EP3362645B1 - Internal combustion engine with double crank drive and variable compression ratio - Google Patents

Internal combustion engine with double crank drive and variable compression ratio Download PDF

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Publication number
EP3362645B1
EP3362645B1 EP16784788.8A EP16784788A EP3362645B1 EP 3362645 B1 EP3362645 B1 EP 3362645B1 EP 16784788 A EP16784788 A EP 16784788A EP 3362645 B1 EP3362645 B1 EP 3362645B1
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EP
European Patent Office
Prior art keywords
rod
piston
piston rod
internal combustion
combustion engine
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EP16784788.8A
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German (de)
French (fr)
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EP3362645A1 (en
Inventor
Peter Pelz
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/10—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with more than one main shaft, e.g. coupled to common output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/06—Engines with means for equalising torque
    • F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • the invention relates to an internal combustion engine, in particular reciprocating internal combustion engine, with double crank drive and variable compression.
  • a reciprocating internal combustion engine with double crank drive is for example from the DE 102 47 106 B4 known.
  • reciprocating internal combustion engines with double crank drive have numerous advantages. From Doppelkurbeltrieb forth no lateral forces are exerted on the piston, whereby the friction is reduced, the vibration excitation is lower and the piston can be made flat and shirtless, which is advantageous for the, if necessary, lubrication of the sliding piston ring / cylinder wall or a Can make piston lubrication redundant.
  • the angle of rotation of the crank disks is different from the rotational angle in the subsequent movement of the piston from BDC to TDC when the piston moves from TDC to TDC. This can be used advantageously in the combustion.
  • the torque output is made uniform, which is further supported by the fact that compared to conventional engines with the same piston stroke smaller crank radii of double cranks are required.
  • the compression of a reciprocating internal combustion engine that is, the ratio between the volume of a working chamber formed in the cylinder above the piston at bottom dead center (UT) piston to at top dead center (TDC) piston has, among other things, strong influence on consumption. For example, a higher compression is desired in the partial load range.
  • the compression ratio is typically limited by the tendency to knock, and it may be greater in naturally aspirated engines than in turbocharged engines.
  • diesel engine especially for a safe start a high compression ratio is required. During operation of the diesel engine lowering of the compression ratio is advantageous for low pollutant content in the exhaust gas and friction reasons.
  • variable compression is created only with great effort.
  • the adjustment takes place in known engines only in a very small area.
  • variable compression internal combustion engine which has an eccentric crankshaft bearing, wherein a torsionally rigid connection is arranged between the crankshaft bearing and a gear comprising at least one gear segment and a gearwheel.
  • the gear segment is fixed to an axially outer crankshaft bearing and by means of the gear is for adjusting the eccentric crankshaft bearing torque on the gear segment can be introduced.
  • the previously known internal combustion engine could not prevail.
  • the DE 195 06 963 A1 discloses a changeover motor in which the degree of expansion is greater than the degree of compression.
  • Other relevant to the prior art documents are the CN 203 939 575 U , the US 2,229,778 , the EP 1 710 394 A1 , the GB 441,666 , the EP 2 792 846 A1 and the DE 100 19 959 A1 ,
  • the invention has for its object to provide a reciprocating internal combustion engine with variable compression.
  • the invention can be used for substantially all types of reciprocating internal combustion engines, such as single and multi-cylinder engines, gasoline, diesel, and gas engines, two-stroke and four-stroke engines.
  • the invention reduces the risk of damage to the entire engine and the load on its parts.
  • the entire engine design is easier and less risky. There are advantages in terms of size and weight, friction, design effort and cost of manufacture, service cost, tolerances and fits, and motor life extension. The crime and the emissions are reduced.
  • a reciprocating internal combustion engine includes a cylinder 10 in which a piston 12 is movable along the axis of the cylinder.
  • the piston 12 formed, for example, shirtless is preferably rigidly connected to a piston rod 14 which is guided under sealing linearly movable through a passage 16 which is formed in a partition wall 18, the interior of the cylinder 10 according to Fig. 1 closes down.
  • a working chamber 20 is formed above the piston 12 between the piston 12 and the cylinder head 22 and an upper wall of the cylinder and below the piston 12 between the piston 12 and the partition wall 18, a fresh air chamber 24 is formed.
  • An inlet opening formed in the lower region of the fresh air chamber 24 is connected to an intake passage 26, which can be closed with an intake valve 28.
  • an outlet opening leads into a connecting channel 32, in which an intermediate valve 34 is arranged and which is connected to an inlet channel 36, which leads into the working chamber 20 of the internal combustion engine and can be closed by means of an inlet valve 38, for example designed as a poppet valve ,
  • an outlet channel 40 leads through an unillustrated exhaust system of the reciprocating internal combustion engine to the outside.
  • the outlet channel 40 can be closed by means of an outlet valve 42 designed, for example, as a poppet valve.
  • the piston rod 14 passes through the partition wall 18 into the interior of a double crank drive receiving crankcase 44, in which two crank disks 46 and 48 are rotatably mounted to housing fixed axes of rotation A and B.
  • the crank pulleys 46 and 48 have at circumferences formed with the same diameter circumferential teeth, which mesh with each other.
  • the axes of rotation A and B of the crank disks 46 and 48 extend in a direction perpendicular to the piston rod 14 level and are equidistant from the piston rod 14.
  • the piston rod 14 extends to below the plane in which the axes of rotation A and B lie, such that their lower end is also in the top dead center of the piston 12 below the axes of rotation A and B.
  • the lower end of the piston rod 14 is pivotally connected via connecting rods 50, 52 with connecting rods 54 and 56, respectively, which are arranged on the crank disks 46 and 48 radially within the peripheral teeth eccentric to the axes of rotation A and B of the crank disks 46 and 48.
  • piston 12 is shown in a position approximately between top dead center (TDC) and bottom dead center (TDC).
  • valves 34 and 38 When operating in the four-stroke process, the valves 34 and 38 are closed and the valves 28 and 42 open starting from located in the bottom dead center piston 12 at an exhaust or exhaust stroke.
  • the piston pushes burned charge out of the working chamber during the exhaust stroke and simultaneously draws in fresh air into the fresh air chamber 24.
  • the valves 28 and 42 are on and the valves 34 and 38 are on, so that in the connecting channel 32 and the fresh air chamber 24 fresh air is pushed through the open valves 34 and 38 into the working chamber 20.
  • only the intake valve 28 is open, so that fresh air is sucked into the fresh air chamber 24 during the compression of the charge located in the working chamber 20.
  • crank disks By means of the external toothings of the crank disks and corresponding grooves etc. in the crankcase, the crank disks can assume the function of liquid pumps for lubrication.
  • Fig. 1 forms a bulge 45 of the crankcase 44 (FIG. Fig. 1 ), whose minimum depth is determined by the position of the connecting rod 14 in the UT of the piston 12, a collecting container for a liquid sump 69.
  • a simple liquid pump designed only for pressureless delivery (not shown) sucks liquid from the liquid sump 70 and leads them Crankshafts 46, 48 for further promotion.
  • a fundamental advantage of a double-cranked internal combustion engine is that the crankcase is completely separated from the piston chamber.
  • the piston must not be lubricated because of its lateral force-free guidance with appropriate material pairing between the outside of the piston or one or more provided there piston rings and the inner wall of the cylinder, so that the lubricating oil is not exposed to aging due to the influence of combustion residues or high temperatures and can be present as a lifetime filling.
  • Next can also be dispensed with temporarily or completely on the piston rings and their number can be reduced.
  • Fig. 2 schematically shows an example of the connection of the piston rod 14 to the crank disks 46 and 48 (the in Fig. 2 shown rotational position is not necessarily to simplify the presentation with the in Fig. 1 shown).
  • the crank disks 46 and 48 have bearing pins 92 and 94, with which they are rotatably mounted on the crankcase.
  • the crank disks 46 and 48 on the side facing away from the bearing journal 92, 94 cylindrical projection portions 60, 62 on which connecting rods 54 and 56 are formed (in Fig. 2 shown only schematically).
  • At the connecting rod 54 and 56 first ends of the connecting rods 50 and 52 are mounted.
  • a connecting rod connecting member 64 having a central sleeve-shaped portion 65 and two protruding ears 66 and 68 extending on opposite sides of the central sleeve-shaped portion 65 away from the central one sleeve-shaped portion 65 extend.
  • Each of the lugs 66, 68 is connected via a connecting bolt 70, 72 with the other (in Fig. 1 lower end of the corresponding connecting rod 50, 52 coupled.
  • an external thread 74 is formed at the end of the piston rod 14 facing away from the piston 12.
  • the external thread 74 extends from the piston 12 facing away from the end of the piston rod 14 over a first length 11 in the longitudinal direction of the piston rod 14.
  • the piston rod 14 is additionally starting from the piston 12 remote from the end of the piston rod 14 via a second length 12 in the longitudinal direction the piston rod 14 is hollow.
  • the internal cross-sectional shape of the piston rod 14 is perpendicular to its longitudinal direction in the hollow piston rod portion 78 in the present embodiment square.
  • the connecting rod connection component 64 has an internal thread 76 formed in the central sleeve-shaped region 65, which can be screwed onto the external thread 74 of the piston rod 14.
  • the length of the internal thread 76 is preferably shorter than the length of the external thread 74, so that the connecting rod connecting member 64 with respect to the piston rod 14 between the fully screwed state and the maximum unscrewed state in which the threads still securely interlock by a predetermined third length 13 (FIG. Adjustment, Verstellin) in the longitudinal direction of the piston rod 14 are movable relative to each other.
  • Fig. 1 shows a maximum screwed-in position of the connecting rod connecting member 64 (minimum compression ratio position) in which the connecting rod connecting member is located as close as possible to the piston.
  • the length 13 is in Fig. 1 starting from the top Edge of the connecting rod connecting member 64 shown. In the maximum unscrewed position (position with the largest compression ratio), the threads are still securely engaged.
  • an adjusting rod 80 is provided, which is arranged coaxially with the piston rod 14.
  • the adjustment rod 80 has an engagement portion 82 extending from the end facing the piston 12 over at least a fourth length 14 (not shown) equal to or greater than the piston stroke.
  • the outer cross-sectional shape of the engaging portion 82 perpendicular to the longitudinal extent of the adjusting rod 80 is square in the present embodiment according to the inner cross-sectional shape of the hollow piston rod portion 78, so that the engaging portion 82 is slidably inserted in the hollow piston rod portion 78 in the longitudinal direction.
  • the engagement portion 82 and the hollow piston rod portion 78 are non-rotatably coupled to each other due to the complementary outer cross-sectional shape about the longitudinal axis.
  • the depth or length at which the adjusting rod 80 projects into the piston rod 14 depends on the instantaneous position of the piston.
  • the adjusting rod 80 has on the side facing away from the piston 12 of the engaging portion 82 further comprises a feedthrough region 83.
  • the feedthrough area 83 has a rotationally symmetrical (circular) outer cross-sectional shape in the present embodiment.
  • a gear 84 is mounted on the adjusting rod 80 at its end portion facing away from the piston 12 in a conventional manner.
  • the adjusting rod 80 extends in the assembled state of the engine from a lower, relative to the crankcase 44 fixed bearing 86 under seal (not shown) through the bulge 45 of the crankcase 44 into the hollow piston rod portion 78 of the piston rod 14 inside.
  • the total length of the adjusting rod 80 is preferably selected so that the adjusting rod 80 in the TDC of the piston 12 for an adjustment sufficiently with the hollow piston rod portion 78 is engaged or projects into this.
  • the adjusting rod 80 is axially fixed but rotatably mounted in the bearing 86.
  • the engagement portion 82 is arranged and formed such that the piston rod 14 is slidably engaged therewith between the TDC and TDC.
  • a motor (actuator) 88 is provided, which is arranged and formed via a gear 90 for driving the adjusting rod 80.
  • the compression of the reciprocating internal combustion engine can be variably set as follows:
  • the connecting rod connecting member 64 is via its internal thread 76 with the external thread 74 of the piston rod 14 in engagement.
  • a position of the connecting rod connecting member 64 on the piston rod 14 in the longitudinal direction of the piston rod 14 can be changed.
  • the ratio of the volume of the working chamber 20 in UT of the piston 12 to the volume of the working chamber 20 in the TDC of the piston 12 ie the ratio of the maximum volume to the minimum volume (compression ratio) is determined. By changing this position, therefore, the compression ratio can be changed.
  • the connecting rod connecting member 64 is in the present embodiment, due to the two-sided connection or articulation to the connecting rods 50 and 52 is not rotatable with respect to the stationary crankcase 44. An adjustment is therefore carried out by rotating the piston rod 14 by means of the rotationally fixed but axially displaceable in the piston rod 14 Adjustment rod 80.
  • the piston rod 14 can be freely rotated due to its rotationally symmetrical shape in the region of the passage 16 through the partition wall 18, without reducing the seal between the partition wall 18 and the piston rod 14.
  • the non-rotatably connected to the piston rod 14 in this embodiment the piston 12 can be rotated freely in the cylinder 10 due to its rotationally symmetrical shape.
  • the adjusting rod 80 is rotated by operating the electric motor 88 by means of the gears 90 and 84. Due to the sliding in the longitudinal direction of the adjusting rod 80 and the piston rod 14 mounting the adjusting rod 80 in the piston rod 14, the adjusting rod 80 does not prevent the upward and downward movement of the piston rod 14 during operation of the reciprocating internal combustion engine.
  • the compression or the degree of compression can thus be adjusted or adjusted in a simple manner during operation of the reciprocating internal combustion engine.
  • the thread pitch of réellegwindes 76 and the external thread 74 is selected so that self-locking prevails. This will allow that the adjusting rod 80 is guided without torque in the piston rod 14 after adjustment.
  • a second embodiment is shown in which in particular the connecting rod connecting member, the piston rod and the adjusting rod are formed differently from the first embodiment.
  • Fig. 4 shows the cross-sectional view AA Fig. 3 , Since the construction, structure and function of the other reciprocating internal combustion engine is unchanged from the first embodiment, the same is neither shown nor described. For components similar or equal to the first embodiment, the same reference numerals will be used and only the differences from the first embodiment will be described.
  • the piston rod 14 is formed according to the second embodiment, starting from the piston 12 remote from the end of the piston rod 14 via the second length 12 in the longitudinal direction of the piston rod 14 hollow. How out Fig. 3 and 4 can be seen, the piston rod 14 at its end facing away from the piston 12 has a tapered portion 106. In contrast to the first embodiment, the tapered portion has no external thread. The tapered portion 106 instead has a groove portion 108 which forms a circumferential groove in the piston rod 14.
  • a sleeve or cover member 110 is placed on the piston 12 facing away from the end of the piston rod 14 and the tapered portion 106.
  • the sleeve component 110 has a substantially pot-shaped design and has a radially inwardly projecting projection region 114 at its end opposite the bottom of the pot 112.
  • the sleeve member 110 has an inner circumference slightly larger than the outer circumference of the tapered portion 106 of the piston rod 14.
  • the protrusion portion 114 is formed so as to be slightly smaller in width and depth than the groove portion 108 of the piston rod 14.
  • the sleeve component 110 placed on the piston rod 14 is fastened to the piston rod 14 in the longitudinal direction of the piston rod 14 but is freely rotatable relative to the piston rod 14 about the longitudinal axis thereof.
  • the sleeve component 110 itself can for example consist of two halves.
  • the two halves are mounted on the piston rod 14 so that the projection portions 114 engage in the groove portion.
  • the connecting rod connecting member 64 is screwed from below (before the connecting rods are mounted thereto), whereby the two halves fixed to each other and are attached to the piston rod 14.
  • the connecting rod connecting member 54 may be formed of two halves bolted together.
  • an external thread 116 is formed on the (outer) outer side of the sleeve member 110 .
  • a through hole 118 is provided in the pot bottom of the sleeve member 110 .
  • the through-hole 118 preferably has a non-rotationally symmetrical (non-round) inner cross-sectional shape.
  • the structure of the connecting rod connecting member 64 substantially corresponds to that of the first embodiment. That is, as in the first embodiment, the connecting rod connecting member 64 has opposite bosses 66 and 68 for connection to the connecting rods 50 and 52 and a central sleeve-shaped portion 65 in whose inner circumference an internal thread 76 is formed. The internal thread 76 is designed to engage with the external thread 116 of the sleeve component 110.
  • an adjusting rod 80 is formed, which has a preferably circularly symmetrical in cross section (circular) lead-through area 83.
  • the adjusting rod 80 has a gear 84 and is axially fixed but rotatably mounted on a wall, not shown.
  • the engaging portion 82 of the adjusting rod 80 according to the second embodiment is formed similarly as in the first embodiment as a non-rotationally symmetrical (non-circular) outer cross-sectional shape portion so as to be slidably guided in the through hole 118 in the sleeve member 110 in the longitudinal direction of the adjusting rod 80 while being non-rotatable is connected to the sleeve member 110.
  • the position of the connecting rod connecting member 64 with respect to the piston rod 14 is changed by causing relative movement between the sleeve member 110 and the connecting rod connecting member 64 in the longitudinal direction due to rotation of the sleeve member 110 longitudinally engaged with the piston rod 14 the piston rod 14 takes place.
  • the rotation of the sleeve member 110 is achieved by the rotationally fixed engagement with the adjusting rod 80, which is driven by a motor / actuator, not shown.
  • the second embodiment there is no need for relative rotation between the piston rod 14 and the connecting rod connecting member 64 will take place.
  • the piston rod 14 and the piston 12 are therefore not rotated during the adjustment or can rotate independently of the connecting rod connecting member 64 and the adjusting rod 14.
  • the sleeve component 110 described above as being mounted can also be constructed in several parts (for example, from the bottom and a plurality of hollow cylinders which are screwed together) and can be rotatably mounted on the piston rod 14.
  • Fig. 5 shows a third embodiment, in particular, the piston rod and the connecting rod connecting member are formed differently from the second embodiment. Since the construction, structure and function of the other reciprocating internal combustion engine is unchanged, the same is neither shown nor described. Further, for components similar or equal to the first or second embodiment, the same reference numerals will be used and only the differences from the first and second embodiments will be described.
  • the structure of the third embodiment is substantially the same as that of the second embodiment. That is, as in the second embodiment, an adjustment of the point of the connecting rod connecting member 64 on the piston rod 14 by rotating the rotatably mounted on the piston rod 14 sleeve member 110 takes place.
  • the piston rod 14 in its tapered end portion 102 has a slot 103.
  • the length of the elongated hole 103 corresponds at least to the maximum adjustment length 13 of the sleeve component 110 with respect to the connecting rod connecting component 64.
  • at least one threaded bolt 104 is screwed into a threaded bore 105 provided in the connecting rod connecting component 64. The bolt 104 is in the screwed state until in the slot 104 in the piston rod 14 before. Thereby, the piston rod 14 is non-rotatably connected to the connecting rod connecting member 64, so that relative rotation of the piston rod 14 and the piston 12 with respect to the connecting rod connecting member 64 is prevented.
  • the above-described rotationally symmetrical design of the piston rod and the lead-through region of the adjusting rod is not mandatory.
  • the seal on the crankcase can also take place, for example, via a co-rotating seal in the case of non-rotationally symmetrical design (outer circumference of the seal is rotationally symmetrical).
  • the actuation or rotation of the adjusting rod can optionally be done by means of compressed air, vacuum, electric motor, magnetic, etc.
  • a gear can also be mounted directly rigidly on the piston rod. This gear can then be slidably engaged with another (drive) gear in the longitudinal direction of the piston rod following the movement of the piston rod 14. In this case, the tooth widths must be selected so that a continuous engagement of the gears between the TDC and UT is ensured.
  • a gear on the piston rod for example, in a subsequent to the region of the external thread 74 extension region in the longitudinal direction displaceable but rotatably mounted about the longitudinal axis rotatably.
  • the above-mentioned cross-sectional shapes of the adjusting rod or the central sleeve-shaped region to ensure the torque transmission are merely exemplary and can be changed as desired.
  • the connecting rod connection component can be formed in one piece or in several parts, that is, a connecting rod connecting component can be provided for each connecting rod.
  • the bulge of the crankcase described above is provided in particular if a corresponding lubricating oil sump is to be present in the same.
  • the bulge can be omitted.
  • the piston rod is up to the side of the crank disks, which faces away from the piston, out.
  • the present disclosure is not limited to this and is also applicable to reciprocating internal combustion engine with double crank mechanism, in which the piston rod extends only on the piston side facing the centers of the crank mechanisms.
  • connection of the connecting rod to the piston rod can also be used in multi-cylinder engines, if, for example, the bearing pins 92 and 94 crank disks are provided on both sides, wherein one of the pair of crank disks cooperates with the piston rod of one piston and the other pair of crank disks with the piston rod of another piston ,
  • the crank pulley 48 is mounted with its bearing pin 94 fixed to the machine.
  • the bearing pin 94 have, for example, an extension, which leads for example to a clutch via which the crank disk 94 is connected to a transmission of a vehicle.
  • the valves can be actuated via suitable gear and / or belt and / or cam connections via the crankshaft (s).
  • crank disks 46 and 48 via their peripheral teeth in rotationally fixed engagement with each other.
  • the crank discs do not necessarily have to be in rotationally fixed engagement with each other and may be spaced apart by reducing their outer diameter with their circumferences.
  • the synchronous opposite rotation of the crank disks can be ensured in this case via the linearly guided piston rod 14 and the connecting rods 50, 52, wherein the piston rod 14 is advantageously guided in its passage 16 through the partition wall 18 linearly movable.
  • the third length 13, with which the articulation position of the connecting rod connection component on the piston rod can be adjusted in the longitudinal direction of the piston rod, is dimensioned according to a desired compression ratio adjustment.
  • the second length 12 is greater than the intended piston stroke.
  • Fig. 6 instead of providing an internal thread on the connecting rod connecting component and an external thread engaging therein on the piston rod or the sleeve component can also, as exemplified in Fig. 6 is shown, one or more guide pins 120 or guide projections on the outside of the piston rod 14 and correspondingly provided one or more guide grooves 122 in the connecting rod connecting member 64 or vice versa.
  • the guide grooves 122 preferably have a step-shaped course, which is followed by the corresponding guide pin 120 inserted therein.
  • beads 124 may be provided which the guide pin 120 must overflow before moving to the underlying step.
  • the piston tube 14 terminates on its underside in a tooth-shaped contact region 126 and has the connecting rod connection component 64 on the side facing the piston tube 14 a contact region 130 with a shape which is preferably complementary thereto.
  • the contact portion 126 of the piston tube 14 in this embodiment forms the lower end of the piston tube 14 and is formed such that the piston tube 14 has different lengths in the longitudinal direction at different circumferential positions.
  • the surface of the contact region facing the connecting rod connection component 64 thus lies in different planes perpendicular to the longitudinal direction of the piston tube 14.
  • the connecting rod connection component 64 has a central tubular (sleeve-shaped) region 128.
  • the contact region 130 projecting on the inside, with which the contact region 126 of the piston tube 14 inserted into the tubular region 128 at least partially comes into contact.
  • the surface of the contact region 130 facing the piston tube 14 thus lies in different planes perpendicular to the longitudinal direction of the piston tube 14.
  • the inner diameter of the central tubular region 128 is in its upper region, in which the contact region 130 is not provided, so dimensioned that the lower end of the piston tube 14 is inserted and rotatable therein, whereas the inner diameter of the contact region 130 is at least partially smaller than that of the piston tube 14.
  • the contours of the contact regions 126 and 130 are formed such that there is preferably at least one position in which the lower end of the piston tube 14, ie, the contact region 126 is completely (more or less gapless) on the contact region 130 over the entire circumference comes (complete gearing). At least the contour must be formed so that a degree of toothing (overlap perpendicular to the longitudinal direction) of the contact regions 126, 130 can be varied by rotating the piston tube 14 about its longitudinal axis. In normal operation of the engine, the piston tube 14 is always pressed on the connecting rod connecting member 64.
  • the connecting rod connecting member 64 is formed so that the lower end of the piston tube 14 comes to rest directly on a correspondingly contoured upper edge of the connecting rod connecting member 64.
  • the piston tube is not plugged into the connecting rod connecting member and no contact portion projecting inwardly is provided in the connecting rod connecting member.
  • the connecting rod connection component 64 also has different heights / lengths in the longitudinal direction at different circumferential positions.
  • the piston tube and the connecting rod connection component can engage in a first degree in a first end position (uppermost point of engagement of the connecting rod connecting component on the piston tube).
  • first degree in a first end position uppermost point of engagement of the connecting rod connecting component on the piston tube.
  • the piston tube 14 may be guided in its relative movement to the connecting rod connecting member 64 on the same, so that a lifting of the piston rod is prevented.
  • the piston tube 14 has a region 132 which projects downwards within the contact region 126 of the piston tube 14 and has an outer diameter which is smaller than the inner diameter of the contact region 130 of the connecting rod connection component 64.
  • a radially outwardly projecting guide projection 134 is provided.
  • the connecting rod connection component 64 has a guide groove 136 in its lower region (below the contact region 130).
  • the guide groove 136 is formed in the wall of the connecting rod connecting member 64 so that the guide projection 134 is guided therein in accordance with the movement path given by the contact holes 126, 130 when the piston tube 14 is rotated to the connecting rod connecting member 64.
  • the guide projection 134 preferably absorbs substantially only forces that attempt to remove the piston tube 14 from the connecting rod connection component 64, whereas the contact areas absorb the pressure forces acting therebetween.

