EP2764228B1 - Method for the variable adjustment of a compression ratio of a combustion chamber of an internal combustion engine - Google Patents

Method for the variable adjustment of a compression ratio of a combustion chamber of an internal combustion engine Download PDF

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Publication number
EP2764228B1
EP2764228B1 EP20120756109 EP12756109A EP2764228B1 EP 2764228 B1 EP2764228 B1 EP 2764228B1 EP 20120756109 EP20120756109 EP 20120756109 EP 12756109 A EP12756109 A EP 12756109A EP 2764228 B1 EP2764228 B1 EP 2764228B1
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EP
European Patent Office
Prior art keywords
piston
relative
piston pin
pin
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20120756109
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German (de)
French (fr)
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EP2764228A1 (en
Inventor
Dieter Nowak
Tilmann RÖMHELD
Michael Wagenplast
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mercedes Benz Group AG
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Daimler AG
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Publication of EP2764228A1 publication Critical patent/EP2764228A1/en
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Publication of EP2764228B1 publication Critical patent/EP2764228B1/en
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Classifications

    • 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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke

Definitions

  • the invention relates to a method for variably setting a compression ratio of a combustion chamber of an internal combustion engine according to the preamble of patent claim 1.
  • the DE 10 2009 048 172 A1 discloses a piston for a variable compression ratio internal combustion engine having a first piston part and a second piston part.
  • the piston parts are coupled to form an at least first, with a pressure medium, in particular a pressurized fluid, acted upon and variable in volume chamber relative to each other movable.
  • at least one switchable valve device is arranged on the inside on a piston skirt of the piston, by means of which a volume of the pressure medium in the first chamber is adjustable.
  • the WO2010 / 124971 shows a device for modifying the piston kinematics of an internal combustion engine having at least one piston reciprocating in a cylinder, which is connected via a piston pin pivotally connected to a connecting rod, wherein the piston pin rotatably in at least one piston pin bearing of the piston, as well as in a connecting rod bearing Connecting rod is mounted, wherein the piston pin in at least one bearing portion of the piston pin bearing and / or the connecting rod bearing has an eccentric, and wherein the piston pin is rotatable by a rotating device.
  • the rotary device is formed by a torsion spring and that the piston pin against the force of the torsion spring from a rest position in at least one pressure limiting position is rotatable.
  • connection consists of an at least over a part of its longitudinal extension eccentrically designed piston pin.
  • a rotational movement of the piston pin causes a change in a compression ratio of the internal combustion engine and is made possible or prevented by a switchable blocking element.
  • the compression ratio is assigned to the combustion chamber by means of a device Piston adjusted or adjusted.
  • the piston is coupled via respective connecting portions with a piston pin.
  • the piston can be connected to a connecting rod of the internal combustion engine.
  • the piston pin is received in the respective connecting areas, for example in the piston. Likewise, the piston pin is at least partially added to the connecting rod. Due to the articulated coupling of the piston via the piston pin with the connecting rod, the piston can be coupled in an articulated manner to a crankshaft of the internal combustion engine rotatably mounted relative to the crankcase in a crankcase about an axis of rotation. Thus, translational movements of the piston in the combustion chamber relative to the combustion chamber can be converted in a rotational movement of the crankshaft about the axis of rotation.
  • a rotation of the piston pin assigned to the device is effected for setting the compression ratio.
  • the piston pin has at least one eccentric element arranged eccentrically with respect to the at least one connecting region of the piston pin, via which the piston pin is to be connected to the connecting rod.
  • the inventive method thus enables a simple, uncomplicated and cost and space-saving adjustment of the compression ratio.
  • the piston thus has a particularly advantageous noise behavior (NVH behavior).
  • NVH behavior noise behavior
  • the internal combustion engine with the variably adjustable compression ratio on a particularly high share of equal parts to the conventional internal combustion engine.
  • the method according to the invention also enables the very rapid adjustment of the compression ratio, so that the compression ratio can be adapted to different operating points of the internal combustion engine within only a short time.
  • the internal combustion engine can be operated efficiently over a particularly long period of time with the demand-based compression ratio, which benefits an efficient and fuel-efficient operation of the internal combustion engine with only low emissions.
