the other components such as cylinder block 4 and crank mechanism. It is provided that a rotary ball valve 3 is arranged above each cylinder, the axis of rotation of which extends transversely to the direction in which the cylinders line up. A height that is lower than that of poppet valves can be achieved. In addition, spatial shapes of the combustion chamber can be formed which, from the point of view of combustion technology, approach the optimum. No complicated sealing ring shapes or sealing sleeves are required. The storage of the spherical body 15 is moved to the journal 14a, 14b and not on the surface of the ball, such as the z. B. is the case with known roller valves. There can even be a gap 20 between the spherical surface 13 and the spherical surface be that does not have to be filled with an oil film.

The use of a ball 15 as a control body brings unexpected advantages. Simple components can be used, so that production is inexpensive. The rotationally symmetrical components of the rotary valve have no local accumulations of material, so that the control body cannot be warped due to the effects of temperature changes and different heat loads. The spatial shape of the rotary valve 3 remains uniform. The sealing ring 12 pressing against the spherical surface 13 can be made of different materials, e.g. B. made of ceramic, because the control body experiences no dimensional changes.

Additional lubrication can be dispensed with in the case of the ball rotary slide valve 3 if the ball surface 13 only rests on the sealing edge of the sealing ring 12. The gap 20 between the spherical surface 13 and counter surfaces in the cylinder head can be approximately 0.08 to 0.2 mm. The control body and the sealing ring 12 can, for. B. consist of ceramic materials. A metal ball 15 can also be used with ceramic materials such. B. plasma spraying. These embodiments are possible because lubrication in the conventional manner and scope is not required.

The rotary valve arrangement according to the invention can be optimally cooled because the spatial shapes of the components are simple. Bulk accumulations are missing. This favors the production of the parts from ceramic materials. The introduction of pressure force during the compression process is extremely favorable for the ball 15 due to the shape of the arch. The production of the spherical shape is particularly simple and straightforward compared to a cylindrical shape.

The storage of the rotary ball valve 3 on the bearing journal is possible because the journal journals are not exposed to considerable temperature changes and consequently none due to the action of heat

Experience spatial shape change. The injection pump is also advantageously affected by these favorable conditions. For this reason, the bearing lubrication is also easy.

The combustion chamber or cover 2 can be kept very small, in particular if the surface of the piston 6 is dome-shaped and the radius of the dome surface is adapted to the radius of the ball 15.

A further advantage results from the cool combustion chamber walls, since both the side wall ring and the rotary slide ball can be cooled intensively with a suitable coolant. In contrast to the valve engine, the hot exhaust valves are also missing. Due to the lack of hot spots in the combustion chamber, a much higher compression ratio and thus a higher engine output can be achieved.

The sealing ring 12 can be tilted from the plane parallel to the rotary valve rotation axis in order to generate relative speed differences at the sealing edge of the rotary valve ball sealing ring by different spherical segment circumferences and thus to enable the seal to rotate about its axis of rotation, which leads to an increased service life and sealing ability of the seal.

The sealing ring 12 can also act at the areas closest to the rotary slide ball bearings with different spring forces on the rotary slide ball, which cause a difference in frictional force on the sealing edge of the rotary slide ball sealing ring and thus, due to the torque, cause the seal to rotate about its axis of rotation, which also results in an increased service life and sealing ability the seal leads.

The injection device, generally designated 26, comprises, as a high-pressure injection pump 27 in particular, an axial piston pump, the working chamber 28 of which through pressure channels with an injection nozzle 29 is connected, which can be closed by a closure member which opens in the presence of a certain injection pressure.

In the present exemplary embodiment, the piston 31 of the injection pump 27 is arranged parallel to the axis of rotation 32 of the rotary slide valve 3, namely at a radial distance a such that the injection pump 27 is located outside or on the circumference of an imaginary envelope aligned with the bearing pins 14a, 14b. The injection pump 27 is thus arranged in the secantial section of the spherical body 15, which rises radially above the bearing journals 14a, 14b. The piston arrangement of the injection pump 27, generally designated 33, protrudes from the ball 15 with its drive-side end, wherein it extends into an annular free space 34, which is provided in the transition region between the ball body 15 and the bearing journal 14b and is delimited by the inner peripheral wall of the cover 2 is. In the present exemplary embodiment, the injection pump 27 protrudes axially parallel to the axis of rotation 32 from a radial end face 35 of a ring shoulder 36, which is delimited on the circumference by a rotationally symmetrical cylinder surface 37 and represents a lateral shoulder of the spherical body 15 with a triangular cross section. The bearing length for the piston arrangement 33 in the spherical body 15 can be effectively extended by means of this ring extension 36.

The piston arrangement 33 consists of two parts arranged axially next to one another, namely the piston 31 and a roller tappet 38 with a roller 39, which is freely rotatably mounted on a cross pin 41 which is round in cross section and which supports the legs or the wall 42 of the forked or pot-shaped roller tappet 38 grasped in bores and stored therein. The roller tappet 38 bears on its side facing the spherical body 15 against the associated end face of the piston 31, the control sections at its other end facing the injection nozzle 29 and inner end having control edges extending transversely to its circumferential direction, here parallel to the longitudinal axis 43 of the piston 31 44, which with cooperate with the openings of radial feed fuel passage portions 45 in a manner to be described. The control part, generally designated 46, contains the working surface of the piston 31 on the front side, with which the piston 31 generates the pump pressure when it is displaced into the spherical body 15. The shaft of the piston 31 carrying the control part 46 is guided in the cylinder bore of a pump sleeve 47 which is inserted in a blind bore 48 which extends parallel to the piston arrangement 33 and in the inner wall of which an annular groove 51 is machined in the area of the working chamber 28 and which is filled with a fuel Supply channel 50 is connected and the fuel channel sections 45 open. At a distance from the inner end of the pump sleeve 47, this has on its periphery a shoulder on which the inner end of a compression spring 52 is supported, the outer end of which acts against a spring plate 53 which is U-shaped in cross section and which is attached to the piston 31 is axially fixed to this. With this compression spring 52, the piston arrangement 33 is preloaded with respect to its reception in the spherical body 15 against the pump drive, generally designated 49, in the form of a cam track on a cam ring 54, which bears against the wall of the free space 34 opposite the piston arrangement 33 and axially by a radial one Locking pin 55 is held, which engages in a circumferential groove 56 of the cam ring 54.

