EP0369461A1 - Brennkraftmaschine mit mindestens einem rotierenden Steuerelement je Zylinder - Google Patents

Brennkraftmaschine mit mindestens einem rotierenden Steuerelement je Zylinder Download PDF

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Publication number
EP0369461A1
EP0369461A1 EP89121302A EP89121302A EP0369461A1 EP 0369461 A1 EP0369461 A1 EP 0369461A1 EP 89121302 A EP89121302 A EP 89121302A EP 89121302 A EP89121302 A EP 89121302A EP 0369461 A1 EP0369461 A1 EP 0369461A1
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EP
European Patent Office
Prior art keywords
combustion engine
internal combustion
engine according
injection
ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP89121302A
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German (de)
English (en)
French (fr)
Inventor
Franz Sinseder
Reinhold Ficht
Manfred Schindler
Andreas Baumüller
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Ficht GmbH
Original Assignee
Ficht GmbH
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Filing date
Publication date
Application filed by Ficht GmbH filed Critical Ficht GmbH
Publication of EP0369461A1 publication Critical patent/EP0369461A1/de
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/10—Rotary or oscillatory slide valve-gear or valve arrangements with valves of other specific shape, e.g. spherical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/18—Component parts, details, or accessories not provided for in preceding subgroups of this group
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/04—Fuel-injectors combined or associated with other devices the devices being combustion-air intake or exhaust valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump

Definitions

  • 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.
  • 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.
  • the injection pump is mounted in the spherical control body or is integrated therein.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • the compression spring 77 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the bearing journal 14a is specially designed.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • two spaced-apart sealing lips 109 see enlarged and perspective detail in FIG.
  • 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.
  • 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.
  • 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.
  • the cylinder surface 37 must have a correspondingly wide dimension.
  • 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.
  • 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.
  • 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.
  • the nozzle needle 76 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.
  • 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.
  • leaks between the piston 31 and the pump sleeve 47 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.
  • 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.
  • 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.
  • 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.
  • LP fuel pump low-pressure fuel system
  • HP injection pump 26 high-pressure fuel system
  • 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.
  • the injection pump 27 and the injection nozzle 29 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.
  • 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.
  • a central pin 283 preferably with a round cross section.
  • a disk 284 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.
  • the disc 284 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the rotary slide valve 403 shown in FIG.
  • the 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.
  • 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.
  • the respective adjacent rotary valve 403 is axially offset to the other side.
  • 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.
  • 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.
  • a combustion chamber recess 426 is embedded in the top of the piston 406, which is also offset in the opposite direction of displacement.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
EP89121302A 1988-11-17 1989-11-17 Brennkraftmaschine mit mindestens einem rotierenden Steuerelement je Zylinder Ceased EP0369461A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3838944 1988-11-17
DE19883838944 DE3838944A1 (de) 1988-11-17 1988-11-17 Brennkraftmaschine mit mindestens einem rotierenden steuerelement je zylinder

Publications (1)

Publication Number Publication Date
EP0369461A1 true EP0369461A1 (de) 1990-05-23

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EP89121302A Ceased EP0369461A1 (de) 1988-11-17 1989-11-17 Brennkraftmaschine mit mindestens einem rotierenden Steuerelement je Zylinder

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EP (1) EP0369461A1 (enrdf_load_stackoverflow)
DE (1) DE3838944A1 (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2205278C1 (ru) * 2001-10-17 2003-05-27 Голубков Евгений Петрович Бесшатунный поршневой двигатель внутреннего сгорания
WO2004011779A1 (en) * 2002-07-25 2004-02-05 Jung Wook Lee Spherical rotary engine valve assembly
WO2004067919A3 (en) * 2002-08-01 2004-11-04 Gheorghe Bordeianu Cylinder head for internal combustion engines
RU2286467C2 (ru) * 2005-01-11 2006-10-27 Виталий Дмитриевич Корнилов Шаровой механизм газораспределения двигателя

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4430351C2 (de) * 1994-08-26 1997-07-17 Johann Morath Fa Verbrennungsmotor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0222260A2 (de) * 1985-11-14 1987-05-20 Ficht GmbH Brennkraftmaschine
DE8706821U1 (de) * 1987-05-12 1988-09-15 Ficht GmbH, 8011 Kirchseeon Brennkraftmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3715847A1 (de) * 1987-05-12 1988-12-08 Ficht Gmbh Brennkraftmaschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0222260A2 (de) * 1985-11-14 1987-05-20 Ficht GmbH Brennkraftmaschine
DE8706821U1 (de) * 1987-05-12 1988-09-15 Ficht GmbH, 8011 Kirchseeon Brennkraftmaschine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2205278C1 (ru) * 2001-10-17 2003-05-27 Голубков Евгений Петрович Бесшатунный поршневой двигатель внутреннего сгорания
WO2004011779A1 (en) * 2002-07-25 2004-02-05 Jung Wook Lee Spherical rotary engine valve assembly
US7121247B2 (en) 2002-07-25 2006-10-17 Lee Jung W Spherical rotary engine valve assembly
WO2004067919A3 (en) * 2002-08-01 2004-11-04 Gheorghe Bordeianu Cylinder head for internal combustion engines
RU2286467C2 (ru) * 2005-01-11 2006-10-27 Виталий Дмитриевич Корнилов Шаровой механизм газораспределения двигателя

Also Published As

Publication number Publication date
DE3838944A1 (de) 1990-05-23
DE3838944C2 (enrdf_load_stackoverflow) 1992-08-20

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