WO1988008920A1

WO1988008920A1 - Internal combustion engine

Info

Publication number: WO1988008920A1
Application number: PCT/EP1988/000411
Authority: WO
Inventors: Reinhold Ficht; Franz Sinseder
Original assignee: Ficht Gmbh
Priority date: 1987-05-12
Filing date: 1988-05-11
Publication date: 1988-11-17
Also published as: DE3715847A1

Abstract

An internal combustion engine comprises cylinders, either separate or arranged in rows, for each cylinder a rotary control element for controlling the interchange of gases arranged between the cylinder block (64) and the cylinder cover (53) and having an axis of rotation perpendicular the axes of the cylinders, and a control device (11) arranged between two trunnions (11a, 11b) extending in the direction of the axis of rotation, the said control device (11) being secured to one of the trunnions. Counter surfaces of the cylinder head having the same configuration as the control device and the trunnions surround the control device and the trunnion. Through each trunnion passes an axial gas channel (12, 13) arranged in the control device and opening on to the surface of a curved gas channel. Means are provided for transmitting the rotary movement of the crankshaft to the control device, which has a spherical shape. This internal combustion engine is a diesel engine having a fuel injection device the nozzle holder (6) of which is mounted in the ball of the rotary distributor (11).

Description

Internal combustion engine

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

Such an internal combustion engine is described in European patent application 86115033.2. It is an internal combustion engine with a rotary valve as a control body.

The object of the invention is to provide an arrangement for a fuel injection device for a diesel internal combustion engine.

This object is achieved by the features of the characterizing part of claim 1. Advantageous further developments of the invention are characterized in the subclaims. ^J

Based on the example shown in the drawing, the invention is explained in more detail below. Show it:

Fig. 1 in perspective a longitudinal section through a

Part of the cylinder head of the internal combustion engine,

2 shows a cross section along the line II-II in FIG. 1. An internal combustion engine shown only partially in FIG. 1 has a cylinder head housing cover 53 and a cylinder head housing lower part 54. Between the cover 53 and ^"the lower part 54 a ball rotary vane rotatably supports 11 and below the lower part 54 cylinder block 64 in the bush 56 is a piston 57. The lid 53 is connected to the lower part 54 to the underlying cylinder block and 64 releasably connected via clamping screws The cover 53 has a dome-shaped counter surface on the inside and a spherical-arch-shaped counter surface is arranged in the lower part 54 in the region of the upper end of the cylinder liner 56. Cooling channels 55 are provided in the lower part 54. The piston 57 has a front surface 58 which is preferably rotationally symmetrical An annular sealing strip 63 is introduced into a groove in the counter surface of the lower part 54, which is supported against the bottom of the groove and against the ball surface.

The rotary ball valve 11 consists of two spherical shell-shaped parts welded to one another in a gastight manner, to each of which a tubular bearing journal 11a and 11b is welded centrally on opposite sides, or can be connected in some other way to the spherical shell-shaped parts. The parts which complement a hollow ball in the equatorially arranged dividing seam are penetrated by two elbow-shaped control channels 12 and 13, the ends of which open in a form-fitting manner in control openings in the spherical body, while the other ends coaxially penetrate the tubular bearing journals 11a and 11b in such a way that that limited cooling channels arise from the outer surface of the control channel and the inner surface of the journal.

The bearing journal 11b furthermore has a flange ring-like on its outer surface, which extends radially outward extending ring-shaped projection with a gear rim fastened thereon with radially extending teeth, which is arranged outside the bearing opening and via which the rotary ball slide valve 11 is driven in a uniform manner by the drive shaft, which is also not shown, by way of which it is not shown. The outer circumferential surface of the other bearing pin 11a likewise has a flange-ring-like, radially extending, annular projection. The projection is arranged outside the bearing opening and lies with a slide ring or the like. on the end face of the Zylin¬ dergehäuses, whereby the rotary valve is axially fixed because the drive is designed so that it pulls the flange against the end face. Both bores are radially penetrated by a plurality of bores, so that the cooling channels communicate via these bores with a channel carrying coolant and a channel discharging coolant.