The injection pump 27 is assigned an injection quantity adjusting device, generally designated 61, with the following parts, which can best be seen in FIG. 2, namely a part 62 surrounding the suction-side bearing journal 14b here, on the wall 62 of the cover 2 surrounding the annular space 34 axially to the axis of rotation 32 a drive device A, shown in simplified form, with an axially displaceable injection quantity adjustment ring 63, a regulating sleeve 64 arranged coaxially to the longitudinal axis 43 of the piston arrangement 33, which is axially displaceably mounted in an outer, enlarged diameter section 48.1 of the blind bore 48 and with a radially outer slide 65 in an inner, rotationally symmetrical circumferential groove 66 of the adjusting ring 63 is held axially immovable relative to the latter, and a displacement-twist connection 67 between the control sleeve 64 and the piston 31, which on the one hand allows an axial displacement of the piston 31, but a relative rotation of the Prevents piston 31 relative to the control sleeve 64, and on the other hand causes the piston 31 to rotate when the control sleeve 64 is axially displaced. This connection 67 is formed by a control bolt 69 which transversely engages the control sleeve 64 in oblique or curved guide slots 68 and which engages the fork end 71 of the piston 31 which faces the roller tappet 38 and which engages in the control sleeve 64 in the existing transverse groove 70. The roller tappet 38 is axially displaceably mounted in the control sleeve 64, the cross bolt 41 engaging the radially inner wall of the control sleeve 64 in a longitudinal slot 72 and axially displaceable in a longitudinal groove 73 on the circumference of the bearing pin 14b, whereby the roller tappet 38 and also the Control sleeve 64 is axially displaceable independently of one another, but is secured against rotation.

In the present exemplary embodiment, the drive device A is formed by a worm drive. The adjusting ring 63 has at one point on its outer circumference an axially arranged groove 63a, into which the spring 63b of a worm gear segment 63c engages, which can preferably be attached to the circumferential surface of the adjusting ring 63 with correspondingly shaped contact surfaces and axially in a manner not shown in the cylinder head cover 2 is held. A worm 63d mounted in the cylinder head cover 2 with a rotary shaft and bearing points arranged on both sides of the worm toothing is arranged tangentially to the adjusting ring 63 and, with its worm toothing, is in engagement with a toothing on the outer circumference of the worm wheel segment 63c. The unit formed in this way is preferably integrated in the cylinder head cover 2.

The adjusting ring 63 is in its on the inner peripheral wall 2.3 of the Cylinder head cover 2 stored position guided by two or more diametrically or star-shaped opposite sliding bolts 63e, which are inserted into holes 63f of the wall of the cylinder head cover 2 and border in sliding grooves 63g with a helical pitch in the outer peripheral surface of the adjusting ring 63.

The injection nozzle 29, which is preferably arranged in the axial plane of the injection pump 27, is oriented radially with respect to the center 74 of the spherical body 15, and is inclined by the angle w relative to the plane of rotation of the rotary ball valve 3 which intersects the center point. The nozzle holding body 75 containing the injection nozzle 29 supports an axially displaceable nozzle needle 76 which is biased from the inside against the nozzle opening 29.1 by a compression spring 77. The nozzle holding body 75 is immovably inserted with respect to its longitudinal axis in a stepped blind bore 78 which is inclined in accordance with the angle w, whereby it approximately closes with the spherical surface 13 and rests against the shoulder of the blind bore 78 with a shoulder 79, one of which is used to secure it against rotation Shoulder 79 axially projecting anti-rotation pin 81 is provided. At the bottom of the blind bore 78 is supported the compression spring 77 which, by means of a spring plate 82, prestresses the nozzle needle 76 with its conical closure end projecting into the nozzle opening 29.1 against the nozzle opening 29.1, and thus normally closes the injection nozzle 29. The nozzle needle 76 has two cylindrical longitudinal sections 83, 84, of which the longitudinal section 83 facing away from the nozzle opening 29.1 is axially displaceably mounted in a guide bore in the nozzle holding body 75 and the front longitudinal section 84 tapered by means of a shoulder 85 moves radially in one between the two Extends nozzle opening 29.1 and the guide bore extending bore section 86 of the nozzle holder body 75, which is connected to the working space 28 by means of generally designated 87, in the present embodiment penetrating the shoulder 79 channel sections. The

Nozzle holding body 75 extends at a distance of only a few mm next to the working space 28, the injection pump 27, so that the length of the or the channel sections 87 extending between the working space 28 and the annular channel 86 is also only a few mm.

The functional parts of the injector 29 and also of the injection pump 27 are arranged in material projections 91, 92, which are radially inward from the inner wall 93 of the spherical body 15. In the present exemplary embodiment, the material approaches 91, 92 merge into one another, a cooling channel section extending in the circumferential direction being provided between the material approach 91 of the injection pump 27 and the shell wall of the spherical body 15. When the spherical body 15 is designed as a casting, the material attachment 92 of the injection nozzle 29 can pass into the wall 94 of the inlet control channel 16 facing it at its radially inner end. The cavity between the material attachments 91, 92 and the wall 94 is fluidly connected as a cooling channel section 8.3 to the cooling channels 8.1, 8.2. The material approach 92 of the injection nozzle 29 is at a distance from the wall 95 of the outlet control channel 17 facing it, which results in a cooling channel section 8.4 which is part of a cooling channel section 8.5 surrounding the outlet control channel 17 and which is connected to the cooling channels 8.1, 8.2 is. Thus, not only the material approach 91 of the injection pump, but also the material approach 92 of the injection nozzle 29 is surrounded on the largest sections of its circumferential surface by cooling channel sections and is thus excellently cooled.

In order to effectively cool the section of the injection pump 27 projecting axially from the spherical body 15, a small hollow base 96 is arranged on the lower cover part 2.2, in which extends a cooling channel section 8. 6 surrounding the passage between the piston chamber and the rotary ball valve 3, which section corresponds to the associated section the annular wall 62 surrounding the annular free space 34 and thus the assigned area of the injection pump 27 is able to cool effectively from the outside. On the inside, the injection pump 27 is cooled by the cooling channel section 8.3 and the supplied combustion air by means of the wall 94 of the inlet control channel 16 or the wall of the bearing journal 14b, so that an effective cooling of the injection pump 27 also proceeds from here. On the opposite side, a cooling channel section 8.7 is provided between the walls of the inlet control channel 16 and the annular extension 36, which is connected to the coolant cavity 8 and to the associated coolant channel sections 8.1, 8.8. In addition, between the material approach 91 and the wall 93 of the heat sink 15 there is a cooling channel section 8.8, which contributes to cooling the wall 93, the injection pump 27 and the nozzle 29. The individual cooling duct sections are connected to the cooling duct circuit extending within the rotary ball valve 3 in such a way that effective cooling takes place, compare the flow arrows shown. In the present embodiment, the cooling duct section 8.6 extending in a ring around the cylinder axis is connected to the cooling ducts 9 running in the cylinder block 4 through at least one opening 8.9 in the bottom wall facing the cylinder block 4.