  • At least one locking element of the device held on the piston pin is moved from a blocking position preventing the rotation to a rotation enabling position relative to the piston pin and relative to the piston.
  • the rotation of the piston pin takes place relative to the piston as a result of centrifugal and / or inertial forces of the piston moving in the combustion chamber and / or as a result of pressure forces in the combustion chamber.
  • active actuators for rotating the piston pin relative to the piston are not provided and are not required.
  • the rotation of the piston pin relative to the piston is rather passive. This keeps the weight and complexity of the internal combustion engine low, so that it has a particularly high functional performance safety.
  • crankcase assigned to the combustion chamber and the piston by means of at least one actuating element opposite at least one further space adjoining the crank chamber, in particular crank space, the crankcase is sealed. This takes place in such a way that the actuating element is adjusted from a first position into a second position sealing the crank chamber in comparison to the first position against the further space.
  • the actuator is, for example, a Schmierölabweiser in the crankcase.
  • the lubricating oil deflector is switchable and at least substantially gas-tight, so that the lubricating oil deflector can at least substantially seal the crank chamber.
  • At least one ventilation opening of the crank chamber can be at least essentially locked and, by contrast, released by means of the adjusting element. In the second position of the actuating element, the ventilation opening is blocked relative to the first position of the actuating element and thus connected at least substantially gas-tight, resulting in increasing the pressure in the crank chamber of the first position.
  • the adjusting element moves automatically from the second to the first position when the pressure in the crank chamber exceeds a threshold value.
  • the automatic adjustment of the actuating element is for example realized in such a way that a spring element cooperating with the actuating element is provided.
  • the actuator is held under Federkraftbeetzschung by the spring element in the second position. If the pressure in the crank chamber reaches or exceeds the predefinable threshold value, then the actuating element is displaced from the second position into the first position by the pressure against the spring force application by the spring element. In the first position, the crank chamber can be vented, so that the pressure in the crank chamber is reduced. Thus, the pressure in the crank chamber drops below the threshold value, the actuator is adjusted under Federkraftbeetzschung by the spring element back into its position in which the crank chamber is sealed compared to the first position against the other room.
  • the pressure in the crank chamber can be adapted as required for the adjustment or adjustment of the compression ratio and controlled, in particular regulated.
  • a balance shaft in particular a Lanchester mass balance
  • the Internal combustion engine is used as a shift drum to avoid an undesirably high pressure in the crankcase. This also allows the demand-based adjustment of the pressure in the crankcase.
  • the Fig. 1 and 2 show a piston pin 10 of a piston assembly 12 ( Fig. 3 ), via which a piston 14 of the piston assembly with a connecting rod 16 of a combustion engine designed as a reciprocating internal combustion engine is to be coupled articulated.
  • the internal combustion engine comprises a crankshaft 18 which is rotatably mounted in a crankcase about an axis of rotation 20 relative to the crankcase.
  • the crankshaft 18 includes a crank pin on which the connecting rod 16 is articulated via a large connecting rod.
  • the connecting rod 16 further comprises a small connecting rod eye, in which the piston pin 10 is partially received.
  • the piston pin 10 is coupled to the piston 14 via respective connection portions 22.
  • the connecting regions 22 of the piston pin 10 are formed by an outer peripheral surface of the piston pin 10, wherein the connecting portions are formed at least substantially in the form of a right circular cylinder.
  • the connecting regions 22 are accommodated at least in regions in respective receiving openings 26 of the piston 14, which are designed as passage openings in the present case.
  • the piston pin 10 is indirectly connected to the piston 14.
  • the piston assembly 12 comprises a piston pin bushing 28, in which the right connection portion 22 of the piston pin 10 is arranged.
  • the piston pin bushing 28 is received in the corresponding receiving opening 26.
  • the piston pin bushing 28 acts as a stop for the piston pin 10 and allows easy mounting of the piston pin 10 on or in the piston 14th
  • the piston pin 10 has an eccentric element 23, which is formed at least substantially in the form of a straight circular cylinder and is arranged eccentrically relative to the connecting regions 22.
  • the longitudinal central axis of the eccentric element is offset perpendicularly to the respective, coaxially arranged longitudinal central axes of the connecting regions 22.
  • the piston pin 10 is pivotally connected to the connecting rod 16.
  • the piston 14 is pivotally coupled to the connecting rod 16.