Description

Die Erfindung betrifft eine Brennkraftmaschine, insbesondere Hubkolbenbrennkraftmaschine, mit Doppelkurbeltrieb und variabler Verdichtung.The invention relates to an internal combustion engine, in particular reciprocating internal combustion engine, with double crank drive and variable compression.

Eine Hubkolbenbrennkraftmaschine mit Doppelkurbeltrieb ist beispielsweise aus der DE 102 47 106 B4 bekannt. Gegenüber konventionellen Brennkraftmaschinen, bei denen ein Kolben über jeweils ein Pleuel mit einer Kurbelwelle verbunden ist, haben Hubkolbenbrennkraftmaschinen mit Doppelkurbeltrieb zahlreiche Vorteile. Vom Doppelkurbeltrieb her werden auf den Kolben keinerlei Seitenkräfte ausgeübt, wodurch die Reibung vermindert wird, die Schwingungsanregung geringer ist und der Kolben flach und ohne Hemd ausgeführt sein kann, was für die, falls erforderlich, Schmierung der Gleitberührung Kolbenring / Zylinderwand vorteilhaft ist bzw. eine Kolbenschmierung überflüssig machen kann. Aufgrund des seitlichen Versatzes der Drehachsen der gegenläufig drehenden Kurbelscheiben relativ zur linearen Bewegung der Kolbenstange ist der Drehwinkel der Kurbelscheiben bei Bewegung des Kolbens vom OT zum UT ungleich dem Drehwinkel bei der anschließenden Bewegung des Kolbens vom UT zum OT. Dies kann bei der Verbrennung vorteilhaft genutzt werden. Die Drehmomentabgabe wird vergleichmäßigt, was zusätzlich dadurch unterstützt wird, das im Vergleich zu herkömmlichen Motoren bei gleichem Kolbenhub kleinere Kurbelradien der Doppelkurbeln erforderlich sind.A reciprocating internal combustion engine with double crank drive is for example from the DE 102 47 106 B4 known. Compared to conventional internal combustion engines, in which a piston is connected via a connecting rod with a crankshaft, reciprocating internal combustion engines with double crank drive have numerous advantages. From Doppelkurbeltrieb forth no lateral forces are exerted on the piston, whereby the friction is reduced, the vibration excitation is lower and the piston can be made flat and shirtless, which is advantageous for the, if necessary, lubrication of the sliding piston ring / cylinder wall or a Can make piston lubrication redundant. Due to the lateral offset of the axes of rotation of the counter-rotating crank disks relative to the linear movement of the piston rod, the angle of rotation of the crank disks is different from the rotational angle in the subsequent movement of the piston from BDC to TDC when the piston moves from TDC to TDC. This can be used advantageously in the combustion. The torque output is made uniform, which is further supported by the fact that compared to conventional engines with the same piston stroke smaller crank radii of double cranks are required.