The spherical body 15 is exposed to high temperatures during operation of the internal combustion engine, which act on it from the combustion chamber. Inadmissibly high thermal loads lead to surface damage and warpage. In the present embodiment, the spherical body 15 is connected to the cooling circuit of the engine, the cooling channels 9 of which emerge from the cylinder head surface and are connected via the openings 8.9 to the cooling channels of the cylinder head cover 2 already mentioned. The liquid coolant passes from the annular cooling channel section 8.6 surrounding the combustion chamber 125 to an annular channel 8.10 surrounding the bearing journal 14a, from which the coolant passes through the cooling channel 8.1 running axially in the journal 144 into the cavity 8 of the spherical body 15 and then through the likewise axial cooling channel 8.2 in the journal 14a to an outside next to the Ring channel 8.10 arranged ring channel 8.11 arrives, from which an axial line connection LA starts at the left end of the cylinder head cover 2, through which the coolant flows out in the circuit.

In order to ensure a continuous flow, the bearing journal 14a is specially designed. As can best be seen from FIG. 3, the annular space located between the journal wall 14c and the outlet control channel wall 17a is divided by longitudinal webs 98 into a plurality of longitudinal channels, preferably an even number and the same size, with four being offset by 90 ° to one another in the present exemplary embodiment Longitudinal webs 98 are provided, each forming two diametrically opposite cooling channels 8.1 and 8.2. The ring channels 8.10 and 8.11 run at their inner ends into the cavity 8 of the spherical body. At their outer ends, they are axially delimited by an annular web 17b which connects the tubular control channel wall 17a and the tubular bearing section wall 14c to one another.

The ring channels 8.10 and 8.11 are separated by a radial partition 99, which extends radially between the outer wall of the cylinder head cover 2 to the bearing section wall 14c and has a small clearance or gap from it as a running clearance, which can be approximately 0.5 mm. In the present embodiment, the partition 99 is part of an annular flange 100 which can be screwed onto the end face of the cylinder head cover 2 and which surrounds the free end of the bearing section 14a and is sealed against the annular web 17b by means of a shaft seal 101. The partition wall 99 is preferably an annular disk which is inserted in a corresponding annular recess of the annular flange in a form-fitting or non-positive manner adjacent to the contact surface of the annular flange 100. In the axial regions of the ring channels 8.10 and 8.11, designated c and d, there are slots 102, 103 in the journal wall 14c, which extend in the circumferential direction from the longitudinal web 98 to the longitudinal web 98, the number of cooling channels 8.1, 8.2 existing slots 102, 103 are provided and correspondingly assigned, in this embodiment four pieces, of which - like the cooling channels 8.1, 8.2 - the slots 102 assigned to the ring channel 8.10, taking into account the axial offset V, the slots 103 assigned to the ring channel 8.11 diametrically can face each other. In the preferred embodiment according to FIG. 3 it is provided that the two input cooling channels 8.1 with associated slots 102 are diametrically opposite one another and the output cooling channels 8.2 with associated slots 103 are diametrically opposite one another. Such an arrangement of the coolant channels 8.1 and 8.2 should preferably be provided in order to largely prevent the bearing journal 14a and the tubular exhaust gas channel 17 from being distorted as a result of the different coolant temperatures in the coolant channels 8.1 (inlet) and 8.2 (outlet).

The longitudinal webs 98 can extend from or be attached to the journal wall 14c or from the control channel wall 17a, and they can also protrude into the cavity 8 of the spherical body 15 if this is conducive to the flow process. As can best be seen from FIG. 3, it is advantageous to reinforce the journal wall 14c in the region of the partition wall 99 by means of an annular web 104 or bead. Because of the configuration described above, a continuous flow is possible, although the rotary ball valve 3 rotates with respect to the cylinder head cover 2.

The fuel supply takes place through a supply line connection 105 indicated in FIG. 1, which is arranged on the outer wall of the cover 2 in the area of the ring extension 36, preferably in the radial central plane of the cylinder surface 37. The line connection 105 is also connected through a radial channel section an annular groove 106 connected, which is incorporated into the base of a substantially wider annular groove 107, which is open on the inner wall of the cover 2. In this annular groove 107, a shaft seal 108 cooperating with the cylinder surface 37 is inserted for the purpose of sealing the fuel supply line against the ball cavity or the combustion chamber and the annular free space 34. For this purpose, two spaced-apart sealing lips 109 (see enlarged and perspective detail in FIG. 4) serve the shaft seal 108, which interact with the cylindrical surface 37 of the rotary valve 3 . The elastic sealing lips 109 are arranged at the free ends of a U- or C-shaped sealing body and either due to their elasticity or by means of a tendon, for. B. a coil spring 111, biased against the cylindrical surface 37, the coil spring 111 can be embedded in the free ends of the sealing lips 109 or arranged in a circumferential groove provided for this purpose. The sealing body designated 113 has at least one, preferably a plurality of radial channels 114 distributed in the circumference in its web 115. Between the sealing lips 109, in the area of the injection pump 27, a radial channel section 116 is arranged in the cylinder surface 37, which leads to a channel section 117 as part of the fuel supply channel 50, which extends parallel to the axis of rotation 32 in the material attachment 91 to the injection nozzle 29, and preferably on the side of the material attachment 91 facing away from the axis of rotation 32. This axial channel section 117 intersects the annular groove 51.

In particular when the shaft seal 108 is also intended to seal off its annular cavity 118, second sealing lips 120 are arranged on the legs 119 of the sealing body 113 outside the first sealing lips 109, which are preferably directed away from one another and also interact with the cylinder surface 37. In this case, the cylinder surface 37 must have a correspondingly wide dimension. In the present exemplary embodiment, the second sealing lips 120 are arranged at the free ends of the U-shaped sealing body 113, the legs 119 carrying the first sealing lips 109 also projecting obliquely toward one another from these free ends.

The seal of the shaft seal in the annular groove 107 can by The preferably elastic sealing body 113 is glued or pressed in. In the present exemplary embodiment, the sealing body 113 is reinforced by a U-shaped reinforcing part which is embedded in the elastic sealing body material in the region of the web 115 and the web walls 121 lying opposite one another.