The rotary ball valve 11 is supported by means of its journals 11a and 11b in cylindrical bearing openings, each of which is located half in the cylinder head housing cover 53 and half in the lower cylinder head housing part 54, in order to enable the mounting of the rotary ball valve.

The rotary ball valve 11 is rotatably supported in the bearing openings with the interposition of rotary bearings 16. The elbow seals 17 ensure a secure seal between the gas, coolant and lubricant channels. In operation, the rotary ball valve 11 is driven uniformly in the direction of arrow 60 by the drive shaft, not shown, via transmission elements, also not shown, which are in engagement with the toothed ring, in such a way that only the gas inlet and after via the control channels 12 and 13 Compression and ignition of the flushed-in mixture, the gas outlet communicates with the combustion chamber, that is to say with the cylinder 56.

The rotary valve 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 can be formed 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 valve 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 configurations of the piston and the cylinder cover 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 the cylinder block and crank mechanism. It is provided that a rotary ball valve is arranged above each cylinder, the axis of rotation of which extends transversely to the direction in which the cylinders are lined up. it is to achieve an overall height that is lower ^'than for poppet valves. in addition, three-dimensional shapes of the combustion chamber formable which, viewed from a technical point of combustion, approach the optimum. No complicated sealing ring shapes or sealing sleeves are required. The bearing of the spherical body is laid on the bearing journal and not on the spherical surface, as was the case, for example, in the known roller slides with the roller surface. There may even be a gap between the spherical surface and the spherical surface, which does not have to be filled with an oil film.

Using a ball as a control body brings unexpected benefits. Simple components can be used, so that production is inexpensive. The rotationally symmetrical components of the rotary ball valve have no local material accumulations, 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 ball valve remains uniform. The sealing ring pressing against the spherical surface can be made of different materials e.g. ceramics also exist because the control body does not experience any dimensional changes. By means of a slightly inclined mounting, it can rotate about its center point and thereby ensure the sealing effect over a long period of time.

Additional lubrication can be dispensed with in the case of the rotary rotary valve, since the surface of the ball only rests on the sealing edge of the sealing ring. There is even a gap between the spherical surface and counter surfaces in the cylinder head, which can be approximately 0.08 to 0.2 mm. The control body and the sealing ring can consist, for example, of ceramic materials. A ball made of metal can also be used with ceramic Materials can be coated by, for example, plasma spraying. These embodiments are possible because lubrication in the conventional manner and scope is not required.

The rotary ball 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 parts from ceramic materials. The introduction of compressive force during the compression process is extremely favorable for the ball due to the shape of the arch. The production of the spherical shape is particularly simple and problem-free compared to a cylindrical shape.

The mounting of the rotary ball valve on the bearing journal is possible because the bearing journals are not exposed to considerable temperature changes and consequently do not experience any change in shape due to the action of heat. The ^'bearing lubrication is wrong for this reason also without problems.

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

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 addition, unlike the valve engine, the hot exhaust valves are missing. Due to the lack of hot spots in the combustion chamber, a much higher compression ratio and thus higher engine output can be achieved. The sealing ring can be tilted out of the plane parallel to the rotary slide rotation axis and can generate relative speed differences at the sealing edge of the rotary slide ball sealing ring due to different spherical section circumferences and thus allow the seal to rotate about its axis of rotation, which results in an increased service life and sealing ability Seal leads.

The sealing ring can also to de ^'of Drehschieberkugel- n deposits next fields with different Fe¬ derkräften act on the rotary valve ball comprising a Reibkraftdifferenz at the sealing edge rotary valve ball - the sealing ring and thus a rotation of the sealing effect due to the torque about its axis of rotation, which also results in leads to an increased service life and sealing ability of the seal.

The arrangement of the fuel injection device described below has been created for the internal combustion engine designed as a diesel engine.