Die Verdichtung einer Hubkolbenbrennkraftmaschine, das heißt, das Verhältnis zwischen dem Volumen einer im Zylinder oberhalb des Kolbens ausgebildeten Arbeitskammer bei im unteren Totpunkt (UT) befindlichem Kolben zu bei im oberen Totpunkt (OT) befindlichen Kolben, hat unter anderem starken Einfluss auf den Verbrauch. Beispielsweise ist im Teillastbereich eine höhere Verdichtung gewünscht. Beim Ottomotor ist das Verdichtungsverhältnis typischerweise durch die Klopfneigung begrenzt, wobei es bei Saugmotoren größer sein kann als bei aufgeladenen Motoren. Beim Dieselmotor ist insbesondere für ein sicheres Anlassen ein hohes Verdichtungsverhältnis erforderlich. Während des Betriebs des Dieselmotors ist für geringen Schadstoffgehalt im Abgas sowie aus Reibungsgründen eine Absenkung des Verdichtungsverhältnisses vorteilhaft.The compression of a reciprocating internal combustion engine, that is, the ratio between the volume of a working chamber formed in the cylinder above the piston at bottom dead center (UT) piston to at top dead center (TDC) piston has, among other things, strong influence on consumption. For example, a higher compression is desired in the partial load range. In the Otto engine, the compression ratio is typically limited by the tendency to knock, and it may be greater in naturally aspirated engines than in turbocharged engines. When diesel engine especially for a safe start a high compression ratio is required. During operation of the diesel engine lowering of the compression ratio is advantageous for low pollutant content in the exhaust gas and friction reasons.

In bekannten Motoren wird eine variable Verdichtung nur mit größtem Aufwand erstellt. Die Verstellung erfolgt in bekannten Motoren nur in einem sehr kleinen Bereich.In known engines variable compression is created only with great effort. The adjustment takes place in known engines only in a very small area.

Aus der DE 10 2011 120162 A1 ist eine Brennkraftmaschine mit variabler Verdichtung bekannt, die eine exzentrische Kurbelwellenlagerung aufweist, wobei zwischen der Kurbelwellenlagerung und einem zumindest ein Zahnradsegment und ein Zahnrad umfassendes Getriebe eine torsionssteife Verbindung angeordnet ist. Das Zahnradsegment ist an einem axial äußeren Kurbelwellenlager befestigt und mittels des Zahnrades ist zur Verstellung der exzentrischen Kurbelwellenlagerung ein Drehmoment auf das Zahnradsegment einleitbar. In der Praxis konnte sich die vorbekannte Brennkraftmaschine nicht durchsetzen.From the DE 10 2011 120162 A1 a variable compression internal combustion engine is known which has an eccentric crankshaft bearing, wherein a torsionally rigid connection is arranged between the crankshaft bearing and a gear comprising at least one gear segment and a gearwheel. The gear segment is fixed to an axially outer crankshaft bearing and by means of the gear is for adjusting the eccentric crankshaft bearing torque on the gear segment can be introduced. In practice, the previously known internal combustion engine could not prevail.

Die DE 195 06 963 A1 offenbart einen Wechselhubmotor, bei dem der Expansionsgrad größer als der Kompressionsgrad ist. Weitere zum Stand der Technik relevante Dokumente sind die CN 203 939 575 U , die US 2,229,778 , die EP 1 710 394 A1 , die GB 441,666 , die EP 2 792 846 A1 und die DE 100 19 959 A1 .The DE 195 06 963 A1 discloses a changeover motor in which the degree of expansion is greater than the degree of compression. Other relevant to the prior art documents are the CN 203 939 575 U , the US 2,229,778 , the EP 1 710 394 A1 , the GB 441,666 , the EP 2 792 846 A1 and the DE 100 19 959 A1 ,

Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolbenbrennkraftmaschine mit variabler Verdichtung anzugeben.The invention has for its object to provide a reciprocating internal combustion engine with variable compression.

Diese Aufgabe wird gelöst durch eine Hubkolbenbrennkraftmaschine gemäß dem unabhängigen Anspruch 1.This object is achieved by a reciprocating internal combustion engine according to independent claim 1.

Die Unteransprüche sind auf vorteilhafte Ausführungsformen und Weiterbildungen der Brennkraftmaschine gerichtet.The subclaims are directed to advantageous embodiments and refinements of the internal combustion engine.

Die Erfindung ist für weitgehend alle Arten von Hubkolbenbrennkraftmaschinen einsetzbar, beispielsweise Ein- und Mehrzylindermotoren, Otto-, Diesel-, und Gasmotoren, Zweitakt- und Viertaktmotoren.The invention can be used for substantially all types of reciprocating internal combustion engines, such as single and multi-cylinder engines, gasoline, diesel, and gas engines, two-stroke and four-stroke engines.

Durch die Erfindung wird das Schadensrisiko des gesamten Motors und die Belastung seiner Teile reduziert. Die gesamte Motorauslegung wird einfacher und risikoärmer. Es ergeben sich Vorteile bezüglich der Größe und des Gewichts, der Reibung, des konstruktiven Aufwands und der Herstellungskosten, des Servicekostenaufwands, der Toleranzen und Passlängen und der Laufzeitverlängerung des Motors. Der Verbrach und die Emissionen werden reduziert.The invention reduces the risk of damage to the entire engine and the load on its parts. The entire engine design is easier and less risky. There are advantages in terms of size and weight, friction, design effort and cost of manufacture, service cost, tolerances and fits, and motor life extension. The crime and the emissions are reduced.

Die Erfindung wird im Folgenden anhand schematischer Zeichnungen beispielsweise und mit weiteren Einzelheiten erläutert:
In den Figuren stellen dar:

Fig. 1
einen Mittelschnitt durch eine Hubkolbenbrennkraftmaschine mit Doppelkurbeltrieb und variabler Verdichtung gemäß einer ersten Ausführungsform,
Fig. 2
eine schematische Querschnittsansicht des Doppelkurbeltriebs gemäß der ersten Ausführungsform,
Fig. 3
eine vergrößerte Querschnittsansicht eines Kolbens mit Kolbenstange, eines Pleuelverbindungsbauteils und einer Verstellstange gemäß einer zweiten Ausführungsform,
Fig. 4
eine vergrößerte Darstellung eines Teils der Kolbenstange, des Pleuelverbindungsbauteils und der Verstellstange gemäß der zweiten Ausführungsform,
Fig. 5
eine vergrößerte Querschnittsansicht eines Kolbens mit Kolbenstange, eines Pleuelverbindungsbauteils und einer Verstellstange gemäß einer dritten Ausführungsform,
Fig. 6
eine vergrößerte Darstellung eines Teils der Kolbenstange, des Pleuelverbindungsbauteils und der Verstellstange gemäß einer weiteren Ausführungsform,
Fig. 7
eine vergrößerte Darstellung eines Teils der Kolbenstange, des Pleuelverbindungsbauteils und der Verstellstange gemäß einer weiteren Ausführungsform, und
Fig. 8
eine vergrößerte Darstellung eines Teils der Kolbenstange, des Pleuelverbindungsbauteils und der Verstellstange gemäß einer weiteren Ausführungsform.
The invention is explained below with reference to schematic drawings, for example and with further details:
In the figures represent:
Fig. 1
FIG. 2 is a central section through a double crank drive variable compression piston internal combustion engine according to a first embodiment; FIG.
Fig. 2
a schematic cross-sectional view of the double crank mechanism according to the first embodiment,
Fig. 3
an enlarged cross-sectional view of a piston with a piston rod, a connecting rod connecting member and an adjusting rod according to a second embodiment,
Fig. 4
an enlarged view of a part of the piston rod, the connecting rod connecting member and the adjusting rod according to the second embodiment,
Fig. 5
an enlarged cross-sectional view of a piston with a piston rod, a connecting rod connecting member and an adjusting rod according to a third embodiment,
Fig. 6
an enlarged view of a part of the piston rod, the connecting rod connecting member and the adjusting rod according to another embodiment,
Fig. 7
an enlarged view of a portion of the piston rod, the connecting rod connecting member and the adjusting rod according to another embodiment, and
Fig. 8
an enlarged view of a portion of the piston rod, the connecting rod connecting member and the adjusting rod according to another embodiment.

Gemäß Fig. 1 weist eine Hubkolbenbrennkraftmaschine (Brennkraftmaschine) einen Zylinder 10 auf, in dem ein Kolben 12 längs der Achse des Zylinders beweglich ist. Der beispielsweise hemdlos ausgebildete Kolben 12 ist vorzugsweise starr mit einer Kolbenstange 14 verbunden, die unter Abdichtung linear beweglich durch eine Durchführung 16 hindurch geführt ist, die in einer Trennwand 18 ausgebildet ist, die den Innenraum des Zylinders 10 gemäß Fig. 1 nach unten abschließt. Auf diese Weise ist oberhalb des Kolbens 12 eine Arbeitskammer 20 zwischen dem Kolben 12 und dem Zylinderkopf 22 bzw. einer Oberwand des Zylinders ausgebildet und unterhalb des Kolbens 12 zwischen dem Kolben 12 und der Trennwand 18 eine Frischluftkammer 24 ausgebildet. Eine im unteren Bereich der Frischluftkammer 24 ausgebildete Einlassöffnung ist an einen Ansaugkanal 26 angeschlossen, der mit einem Ansaugventil 28 verschließbar ist. Aus dem unteren Bereich der Frischluftkammer 24 führt eine Auslassöffnung in einen Verbindungskanal 32, in dem ein Zwischenventil 34 angeordnet ist und der mit einem Einlasskanal 36 verbunden ist, der in die Arbeitskammer 20 der Brennkraftmaschine führt und mittels eines beispielsweise als Tellerventil ausgebildeten Einlassventils 38 schließbar ist.According to Fig. 1 For example, a reciprocating internal combustion engine (internal combustion engine) includes a cylinder 10 in which a piston 12 is movable along the axis of the cylinder. The piston 12 formed, for example, shirtless is preferably rigidly connected to a piston rod 14 which is guided under sealing linearly movable through a passage 16 which is formed in a partition wall 18, the interior of the cylinder 10 according to Fig. 1 closes down. In this way, a working chamber 20 is formed above the piston 12 between the piston 12 and the cylinder head 22 and an upper wall of the cylinder and below the piston 12 between the piston 12 and the partition wall 18, a fresh air chamber 24 is formed. An inlet opening formed in the lower region of the fresh air chamber 24 is connected to an intake passage 26, which can be closed with an intake valve 28. From the lower region of the fresh air chamber 24, an outlet opening leads into a connecting channel 32, in which an intermediate valve 34 is arranged and which is connected to an inlet channel 36, which leads into the working chamber 20 of the internal combustion engine and can be closed by means of an inlet valve 38, for example designed as a poppet valve ,

Aus der Arbeitskammer 20 führt ein Auslasskanal 40 durch ein nicht dargestelltes Abgassystem der Hubkolbenbrennkraftmaschine ins Freie. Der Auslasskanal 40 ist mittels eines beispielsweise als Tellerventil ausgebildeten Auslassventils 42 verschließbar.From the working chamber 20, an outlet channel 40 leads through an unillustrated exhaust system of the reciprocating internal combustion engine to the outside. The outlet channel 40 can be closed by means of an outlet valve 42 designed, for example, as a poppet valve.

Die Kolbenstange 14 führt durch die Trennwand 18 hindurch in den Innenraum eines den Doppelkurbeltrieb aufnehmenden Kurbelgehäuses 44, in dem zwei Kurbelscheiben 46 und 48 um gehäusefeste Drehachsen A und B drehbar gelagert sind. Die Kurbelscheiben 46 und 48 weisen an mit gleichem Durchmesser ausgebildeten Umfängen Umfangsverzahnungen auf, die miteinander kämmen. Die Drehachsen A und B der Kurbelscheiben 46 und 48 verlaufen in einer senkrecht zur Kolbenstange 14 ausgerichteten Ebene und sind von der Kolbenstange 14 gleich weit entfernt. In der vorliegenden Ausführungsform erstreckt die Kolbenstange 14 sich bis unterhalb der Ebene, in der die Drehachsen A und B liegen, derart, dass ihr unteres Ende auch im oberen Totpunkt des Kolbens 12 unterhalb der Drehachsen A und B ist. Das untere Ende der Kolbenstange 14 ist über Pleuel 50, 52 gelenkig mit Pleuelzapfen 54 bzw. 56 verbunden, die an den Kurbelscheiben 46 und 48radial innerhalb der Umfangsverzahnungen exzentrisch zu den Drehachsen A und B der Kurbelscheiben 46 und 48 angeordnet sind.The piston rod 14 passes through the partition wall 18 into the interior of a double crank drive receiving crankcase 44, in which two crank disks 46 and 48 are rotatably mounted to housing fixed axes of rotation A and B. The crank pulleys 46 and 48 have at circumferences formed with the same diameter circumferential teeth, which mesh with each other. The axes of rotation A and B of the crank disks 46 and 48 extend in a direction perpendicular to the piston rod 14 level and are equidistant from the piston rod 14. In the present embodiment, the piston rod 14 extends to below the plane in which the axes of rotation A and B lie, such that their lower end is also in the top dead center of the piston 12 below the axes of rotation A and B. The lower end of the piston rod 14 is pivotally connected via connecting rods 50, 52 with connecting rods 54 and 56, respectively, which are arranged on the crank disks 46 and 48 radially within the peripheral teeth eccentric to the axes of rotation A and B of the crank disks 46 and 48.

In Fig. 1 ist der Kolben 12 in einer Position ungefähr zwischen dem oberen Totpunkt (OT) und dem unteren Totpunkt (UT) dargestellt.In Fig. 1 For example, piston 12 is shown in a position approximately between top dead center (TDC) and bottom dead center (TDC).

Aufbau und Funktion der bisher beschriebenen Hubkolbenbrennkraftmaschine sind an sich bekannt.Structure and function of the previously described reciprocating internal combustion engine are known per se.