In order to simplify the construction, it is advantageous to separate the shaft seal 108 radially and to assemble it by means of two shaft seal parts (not shown) that are angular in cross-section and are designed to be mirror images of one another.

The function of the injection device 26 is described below.

The fuel is drawn in by a low-pressure fuel pump (not shown) arranged on the outside of the internal combustion engine and conveyed via the line connection 105 to the annular groove 106 in the upper and lower parts 2.1, 2.2 of the cover. From here it reaches the working space 28 via the channel sections 114, 116, 117, 51 and 45. The roller tappet 38, which rotates around the axis of rotation 32 at a uniform angular velocity in operation with the piston arrangement 33 and the rotary ball valve 3, presses the piston 31 when the cam 54.1 overflows into the working space 28. The fuel, which is controlled by the at least one control edge 44 on the control part 46 of the piston 31 and is still in the working space 28, now becomes through the duct sections 87 and the annular duct 86 to the nozzle opening still closed by the nozzle needle 76 29.1 funded.

Due to the pressure of the fuel, the nozzle needle 76 is pushed in against the pretension of the compression spring 77, the fuel being injected axially through the nozzle opening 29.1 into the combustion chamber 125, where the combustion of the fuel-air mixture takes place in a known manner. If the fuel pressure due to the end of the stroke of the piston 31, the compression spring 77 presses the nozzle needle 76 back onto the needle seat, as a result of which the injection process is ended. The opening pressure of the injector 29 can be adjusted by a corresponding change in the pretension of the compression spring 77, which is done here by inserting or removing the adjusting springs 126 supporting the compression spring 77.

Fuel, which (leaks) through the guide bore into the space of the blind bore 78 receiving the compression spring 77, is returned to the axial fuel feed channel section 50, 117 via return channels 127 which essentially run on the circumference of the nozzle holding body 75 and in the present exemplary embodiment cross the pin 81 fed. The same applies to leaks between the piston 31 and the pump sleeve 47. These leaks are fed to the axial channel section 50, 117 through radial channels 128 and a ring channel 129 starting from a receiving ring channel.

The injection quantity adjustment for speed adjustment takes place by turning in one of the two directions of rotation z of the worm 63d, the injection quantity adjustment ring 63 being rotated in the y direction about the axis 43 by the worm gear segment 63c which is in the rotational driving connection. When the adjusting ring 63 is rotated, it is axially displaced in the direction x due to the engagement of the stationary sliding bolts 63e in the sliding grooves 63g, whereby the regulating sleeve 64 is axially entrained by means of the sliding piece 65, that is to say displaced in the same axial direction. The axial movement of the regulating sleeve 64 causes the regulating bolt 69 enclosing the guide slots 68 to rotate about the longitudinal axis 43 of the piston 31, as a result of which the piston 31 is rotated due to the engagement of the regulating bolt 69 in the transverse groove 70. As a result of this setting, the control edges 44 of the piston 31 and the radial channels 45 come to different overlaps, as a result of which corresponding fuel delivery quantities are set. The worm gear segment 63c is in this way Cylinder head cover 2 is held or mounted so that it can be rotated together with the adjusting ring 63 in the directions of rotation y, but is held in the cylinder head cover 2 in an unadjustable manner against movement in the axial directions of movement x. In contrast, the adjusting ring 63 is axially displaceable relative to the worm gear segment 63c, which is made possible here by the parallel key connection.

The time of injection is also dependent on the position of the injector 29 in the circumferential direction of the rotary slide valve 3 with respect to the control opening 18 of the inlet control channel 16. This position is to be determined on the basis of functional principles. A spindle drive comparable to the spindle drive A can be used to rotate the cam ring 54 for the purpose of adjusting the injection time, wherein an axial displacement of the cam ring 54 is not required, but only a rotation. Such a drive for the cam ring 54 is not shown.

A further advantage of the exemplary embodiment described above is as follows: The separate arrangement of a low-pressure fuel system (LP fuel pump) and a high-pressure fuel system (HP injection pump 26) results in two structural or functional groups with inherently "stationary" states.

The fuel passes from the low-pressure low-pressure fuel pump, which is arranged on the machine body, for example, into the rotary ball valve 3, which enables problem-free sealing, in particular with the shaft seal 108 according to the invention. There is also a small, compact design and short distances between the injection pump 27 and the injection nozzle 29, as a result of which massive, thick-walled pressure line walls for maximum pressures can be realized without "breathing". In addition, pressure waves are largely avoided.

The exemplary embodiment according to FIGS. 5 and 6 differs from the previously described exemplary embodiment by a modified injection nozzle 229, while the other parts of the device remain essentially unchanged and a further description of these parts of the device is therefore not necessary.

The injection valve 229, which is inclined by the angle w in accordance with the first exemplary embodiment, is a so-called diaphragm valve with a valve holding body 275 inserted into the existing material approach 292 in a stepped blind bore 278. The valve holding body 275 has a central longitudinal channel section 276 starting from its inner end , in which at the inner end of the valve holding body 275 a channel section 277, which runs parallel to the axis of rotation 32 of the rotary ball valve 3 and runs from the working space 28 of the injection pump 27, opens. In front of the end containing the valve opening 29.1, the channel section 276 branches out with at least two Y-branching channel branches 279, 280 to form a concentric annular channel 281 on the end face of the valve holding body 275. Between the annular channel 281 there is a central pin 283, preferably with a round cross section. Arranged on the end face in a position covering the annular channel 281 is a disk 284 which forms the membrane of the diaphragm valve and is clamped on its outer peripheral edge by a screw part 285 countersunk in the spherical body 15 with the interposition of a sealing ring 286 against the end face of the valve holding body 275. In the center of the disk 284 there is a bore 287 with a diameter d that is slightly smaller than the diameter D of the pin 283. With this inner edge 288, the disk 284 bears against the end face of the pin 283, which is preferably punched free in its center , so that the outer peripheral edge of the pin 283 and the inner peripheral edge of the disk 284 overlap slightly.

In the presence of an injection pressure in the channel branches 279, 280, the disc 284 becomes due to the hyrostatic pressure by bending in its central region lifted off the pin 283, which creates an annular gap from which the fuel can spray out in a ring and finely divided. In order not to hinder this spraying process, the bore 287 is chamfered on the outside.

After the injection pressure drops, the diaphragm valve closes automatically.

The use of a diaphragm valve enables a small construction for the injection valve 229, which can already be seen from the fact that the material approach 292 receiving the diaphragm valve is smaller than the material approach 92 receiving the injection pump 227. This makes more space for the outlet control channel 17 and / or the cooling channel section 208.4 extending therebetween.