An approximately cylindrical bearing housing 53a is arranged on the housing cover part 53 above the ball slide valve 11, which can be connected in one piece to the cylinder head cover 53 and has a cylindrical bottom 53b and 53c on both sides as a finish, with centrally projecting outward protrusions Bearing caps 53d and 53e are attached. The bottom 53c is detachably attached to the bearing housing 53a. The bearing housing 3a preferably extends axially parallel to the axis of rotation of the rotary ball valve 11, specifically the bottom 53b is located approximately in the region of the equator of the ball of the rotary ball valve 11 and the bottom 53c approximately at the end of the journal 11b. A pump housing 45 is rotatably inserted in the bearing housing, composed of the cylindrical parts 45a and 45b, each of which has a bearing pin 45c and 45d projecting outwards centrally from the front. The bearing journals 45c, 45d are supported by ball bearings 38 in the bearing caps 53d, 53e.

At the end of the cylinder 45b of the pump housing 45, which is adjacent to the bearing pin 45d, a toothed ring 47 is firmly seated on the cylinder. In the plane of this toothed ring, a drive gearwheel 18 is fixedly arranged on the bearing pin 11b of the rotary ball valve 11, which leads into the interior of the bearing housing 53a projects and meshes the ring gear 47 so that the rotation of the rotary ball valve 11 is transmitted to the entire pump housing 45.

In the inner space 48 of the pump housing 45, eccentrically, extending parallel to the axis of rotation in the area between the bearing journals 45c, 45d, in two bearing blocks 45e and 45f arranged at a central distance with a gap 45a, there is a fuel injection pump of known type with a Piston 28. A bushing 40 is inserted into the bearing block 45d, into which the piston front part 28a of the piston 28 is immersed. The rear end of the piston 28 is in a spring plate 30, which is seated frontally on a tappet head 31a, which is slidable back and forth in the bearing block 45 f. A pump flange 42 is placed against the bushing 40 so that a piston spring 29 can be supported against the flange 42 and the plate 30. In the area between the flange 42 and the plate 30, a radially extending piston lug 27 is arranged on the piston 28 and fits into a longitudinal slot of a piston lobe 27 seated on the piston 28

Control bush 26 engages positively. In the plunger head 31a rotatably supports a roller tappet 31 with shaft ends 31b, which extend perpendicular to the longitudinal axis of the piston 28, which rolls on a cam track 52 arranged on the inner wall of the bottom 53c when the pump housing 45 rotates, as a result of which the pump piston 28 is operated.

In the bearing cap 53d there is a rotary union 43, known per se, with a fuel feed line 59, which opens into a fuel supply bore 41, which is introduced into the bearing journal 45c and merges into bores 41b in the bearing block 4e, which bores into the cylinder space 28b the pump.

A central hole 50 in the bearing cap 53e and a corresponding bore or bushing 44 in the bearing journal 45d are penetrated by an axially extending regulator rod 20 which projects into the interior 48 of the pump housing 45 and is connected to an articulated rod 23 via a ball head 22 stands, which sits with a knee lever joint 24a on an arm of a knee lever 24, the knee 21 of which is rotatably mounted on the cylinder jacket 45b. The other arm of the toggle lever 24 is connected via a joint 24b to one end of a pull rod 25, the other end of which is connected to the control bushing 26, in such a way that the control bushing 26 and thus the piston 28 can be rotated about its longitudinal axis if the regulator rod 20 is pulled forwards or backwards.

The cylinder space 28b opens into the cylindrical interior of a bore 37a via at least one bore 28c, approximately in the region of its longitudinal center, the bore 37a perpendicular to the longitudinal extension of the piston 28 is introduced into the bearing socket 45c and into a contact socket 45h of the pump housing 45 which extends at right angles to the bearing socket 45c. The bore 37a is closed in its extension in the bore 37b with a lock nut 37. Under the locking nut 37 there is a compression spring 33 which is supported against the nut 37 and against a lifting plunger 32 which is slidably seated in the bores 37a and 37b against the spring pressure and otherwise protrudes a bit from the bore. An annular edge 32a of the lifting plunger 32 interacts with a mating ring edge 45i of the contact piece 45g in such a way that the plunger travel is limited.