  • the one indicated by a direction arrow 30 longitudinal extension piston pin 10 has a receiving opening 32 which is formed for example as a passage opening.
  • the receiving opening 32 extends at least substantially perpendicular to the longitudinal extent (direction arrow 30) of the piston pin 10th
  • a locking element in the form of a locking bolt 34 is received in the receiving opening 32.
  • the locking pin 34 is guided in the receiving opening 32 perpendicular to the longitudinal extent of the piston pin 10 relative to the piston pin 10 slidably.
  • a device 36 of the piston assembly 12 are assigned. By means of the device 36, it is possible to adjust the compression ratio of the piston assembly 12 associated cylinder of the internal combustion engine variable.
  • the device 36 also includes a control in the form of a spool 38.
  • the spool 38 is held on the piston 14 and displaceable relative to the piston 14 and relative to the piston pin 10 between two positions.
  • the spool 38 is displaceable only between the two positions. In the spool 38 is thus a so-called bistable control piston.
  • first position of the spool 38 this is held by a first magnet.
  • the first magnet is arranged on the piston 14.
  • the spool 38 is held by a second magnet, wherein the second magnet is held on the piston 14.
  • a sleeve 44 of the device 36 can be seen, in which the spool 38 is slidably received.
  • a movement of the locking bolt 34 between a release position and a locking position of the locking bolt 34 can be effected or prevented or locked.
  • the displacement of the spool 38 between its two positions can in turn be done by means of an actuator, such as an electromagnet or by means of oil pressure.
  • the spool 38 is moved by means of oil pressure.
  • the piston 14 in its piston skirt 40 two opposing through holes 42.
  • the through holes 42 pass through the piston skirt 40 and thus an outer peripheral side surface of the piston 14 completely.
  • the passage openings are followed by grooves 43 which extend in the axial direction of the piston 14 and which are connected to the passage openings 42. In other words, the grooves 43 open into the passage openings.
  • the adjustment of the compression ratio is in particular based on the Fig. 8a - e to recognize.
  • Lubricating oil of the internal combustion engine is injected into the grooves 43 and into the through-holes 42 via an impingement element 46, for example an oil-injection nozzle, while the piston 14 moves in the cylinder.
  • an impingement element 46 for example an oil-injection nozzle
  • the control with the lubricating oil is carried out over 150 ° crank angle of the crankshaft 18, wherein the application, ie the activations of the spool 38 at a rotational position of the crankshaft 18 according to Fig. 8b begins and at a further rotational position of the crankshaft 18 according to Fig. 8e ends.
  • each acted upon with lubricating oil end opposite other corresponding end face of the spool 38 is not acted upon by lubricating oil, which is ensured for example by mutually locked switching valves.
  • the spool 38 is displaced in the direction of the other end face, which is not acted upon by lubricating oil.
  • an oil spray nozzle 47 can be seen, by means of which the piston 14 is sprayed with lubricating oil and thus can be cooled.
  • the biasing element 46 is arranged in the cylinder bore of the cylinder. In other words, the application or the control of the spool 38 takes place from outside the piston 14 via the cylinder bore and thus from outside the piston 14 ago.
  • the grooves 43 which may also be formed as elongated holes serve to receive the lubricating oil via the rotation of the crankshaft 18 and thus over the translational movement of the piston 14 in the cylinder and guide the lubricating oil to the through holes 42 and over to the spool 38th ,
  • the spool 38 serves for the so-called pilot control of lubricating oil of the internal combustion engine, by means of which the locking bolt 34 is moved between at least one release position and at least one locking position of the locking bolt 34.
  • the lubricating oil for adjusting the locking bolt 34 is transferred via bearings of the crankshaft 18 on the crankcase to the crankshaft 18 and via appropriate channels on to the connecting rod 16. From the connecting rod 16, the lubricating oil flows to an outer circumferential side circumferentially completely circumferential first groove 48 of the piston pin 10. From the first groove 48, the lubricating oil flows through at least one corresponding connecting channel to a second groove 50 of the piston pin 10, which in the circumferential direction of the piston pin 10 on the outer circumference just as completely revolving. From the second groove 50, the lubricating oil can flow to corresponding channels 56, 58 in the piston 14.
  • the lubricating oil can flow through the first channel 56 or the second channel 58, too get the locking pin 34, and move it.
  • the channels 56, 58 are integrated directly into the piston 14, that is formed by walls of the piston 14 and limited. The exiting at the spool 38 from the passage opening 42 when switching oil can be used for cooling.
  • the connecting channel of the grooves 48, 50 must ensure the pressure build-up behind the locking bolt and should therefore have no unnecessary leakage to the outside.
  • the Fig. 5 shows the spool 38 in its first position.