In the exemplary embodiment according to FIGS. 7 to 9, an injection pump 327 with a modified design and a diaphragm valve 329 shown in simplified form are used, which is essentially comparable to the diaphragm valve 229 described above.

The injection pump 327 is preferably also arranged at a distance a parallel to the axis of rotation 32 of the rotary valve 3. Starting from the ring extension 36, a tulip-shaped material extension 391 extends axially parallel, which at its free end merges with an extension 392 for the diaphragm valve 329, the material extensions 391, 392 extending in a bridge-like manner over a cooling space section 308.8 of the cavity 8 of the spherical body 15. A pump cylinder 347 is non-positively drawn into the material attachment 391, in which a piston 331 is axially displaceable through the cam ring designated here by 354. As already in the embodiment according to FIG. 1, the piston is formed from at least two parts and is telescopic, which serves to adjust the injection quantity. The actual piston 331 has a flange 331.1 through which between it and the pump cylinder 347 clamped, the piston 331 surrounding compression spring 332 is biased towards its rear end against an adjusting ring 360, which can be described axially displaceably in the cylinder head cover 2, preferably in a position surrounding the rotary valve 3 indirectly or directly on the outer wall of the cylinder head cover 2 is mounted.

At its rear end, the piston 331 has a coaxial guide bore 331.2, in which a connecting bolt 357 can be axially displaced, which is inserted and fastened in a transmission bolt 352 arranged on the rear side of the piston 331, for example by being pressed into the existing bore in the transmission bolt 352. Between a flange-shaped sliding head 352.1 facing the cam ring 352.1 of the transmission pin 352 and the flange 331.1, a second compression spring 356 is clamped, the spring force of which is less than that of the compression spring 332, so that the retraction of the piston 331 and the contact of the sliding head 352.1 with the cam track 354.1 of the Cam ring 354 is guaranteed. The adjusting ring 360 has one or more diametrically or star-shaped radial and helically arranged sliding grooves 360.1, into which sliding pins 361 from outside engage with little movement play, which sit in radial bores 358.2 of an adjusting ring 360 surrounding the adjusting ring 360 and bearing or guiding it , which is rotatably and axially displaceably mounted on the outer wall of the cylinder head cover 2 and is axially secured by means of one or more diametrically or star-shaped sliding bolts 359 which sit in radial bores of the outer wall 2.3 and with little movement play in helically arranged sliding grooves Insert 358.1 in the adjustable bearing ring 358. In the present embodiment, the sliding grooves 360.1 and 358.1 in the adjusting ring 360 and in the adjusting bearing ring 358 are inclined in opposite directions. However, they can also have the same direction of inclination with the same and also different pitch.

On the cylindrical projection 36 sits with its sealing edges a shaft sealing ring 308 corresponding to the above-described embodiment, which is also mounted in the cylinder head cover 2. A bore 362 extends from the gap between the two sealing edges to an axial bore 363 machined from the outside in the material attachment 391, in which a valve body 364 with a suction valve 365 is inserted and closed by a screw plug 366. Two axial channels 367 and 368 lead from the bore 363 into the front area of the piston 331, of which the channel labeled 367 connects behind the suction valve 365, while the channel labeled 368 branches off before the suction valve 365, here with a radial bore 364.1 is connected in the valve body 364. The channel 367 at the head end of the pump cylinder 347 is connected to the working space 328 of the injection pump 327 by a radial channel section 369. Further radial channel sections 371 and 372 are approximately in the middle and in the lower third of the pump cylinder 347, i. that is, arranged in the guide area thereof and connect the guide section for the piston 331 to the channel 368, which is bypassing the suction valve 365 and connected to the low-pressure line generally designated 373.

When the piston 331 moves backward, the liquid fuel is sucked into the working space 328 via the suction valve 365. During the delivery stroke, the fuel is conveyed through the pressure valve 375 arranged in front of the working space 328 and the pressure line 376 adjoining it to the diaphragm valve 329, where the injection takes place. The backflow of the fuel is prevented by the check valve in the suction valve 365. The fuel (leak oil) flowing out in the guide gap of the pump cylinder 347 is led to the low pressure line 373 via the channels 371 and 372. This leak oil also serves to cool and lubricate the injection pump parts.

In the pressure valve 375 there is also a check valve which prevents fuel from flowing back from the pressure line 376 during the suction stroke of the piston 331.

As can be seen in particular from FIG. 9, the return stroke of the piston 331 is limited by the adjusting ring 360, the transmission bolt 352 following the cam track 354.1 due to its telescopability and therefore being in constant contact with it. This leads to a relatively "soft" loading of the piston 331 during the delivery stroke due to the effectiveness of the compression spring 356. The axial connection between the transmission pin 352 and the piston 331 is ensured by the connecting pin 357, which is axially displaceably mounted in the guide bore 331.2 and on the transmission pin 352 is attached. The radial bore 331.3 is located in the guide area of the connecting bolt 357 and serves to supply the lubricant. A radial hole 331.4 arranged at the inner end of the guide hole 331.2 serves as a ventilation hole.

The engine speed or the fuel flow rate is regulated with the adjusting ring 360, which can be driven by a spindle drive comparable to the spindle drive A according to FIG. 2 for the purpose of rotating the adjusting ring 360. Here, the adjusting ring 360 is due to the engagement of the adjusting ring 358 " stationary "and axially displaced in the helical sliding grooves 360.1 sliding pin 361. Since the adjusting ring 360 rests non-positively on the end face on the flange 331.1 due to the force of the compression spring 332, the axial displacement of the adjusting ring 360 mentioned above results in a corresponding limitation of the return stroke of the piston 331 and thus a corresponding limitation in the immersion depth in the pump cylinder 347. As a result, this changes Delivery volume for each subsequent delivery stroke. An adjustment of the adjustment ring 360 in FIG. 9 to the left leads to a reduction in the delivery rate, and an adjustment to the right leads to an increase in the delivery rate. In the position shown in Fig. 9 there is

"Zero conveying", in which only the transmission pin 352 moves back and forth between the base line and the cam tip of the cam track 354.1 and thereby carries out an "idle stroke".

Since internal combustion engines require a slightly higher amount of fuel during warm-up in order to ensure "round" engine running, the adjusting bearing ring 358 is provided, which is preferably rotatable by a warm-up sensor, not shown, with an expansion element and a switching device and due to the engagement of the sliding bolts 361 in the helical sliding grooves 358.1 is axially displaced during its rotation and thereby additionally displaces the adjusting ring 360 axially, as a result of which the desired increase or decrease in the fuel setting is achieved. The adjustment bearing ring 358 assumes a maximum rotational position when the engine is cold and a minimum when the engine is warm.