Bei Betrieb im Viertaktverfahren sind ausgehend von im unteren Totpunkt befindlichem Kolben 12 bei einem Auspuff- bzw. Ausstoßtakt die Ventile 34 und 38 geschlossen und die Ventile 28 und 42 offen. Der Kolben schiebt während des Auspufftakts verbrannte Ladung aus der Arbeitskammer aus und saugt gleichzeitig Frischluft in die Frischluftkammer 24 ein. Beim anschließenden Ansaughub bzw. -takt sind die Ventile 28 und 42 zu und die Ventile 34 und 38 auf, so dass in dem Verbindungskanal 32 und der Frischluftkammer 24 befindliche Frischluft durch die offenen Ventile 34 und 38 hindurch in die Arbeitskammer 20 gedrückt wird. Beim anschließenden Verdichtungshub bzw. -takt ist lediglich das Ansaugventil 28 offen, so dass bei der Verdichtung der in der Arbeitskammer 20 befindlichen Ladung Frischluft in die Frischluftkammer 24 eingesaugt wird. Bei dem anschließenden Arbeitshub (Verbrennungstakt) sind alle Ventile mit Ausnahme des Zwischenventils 34 geschlossen, so dass während des Arbeitstakts beim vorherigen Verdichtungstakt angesaugte Frischluft in den Verbindungskanal 32 geschoben wird und dort vorverdichtet wird. Beim anschließenden Auspufftakt beginnt der beschriebene Zyklus von neuem. Die beschriebene Brennkraftmaschine arbeitet somit mit integrierter interner Aufladung, da bei einem Ansaugtakt etwa das Zweifache des Volumens der Frischluftkammer in die Arbeitskammer 20 gelangt, so dass unmittelbar beim Anlassen bereits eine Aufladung vorhanden ist.When operating in the four-stroke process, the valves 34 and 38 are closed and the valves 28 and 42 open starting from located in the bottom dead center piston 12 at an exhaust or exhaust stroke. The piston pushes burned charge out of the working chamber during the exhaust stroke and simultaneously draws in fresh air into the fresh air chamber 24. During the subsequent intake stroke, the valves 28 and 42 are on and the valves 34 and 38 are on, so that in the connecting channel 32 and the fresh air chamber 24 fresh air is pushed through the open valves 34 and 38 into the working chamber 20. During the subsequent compression stroke or stroke, only the intake valve 28 is open, so that fresh air is sucked into the fresh air chamber 24 during the compression of the charge located in the working chamber 20. In the subsequent working stroke (combustion cycle) all valves are closed, with the exception of the intermediate valve 34, so that during the working cycle at the previous compression cycle sucked fresh air is pushed into the connecting channel 32 and is pre-compressed there. During the subsequent exhaust stroke, the cycle described begins again. The described internal combustion engine thus operates with integrated internal charging, since in an intake stroke approximately twice the volume of the fresh air chamber reaches the working chamber 20, so that a charge is already present directly on starting.

Bei der angedeuteten gegensinnigen Drehrichtung der Kurbelscheiben 46 und 48, bei der die in Fig. 1 linke Kurbelscheibe 46 in Uhrzeigerrichtung und die rechte Kurbelscheibe 48 gegen Uhrzeigerrichtung dreht, ist, wie aus der Figur unmittelbar ersichtlich, der Drehwinkel der Kurbelscheiben vom OT zu UT des Kolbens größer als der Drehwinkel der Kurbelscheiben vom UT zum OT. Durch zweckentsprechende Auslegung des Doppelkurbeltriebs kann erreicht werden, dass ein Arbeitstakt sich über bis zu 230° Kurbelwinkel erstreckt, was für eine vollständige Verbrennung und eine gleichmäßigere Drehmomententfaltung vorteilhaft ist.In the indicated opposite direction of rotation of the crank disks 46 and 48, in which the in Fig. 1 left crank 36 in the clockwise direction and the right crank 48 rotates counterclockwise, as can be seen directly from the figure, the angle of rotation of the crank disks from TDC to BDC of the piston is greater than the angle of rotation of the crank disks from BDC to TDC. By appropriate design of the double crank drive can be achieved that a power stroke extends over up to 230 ° crank angle, which is advantageous for complete combustion and a more uniform torque deployment.

Mittels der Außenverzahnungen der Kurbelscheiben und entsprechender Nuten etc. im Kurbelgehäuse können die Kurbelscheiben die Funktion von Flüssigkeitspumpen zur Schmierung übernehmen.By means of the external toothings of the crank disks and corresponding grooves etc. in the crankcase, the crank disks can assume the function of liquid pumps for lubrication.

In Fig. 1 bildet eine Ausbauchung 45 des Kurbelgehäuses 44 (Fig. 1), deren Mindest-Tiefe durch die Stellung der Kurbelstange 14 im UT des Kolbens 12 bestimmt ist, einen Auffangbehälter für einen Flüssigkeitssumpf 69. Eine lediglich zur drucklosen Förderung ausgelegte einfache Flüssigkeitspumpe (nicht dargestellt) saugt Flüssigkeit aus dem Flüssigkeitssumpf 70 an und führt sie den Kurbelscheiben 46, 48 zur weiteren Förderung zu.In Fig. 1 forms a bulge 45 of the crankcase 44 (FIG. Fig. 1 ), whose minimum depth is determined by the position of the connecting rod 14 in the UT of the piston 12, a collecting container for a liquid sump 69. A simple liquid pump designed only for pressureless delivery (not shown) sucks liquid from the liquid sump 70 and leads them Crankshafts 46, 48 for further promotion.

Ein grundsätzlicher Vorteil einer mit Doppelkurbeltrieb ausgerüsteten Brennkraftmaschine liegt darin, dass der Kurbelraum vollständig vom Kolbenraum getrennt ist. Der Kolben muss wegen seiner Seitenkraft-freien Führung bei entsprechender Materialpaarung zwischen der Außenseite des Kolbens bzw. eines oder mehrerer dort vorgesehener Kolbenringe und der Innenwand des Zylinders nicht geschmiert werden, so dass das Schmieröl keiner Alterung durch den Einfluss von Verbrennungsrückständen oder hohen Temperaturen ausgesetzt ist und als Lebensdauerfüllung vorhanden sein kann. Weiter kann auch zeitweise oder ganz auf die Kolbenringe verzichtet werden bzw. deren Anzahl verringert werden.A fundamental advantage of a double-cranked internal combustion engine is that the crankcase is completely separated from the piston chamber. The piston must not be lubricated because of its lateral force-free guidance with appropriate material pairing between the outside of the piston or one or more provided there piston rings and the inner wall of the cylinder, so that the lubricating oil is not exposed to aging due to the influence of combustion residues or high temperatures and can be present as a lifetime filling. Next can also be dispensed with temporarily or completely on the piston rings and their number can be reduced.

Fig. 2 zeigt schematisch ein Beispiel der Anbindung der Kolbenstange 14 an die Kurbelscheiben 46 und 48 (die in Fig. 2 gezeigte Drehposition stimmt zur Vereinfachung der Darstellung nicht unbedingt mit der in Fig. 1 gezeigten überein). Die Kurbelscheiben 46 und 48 weisen Lagerzapfen 92 und 94 auf, mit denen sie drehbar am Kurbelgehäuse gelagert sind. Weiter weisen die Kurbelscheiben 46 und 48 auf der den Lagerzapfen 92, 94 abgewandten Seite zylinderförmige Vorsprungsbereiche 60, 62 auf, an denen Pleuelzapfen 54 und 56 ausgebildet sind (in Fig. 2 nur schematisch gezeigt). An den Pleuelzapfen 54 und 56 sind erste Enden der Pleuel 50 und 52 gelagert. Zur Verbindung der Pleuel 50 und 52 mit der Kolbenstange 14 ist ein Pleuelverbindungsbauteil 64 vorgesehen, welches einen zentralen, muffenförmigen Bereich 65 und zwei als vorstehende Ohren ausgebildete Ansätze 66 und 68 aufweist, die sich auf entgegengesetzten Seiten des zentralen muffenförmigen Bereichs 65 weg von dem zentralen muffenförmigen Bereich 65 erstrecken. Jeder der Ansätze 66, 68 ist über einen Verbindungsbolzen 70, 72 mit dem anderen (in Fig. 1 unteren) Ende des entsprechenden Pleuels 50, 52 gekoppelt. Fig. 2 schematically shows an example of the connection of the piston rod 14 to the crank disks 46 and 48 (the in Fig. 2 shown rotational position is not necessarily to simplify the presentation with the in Fig. 1 shown). The crank disks 46 and 48 have bearing pins 92 and 94, with which they are rotatably mounted on the crankcase. Next, the crank disks 46 and 48 on the side facing away from the bearing journal 92, 94 cylindrical projection portions 60, 62 on which connecting rods 54 and 56 are formed (in Fig. 2 shown only schematically). At the connecting rod 54 and 56 first ends of the connecting rods 50 and 52 are mounted. To connect the connecting rods 50 and 52 to the piston rod 14, there is provided a connecting rod connecting member 64 having a central sleeve-shaped portion 65 and two protruding ears 66 and 68 extending on opposite sides of the central sleeve-shaped portion 65 away from the central one sleeve-shaped portion 65 extend. Each of the lugs 66, 68 is connected via a connecting bolt 70, 72 with the other (in Fig. 1 lower end of the corresponding connecting rod 50, 52 coupled.

Wie aus Fig. 1 und 2 ersichtlich ist, ist an dem dem Kolben 12 abgewandten Ende der Kolbenstange 14 ein Außengewinde 74 ausgebildet. Das Außengewinde 74 erstreckt sich ausgehend von dem dem Kolben 12 abgewandten Ende der Kolbenstange 14 über eine erste Länge 11 in Längsrichtung der Kolbenstange 14. Die Kolbenstange 14 ist zusätzlich ausgehend von dem dem Kolben 12 abgewandten Ende der Kolbenstange 14 über eine zweite Länge 12 in Längsrichtung der Kolbenstange 14 hohl ausgebildet. Wie aus Fig. 2 ersichtlich, ist die Innenquerschnittsform der Kolbenstange 14 senkrecht zu ihrer Längsrichtung in dem hohlen Kolbenstangenbereich 78 in der vorliegenden Ausführungsform quadratisch.How out Fig. 1 and 2 it can be seen, an external thread 74 is formed at the end of the piston rod 14 facing away from the piston 12. The external thread 74 extends from the piston 12 facing away from the end of the piston rod 14 over a first length 11 in the longitudinal direction of the piston rod 14. The piston rod 14 is additionally starting from the piston 12 remote from the end of the piston rod 14 via a second length 12 in the longitudinal direction the piston rod 14 is hollow. How out Fig. 2 As can be seen, the internal cross-sectional shape of the piston rod 14 is perpendicular to its longitudinal direction in the hollow piston rod portion 78 in the present embodiment square.

Das Pleuelverbindungsbauteil 64 weist ein in dem zentralen muffenförmigen Bereich 65 ausgebildetes Innengewinde 76 auf, das auf das Außengewinde 74 der Kolbenstange 14 aufschraubbar ist. Die Länge des Innengewindes 76 ist bevorzugt kürzer als die Länge des Außengewindes 74, so dass das Pleuelverbindungsbauteil 64 bezüglich der Kolbenstange 14 zwischen dem voll eingeschraubten Zustand und dem maximal herausgeschraubten Zustand, bei dem die Gewinde noch sicher ineinandergreifen, um eine vorbestimmte dritte Länge 13 (Verstellweg, Verstelllänge) in Längsrichtung der Kolbenstange 14 relativ zueinander bewegbar sind. Fig. 1 zeigt eine maximal eingeschraubte Position des Pleuelverbindungsbauteils 64 (Position mit kleinstem Verdichtungsverhältnis), in der das Pleuelverbindungsbauteil möglichst nahe am Kolben angeordnet ist. Die Länge 13 ist in Fig. 1 ausgehend von der oberen Kante des Pleuelverbindungsbauteils 64 gezeigt. In der maximal herausgeschraubten Position (Position mit größtem Verdichtungsverhältnis) sind die Gewinde noch sicher im Eingriff.The connecting rod connection component 64 has an internal thread 76 formed in the central sleeve-shaped region 65, which can be screwed onto the external thread 74 of the piston rod 14. The length of the internal thread 76 is preferably shorter than the length of the external thread 74, so that the connecting rod connecting member 64 with respect to the piston rod 14 between the fully screwed state and the maximum unscrewed state in which the threads still securely interlock by a predetermined third length 13 (FIG. Adjustment, Verstelllänge) in the longitudinal direction of the piston rod 14 are movable relative to each other. Fig. 1 shows a maximum screwed-in position of the connecting rod connecting member 64 (minimum compression ratio position) in which the connecting rod connecting member is located as close as possible to the piston. The length 13 is in Fig. 1 starting from the top Edge of the connecting rod connecting member 64 shown. In the maximum unscrewed position (position with the largest compression ratio), the threads are still securely engaged.

Weiter ist eine Verstellstange 80 vorgesehen, die koaxial zu der Kolbenstange 14 angeordnet ist. Die Verstellstange 80 weist einen Eingriffsbereich 82 auf, der sich ausgehend vom dem Ende, das dem Kolben 12 zugewandt ist, über mindestens eine vierte Länge 14 (nicht gezeigt) erstreckt, die gleich oder größer dem Kolbenhub ist. Die Außenquerschnittform des Eingriffsbereichs 82 senkrecht zur Längserstreckung der Verstellstange 80 ist in der vorliegenden Ausführungsform entsprechend der Innenquerschnittsform des hohlen Kolbenstangenbereichs 78 quadratisch ausgebildet ist, so dass der Eingriffsbereich 82 in dem hohlen Kolbenstangenbereich 78 in Längsrichtung gleitend verschiebbar eingesetzt ist. Gleichzeit sind der Eingriffsbereich 82 und der hohle Kolbenstangenbereich 78 aufgrund der komplementären Außenquerschnittsform drehfest um die Längsachse miteinander gekoppelt. Die Tiefe bzw. Länge, mit der die Verstellstange 80 in die Kolbenstange 14 hineinragt, hängt von der momentanen Position des Kolbens ab.Further, an adjusting rod 80 is provided, which is arranged coaxially with the piston rod 14. The adjustment rod 80 has an engagement portion 82 extending from the end facing the piston 12 over at least a fourth length 14 (not shown) equal to or greater than the piston stroke. The outer cross-sectional shape of the engaging portion 82 perpendicular to the longitudinal extent of the adjusting rod 80 is square in the present embodiment according to the inner cross-sectional shape of the hollow piston rod portion 78, so that the engaging portion 82 is slidably inserted in the hollow piston rod portion 78 in the longitudinal direction. Simultaneously, the engagement portion 82 and the hollow piston rod portion 78 are non-rotatably coupled to each other due to the complementary outer cross-sectional shape about the longitudinal axis. The depth or length at which the adjusting rod 80 projects into the piston rod 14 depends on the instantaneous position of the piston.