  • the locking pin 34 is initially in its blocking position in which he on the side of - based on the image plane of Fig. 5 - Right groove 43 cooperates with the piston 14 and prevents rotation of the piston pin 10 relative to the piston 14.
  • the locking pin 34 is partially received in the receiving opening 32 and partially in a arranged on the side of the right groove 43 first receptacle in the piston 14.
  • the first channel 56 in the piston 14 can be supplied with lubricating oil.
  • a supply of the second channel 58 in the piston 14 with lubricating oil is prevented by the spool 38.
  • the lubricating oil flows in the first position of the spool 38 from the connecting rod 16 via the grooves 48, 50 in the right first channel 56 and from there to a right in this position, the piston pin 10 first end face 52 of the locking bolt 34th Dies means that the first end face 52 is acted upon by the lubricating oil.
  • the lubricating oil now presses the locking pin 34 in the radial direction of the piston pin 10 in the receiving opening 32 and so from its blocking position to its release position.
  • a spring element may be arranged, via which the locking pin 34 is supported on the piston pin 10 under Federkraftbeetzung.
  • the spring force is directed in the radial direction of the piston pin 10 to the outside. This means that then the lubricating oil pushes the locking bolt 34 against the spring force into the receiving opening 32 and out of the first receptacle. If the locking pin 34 is completely moved out of the first receptacle, it is in its release position. In the release position, the locking pin 34, a relative rotation of the piston pin 10 to the piston 14 is not prevent more.
  • the piston pin 10 can then be rotated in the small connecting rod eye of the connecting rod 16 about the longitudinal center axis of the eccentric element 23 relative to the connecting rod 16 and in the receiving openings 26 about the respective longitudinal center axes of the connecting portions 22 relative to the piston 14.
  • Such a relative rotation is effected for example by mass and / or centrifugal and / or prevailing in the cylinder and acting on the piston 14 compressive forces due to the eccentric arrangement of the eccentric element 23 relative to the connecting portions 22.
  • the piston 14 is pressed in the direction of the axis of rotation 20. Due to the eccentric arrangement of the eccentric element 23 relative to the connecting regions 22, the distance between the piston 14 and the axis of rotation is reduced or the distance between the piston 14 and a combustion chamber roof of the cylinder is increased, whereby the compression ratio ( ⁇ ) is reduced.
  • the distance between the piston 14 and the rotation axis 20 is increased by pulling the piston 14 away from the rotation axis. This sets a higher compression ratio.
  • the pressing and pulling of the piston 14 causes via its coupling with the piston pin 10, the rotation of the piston pin 10 relative to the piston 14 and relative to the connecting rod 16 when the locking pin 34 is in its release position.
  • the piston pin 10 rotates by 180 degrees - with respect to the image plane of Fig. 5 - to the left, ie counterclockwise. If the receiving opening 32 is formed as a passage opening, the lubricating oil then acts on the first right side channel 56 on a first end face 52 facing away from the second end face 54 of the locking bolt 34 and pushes the locking pin 34 together with the spring force of the spring element in the radial direction out of the Receiving opening 32 addition. The locking pin 34 is thus moved from its release position back to its blocking position. Then, the locking pin 34 acts on the side of - relative to the image plane of Fig. 5 - Left groove 43 with the piston 14 together, so that then again a rotation of the piston pin 10 is prevented relative to the piston 14. The piston pin 10 is locked.
  • the locking pin 34 is for example partially received in the receiving opening 32 and partially in a arranged on the side of the left groove 43 second receptacle in the piston 14.
  • the lubricating oil is not only used to move the locking bolt 34 but also to lock this in the locked position and thus also fulfills a locking function.
  • the supply of the right-hand first channel 56 is ended with lubricating oil.
  • the left second passage 58 is supplied with lubricating oil.
  • the lubricating oil can then flow from the connecting rod 16 via the grooves 48, 50 in the left second channel 58 and from there to the left in the current position of the piston pin first end face 52. This means that now again the first end face 52 (not the second end face 54) is acted upon by lubricating oil.
  • the lubricating oil pushes the locking pin 34 back into its release position.
  • the piston pin can turn 180 degrees again, only this time to the right, so clockwise. This in turn is not caused by an active actuator but essentially passive by the centrifugal and / or mass and / or pressure forces.
  • Analogous to the rotation of the piston pin 10 relative to Relative rotation of the eccentric bushings to the piston 14 by means of the further control spool can then be effected to the piston 14 by displacing the spool 38, thereby displacing the piston 14 relative to the axis of rotation 20 and relative to the combustion chamber roof.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