The exemplary embodiment according to FIGS. 10 and 11 relates to an internal combustion engine, generally designated 401, the cylinder block 404 and preferably the divided cylinder cover 402 according to FIG. 1 and the rotatably shown, rotatably shown ball slide valve 403 are shown in simplified form. In this embodiment, the injection device (not shown) can be integrated into the spherical body 415 of the rotary slide valve 403, as in the exemplary embodiments described above, or a conventional injection device or another mixture preparation device can also be provided. The rotary ball valve can also have cooling channels in accordance with the above-described exemplary embodiments.

This exemplary embodiment is suitable for an internal combustion engine with a plurality of cylinders arranged in series, of which only one with pistons 406 is visible within cylinder block 404 in FIG. 10. The row of cylinders extends straight and is identified in FIG. 11 by the center line labeled ZR. From this center line ZR or middle plane are the Spherical body 415 and the associated mounting in the cover 402 are mutually axially offset or desachsiiert to another side. As a result, the centers, the rotary slide valve 403 or their spherical bodies 415 are mutually equal distances X1, X2 from the cylinder row ZR. This configuration either enables a smaller, compact design of the internal combustion engine 401, because, due to the offset or the decaching, the center distance Y between adjacent rotary ball valves 403 can be reduced, or with a predetermined distance Y between adjacent rotary ball valves 403, larger rotary ball bodies and valve opening cross sections can be realized, which the stability and large passage cross sections benefit both for the fresh gas as well as for the exhaust gas or the cooling channel cross sections. In the position of the rotary slide valve 403 shown in FIG. 10, its intake or inlet control channel 16 is in its loading position, ie the inlet opening 18 of the control channel 16 is above the piston 406 or above the existing one for the purpose of unimpeded entry of the inlet gas or the combustion air Through channel 424 in the lower lid part 402.2, which also represents the combustion chamber 425. In the present exemplary embodiment, the displacement dimension X1 or X2 is dimensioned so large that the edge pointing in the displacement direction of the inlet opening 18, which is substantially smaller in cross section than the piston 406, lies approximately above the edge of the piston 406 to which the spherical body 415 is offset. In the same way, the respective adjacent rotary valve 403 is axially offset to the other side. Within the scope of the invention it is possible to move the ball rotary slide valve 403 as a whole or the ball body 415 to the inlet side or preferably to the outlet side of the ball rotary slide valve 403. It is possible to arrange the rotary ball valve 403 such that the intake control channels 16 and the exhaust control channels 17 are arranged alternately on one and the other side of the cylinder block 404 or preferably on the same side in each case. It is also advantageous to have the recesses for the rotary ball valve 403 in the cylinder cover 402 to move according to the desachiation, so that the same rotary rotary valve 403 can be used. With the possibilities described above, the injection device can be arranged with respect to the radial center plane of the spherical body 415 on the side to which the rotary ball valve 403 or the spherical body 415 is offset, or on the other side. The injection devices can also be arranged alternately or preferably on one side. The arrangement of the injection devices on one side of the cylinder block and in this case on the inlet side of the rotary ball valve 403 is particularly advantageous.

A further use of space is possible if the cross section of the inlet opening and the outlet opening (not shown) in the spherical body 415 is elongated along the row of cylinders ZR, as is the case in the exemplary embodiment where the cross section of the inlet and outlet openings is flattened on both sides ( see A). A maximum offset dimension X1, X2 is hereby achieved.

In order to avoid disturbances in the flow, it is advantageous to let the passage channel 424 or the combustion chamber run downwards at an angle or curved to the side which is opposite to the direction of displacement. As can be clearly seen from FIG. 10, a combustion chamber recess 426 is embedded in the top of the piston 406, which is also offset in the opposite direction of displacement.

It can thus be seen that the configuration according to the invention is advantageous not only with regard to a compact size of the internal combustion engine due to the decaching of the rotary ball valve 403, but also with regard to the arrangement and mounting of the injection pump 27, 327 in the spherical body 415. It turns out that a (not arrangement) of the injection pump on the side to which the center of the spherical body 415 is offset or on the side which is opposite to the offset, is possible and advantageous. In the first case, the injection pump or the secantial section of the spherical body 415 receiving it is more accessible. In the latter case, the injection pump is shifted a significant distance towards the cylinder center plane. The configurations according to the invention are particularly suitable for relatively long injection pumps, preferably for those with axial pistons.

Claims (53)