Die Verstellstange 80 weist auf der dem Kolben 12 abgewandten Seite des Eingriffsbereichs 82 weiter einen Durchführungsbereich 83 auf. Der Durchführungsbereich 83 hat in der vorliegenden Ausführungsform eine rotationssymmetrische (kreisrunde) Außenquerschnittform.The adjusting rod 80 has on the side facing away from the piston 12 of the engaging portion 82 further comprises a feedthrough region 83. The feedthrough area 83 has a rotationally symmetrical (circular) outer cross-sectional shape in the present embodiment.

Weiter ist an der Verstellstange 80 an ihrem dem Kolben 12 abgewandten Endbereich auf herkömmliche Weise ein Zahnrad 84 angebracht. Die Verstellstange 80 erstreckt sich im montierten Zustand des Motors von einem unteren, bezüglich des Kurbelgehäuses 44 feststehenden Lager 86 unter Abdichtung (nicht gezeigt) durch die Ausbuchtung 45 des Kurbelwellengehäuses 44 bis in den hohlen Kolbenstangenbereich 78 der Kolbenstange 14 hinein. Die Gesamtlänge der Verstellstange 80 ist dabei bevorzugt so gewählt, dass die Verstellstange 80 im OT des Kolbens 12 für eine Verstellung ausreichend mit dem hohlen Kolbenstangenbereich 78 im Eingriff ist bzw. in diesen hineinragt. Die Verstellstange 80 ist in dem Lager 86 axial fest aber drehbar gelagert. Der Eingriffsbereich 82 ist so angeordnet und ausgebildet, dass die Kolbenstange 14 zwischen dem OT und UT gleitend mit demselben im Eingriff ist.Further, a gear 84 is mounted on the adjusting rod 80 at its end portion facing away from the piston 12 in a conventional manner. The adjusting rod 80 extends in the assembled state of the engine from a lower, relative to the crankcase 44 fixed bearing 86 under seal (not shown) through the bulge 45 of the crankcase 44 into the hollow piston rod portion 78 of the piston rod 14 inside. The total length of the adjusting rod 80 is preferably selected so that the adjusting rod 80 in the TDC of the piston 12 for an adjustment sufficiently with the hollow piston rod portion 78 is engaged or projects into this. The adjusting rod 80 is axially fixed but rotatably mounted in the bearing 86. The engagement portion 82 is arranged and formed such that the piston rod 14 is slidably engaged therewith between the TDC and TDC.

Weiter ist zum Drehen der Verstellstange 80 um ihre Längsachse ein Motor (Aktuator) 88 vorgesehen, der über ein Zahnrad 90 zum Antreiben der Verstellstange 80 angeordnet und ausgebildet ist.Further, for rotating the adjusting rod 80 about its longitudinal axis, a motor (actuator) 88 is provided, which is arranged and formed via a gear 90 for driving the adjusting rod 80.

Die Verdichtung der Hubkolbenbrennkraftmaschine kann wie folgt variabel eingestellt werden:
Das Pleuelverbindungsbauteil 64 ist über sein Innengewinde 76 mit dem Außengewinde 74 der Kolbenstange 14 im Eingriff. Über eine Relativdrehung zwischen dem Pleuelverbindungsbauteil 64 und der Kolbenstange 14 kann eine Position des Pleuelverbindungsbauteils 64 an der Kolbenstange 14 in Längsrichtung der Kolbenstange 14 verändert werden. Durch die Position des Pleuelverbindungsbauteils 64 an der Kolbenstange 14 wird das Verhältnis des Volumens der Arbeitskammer 20 im UT des Kolbens 12 zu dem Volumen der Arbeitskammer 20 im OT des Kolbens 12, also das Verhältnis des maximalen Volumens zu dem minimalen Volumen (Verdichtungsverhältnis) bestimmt. Durch Ändern dieser Position kann daher das Verdichtungsverhältnis verändert werden.The compression of the reciprocating internal combustion engine can be variably set as follows:
The connecting rod connecting member 64 is via its internal thread 76 with the external thread 74 of the piston rod 14 in engagement. By means of a relative rotation between the connecting rod connecting member 64 and the piston rod 14, a position of the connecting rod connecting member 64 on the piston rod 14 in the longitudinal direction of the piston rod 14 can be changed. By the position of the connecting rod connecting member 64 on the piston rod 14, the ratio of the volume of the working chamber 20 in UT of the piston 12 to the volume of the working chamber 20 in the TDC of the piston 12, ie the ratio of the maximum volume to the minimum volume (compression ratio) is determined. By changing this position, therefore, the compression ratio can be changed.

Das Pleuelverbindungsbauteil 64 ist in der vorliegenden Ausführungsform konstruktionsbedingt aufgrund der beidseitigen Verbindung bzw. Anlenkung an die Pleuel 50 und 52 nicht drehbar bezüglich des ortsfesten Kurbelwellengehäuses 44. Eine Verstellung erfolgt daher durch Verdrehen der Kolbenstange 14 mittels der drehfest aber axial verschiebbar in der Kolbenstange 14 gelagerten Verstellstange 80. Die Kolbenstange 14 kann aufgrund ihrer rotationssymmetrischen Form im Bereich der Durchführung 16 durch die Trennwand 18 frei gedreht werden, ohne die Abdichtung zwischen der Trennwand 18 und der Kolbenstange 14 zu verringern. Auch der mit der Kolbenstange 14 in dieser Ausführungsform drehfest verbundene Kolben 12 kann aufgrund seiner rotationssymmetrischen Form frei im Zylinder 10 gedreht werden.The connecting rod connecting member 64 is in the present embodiment, due to the two-sided connection or articulation to the connecting rods 50 and 52 is not rotatable with respect to the stationary crankcase 44. An adjustment is therefore carried out by rotating the piston rod 14 by means of the rotationally fixed but axially displaceable in the piston rod 14 Adjustment rod 80. The piston rod 14 can be freely rotated due to its rotationally symmetrical shape in the region of the passage 16 through the partition wall 18, without reducing the seal between the partition wall 18 and the piston rod 14. Also, the non-rotatably connected to the piston rod 14 in this embodiment, the piston 12 can be rotated freely in the cylinder 10 due to its rotationally symmetrical shape.

Die Verstellstange 80 wird durch Betätigen des Elektromotors 88 mittels der Zahnräder 90 und 84 gedreht. Aufgrund der in Längsrichtung der Verstellstange 80 bzw. der Kolbenstange 14 gleitenden Lagerung der Verstellstange 80 in der Kolbenstange 14 hindert die Verstellstange 80 nicht die Aufwärts- und Abwärtsbewegung der Kolbenstange 14 während des Betriebs der Hubkolbenbrennkraftmaschine. Die Verdichtung bzw. der Verdichtungsgrad kann damit während des Betriebs der Hubkolbenbrennkraftmaschine auf einfache Weise verstellt bzw. eingestellt werden. Bevorzugt ist die Gewindesteigung des Innengwindes 76 und des Außengewindes 74 so gewählt, dass Selbsthemmung herrscht. Dadurch wird ermöglicht, dass die Verstellstange 80 nach der Verstellung drehmomentfrei in der Kolbenstange 14 geführt ist.The adjusting rod 80 is rotated by operating the electric motor 88 by means of the gears 90 and 84. Due to the sliding in the longitudinal direction of the adjusting rod 80 and the piston rod 14 mounting the adjusting rod 80 in the piston rod 14, the adjusting rod 80 does not prevent the upward and downward movement of the piston rod 14 during operation of the reciprocating internal combustion engine. The compression or the degree of compression can thus be adjusted or adjusted in a simple manner during operation of the reciprocating internal combustion engine. Preferably, the thread pitch of Innengwindes 76 and the external thread 74 is selected so that self-locking prevails. This will allow that the adjusting rod 80 is guided without torque in the piston rod 14 after adjustment.

In Fig. 3 und 4 ist eine zweite Ausführungsform gezeigt, bei der insbesondere das Pleuelverbindungsbauteil, die Kolbenstange und die Verstellstange verschieden zu der ersten Ausführungsform ausgebildet sind. Fig. 4 zeigt die Querschnittansicht A-A aus Fig. 3. Da die Konstruktion, der Aufbau und die Funktion der übrigen Hubkolbenbrennkraftmaschine unverändert gegenüber der ersten Ausführungsform ist, wird dieselbe bzw. derselbe weder gezeigt noch beschrieben. Für Bauteile, die ähnlich oder gleich zu der ersten Ausführungsform sind, werden dieselben Bezugszeichen verwendet und lediglich die Unterschiede zu der ersten Ausführungsform beschrieben.In Fig. 3 and 4 a second embodiment is shown in which in particular the connecting rod connecting member, the piston rod and the adjusting rod are formed differently from the first embodiment. Fig. 4 shows the cross-sectional view AA Fig. 3 , Since the construction, structure and function of the other reciprocating internal combustion engine is unchanged from the first embodiment, the same is neither shown nor described. For components similar or equal to the first embodiment, the same reference numerals will be used and only the differences from the first embodiment will be described.

Wie auch in der ersten Ausführungsform ist die Kolbenstange 14 gemäß der zweiten Ausführungsform ausgehend von dem dem Kolben 12 abgewandten Ende der Kolbenstange 14 über die zweite Länge 12 in Längsrichtung der Kolbenstange 14 hohl ausgebildet. Wie aus Fig. 3 und 4 ersichtlich ist, weist die Kolbenstange 14 an ihrem dem Kolben 12 abgewandten Ende einen verjüngten Bereich 106 auf. Im Gegensatz zu der ersten Ausführungsform weist der verjüngte Bereich kein Außengewinde auf. Der verjüngten Bereich 106 weist stattdessen einen Nutbereich 108 auf, der eine Umfangsnut in der Kolbenstange 14 ausbildet.As in the first embodiment, the piston rod 14 is formed according to the second embodiment, starting from the piston 12 remote from the end of the piston rod 14 via the second length 12 in the longitudinal direction of the piston rod 14 hollow. How out Fig. 3 and 4 can be seen, the piston rod 14 at its end facing away from the piston 12 has a tapered portion 106. In contrast to the first embodiment, the tapered portion has no external thread. The tapered portion 106 instead has a groove portion 108 which forms a circumferential groove in the piston rod 14.

Auf das dem Kolben 12 abgewandte Ende der Kolbenstange 14 bzw. des verjüngten Bereichs 106 ist ein Hülsen- bzw. Deckelbauteil 110 aufgesetzt. Das Hülsenbauteil 110 ist im Wesentlichen topfförmig ausgebildet und weist an seinem dem Topfboden 112 entgegengesetzten Ende einen radial nach Innen vorstehenden Vorsprungsbereich 114 auf. Das Hülsenbauteil 110 weist einen Innenumfang auf, der geringfügig größer als der Außenumfang des verjüngten Bereichs 106 der Kolbenstange 14 ist. Der Vorsprungsbereich 114 ist so ausgebildet, dass er sowohl in Breite als auch Tiefe geringfügig kleiner als der Nutbereich 108 der Kolbenstange 14 ist. Im zusammengebauten Zustand ist das auf die Kolbenstange 14 aufgesetzte Hülsenbauteil 110 in Längsrichtung der Kolbenstange 14 an dieser befestigt aber frei relativ zu der Kolbenstange 14 um die Längsachse derselben drehbar. Das Hülsenbauteil 110 selbst kann beispielswiese aus zwei Hälften bestehen. Zur Montage an der Kolbenstange 14 werden die zwei Hälften auf der Kolbenstange 14 so montiert, dass die Vorsprungsbereiche 114 in den Nutbereich eingreifen. Anschließend wird das Pleuelverbindungsbauteil 64 von unten aufgeschraubt (bevor die Pleuel daran montiert sind), wodurch die zwei Hälften fest aneinander und an der Kolbenstange 14 befestigt sind. Alternativ kann auch das Pleuelverbindungsbauteil 54 aus zwei miteinander verschraubten Hälften ausgebildet sein.On the piston 12 facing away from the end of the piston rod 14 and the tapered portion 106, a sleeve or cover member 110 is placed. The sleeve component 110 has a substantially pot-shaped design and has a radially inwardly projecting projection region 114 at its end opposite the bottom of the pot 112. The sleeve member 110 has an inner circumference slightly larger than the outer circumference of the tapered portion 106 of the piston rod 14. The protrusion portion 114 is formed so as to be slightly smaller in width and depth than the groove portion 108 of the piston rod 14. In the assembled state, the sleeve component 110 placed on the piston rod 14 is fastened to the piston rod 14 in the longitudinal direction of the piston rod 14 but is freely rotatable relative to the piston rod 14 about the longitudinal axis thereof. The sleeve component 110 itself can for example consist of two halves. For mounting on the piston rod 14, the two halves are mounted on the piston rod 14 so that the projection portions 114 engage in the groove portion. Subsequently, the connecting rod connecting member 64 is screwed from below (before the connecting rods are mounted thereto), whereby the two halves fixed to each other and are attached to the piston rod 14. Alternatively, the connecting rod connecting member 54 may be formed of two halves bolted together.

Auf der (gesamten) Außenumfangsseite des Hülsenbauteils 110 ist ein Außengewinde 116 ausgebildet. Zudem ist in dem Topfboden des Hülsenbauteils 110 ein Durchgangsloch 118 vorgesehen. Das Durchgangsloch 118 hat bevorzugt eine nicht rotationssymmetrische (unrunde) Innenquerschnittsform.On the (outer) outer side of the sleeve member 110, an external thread 116 is formed. In addition, in the pot bottom of the sleeve member 110, a through hole 118 is provided. The through-hole 118 preferably has a non-rotationally symmetrical (non-round) inner cross-sectional shape.

Der Aufbau des Pleuelverbindungsbauteils 64 entspricht im Wesentlichen dem der ersten Ausführungsform. Das heißt, wie auch in der ersten Ausführungsform weist das Pleuelverbindungsbauteil 64 gegenüberliegende Ansätze 66 und 68 zur Verbindung mit den Pleueln 50 und 52 und einen zentralen muffenförmigen Bereich 65, in dessen Innenumfang ein Innengewinde 76 ausgebildet ist, auf. Das Innengewinde 76 ist zum Eingriff mit dem Außengewinde 116 des Hülsenbauteils 110 ausgebildet.The structure of the connecting rod connecting member 64 substantially corresponds to that of the first embodiment. That is, as in the first embodiment, the connecting rod connecting member 64 has opposite bosses 66 and 68 for connection to the connecting rods 50 and 52 and a central sleeve-shaped portion 65 in whose inner circumference an internal thread 76 is formed. The internal thread 76 is designed to engage with the external thread 116 of the sleeve component 110.