Die Erfindung betrifft ein Verfahren zum variablen Einstellen eines Verdichtungsverhältnisses eines Brennraums einer Verbrennungskraftmaschine gemäß dem Oberbegriff von Patentanspruch 1.The invention relates to a method for variably setting a compression ratio of a combustion chamber of an internal combustion engine according to the preamble of patent claim 1.

Die DE 10 2009 048 172 A1 offenbart einen Kolben für eine ein veränderbares Kompressionsverhältnis aufweisende Verbrennungskraftmaschine, mit einem ersten Kolbenteil und einem zweiten Kolbenteil. Die Kolbenteile sind unter Ausbildung einer zumindest ersten, mit einem Druckmedium, insbesondere einem Druckfluid, beaufschlagbaren und in ihrem Volumen veränderbaren Kammer relativ zueinander bewegbar gekoppelt. Dabei ist vorgesehen, dass zumindest eine schaltbare Ventileinrichtung innenseitig an einem Kolbenhemd des Kolbens angeordnet ist, mittels welcher ein Volumen des Druckmediums in der ersten Kammer einstellbar ist.The DE 10 2009 048 172 A1 discloses a piston for a variable compression ratio internal combustion engine having a first piston part and a second piston part. The piston parts are coupled to form an at least first, with a pressure medium, in particular a pressurized fluid, acted upon and variable in volume chamber relative to each other movable. It is provided that at least one switchable valve device is arranged on the inside on a piston skirt of the piston, by means of which a volume of the pressure medium in the first chamber is adjustable.