1. Internal combustion engine, preferably a diesel internal combustion engine, in particular a reciprocating piston engine, with internal combustion and with cylinders arranged individually or in series, with an injection pump, preferably a high-pressure injection pump, and an injection device comprising an injection nozzle and with at least one rotating control element per cylinder for the gas charge exchange processes, which is arranged between the cylinder block and the cylinder cover or in the latter with a rotation axis that is preferably perpendicular to the cylinder axis, and between two pins that extend axially in rotation has a control body that is firmly connected to the pin, the control body and the pegs being uniformly surrounding counter surfaces are provided in the cylinder head and each pin is penetrated by an axially extending gas channel, each of which merges into a bend-shaped gas channel arranged in the control body, which on the surface de s control body emerges with an opening, means for transmitting a rotational movement from the crankshaft to the control element being provided, the control body being designed as a spherical, in particular a hollow spherical body and the injection nozzle being mounted in the spherical body,
characterized,
that the injection pump (27, 327) is mounted in the spherical body (15) of the rotary valve (3). 2. Internal combustion engine according to claim 1, characterized in that the injection pump (27, 327) is arranged axially offset next to the injection nozzle (29). 3. Internal combustion engine according to claim 1 or 2, characterized in that the injection pump (27, 327) has an axially displaceable piston (31, 331) which extends substantially parallel to the axis of rotation (32) of the rotary valve (3). 4. Internal combustion engine according to one or more of claims 1 to 3, characterized in that the injection pump (27, 327) in a pin (14a, 14b) radially projecting body part of the spherical control body (15) is arranged. 5. Internal combustion engine according to claim 4, characterized in that axially laterally next to the spherical control body (15) an associated pin (14b) surrounding annular space (34) is provided and the injection pump (27, 327) protrudes secantially from the control body (15) and protrudes into the annular space (34). 6. Internal combustion engine according to claim 5, characterized in that the control body (15) has a lateral, the associated pin (14b) surrounding, preferably cylindrical ring extension (36), from whose substantially radial side surface (35) protrudes the injection pump (27) . 7. Internal combustion engine according to one or more of claims 1 to 6, characterized in that the injection pump (27, 327) is driven by a cam (54.1) which is held on the cylinder cover (2) or an attachment thereof. 8. Internal combustion engine according to claim 7, characterized in that the cam (54.1) is adjustable by a first adjusting device in the circumferential direction of the rotary slide valve (3) and can be locked in the respective adjusting position and is preferably arranged on a cam ring (54) which is rotatably and axially immovably mounted in the cover (2). 9. Internal combustion engine according to one or more of claims 3 to 8, characterized in that the piston (31) at its front end has a control part (46) with at least one, preferably axially parallel control edge (44) which has a fuel supply opening (45) cooperates and can be rotated by a second adjustment device (61) independently of its longitudinal movement and can be locked in the respective rotational position. 10. Internal combustion engine according to claim 9, characterized in that the second adjusting device (61) has a non-rotatable and axially adjustable adjustment part (64) which rotates the piston (31) during its axial displacement. 11. Internal combustion engine according to claim 10, characterized in that the adjusting part is a coaxially to the piston (31) arranged sleeve (64) which is connected by a transverse bolt (69) to the piston (31) which has a longitudinal portion of the piston (31 ) in an axial transverse groove (70) and in guide sleeves (68) which are arranged opposite one another in the sleeve (64) and which run obliquely in the circumferential direction or with an incline. 12. Internal combustion engine according to claim 10 or 11, characterized in that the adjusting part (64) with a control body (15) surrounding adjusting ring (63) is axially immovably connected, which is rotatably and axially displaceably mounted in the cover (2) and by an adjusting mechanism adjustable as well as in the respective adjustment position is noticeable. 13. Internal combustion engine according to claim 12, characterized in that the adjusting ring (63) is guided by radial pins (63e) distributed over the circumference, which are inserted in holes (63f) in the inner wall of the cover (2) and in guide slots (63g ) in the adjustment ring (63), which run obliquely or with an incline in the circumferential direction. 14. Internal combustion engine according to one or more of claims 9 to 13, characterized in that the first and / or the second adjusting device (61) by a worm gear (A), a spur gear or a push / pull rod drive with a preferably articulated by a ball joint connected push-pull rod drive formed. 15. Internal combustion engine according to claim 14, characterized in that the worm shaft (63d) of the worm drive (A) is arranged tangentially or secantially in / on the cylinder head cover (2) and mounted and with the cam ring (54) or the adjusting ring (63) cooperates. 16. Internal combustion engine according to claim 15, characterized in that a worm wheel or a worm gear segment (63c) is provided on the adjusting ring (63) which is immovable in the circumferential direction on the adjusting ring (63) and along the axis (43) of the adjusting ring immovably in the cylinder head cover (2) is mounted, the adjusting ring (63) being displaceably connected to the worm wheel or worm wheel segment (63c) along its axis (43). 17. Internal combustion engine according to one or more of claims 3 to 16, characterized in that the piston (31, 331) is telescopic. 18. Internal combustion engine according to claim 17, characterized in that that the telescopic parts of the piston (31, 331) are rotatably mounted relative to each other. 19. Internal combustion engine according to claim 17 or 18, characterized in that the rear telescopic part is rotatably and longitudinally mounted. 20. Internal combustion engine according to one or more of claims 9 to 19, characterized in that the second adjusting device (361) has a rotatable and axially adjustable adjustment part, preferably in the form of a piston (331) surrounding ring or a sleeve (360) which axially displaces the piston (331) axially. 21. Internal combustion engine according to claim 20, characterized in that the front telescopic part of the piston (331) preferably rests with a flange (331.1) on the back of the adjusting part (360) and is biased by a spring (332) against the adjusting part (360), and that the rear telescopic part (352) is biased by a spring (356) of lower spring force against the cam ring (354). 22. Internal combustion engine according to claim 20 or 21, characterized in that the ring or sleeve (360) is guided by one or more radial pins (361) arranged distributed around the circumference, which are directly or indirectly on the wall of the cylinder head cover ( 2) are held and surround in guide slots (360.1) in the ring or in the sleeve (360), which run obliquely in the circumferential direction or with an incline. 23. Internal combustion engine according to one or more of claims 8 to 22, characterized in that the first and / or second adjusting device has an adjusting element which is temperature-dependent in its expansion, in particular an Expansion element is assigned. 24. Internal combustion engine according to claim 22 and 23, characterized in that the sleeve (360) is rotatably mounted in an adjustment bearing ring (358) which is rotatable about its axis (32) in the cylinder head cover (2) and by one or more each other diametrically or star-shaped opposite radial pins (361) are guided, which are held on the cylinder head cover (2) and surround in guide slots (358.1) in the adjusting bearing ring (358), which run obliquely in the circumferential direction or with an incline. 25. Internal combustion engine according to claim 23 and 24, characterized in that the adjusting member acts on the adjusting bearing ring (358). 26. Internal combustion engine according to one or more of claims 1 to 25, characterized in that the axis of the injection nozzle (29, 229, 329) extends radially with respect to the spherical control body (15). 27. Internal combustion engine according to one or more of claims 1 to 26, characterized in that the axis of the injection nozzle (29) to the side facing away from the injection pump (27, 327) is offset or rotated by an angle (W). 28. Internal combustion engine according to one or more of claims 1 to 27, characterized in that the injection nozzle (29, 229, 329) and the injection pump (27, 327) preferably in a along the axis of rotation (32) of the rotary valve (3) extending Level, and the injection pump (27) with respect to the control channels (14a, 14b) is preferably arranged on the inlet side. 29. Internal combustion engine according to one or more of the claims 1 to 28, characterized in that the injection nozzle (29, 229, 329) is assigned a closing member (76, 284) which is elastically biased into its closed position and can be opened by the injection pressure. 