In the lifting plunger 32, a lifting needle valve of known type is seated in a longitudinal bore 32b with a lifting needle 34 acting against a spring 34a, the tip of which closes a small bore 32c in the bottom of the bore 32b. The spring 34a is supported against a threaded pin 32d, which is supported in the plunger 32. The spring force of the spring 34a can be adjusted by inserting adjusting washers 32f with different washer thicknesses between the threaded pin 32d and the spring 34a. The bore 28c continues in a bore 32e so that the cylinder space 28b communicates with the valve space 32b. Fuel delivered by the pump piston 28 is thus conveyed at high pressure into the valve chamber 32b and, when a certain pressure is reached, is pressed out of the valve chamber 32b via the bore 32c.

In addition to the valve bore 32b, a leakage oil line 36 is arranged in the lifting plunger 32, which merges into a check valve arrangement 35 in the region of the tip of the lifting needle 34. To deliver the fuel from the pump housing 45 into the combustion chamber 58, the invention provides that the nozzle holder body 6 of the fuel injection device is mounted in the rotary slide ball 11. The nozzle holding body 6 passes through a ball, preferably diametrically, and sits in a form-fitting manner in a cylindrical bearing housing 15 which penetrates the ball accordingly.

The nozzle holding body 6 has a construction known per se with a valve body 6a, in which a nozzle needle 1, a compression spring 3, a pressure line 4 and a leakage oil line 5 are introduced.

The nozzle tip 9 passes through an opening 2 of the bearing housing 15 and opens into the combustion chamber 58. At the other end of the nozzle holding body 6, the pressure line 4 opens into a check valve 8 which closes a bore 6b against spring pressure, which lies opposite the bore 32c in the position of the pump housing 45 shown in the drawing.

The leakage oil line 5 opens next to the check valve 8 in a check valve 7, which is opposite the check valve 35.

2 shows the position in which the fuel jet 62 is injected into the combustion chamber 58. The direction of rotation of the pump housing 45 is indicated by arrow 61 and that of the rotary valve 11 by arrow 60. The lifting plunger 32 projects so far radially that it is already shortly before that shown in FIG. 2 Position comes into contact with the nozzle holder body 6. The lifting plunger 32 is then pushed back against the pressure of the spring 33 when turning further, but this ensures that a coupling under pressure between the nozzle holding body 6 and the lifting plunger 32 is maintained in the fuel transfer position (FIG. 2), the valves being opened are. Only after the coupling position shown in FIG. 2 has been exceeded is the contacting removed and the valves closed.

By laying the nozzle holder body 6 in the spherical body of the rotary valve 11 and contacting the rotary valve with a rotating pump housing 45 which supports the high pressure pump and has a contacting tappet 32, it is possible to request the fuel at low pressure and despite the to convey the rotating rotary valve with high pressure centrally into the combustion chamber 58.

Claims

1. Internal combustion engine, in particular reciprocating piston engine with internal combustion and with cylinders arranged individually or in series and with at least one rotating control element per cylinder for the gas charge change processes, which is arranged between the cylinder block and cylinder cover with a rotation axis preferably perpendicular to the cylinder axis and has a control body which is firmly connected to the pegs between two axially extending pegs, the control body and the pegs being provided in the cylinder head in a uniform surrounding area and each peg being penetrated by an axially extending gas channel, each in one elbow-shaped gas channel arranged in the control body merges, which emerges at the surface of the control body with an opening, and means are provided for transmitting a rotational movement from the crankshaft to the control element and the control body rper is designed as a ball, in particular as a hollow ball body, characterized in that the internal combustion engine is designed as a diesel internal combustion engine and has a fuel injection device, the nozzle holding body (6) of the fuel injection device in the ball of the rotary valve (11 ) is stored.

2. Brenπkraftmaschine according to claim 1, characterized ge ¬ indicates that the nozzle holder body (6) of the fuel injection device the ball of the rotary valve (11) is preferably penetrated diametrically, so that the fuel injection nozzle (1) of the nozzle holder body (6) is arranged on the surface of the ball and that at the other end of the nozzle holder body (6) there is a check valve (8) in the region of the ball Surface sits, and that the other parts of the fuel injection device are arranged outside the Kugel¬ rotary valve (11).

3. Internal combustion engine according to claim 1 and / or 2, characterized in that the high-pressure fuel pump device is rotatably mounted about an axis of rotation arranged preferably parallel to the axis of rotation of the rotary ball valve (11).