Weiter ist, wie auch in der ersten Ausführungsform, eine Verstellstange 80 ausgebildet, die einen im Querschnitt bevorzugt rotationssymmetrischen (kreisrunden) Durchführungsbereich 83 aufweist. An dem dem Kolben 12 abgewandten Ende weist die Verstellstange 80 ein Zahnrad 84 auf und ist axial fest aber drehbar an einer nicht gezeigten Wand gelagert.Next, as in the first embodiment, an adjusting rod 80 is formed, which has a preferably circularly symmetrical in cross section (circular) lead-through area 83. At the end facing away from the piston 12, the adjusting rod 80 has a gear 84 and is axially fixed but rotatably mounted on a wall, not shown.

Der Eingriffsbereich 82 der Verstellstange 80 gemäß der zweiten Ausführungsform ist ähnlich wie in der ersten Ausführungsform als Bereich mit nicht-rotationssymmetrischer (unrunder) Außenquerschnittsform ausgebildet, so dass er in dem Durchgangsloch 118 in dem Hülsenbauteil 110 in Längsrichtung der Verstellstange 80 gleitbar geführt und gleichzeitig drehfest mit dem Hülsenbauteil 110 verbunden ist.The engaging portion 82 of the adjusting rod 80 according to the second embodiment is formed similarly as in the first embodiment as a non-rotationally symmetrical (non-circular) outer cross-sectional shape portion so as to be slidably guided in the through hole 118 in the sleeve member 110 in the longitudinal direction of the adjusting rod 80 while being non-rotatable is connected to the sleeve member 110.

Im montierten Zustand wird in dieser Ausführungsform die Position des Pleuelverbindungsbauteils 64 bezüglich der Kolbenstange 14 dadurch verändert, dass aufgrund einer Drehung des Hülsenbauteils 110, das in Längsrichtung mit der Kolbenstange 14 im Eingriff ist, eine Relativbewegung zwischen dem Hülsenbauteil 110 und dem Pleuelverbindungsbauteil 64 in Längsrichtung der Kolbenstange 14 erfolgt. Die Drehung des Hülsenbauteils 110 wird durch den drehfesten Eingriff mit der Verstellstange 80 erreicht, die durch einen nicht gezeigten Motor/Aktuator angetrieben wird. Entgegen der ersten Ausführungsform muss bei der zweiten Ausführungsform keine Relativdrehung zwischen der Kolbenstange 14 und dem Pleuelverbindungsbauteil 64 stattfinden. Die Kolbenstange 14 und der Kolben 12 werden daher bei der Verstellung nicht mitgedreht bzw. können sich unabhängig von dem Pleuelverbindungsbauteil 64 und der Verstellstange 14 drehen.In the assembled state, in this embodiment, the position of the connecting rod connecting member 64 with respect to the piston rod 14 is changed by causing relative movement between the sleeve member 110 and the connecting rod connecting member 64 in the longitudinal direction due to rotation of the sleeve member 110 longitudinally engaged with the piston rod 14 the piston rod 14 takes place. The rotation of the sleeve member 110 is achieved by the rotationally fixed engagement with the adjusting rod 80, which is driven by a motor / actuator, not shown. Contrary to the first embodiment, in the second embodiment, there is no need for relative rotation between the piston rod 14 and the connecting rod connecting member 64 will take place. The piston rod 14 and the piston 12 are therefore not rotated during the adjustment or can rotate independently of the connecting rod connecting member 64 and the adjusting rod 14.

Das oben als aufgesetzt beschriebene Hülsenbauteil 110 kann auch mehrteilig (beispielsweise aus Boden und mehreren Hohlzylindern, die miteinander verschraubt sind) ausgebildet sein und an der Kolbenstange 14 drehbar montiert sein.The sleeve component 110 described above as being mounted can also be constructed in several parts (for example, from the bottom and a plurality of hollow cylinders which are screwed together) and can be rotatably mounted on the piston rod 14.

In Fig. 5 zeigt eine dritte Ausführungsform, bei der insbesondere die Kolbenstange und das Pleuelverbindungsbauteil verschieden zu der zweiten Ausführungsform ausgebildet sind. Da die Konstruktion, der Aufbau und die Funktion der übrigen Hubkolbenbrennkraftmaschine unverändert ist, wird dieselbe weder gezeigt noch beschrieben. Weiter werden für Bauteile, die ähnlich oder gleich zu der ersten oder zweiten Ausführungsform sind, dieselben Bezugszeichen verwendet und werden lediglich die Unterschiede zu der ersten und zweiten Ausführungsform beschrieben.In Fig. 5 shows a third embodiment, in particular, the piston rod and the connecting rod connecting member are formed differently from the second embodiment. Since the construction, structure and function of the other reciprocating internal combustion engine is unchanged, the same is neither shown nor described. Further, for components similar or equal to the first or second embodiment, the same reference numerals will be used and only the differences from the first and second embodiments will be described.

Der Aufbau der dritten Ausführungsform entspricht im Wesentlichen dem der zweiten Ausführungsform. D.h., wie auch in der zweiten Ausführungsform erfolgt eine Verstellung des Angriffspunktes des Pleuelverbindungsbauteils 64 an der Kolbenstange 14 durch Verdrehen des auf die Kolbenstange 14 drehbar aufgesetzten Hülsenbauteils 110.The structure of the third embodiment is substantially the same as that of the second embodiment. That is, as in the second embodiment, an adjustment of the point of the connecting rod connecting member 64 on the piston rod 14 by rotating the rotatably mounted on the piston rod 14 sleeve member 110 takes place.

Zu Sicherung eines Verdrehens des Kolbens 12 bzw. der Kolbenstange 14 in dem Zylinder 10 weist die Kolbenstange 14 in ihrem verjüngten Endbereich 102 ein Langloch 103 auf. Die Länge des Langlochs 103 entspricht mindestens der maximalen Verstelllänge 13 des Hülsenbauteils 110 bezüglich des Pleuelverbindungsbauteils 64. Weiter ist mindestens ein Schraubbolzen 104 in eine in dem Pleuelverbindungsbauteil 64 vorgesehenen Gewindebohrung 105 eingeschraubt. Der Schraubbolzen 104 steht im eingeschraubten Zustand bis in das Langloch 104 in der Kolbenstange 14 vor. Dadurch ist die Kolbenstange 14 drehfest mit dem Pleuelverbindungsbauteil 64 verbunden, so dass eine Relativdrehung der Kolbenstange 14 und des Kolbens 12 bezüglich des Pleuelverbindungsbauteils 64 verhindert wird. Somit wird in dieser Ausführungsform auch beim Verstellen des Verdichtungsverhältnisses der Kolben bezüglich des Zylinders 10 nicht gedreht. Der Schraubbolzen 104 steht soweit nach innen vor, dass er nicht in Kontakt mit der Verstellstange 80 ist, die in dem hohlen Kolbenstangebereich 78 entsprechend der Hubbewegung hin und her bewegbar angeordnet ist.To ensure a rotation of the piston 12 and the piston rod 14 in the cylinder 10, the piston rod 14 in its tapered end portion 102 has a slot 103. The length of the elongated hole 103 corresponds at least to the maximum adjustment length 13 of the sleeve component 110 with respect to the connecting rod connecting component 64. Furthermore, at least one threaded bolt 104 is screwed into a threaded bore 105 provided in the connecting rod connecting component 64. The bolt 104 is in the screwed state until in the slot 104 in the piston rod 14 before. Thereby, the piston rod 14 is non-rotatably connected to the connecting rod connecting member 64, so that relative rotation of the piston rod 14 and the piston 12 with respect to the connecting rod connecting member 64 is prevented. Thus, in this embodiment, even when adjusting the compression ratio of the piston with respect to the cylinder 10 is not rotated. The bolt 104 protrudes inwardly so far that it is not in contact with the adjusting rod 80 which is reciprocally movable in the hollow piston rod portion 78 in accordance with the reciprocating motion.

Im Weiteren werden weitere mögliche Abwandlungen beschrieben.In the following further possible modifications are described.

Die oben beschriebene rotationssymmetrische Ausbildung der Kolbenstange und des Durchführungsbereichs der Verstellstange ist nicht zwingend. die Abdichtung an dem Kurbelgehäuse kann bei nicht rotationssymmetrischer Ausbildung auch beispielsweise über eine sich mitdrehende Abdichtung erfolgen (Außenumfang der Abdichtung ist rotationssymmetrisch).The above-described rotationally symmetrical design of the piston rod and the lead-through region of the adjusting rod is not mandatory. the seal on the crankcase can also take place, for example, via a co-rotating seal in the case of non-rotationally symmetrical design (outer circumference of the seal is rotationally symmetrical).

Die Betätigung bzw. Verdrehung der Verstellstange kann wahlweise mittels Pressluft, Vakuum, elektromotorisch, magnetisch etc. erfolgen.The actuation or rotation of the adjusting rod can optionally be done by means of compressed air, vacuum, electric motor, magnetic, etc.

Statt dem Vorsehen einer Verstellstange kann ein Zahnrad auch direkt starr an der Kolbenstange angebracht sein. Dieses Zahnrad kann dann der Bewegung der Kolbenstange 14 folgend mit einem weiteren (Antriebs-) Zahnrad in Längsrichtung der Kolbenstange gleitend im Eingriff sein. In diesem Fall müssen die Zahnbreiten so gewählt sein, dass ein durchgehender Eingriff der Zahnräder zwischen dem OT und UT gewährleistet ist. Alternativ kann ein Zahnrad an der Kolbenstange beispielsweise in einem sich an den Bereich des Außengewindes 74 anschließenden Verlängerungsbereich in Längsrichtung verschiebbar aber um die Längsachse drehfest drehfest montiert sein.Instead of providing an adjusting rod, a gear can also be mounted directly rigidly on the piston rod. This gear can then be slidably engaged with another (drive) gear in the longitudinal direction of the piston rod following the movement of the piston rod 14. In this case, the tooth widths must be selected so that a continuous engagement of the gears between the TDC and UT is ensured. Alternatively, a gear on the piston rod, for example, in a subsequent to the region of the external thread 74 extension region in the longitudinal direction displaceable but rotatably mounted about the longitudinal axis rotatably.

Die oben angegeben Querschnittformen der Verstellstange bzw. des zentralen muffenförmigen Bereichs zur Sicherstellung der Drehmomentübertragung sind lediglich beispielhaft und können beliebig abgeändert werden. Das Pleuelverbindungsbauteil kann einteilig oder mehrteilig ausgebildet sein, d.h., es kann für jedes Pleuel ein Pleuelverbindungsbauteil vorgesehen sein.The above-mentioned cross-sectional shapes of the adjusting rod or the central sleeve-shaped region to ensure the torque transmission are merely exemplary and can be changed as desired. The connecting rod connection component can be formed in one piece or in several parts, that is, a connecting rod connecting component can be provided for each connecting rod.

Die oben beschriebene Ausbauchung des Kurbelgehäuses wird insbesondere vorgesehen, wenn ein entsprechender Schmierölsumpf in derselben vorhanden sein soll. Bei schmiermittelfreier Ausbildung der Hubkolbenbrennkraftmaschine kann die Ausbauchung weggelassen werden. Insbesondere kann bei schmiermittelfreier Ausbildung der Hubkolbenbrennkraftmaschine auf eine Durchführung der Verstellstange auf die Außenseite des Kurbelgehäuses verzichtet werden und die Verstellstange samt ihrem Antrieb in dem Kurbelgehäuse vorgesehen sein.The bulge of the crankcase described above is provided in particular if a corresponding lubricating oil sump is to be present in the same. With lubricant-free design of the reciprocating internal combustion engine, the bulge can be omitted. In particular, with lubrication-free design of the reciprocating internal combustion engine, it is possible to dispense with carrying out the adjustment rod on the outside of the crankcase and to provide the adjusting rod together with its drive in the crankcase.

Bei der in Fig. 1 dargestellten Hubkolbenbrennkraftmaschine ist die Kolbenstange bis auf die Seite der Kurbelscheiben, die dem Kolben abgewandt ist, geführt. Die vorliegende Offenbarung ist nicht hierauf beschränkt und auch anwendbar auf Hubkolbenbrennkraftmaschinen mit Doppelkurbeltrieb, bei denen sich die Kolbenstange nur auf der dem Kolben zugewandten Seite der Mittelpunkte der Kurbeltriebe erstreckt.At the in Fig. 1 shown reciprocating internal combustion engine, the piston rod is up to the side of the crank disks, which faces away from the piston, out. The present disclosure is not limited to this and is also applicable to reciprocating internal combustion engine with double crank mechanism, in which the piston rod extends only on the piston side facing the centers of the crank mechanisms.

Die oben beschriebene Anordnung der Lufteinlass- und Luftauslasspfade, der Ventile, des Kurbelgehäuses etc. und die in Fig. 1 gezeigte Anordnung einer Zündkerze sind rein beispielhaft und können beliebig geändert werden. Die oben beschriebene integrierte Aufladung mit den verschiedenen Ventilen ist optional.The above-described arrangement of the air intake and Luftauslasspfade, the valves, the crankcase, etc. and the in Fig. 1 shown arrangement of a spark plug are purely exemplary and can be changed arbitrarily. The above-described integrated charging with the various valves is optional.

Die vorstehend beschriebene Anbindung der Pleuel an die Kolbenstange kann auch bei mehrzylindrigen Motoren angewendet werden, wenn beispielsweise beidseitig der Lagerzapfen 92 und 94 Kurbelscheiben vorgesehen sind, wobei eines der Kurbelscheibenpaare mit der Kolbenstange eines Kolbens und das andere der Kurbelscheibenpaare mit der Kolbenstange eines weiteren Kolbens zusammenwirkt.The above-described connection of the connecting rod to the piston rod can also be used in multi-cylinder engines, if, for example, the bearing pins 92 and 94 crank disks are provided on both sides, wherein one of the pair of crank disks cooperates with the piston rod of one piston and the other pair of crank disks with the piston rod of another piston ,

Die Kurbelscheibe 48 ist mit ihrem Lagerzapfen 94 maschinenfest gelagert. Der Lagerzapfen 94 weisen beispielsweise eine Verlängerung auf, die beispielsweise zu einer Kupplung führt, über die die Kurbelscheibe 94 mit einem Getriebe eines Fahrzeugs verbunden ist. Die Ventile können über geeignete Zahnrad- und/oder Riemen- und/oder Nockenverbindungen über die Kurbelwelle(n) betätigt werden.The crank pulley 48 is mounted with its bearing pin 94 fixed to the machine. The bearing pin 94 have, for example, an extension, which leads for example to a clutch via which the crank disk 94 is connected to a transmission of a vehicle. The valves can be actuated via suitable gear and / or belt and / or cam connections via the crankshaft (s).