Die WO2010/124971 zeigt eine Einrichtung zur Modifikation der Kolbenkinematik einer Brennkraftmaschine mit zumindest einem in einem Zylinder hin- und hergehenden Kolben, welcher über einen Kolbenbolzen schwenkbar mit einer Pleuelstange verbunden ist, wobei der Kolbenbolzen drehbar sowohl in zumindest einem Kolbenbolzenlager des Kolbens, als auch in einem Pleuellager der Pleuelstange gelagert ist, wobei der Kolbenbolzen in zumindest einem Lagerbereich des Kolbenbolzenlagers und/oder des Pleuellagers einen Exzenter aufweist, und wobei der Kolbenbolzen durch eine Drehvorrichtung drehbar ist. Es ist vorgesehen, dass die Drehvorrichtung durch eine Drehfeder gebildet ist und dass der Kolbenbolzen entgegen der Kraft der Drehfeder aus einer Ruhelage in zumindest eine Druckbegrenzungslage verdrehbar ist.The WO2010 / 124971 shows a device for modifying the piston kinematics of an internal combustion engine having at least one piston reciprocating in a cylinder, which is connected via a piston pin pivotally connected to a connecting rod, wherein the piston pin rotatably in at least one piston pin bearing of the piston, as well as in a connecting rod bearing Connecting rod is mounted, wherein the piston pin in at least one bearing portion of the piston pin bearing and / or the connecting rod bearing has an eccentric, and wherein the piston pin is rotatable by a rotating device. It is provided that the rotary device is formed by a torsion spring and that the piston pin against the force of the torsion spring from a rest position in at least one pressure limiting position is rotatable.

Weiterhin zeigen die EP 219 634 A2 , die EP 297 904 A2 , die US 4 687 348 A , die US 5 427 185 A und die DE 10 2005 055199 A1 Verbindungen zwischen Kolben und Pleuelstangen bei Brennkraftmaschinen, wobei die Verbindung aus einem zumindest über einen Teil seiner Längserstreckung exzentrisch ausgeführten Kolbenbolzen besteht. Eine Drehbewegung des Kolbenbolzens bewirkt eine Veränderung eines Verdichtungsverhältnisses der Brennkraftmaschine und wird durch ein schaltbares Sperrelement ermöglicht oder verhindert.Furthermore, the show EP 219 634 A2 , the EP 297 904 A2 , the US 4,687,348 A , the US 5 427 185 A and the DE 10 2005 055199 A1 Connections between pistons and connecting rods in internal combustion engines, wherein the connection consists of an at least over a part of its longitudinal extension eccentrically designed piston pin. A rotational movement of the piston pin causes a change in a compression ratio of the internal combustion engine and is made possible or prevented by a switchable blocking element.

Es ist Aufgabe der vorliegenden Erfindung ein Verfahren zum variablen Einstellen eines Verdichtungsverhältnisses eines Brennraums einer Verbrennungskraftmaschine bereitzustellen, mittels welchem eine besonders einfache Einstellung bzw. Verstellung des Verdichtungsverhältnisses ermöglicht ist.It is an object of the present invention to provide a method for variably setting a compression ratio of a combustion chamber of an internal combustion engine, by means of which a particularly simple adjustment of the compression ratio is made possible.

Diese Aufgabe wird durch ein Verfahren mit den Merkmalen des Patentanspruchs 1 gelöst. Vorteilhafte Ausgestaltungen mit zweckmäßigen und nicht-trivialen Weiterbildungen der Erfindung sind in den übrigen Ansprüchen angegeben.This object is achieved by a method having the features of patent claim 1. Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the remaining claims.