4. Breπnkraf machine according to claim 3, characterized g e k e n n z e i c h n e t that coupling elements for transmitting the rotational movement of the ball valve (11) to the high pressure fuel pump device are arranged between the rotary ball valve (11) and the high pressure fuel pump device.

5. Internal combustion engine according to one or more of claims 1 to 4, characterized in that between the high-pressure fuel pump and the nozzle holding body (6) a lifting tappet device (32) with a check valve (34) is arranged such that they take over the fuel from the fuel pump and can transfer it via the check valve (34) to the check valve (8) of the nozzle holder body (6) during the rotation of the high-pressure fuel pump device and of the rotary ball valve (11), the lifting plunger being the Lifting plunger device (32) performs a lifting movement, preferably perpendicular to the axis of rotation of the rotary slide valve.

6. Internal combustion engine according to one or more of claims 1 to 5, characterized in that the nozzle holding body (6) has a known construction with a valve body (6a) in which the nozzle needle (1) has a compression spring ( 3), a pressure line (4) and a leakage oil line (5) are introduced, the nozzle holding body (6) being stuck in a bearing housing (15) provided in the ball of the rotary ball valve (11) and the nozzle tip (9) of the nozzle needle (1) an opening (2) of the bearing housing (15) passes through and opens into the ßrenn- space (58) and the pressure line at the other end

(4) ends with the check valve (8), which closes a bore (6b) in the nozzle holding body (6) against spring pressure, which lies opposite a bore (32c) of the lifting tappet device (32) during the coupling phase.

7. Internal combustion engine according to claim 7, characterized ge ¬ indicates that the leak oil line (5) next to the check valve (8) opens into a Rückschlag¬ valve (7) which a check valve (35) _, in the lifter device (32) during the coupling phase is arranged opposite.

8. Internal combustion engine according to one or more of claims 1 to 7, characterized in that an approximately cylindrical bearing housing (53 a) is arranged on a housing cover part (53), preferably above the ball slide valve (11), which with the cylinder head cover (53 ) is connected and on both sides at the end has a cylindrical bottom (53b and 53c), on which bearing caps (53d and 53e) projecting outwards are attached, the bearing housing (53a) preferably extending axially parallel to the axis of rotation of the rotary ball valve (11) .

9. Internal combustion engine according to claim 8, characterized in that the base (53b) is preferably located approximately in the region of the equator of the ball of the rotary valve (11) and the base (53c) is approximately at the end of the bearing journal (11b).

10. Internal combustion engine according to claim 8 and / or 9, characterized in that in the bearing housing (53a) is rotatably inserted a pump housing (45), the cylin¬ drical parts (45a and 45b) and frontally centrally an outwardly projecting bearing pin (45c and 45d), the bearing pins being rotatably mounted in the bearing caps (53d, 53e).

11. Internal combustion engine according to claim 10, characterized ge ¬ indicates that preferably at the end of the cylinder (45b) of the pump housing (45), which is adjacent to the bearing journal (45d), a toothed ring (47) sits in On the plane or at an angle to this plane of this ring gear on the journal (11b) of the rotary slide valve (11) a drive gear (18) is fixedly arranged, which projects into the interior of the bearing housing (53a) and meshes the ring gear (47).

12. Internal combustion engine according to one or more of claims 8 to 11, characterized in that in the interior space (48) of the pump housing - (45) eccentrically, ie next to the axis of rotation itself Extending parallel to the axis of rotation in the area between the bearing journals (45c and 45d), in two bearing blocks (45e and 45f) arranged at a central distance with a gap (45g), the fuel injection pump with a piston (28 ) plugged.

13. Internal combustion engine according to claim 12, characterized in that in the bearing block (45e) a bushing (40) is introduced into which the piston front part (28a) of the piston (28) dips and that the rear end of the piston (28) is located in a spring plate (30), which sits frontally on a tappet head (31), which is slidable back and forth in the bearing block (45f).

14. Breπnkraftmaschine according to claim 13, characterized in that a pump flange (42) is placed against the bushing (40) so that a piston spring (29) can be supported against the flange (42) and the plate (30).