Bei der Brennkraftmaschine gemäß Fig. 1 sind die beiden Kurbelscheiben 46 und 48 über ihre Umfangsverzahnungen in drehfestem Eingriff miteinander. Die Kurbelscheiben müssen nicht zwangsläufig in drehfestem Eingriff miteinander sein und können unter Verringerung ihres Außendurchmessers mit ihren Umfängen beabstandet angeordnet sein. Die synchrone gegenläufige Drehung der Kurbelscheiben kann in diesem Fall über die linear geführte Kolbenstange 14 und die Pleuel 50, 52 gewährleistet werden, wobei die Kolbenstange 14 vorteilhafterweise in ihrer Durchführung 16 durch die Trennwand 18 linear beweglich geführt ist.In the internal combustion engine according to Fig. 1 are the two crank disks 46 and 48 via their peripheral teeth in rotationally fixed engagement with each other. The crank discs do not necessarily have to be in rotationally fixed engagement with each other and may be spaced apart by reducing their outer diameter with their circumferences. The synchronous opposite rotation of the crank disks can be ensured in this case via the linearly guided piston rod 14 and the connecting rods 50, 52, wherein the piston rod 14 is advantageously guided in its passage 16 through the partition wall 18 linearly movable.

Die dritte Länge 13, mit der die Anlenkposition des Pleuelverbindungsbauteils an der Kolbenstange in Längsrichtung der Kolbenstange verstellt werden kann, ist entsprechend einer gewünschten Verdichtungsverhältnisverstellung bemessen.The third length 13, with which the articulation position of the connecting rod connection component on the piston rod can be adjusted in the longitudinal direction of the piston rod, is dimensioned according to a desired compression ratio adjustment.

Die zweite Länge 12 ist größer als der vorgesehene Kolbenhub.The second length 12 is greater than the intended piston stroke.

Statt dem Vorsehen eines Innengewindes am Pleuelverbindungsbauteil und eines darin eingreifenden Außengewindes an der Kolbenstange oder dem Hülsenbauteil können auch, wie es beispielhaft in Fig. 6 gezeigt ist, ein oder mehrere Führungsbolzen 120 oder Führungsvorsprünge außen an der Kolbenstange 14 und entsprechend ein oder mehrere Führungsnuten 122 im Pleuelverbindungsbauteil 64 oder umgekehrt vorgesehen sein. Die Führungsnuten 122 haben bevorzugt einen stufenförmigen Verlauf, dem der entsprechende darin eingesetzte Führungsbolzen 120 folgt. Durch die Führungsnut 122 kann eine gegenüber einem Standardgewinde größere Verstellung des Angriffspunktes (Position der Anlenkung) der Pleuel am Kolben mit Bezug den Winkel, um den die Kolbenstange gedreht wird, erreicht werden. Durch den stufenförmigen Verlauf kann bevorzugt eine vollständige Selbsthemmung erreicht werden, so dass ein selbstständiges Rückdrehen vermieden wird. Bevorzugt können zur weiteren Absicherung gegen ungewolltes Rückdrehen an den Rändern der Stufen Wulste 124 vorgesehen sein, die der Führungsbolzen 120 überlaufen muss, bevor er sich auf die darunter liegende Stufe bewegt.Instead of providing an internal thread on the connecting rod connecting component and an external thread engaging therein on the piston rod or the sleeve component can also, as exemplified in Fig. 6 is shown, one or more guide pins 120 or guide projections on the outside of the piston rod 14 and correspondingly provided one or more guide grooves 122 in the connecting rod connecting member 64 or vice versa. The guide grooves 122 preferably have a step-shaped course, which is followed by the corresponding guide pin 120 inserted therein. By the guide groove 122 can be compared to a standard thread greater adjustment of the point (position of the linkage) of the connecting rod on the piston with respect to the angle by which the piston rod is rotated, can be achieved. Due to the step-shaped course, a complete self-locking can preferably be achieved, so that an independent turning back is avoided. Preferably, to further protect against unintentional reverse rotation at the edges of the steps, beads 124 may be provided which the guide pin 120 must overflow before moving to the underlying step.

In einer weiteren in Fig. 7 gezeigten Ausgestaltung endet das Kolbenrohr 14 an seiner Unterseite in einem zahnförmigen Berührbereich 126 und hat das Pleuelverbindungsbauteil 64 auf der dem Kolbenrohr 14 zugewandten Seite einen Berührbereich 130 mit einer dazu bevorzugt komplementären Form. Der Berührbereich 126 des Kolbenrohrs 14 bildet in dieser Ausführungsform das untere Ende des Kolbenrohrs 14 und ist derart ausgebildet, dass das Kolbenrohr 14 an verschiedenen Umfangspositionen verschiedene Längen in der Längsrichtung hat. Die dem Pleuelverbindungsbauteil 64 zugewandte Oberfläche des Berührbereichs liegt somit in verschiedenen Ebenen senkrecht zu der Längsrichtung des Kolbenrohrs 14.In another in Fig. 7 In the embodiment shown, the piston tube 14 terminates on its underside in a tooth-shaped contact region 126 and has the connecting rod connection component 64 on the side facing the piston tube 14 a contact region 130 with a shape which is preferably complementary thereto. The contact portion 126 of the piston tube 14 in this embodiment forms the lower end of the piston tube 14 and is formed such that the piston tube 14 has different lengths in the longitudinal direction at different circumferential positions. The surface of the contact region facing the connecting rod connection component 64 thus lies in different planes perpendicular to the longitudinal direction of the piston tube 14.

In der in Fig. 7 gezeigten Ausführungsform weist das Pleuelverbindungsbauteil 64 einen zentralen rohrförmigen (muffenförmigen) Bereich 128 auf. Auf der Innenseite des rohrförmigen Bereichs 128 ist der auf die Innenseite vorstehende Berührbereich 130 vorgesehen, mit dem der Berührbereich 126 des in den rohrförmigen Bereich 128 eingesteckten Kolbenrohrs 14 wenigstens teilweise in Berührung kommt. Die dem Kolbenrohr 14 zugewandte Oberfläche des Berührbereichs 130 liegt somit in verschiedenen Ebenen senkrecht zu der Längsrichtung des Kolbenrohrs 14. Der Innendurchmesser des zentralen röhrenförmigen Bereichs 128 ist in seinem oberen Bereich, in dem der Berührbereich 130 nicht vorgesehen ist, so bemessen, dass das untere Ende des Kolbenrohres 14 einsteckbar und darin drehbar ist, wohingegen der Innendurchmesser des Berührbereichs 130 zumindest abschnittsweise kleiner als der des Kolbenrohres 14 ist. Die Konturen der Berührbereiche 126 und 130 sind so ausgebildet, dass es bevorzugt wenigstens eine Position gibt, in der das untere Ende des Kolbenrohres 14, d.h., der Berührbereich 126 vollständig (mehr oder weniger lückenlos) auf dem Berührbereich 130 über den gesamten Umfang zum liegen kommt (vollständige Verzahnung). Zumindest muss die Kontur so ausgebildet sein, das ein Grad der Verzahnung (Überlappung senkrecht zu der Längsrichtung) der Berührbereiche 126, 130 durch Drehen des Kolbenrohres 14 um seine Längsachse variiert werden kann. Im normalen Betrieb des Motors wird das Kolbenrohr 14 immer auf das Pleuelverbindungsbauteil 64 gedrückt.In the in Fig. 7 In the embodiment shown, the connecting rod connection component 64 has a central tubular (sleeve-shaped) region 128. Provided on the inside of the tubular region 128 is the contact region 130 projecting on the inside, with which the contact region 126 of the piston tube 14 inserted into the tubular region 128 at least partially comes into contact. The surface of the contact region 130 facing the piston tube 14 thus lies in different planes perpendicular to the longitudinal direction of the piston tube 14. The inner diameter of the central tubular region 128 is in its upper region, in which the contact region 130 is not provided, so dimensioned that the lower end of the piston tube 14 is inserted and rotatable therein, whereas the inner diameter of the contact region 130 is at least partially smaller than that of the piston tube 14. The contours of the contact regions 126 and 130 are formed such that there is preferably at least one position in which the lower end of the piston tube 14, ie, the contact region 126 is completely (more or less gapless) on the contact region 130 over the entire circumference comes (complete gearing). At least the contour must be formed so that a degree of toothing (overlap perpendicular to the longitudinal direction) of the contact regions 126, 130 can be varied by rotating the piston tube 14 about its longitudinal axis. In normal operation of the engine, the piston tube 14 is always pressed on the connecting rod connecting member 64.

In einer nicht dargestellten Alternative ist das Pleuelverbindungsbauteil 64 so ausgebildet, dass das untere Ende des Kolbenrohres 14 direkt auf einem entsprechend konturierten oberen Rand des Pleuelverbindungsbauteils 64 zum Liegen kommt. In einer solchen Alternative wird das Kolbenrohr somit nicht in das Pleuelverbindungsbauteil eingesteckt und ist kein Berührbereich, der nach innen vorsteht, in dem Pleuelverbindungsbauteil vorgesehen. Entsprechend weist auch das Pleuelverbindungsbauteil 64 an verschiedenen Umfangspositionen verschiedene Höhen/Längen in der Längsrichtung auf.In an alternative, not shown, the connecting rod connecting member 64 is formed so that the lower end of the piston tube 14 comes to rest directly on a correspondingly contoured upper edge of the connecting rod connecting member 64. Thus, in such an alternative, the piston tube is not plugged into the connecting rod connecting member and no contact portion projecting inwardly is provided in the connecting rod connecting member. Correspondingly, the connecting rod connection component 64 also has different heights / lengths in the longitudinal direction at different circumferential positions.

Durch die komplementäre bzw. aufeinander abgestimmte Form der Berührbereiche können das Kolbenrohr und das Pleuelverbindungsbauteil in einer ersten Endposition (oberster Angriffspunkt des Pleuelverbindungsbauteils an dem Kolbenrohr) mit einem ersten Grad ineinandergreifen. Wird nun das Kolbenrohr verdreht, wird der Eingriff bzw. die Überlappung der Bauteile senkrecht zu der Längsrichtung gesehen unter gleichzeitiger Bewegung des Kolbenrohrs vom Pleuelverbindungsbauteil weg verringert oder ganz aufgehoben wird. Hierdurch wird der Angriffspunkt des Pleuelverbindungsbauteils an dem Kolbenrohr nach unten verschoben. Je nach Grad der Verdrehung bezüglich der Eingriffsposition, in der beide Bauteile vollständig oder möglichst weit ineinandergreifen, können somit unterschiedliche Angriffspositionen erreicht werden. Gleichzeitig können aufgrund des unmittelbaren Kontaktes zwischen Kolbenrohr und Pleuelverbindungsbauteil hohe Kräfte zwischen denselben übertragen werden.Due to the complementary or coordinated shape of the contact regions, the piston tube and the connecting rod connection component can engage in a first degree in a first end position (uppermost point of engagement of the connecting rod connecting component on the piston tube). Now, if the piston tube is rotated, the engagement or the overlap of the components is seen perpendicular to the longitudinal direction with simultaneous movement of the piston tube away from the connecting rod connection component or canceled completely. As a result, the point of application of the connecting rod connection component is displaced downwards on the piston tube. Depending on the degree of rotation with respect to the engagement position, in which both components fully or as far as possible interlock, thus different attack positions can be achieved. At the same time high forces can be transmitted between them due to the direct contact between the piston tube and connecting rod connection component.

Bei der in Fig. 7 gezeigten Ausführungsform ist ein Abheben des Kolbenrohrs vom Pleuelverbindungsbauteil möglich. Um dies zu verhindern kann, wie es in Fig. 8 gezeigt ist, das Kolbenrohr 14 in seiner Relativbewegung zu dem Pleuelverbindungsbauteil 64 an demselben geführt sein, so dass ein Abheben der Kolbenstange verhindert wird. In der in Fig. 8 gezeigten Ausführungsform wird dies dadurch realisiert, dass das Kolbenrohr 14 einen innerhalb des Berührbereichs 126 des Kolbenrohrs 14 nach unten vorstehenden Bereich 132 mit einem Außendurchmesser aufweist, der kleiner als der Innendurchmesser des Berührbereichs 130 des Pleuelverbindungsbauteils 64 ist. An diesem nach unten vorstehenden Bereich 132 ist ein radial nach außen vorstehender Führungsvorsprung 134 vorgesehen. Für diesen weist das Pleuelverbindungsbauteil 64 in seinem unteren Bereich (unterhalb des Berührbereichs 130) eine Führungsnut 136 auf. Die Führungsnut 136 ist in der Wand des Pleuelverbindungsbauteils 64 so ausgebildet, dass der Führungsvorsprung 134 darin entsprechend der durch die Berührberieche 126, 130 vorgegebenen Bewegungsbahn beim Verdrehen des Kolbenrohrs 14 zu dem Pleuelverbindungsbauteil 64 geführt wird. Durch den Führungsvorsprung 134 werden bevorzugt im Wesentlichen nur Kräfte aufgenommen, die das Kolbenrohr 14 von dem Pleuelverbindungsbauteil 64 zu entfernen versuchen, wohingegen durch die Berührbereiche die zwischen diesen wirkende Druckkräfte aufnehmen.At the in Fig. 7 shown embodiment, a lifting of the piston tube from the connecting rod connecting member is possible. To prevent this, as it can in Fig. 8 is shown, the piston tube 14 may be guided in its relative movement to the connecting rod connecting member 64 on the same, so that a lifting of the piston rod is prevented. In the in Fig. 8 In the embodiment shown, this is realized in that the piston tube 14 has a region 132 which projects downwards within the contact region 126 of the piston tube 14 and has an outer diameter which is smaller than the inner diameter of the contact region 130 of the connecting rod connection component 64. At this downwardly projecting portion 132, a radially outwardly projecting guide projection 134 is provided. For this, the connecting rod connection component 64 has a guide groove 136 in its lower region (below the contact region 130). The guide groove 136 is formed in the wall of the connecting rod connecting member 64 so that the guide projection 134 is guided therein in accordance with the movement path given by the contact holes 126, 130 when the piston tube 14 is rotated to the connecting rod connecting member 64. The guide projection 134 preferably absorbs substantially only forces that attempt to remove the piston tube 14 from the connecting rod connection component 64, whereas the contact areas absorb the pressure forces acting therebetween.