Bei einem solchen Verfahren zum variablen Einstellen eines Verdichtungsverhältnisses eines Brennraums, insbesondere eines Zylinders, einer beispielsweise als Hubkolben-Verbrennungskraftmaschine ausgebildeten Verbrennungskraftmaschine wird das Verdichtungsverhältnis mittels einer Einrichtung eines dem Brennraum zugeordneten Kolbens eingestellt bzw. verstellt. Der Kolben ist über jeweilige Verbindungsbereiche mit einem Kolbenbolzen gekoppelt. Über den Kolbenbolzen kann der Kolben mit einem Pleuel der Verbrennungskraftmaschine verbunden werden.In such a method for variably setting a compression ratio of a combustion chamber, in particular a cylinder, of an internal combustion engine designed, for example, as a reciprocating internal combustion engine, the compression ratio is assigned to the combustion chamber by means of a device Piston adjusted or adjusted. The piston is coupled via respective connecting portions with a piston pin. About the piston pin, the piston can be connected to a connecting rod of the internal combustion engine.

Der Kolbenbolzen ist in den jeweiligen Verbindungsbereichen beispielsweise in dem Kolben aufgenommen. Ebenso ist der Kolbenbolzen zumindest bereichsweise in den Pleuel aufgenommen. Durch die gelenkige Kopplung des Kolbens über den Kolbenbolzen mit dem Pleuel kann der Kolben gelenkig mit einer in einem Kurbelgehäuse um eine Drehachse relativ zu dem Kurbelgehäuse drehbar gelagerten Kurbelwelle der Verbrennungskraftmaschine gekoppelt werden. So können translatorische Bewegungen des Kolbens in dem Brennraum relativ zu dem Brennraum in einer rotatorische Bewegung der Kurbelwelle um die Drehachse umgewandelt werden.The piston pin is received in the respective connecting areas, for example in the piston. Likewise, the piston pin is at least partially added to the connecting rod. Due to the articulated coupling of the piston via the piston pin with the connecting rod, the piston can be coupled in an articulated manner to a crankshaft of the internal combustion engine rotatably mounted relative to the crankcase in a crankcase about an axis of rotation. Thus, translational movements of the piston in the combustion chamber relative to the combustion chamber can be converted in a rotational movement of the crankshaft about the axis of rotation.

Erfindungsgemäß ist vorgesehen, dass zum Einstellen des Verdichtungsverhältnisses eine Drehung des der Einrichtung zugeordneten Kolbenbolzens bewirkt wird. Der Kolbenbolzen weist dabei wenigstens ein bezogen auf den zumindest einen Verbindungsbereich des Kolbenbolzens exzentrisch angeordnetes Exzenterelement auf, über das der Kolbenbolzen mit dem Pleuel zu verbinden ist.According to the invention, a rotation of the piston pin assigned to the device is effected for setting the compression ratio. In this case, the piston pin has at least one eccentric element arranged eccentrically with respect to the at least one connecting region of the piston pin, via which the piston pin is to be connected to the connecting rod.