15. Internal combustion engine according to one or more of claims 12 to 14, characterized g e k e n n - z e i c h n e t that in the area between the

Flange (42) and the plate (30) on the piston (28) a radially extending piston lug (27) is arranged, which engages in a longitudinal slot of a control bushing (26) seated on the piston (28) with a positive fit.

16. Internal combustion engine according to one or more of claims 12 to 15, characterized - shows that in the plunger head (31a) with shaft stumps (31b) which extend perpendicular to the longitudinal axis of the piston (28), a roller plunger (31) rotates, which is arranged on one of the inner walls of the bottom (53c) Can roll cam track (52) when the pump housing (45) rotates, whereby the pump piston (28) is operated.

17. Internal combustion engine according to one or more of claims 8 to 16, characterized in that in the bearing cap (53d) centrally a known rotary union (43) with a fuel feed line (59) which opens into a fuel supply bore (41) that in the

Bearing pin (45c) is introduced and in the bearing block (45e) passes into bores (41b) which open into the cylinder space (28b) of the pump.

18. Breπnkraftmaschine according to one or more of claims 8 to 17, characterized in that a central hole in the bearing cap (53e) and a corresponding bore in the bushing (44) in the journal (45d) of an axially extending control rod ( 20) are gripped which protrudes into the interior (48) of the pump housing (45) and is connected to the control bushing (26) in such a way that the control bushing (26) and thus the piston (28) about its longitudinal axis can be turned when the control rod (20) is pulled forwards or backwards.

19. Internal combustion engine according to claim 18, ^* characterized in that the control rod (20) is connected via a ball head (22) to a joint rod (23) which is connected to a knee lever joint (24a) on an arm of a knee lever ( 24), whose knee (21) is rotatably mounted on the cylinder jacket (45b), the other arm of the knee lever (24) is connected via a joint (24b) to one end of a pull rod (25), the other end of which is connected to the control bushing (26) communicates.

20. Breπnkraftmaschine according to one or more of claims 8 to 19, characterized in that the cylinder chamber (28b) of the high-pressure fuel pump opens via a slot or a bore (28c) into the lifting tappet device (32).

21. Internal combustion engine according to claim 20, characterized in that the slot or bore (28c) opens into the cylindrical interior of a bore (37a), approximately in the region of its longitudinal center, the bore (37a) perpendicular to the longitudinal extension of the piston ( 28) is introduced into the bearing socket (45c) and into a contact socket (45h) of the pump housing (45) which extends at right angles to the bearing socket (45c), the bore (37b) also being in the extension of the hole (37a) on the bearing socket side a ^' locking nut (37) is closed, under which a compression spring (33) is seated, which is supported against the nut (37) and against the lifting plunger (32) of the lifting plunger device, which can slide against the spring pressure in a form-fitting manner in the bores (37a and 37b) is seated and at the other end protrudes a bit from the bore, wherein an annular edge (32a) of the lifting plunger (32) interacts with a mating ring edge (45i) of the contact piece (45g) in such a way that the plunger travel is limited.

22. Internal combustion engine according to claim 20 and / or 21, characterized in that in the stroke tappet (32) in a longitudinal bore (32b) which is connected to the bore (37a) via a hole or a slot in connection, a lifting needle valve Known type with a lifting needle (34) acting against a spring (34a), the tip of which closes a small hole (32c) in the bottom of the hole (32b), the spring (34a) ab¬ against a threaded pin (32d) supports, which rests in the plunger (32) and an adjustment of the spring (34a) is possible by inserting shims (32f) with different disc thicknesses between threaded pin (32d) and the spring (34a).

23. Internal combustion engine according to one or more of claims 20 to 22, characterized in that the bore (28c) continues in a bore (32e) so that the cylinder space (28b) communicates with the valve space (32b).

24. Internal combustion engine according to one or more of the

Claims 20 to 23, characterized in that in addition to the valve bore (32b) a leakage oil line (36) is arranged in the lifting plunger (32), which merges into a non-return valve (35) in the region of the tip of the lifting needle (34) and Has connecting channels to the fuel channels (41).