Neben den dargestellten Mechanismen können auch alternative, nicht gezeigte Mechanismen zum Einsatz kommen, bei denen die Verstellung des Angriffspunktes des Pleuelverbindungsbauteils bzw. der Pleuel an der Kolbenstange beispielsweise durch aufeinander gleitende schräge, stufenförmige, wellige oder irgendwie geartete Ebenen, Verzahnungen, oder Berührungsbereiche sichergestellt wird. Zur Verhinderung einer ungewollten Rückstellung und/oder zur Sicherstellung, dass im stationären Betrieb nicht dauerhaft Rückstellkräfte auf die Verstellstange wirken, können auch Klemmmechanismen oder das Vorsehen einer erhöhten Reibung zur Anwendung kommen.In addition to the mechanisms shown, it is also possible to use alternative mechanisms, not shown, in which the adjustment of the point of engagement of the connecting rod connection component or the connecting rod to the piston rod is ensured, for example, by sliding inclined, step-shaped, wavy or somewhat different planes, toothings or contact regions , In order to prevent an unwanted reset and / or to ensure that in stationary operation do not permanently restoring forces acting on the adjusting rod, clamping mechanisms or the provision of increased friction can be used.

Es wird explizit betont, dass alle in der Beschreibung und/oder den Ansprüchen offenbarten Merkmale als getrennt und unabhängig voneinander zum Zweck der ursprünglichen Offenbarung ebenso wie zum Zweck des Einschränkens der beanspruchten Erfindung unabhängig von den Merkmalskombinationen in den Ausführungsformen und/oder den Ansprüchen angesehen werden sollen. Es wird explizit festgehalten, dass alle Bereichsangaben oder Angaben von Gruppen von Einheiten jeden möglichen Zwischenwert oder Untergruppe von Einheiten zum Zweck der ursprünglichen Offenbarung ebenso wie zum Zweck des Einschränkens der beanspruchten Erfindung offenbaren, insbesondere auch als Grenze einer Bereichsangabe. Bezugszeichenliste 70 Verbindungsbolzen 10 Zylinder 72 Verbindungsbolzen 12 Kolben 74 Außengewinde 14 Kolbenstange 76 Innengewinde 16 Durchführung (Öffnung) 78 hohler Kolbenstangenbereich 18 Trennwand 80 Verstellstange 20 Arbeitskammer 82 Eingriffsbereich 22 Zylinderkopf 83 Durchführungsbereich 24 Frischluftkammer 84 Zahnrad 26 Ansaugkanal 86 Lager 28 Ansaugventil 88 Motor (Aktuator) 30 Auslassöffnung 90 Zahnrad 32 Verbindungskanal 92 Lagerzapfen 34 Zwischenventil 94 Lagerzapfen 36 Einlasskanal 102 verjüngter Bereich 38 Einlassventil 103 Langloch 40 Auslasskanal 104 Schraubbolzen 42 Auslassventil 105 Gewindebohrung 44 Kurbelgehäuse 106 verjüngter Bereich 45 Ausbauchung (Kurbelgehäusewand) 108 Nutbereich 110 Hülsenbauteil 46 Kurbelscheibe (Kurbel) 112 Topfboden 48 Kurbelscheibe (Kurbel) 114 Vorsprungsbereich 50 Pleuel 116 Außengewinde 52 Pleuel 118 Durchgangsloch 54 Pleuelzapfen 120 Führungsbolzen 56 Pleuelzapfen 122 Führungsnut 60 Vorsprungsbereich 124 Wulst 62 Vorsprungsbereich 126 Berührbereich 64 Pleuelverbindungsbauteil 128 rohrförmiger Bereich 65 zentraler muffenförmiger Bereich 130 Berührbereich 66 Ansatz 132 nach unten vorstehender Bereich 68 Ansatz 134 Führungsvorsprung 69 Flüssigkeitssumpf 136 Führungsnut It is explicitly pointed out that all features disclosed in the description and / or the claims are considered separate and independent of each other for the purpose of original disclosure as well as for the purpose of limiting the claimed invention independently of the feature combinations in the embodiments and / or the claims should. It is explicitly stated that all ranges or indications of groups of units represent every possible intermediate value or subgroup of units for Purpose of the original disclosure as well as for the purpose of limiting the claimed invention, in particular also as a limit of an area indication. LIST OF REFERENCE NUMBERS 70 connecting bolts 10 cylinder 72 connecting bolts 12 piston 74 external thread 14 piston rod 76 inner thread 16 Execution (opening) 78 hollow piston rod area 18 partition wall 80 control rod 20 working chamber 82 engagement area 22 cylinder head 83 Through region 24 Fresh air chamber 84 gear 26 intake port 86 camp 28 intake valve 88 Motor (actuator) 30 outlet 90 gear 32 connecting channel 92 pivot 34 between the valve 94 pivot 36 inlet channel 102 rejuvenated area 38 intake valve 103 Long hole 40 exhaust port 104 bolts 42 outlet valve 105 threaded hole 44 crankcase 106 rejuvenated area 45 Bulge (crankcase wall) 108 groove region 110 sleeve member 46 Crank disc (crank) 112 pot base 48 Crank disc (crank) 114 projection portion 50 pleuel 116 external thread 52 pleuel 118 Through Hole 54 connecting rod journals 120 guide pins 56 connecting rod journals 122 guide 60 projection portion 124 bead 62 projection portion 126 contact area 64 Pleuelverbindungsbauteil 128 tubular area 65 central sleeve-shaped area 130 contact area 66 approach 132 downwardly projecting area 68 approach 134 guide projection 69 liquid sump 136 guide

Claims (14)

  1. Internal combustion engine with variable compression with
    at least one cylinder (10),
    a piston (12) reciprocatable within the cylinder (10), wherein a working chamber (20) is formed in the cylinder (10) above the piston (12),
    a piston rod (14) attached to the piston (12) on the side of the piston (12) facing away from the working chamber (20),
    a double crank drive disposed on the side of the piston (12) facing away from the working chamber (20) with two cranks (46, 48) counter-rotating with equal rotation speed, which are respectively hinged via at least one con rod (50, 52) to a con rod connection member (64), via which the con rod (50, 52) is connected to the piston rod (14), wherein
    the position of the con rod connection member (64) at the piston rod (14) is changed in longitudinal direction thereof to adjust a compression ratio.
  2. Internal combustion engine according to claim 1, wherein the position of the con rod connection member (64) at the piston rod (14) is adjustable in longitudinal direction thereof by rotating the piston rod (14) around its longitudinal axis.
  3. Internal combustion engine according to claim 1, wherein
    the con rod connection member (64) comprises a female thread (76) engaged with a male thread (74) formed on the outer side of the piston rod (14), and
    the position of the con rod connection member (64) at the piston rod (14) is changeable in longitudinal direction thereof by rotating the piston rod (14) relative to the con rod connection member (64).
  4. Internal combustion engine according to claim 1, wherein
    the con rod connection member (64) comprises a guide groove (122), into which a guide projection (120) or guide bolt formed on the outer side of the piston rod (14) engages, and
    the guide groove (122) is configured such that the position of the con rod connection member (64) at the piston rod (14) is changeable in longitudinal direction thereof by rotating the piston rod (14) relative to the con rod connection member (64).
  5. Internal combustion engine according to claim 1, wherein
    the con rod connection member (64) comprises a contact region (130) on the side facing the piston, the surface of which facing the piston rod (14) is disposed in different planes perpendicular to the longitudinal direction of the piston rod (14),
    the piston rod (14) comprises a contact region (126) on the side facing the con rod connection member (64), the surface of which facing the con rod connection member (64) is disposed in different planes perpendicular to the longitudinal direction of the piston rod (14),
    the contact region (126) of the piston rod (14) and the contact region (130) of the con rod connection member (64) are configured to at least partially contact each other and are adjusted to each other such that, by rotating the piston rod (14) relative to the con rod connection member (64), the degree of overlap of the contact regions or the engagement of the contact regions with each other is changeable to adjust the position of the con rod connection member (64) at the piston rod (14) in longitudinal direction thereof.
  6. Internal combustion engine according to any one of claims 2 to 5, further comprising
    an adjustment rod (80) to adjust the compression ratio,
    wherein
    the end of the piston rod (14) facing away from the piston (12) is formed in a hollow manner, and
    the adjustment rod (80) protrudes into the hollow end of the piston rod (14) and is slidably supported in the piston rod (14) in the longitudinal direction of the adjustment rod (80) and in a rotation-proof manner around the longitudinal axis such that a rotation of the adjustment rod (80) around its longitudinal axis results in a rotation of the piston rod (14) relative to the con rod connection member (64).
  7. Internal combustion engine according to claim 1, wherein
    the con rod connection member (64) comprises a female thread (76) engaged with a male thread (116) of a sleeve member (110) attached to the piston rod (14) rotatably around its longitudinal axis but not movably in longitudinal direction of the piston rod (14), and
    the position of the con rod connection member (64) at the piston rod (14) is changeable in longitudinal direction thereof by rotating the sleeve member (110) relative to the con rod connection member (64).
  8. Internal combustion engine according to claim 7, further comprising
    an adjustment rod (80) to adjust the compression ratio,
    wherein
    the end of the piston rod (14) facing away from the piston (12) is formed in a hollow manner, and
    the sleeve member (110) is attached on the hollow end of the piston rod (14) and is formed in a hollow manner, and
    the adjustment rod (80) protrudes into the hollow end of the piston rod (14) and is slidably supported in the sleeve member (110) in the longitudinal direction of the adjustment rod (80) and in a rotation-proof manner around the longitudinal axis such that a rotation of the adjustment rod (80) around its longitudinal axis results in a rotation of the sleeve member (110) relative to the con rod connection member (64).
  9. Internal combustion engine according to claim 6 or 8, wherein the adjustment rod (80) is rotatable by an actuator (88).
  10. Internal combustion engine according to any one of claims 6, 8, or 9, wherein at least the part of the adjustment rod (80) sliding in the piston rod (14) or in the sleeve member (110) in longitudinal direction comprises an outer shape, which is not rotationally symmetric in a cross-section to the longitudinal direction of the adjustment rod, over a length, which is larger or equal to the stroke of the piston (12), with constant cross-section perpendicular to the longitudinal direction in longitudinal direction.
  11. Internal combustion engine according to any one of claims 6, 8, 9 or 10, wherein the adjustment rod (80) is guided by a crank case wall (45) while sealing and is rotationally driven outside of the crank case and/or
    the adjustment rod (80) comprises a rotationally symmetric cross-section perpendicular to the longitudinal direction in a certain area.
  12. Internal combustion engine according to any one of the preceding claims, wherein the piston rod (14) is hollow starting from its lower end over a length, which is larger or equal to the stroke of the piston (12).
  13. Internal combustion engine according to any one of the preceding claims, wherein
    the piston rod (14) is linearly movably passed through an opening (16) in a separation wall (18) of the cylinder (10) disposed below the piston (12) while sealing, and
    between the piston (12) and the separation wall (18), a fresh charge chamber (24) is disposed, from which compressed fresh air is supplyable to the working chamber (20).
  14. Internal combustion engine according to any one of the preceding claims, wherein the piston rod (14) is rigidly attached to the piston.
EP16784788.8A 2015-10-16 2016-10-17 Internal combustion engine with double crank drive and variable compression ratio Active EP3362645B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015013489.2A DE102015013489A1 (en) 2015-10-16 2015-10-16 Internal combustion engine with double crank drive and variable compression
PCT/EP2016/001714 WO2017063751A1 (en) 2015-10-16 2016-10-17 Internal combustion engine with double crank drive and variable compression ratio

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EP3362645A1 EP3362645A1 (en) 2018-08-22
EP3362645B1 true EP3362645B1 (en) 2019-12-04

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018100559B4 (en) * 2018-01-11 2021-10-28 Albert Raum Internal combustion engine with double crank drive and variable compression
DE102019122325B4 (en) * 2019-08-20 2021-05-27 Peter Pelz Reciprocating internal combustion engine with double crank drive and variable timing
DE102020120204A1 (en) 2020-07-30 2022-02-03 Peter Pelz Lifting device and diaphragm single-stroke motor
US11371424B1 (en) * 2021-07-28 2022-06-28 Jose Oreste Mazzini Piston external pin boss, longer combustion time, and power control valve
DE102022102029A1 (en) 2022-01-28 2023-08-03 Heinrich Schiller Crank mechanism of an engine or a compressor

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GB441666A (en) * 1934-05-25 1936-01-23 Louis De Monge Improvements in or relating to means for varying the cylinder clearance in internal combustion engines
US2229788A (en) * 1939-03-14 1941-01-28 Appleton Thomas Jay Dual crankshaft engine
DE19506963A1 (en) * 1995-02-28 1995-07-20 Viktor Hammermeister Variable stroke combustion engine
DE10019959A1 (en) * 2000-04-20 2001-10-25 Gerhard Klaiber Control method for IC engine uses variation in engine compression and alteration of crankshaft synchronization to change their relative positions
DE10247196B4 (en) 2002-08-12 2006-07-13 Peter Pelz Reciprocating internal combustion engine and piston for it
RU2262602C1 (en) * 2004-01-20 2005-10-20 Общество С Ограниченной Ответственностью "Мидера-К" Piston machine
DE102011120162A1 (en) 2011-12-06 2013-06-06 Fev Gmbh Internal combustion engine has cylinder crankcase, variable compression and multiple connecting rods supported at piston, where connecting rods are mounted on crankshaft, and gear is provided for adjusting crankshaft position
EP2792846A1 (en) * 2013-04-19 2014-10-22 Capricorn Automotive GmbH Double crankshaft combustion engine
CN203939575U (en) * 2014-05-15 2014-11-12 天津潜景技术咨询有限公司 Double-crankshaft variable compression ratio engine

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EP3362645A1 (en) 2018-08-22
DE102015013489A1 (en) 2017-04-20

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