30. Internal combustion engine according to claim 29, characterized in that the closing member is formed by an inside of the nozzle opening, longitudinally displaceably guided nozzle needle (76). 31. Internal combustion engine according to claim 30, characterized in that the preferably with a conical section in the nozzle opening (29.1) projecting nozzle needle (76) facing away from the nozzle opening (29.1) guide section (83) and one facing the nozzle opening (29.1), opposite Guide section (83) has a tapered needle section (84) penetrating an axial channel (88) of the nozzle holder body (75) with radial clearance and that the channel (88) is connected to the pressure chamber (28) of the injection pump (27). 32. Internal combustion engine according to claim 29, characterized in that the injection nozzle (29) is formed by a membrane valve, preferably with a membrane (284) which in the closed position with the edge of a central opening (287) on a coaxial pin (283) is present. 33. Internal combustion engine according to one or more of claims 1 to 32, characterized in that the injection pump (27, 327) and the injection nozzle (29, 229, 329) in one or in each case one of the inner wall of the hollow spherical control body (17) radially inward protruding projections (91, 92) are arranged. 34. Internal combustion engine according to at least one of claims 1 to 33, characterized in that in the control body (15) and in at least one pin (14a) of the rotary slide valve (3) at least one cooling duct, which at least partially surrounds the walls of the injection pump (27) and / or the injection nozzle (29) or the latter, or protrusions (91, 92), preferably extends through openings or Channel sections in the cylinder head cover (2) are connected to the cooling channels (9) of the cylinder block (4) of the internal combustion engine. 35. Internal combustion engine according to one or more of claims 1 to 34, characterized in that the cylinder cover (2) from an axially to the rotary ball valve (3) divided upper lid part (2.1) and lower lid part (2.2) is formed that in the lower lid part (2.2) there is provided a passage channel extending from the spherical control bodies (15) to the combustion chamber (125), and that this passage channel is sealed by an annular seal (12) arranged in the lower lid part (2.2), preferably rotatable about its central axis, in an annular groove in the lower lid part (2.2). 36. Internal combustion engine according to claim 35, characterized in that the ring seal (12) to the side facing away from the injection pump (27) is inclined, preferably arranged coaxially to the axis of the injection nozzle (29). 37. Internal combustion engine according to one or more of claims 6 to 36, characterized in that the cylindrical peripheral surface (37) of the ring extension (36) is sealed by a shaft seal (108), which is preferably on the inner wall of the cover (2) in an annular groove (107) is held. 38. Internal combustion engine according to claim 37, characterized in that the shaft seal (108) is a substantially cylindrical web part (115), two radially extending from the edges of the wall parts (121) and two outgoing and has sealing legs (119) which extend towards one another and each have a first and optionally also a second sealing lip (109, 120). 39. Internal combustion engine according to claim 37, characterized in that two identical shaft seals, each with a substantially cylindrical web part (115) and a radial sealing wall part are formed and arranged in mirror image to one another that the web parts (115) and those emanating from the wall parts , first and optionally also second sealing lips (109, 120) having sealing legs (119) facing each other. 40. Internal combustion engine according to claim 38 or 39, characterized in that the fuel supply line is guided radially inward through the cavity (118) of the shaft seal (108) and a line connection (105) on the jacket of the cover (2), a radial and / or annular channel section (106) has at least one opening (114) in or in the web parts (115), a radial channel section (116) arranged between the first sealing lips (109) and further axial, radial and / or annular channel sections. 41. Internal combustion engine according to claim 40, characterized in that the injection pump (27, 327) is a high-pressure injection pump, and the internal combustion engine (1) is associated with a low-pressure fuel pump, which is connected to the line connection (105). 42. Internal combustion engine, in particular according to one or more of claims 1 to 41, characterized in that the cavity (8) of the spherical body (15) is connected to the cooling circuit of the internal combustion engine. 43. Internal combustion engine according to claim 42, characterized in that two cooling duct sections (8.6, 8.10, 8.11) are provided in the cylinder head cover (2), one of which passes through at least one opening (8.9) in the bottom wall of the cover (2) to the cooling duct (9) of the cylinder (4) is connected and by means of a first annular channel (8.10) surrounding a bearing pin (14a) of the rotary ball valve (3) with at least one first axial cooling channel (8.1) leading to the cavity (8) in the bearing pin (14a) through a radial slot (102) is connected, and of which the other cooling duct section by means of a second annular duct (8.11) surrounding the bearing journal (14a) with a second axial cooling duct emanating from the cavity (8) in the bearing journal (14a) and offset in the circumferential direction from the first cooling duct (8.1) (8.2) is connected by a radial slot (103) and opens at the surface of the cylinder head cover (2), the ring channels (8.10, 8.11) and the radial slots (102, 103) being axially offset (v) to each other arranged et are. 44. Internal combustion engine according to claim 43, characterized in that the axial cooling channels (8.10, 8.11) or the axial cooling channels (8.1, 8.2) are assigned to or arranged in or in the exhaust gas channel (17) bearing journals (14a) . 45. Internal combustion engine according to claim 43 or 44, characterized in that a radial space forming an annular space is provided between the journal wall (14c) and the gas channel wall (17a) and the axial cooling channels (8.1, 8.2) are separated from one another by longitudinal webs (98) which preferably extend radially in one piece from the gas channel wall (17a) and / or the journal wall (14c), and the cooling channels (8.1, 8.2) are delimited at their outer ends by a radial web wall (17b). 46. Device according to one or more of claims 43 to 45, characterized in that axial cooling channels (8.1, 8.2), preferably in the number of an even number, in particular four, are arranged diametrically or star-shaped opposite one another, with more than two cooling channels (8.1, 8.2) having the same flow direction diametrically opposite one another or are adjacent in the circumferential direction. 47. Device according to one or more of claims 42 to 46, characterized in that in the region of the partition (99) between the annular channels (8.10, 8.11) the cylinder head housing is divided radially and the partition (99) part of one, preferably axially outer housing part (100). 48. Internal combustion engine, in particular according to one of claims 1 to 47, wherein a plurality of cylinders are arranged in a row and each cylinder is associated with a rotary valve extending transversely to the row, characterized in that the spherical control bodies (415) opposite adjacent rotary valve (403) the row (ZR) are axially offset in opposite directions. 49. Internal combustion engine according to claim 48, characterized in that the injection device or pump (26, 326) is in each case arranged on the side of the spherical control body (415) in which the direction of displacement points or preferably faces away from the direction of displacement. 50. Internal combustion engine according to claim 48 or 49, characterized in that the input and output control channels (16, 17) are arranged alternately on one and the other side of the cylinder block (404) or preferably in each case on the same side of the cylinder block (404) . 51. Internal combustion engine according to one or more of the claims 48 to 50, characterized in that the injection devices or pumps (26, 326) are located on one and the same side of the internal combustion engine and in particular on the outlet side or preferably on the inlet side of the rotary ball valve (403) or control body (415) are arranged. 52. Internal combustion engine according to one or more of claims 48 to 51, characterized in that the passage channel in the lower lid part (402.2) is inclined or curved to the side to which the associated control body (415) is offset. 53. Internal combustion engine according to one or more of claims 48 to 52, characterized in that the passage channels (424) in the lower lid part (402.2) have an elongated cross section directed along the row (ZR).

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