Wird das zumindest bereichsweise in dem Pleuel aufgenommene und zumindest im Wesentlichen die Form eines geraden Kreiszylinders aufweisende Exzenterelement um dessen Längsmittelachse relativ zu dem Pleuel gedreht und wird der in den Verbindungsbereichen des Kolbenbolzens und des Kolbens zumindest teilweise in dem Kolben aufgenommene Kolbenbolzen um die Längsmittelachse des zumindest im Wesentlichen die Form eines geraden Kreiszylinders aufweisenden Verbindungsbereichs des Kolbenbolzens relativ zum Kolben gedreht, so wird dadurch infolge der exzentrischen Anordnung des Exzenterelements zu dem Verbindungsbereich des Kolbenbolzens der Abstand des Kolbens von der Drehachse der Kurbelwelle sowie der Abstand des Kolbens von einem Brennraumdach des Brennraums in Längserstreckungsrichtung des Pleuels verändert. Dies geht einher mit der Veränderung des Verdichtungsverhältnisses des Brennraums. Das erfindungsgemäße Verfahren ermöglicht somit eine einfache, unkomplexe sowie kosten- und bauraumgünstige Verstellung des Verdichtungsverhältnisses. Zudem ist die Entstehung von unerwünschten Geräuschen bei dem Einstellen bzw. Verstellen des Verdichtungsverhältnisses vermieden. Der Kolben weist somit ein besonders vorteilhaftes Geräuschverhalten (NVH-Verhalten) auf. Darüber hinaus ist es möglich, eine herkömmliche Verbrennungskraftmaschine, bei der ein Verstellen des Verdichtungsverhältnisses nicht möglich ist, auf einfache und kostengünstige Weise mit der Einrichtung zu versehen und ohne oder mit nur geringfügigen Änderungen des Kolbens der herkömmlichen Verbrennungskraftmaschine zu einer Verbrennungskraftmaschine mit variablem Verdichtungsverhältnis zu ergänzen, bei welcher das erfindungsgemäßes Verfahren durchführbar ist. Dabei weist die Verbrennungskraftmaschine mit dem variabel einstellbaren Verdichtungsverhältnis einen besonders hohen Gleichteilanteil zu der herkömmlichen Verbrennungskraftmaschine auf.If the eccentric element accommodated in the connecting rod and at least substantially in the shape of a straight circular cylinder is rotated relative to the connecting rod about its longitudinal center axis, and the piston pin accommodated at least partially in the connecting areas of the piston pin and the piston becomes about the longitudinal center axis of the at least As a result of the eccentric arrangement of the eccentric element relative to the connecting region of the piston pin, the distance of the piston from the axis of rotation of the crankshaft and the distance of the piston from a combustion chamber roof of the combustion chamber in due to the shape of a straight circular cylinder having Lengthwise direction of the connecting rod changed. This is accompanied by the change in the compression ratio of the combustion chamber. The inventive method thus enables a simple, uncomplicated and cost and space-saving adjustment of the compression ratio. In addition, the emergence of unwanted noise in the adjustment or adjustment of the compression ratio is avoided. The piston thus has a particularly advantageous noise behavior (NVH behavior). Moreover, it is possible to provide a conventional internal combustion engine in which adjustment of the compression ratio is not possible to provide the device in a simple and inexpensive manner and to supplement it with a variable compression ratio internal combustion engine with little or no change in the piston of the conventional internal combustion engine in which the method according to the invention can be carried out. In this case, the internal combustion engine with the variably adjustable compression ratio on a particularly high share of equal parts to the conventional internal combustion engine.

Das erfindungsgemäße Verfahren ermöglicht auch die sehr schnelle Verstellung des Verdichtungsverhältnisses, so dass das Verdichtungsverhältnis innerhalb einer nur geringen Zeit an unterschiedliche Betriebspunkte der Verbrennungskraftmaschine angepasst werden kann. So kann die Verbrennungskraftmaschine über einen besonders langen Zeitraum effizient mit dem bedarfsgerechten Verdichtungsverhältnis betrieben werden, was zu einem effizienten und kraftstoffarmen Betrieb der Verbrennungskraftmaschine mit nur geringen Emissionen zugute kommt.The method according to the invention also enables the very rapid adjustment of the compression ratio, so that the compression ratio can be adapted to different operating points of the internal combustion engine within only a short time. Thus, the internal combustion engine can be operated efficiently over a particularly long period of time with the demand-based compression ratio, which benefits an efficient and fuel-efficient operation of the internal combustion engine with only low emissions.

Erfindungsgemäß ist vorgesehen, dass zum Bewirken der Drehung wenigstens ein an dem Kolbenbolzen gehaltenes Sperrelement der Einrichtung von einer die Drehung verhindernden Sperrstellung in eine die Drehung ermöglichende Freigabestellung relativ zu dem Kolbenbolzen und relativ zu dem Kolben bewegt wird. Dadurch erfolgt die Drehung des Kolbenbolzens relativ zu dem Kolben in Folge von Flieh- und/oder Massenkräften des sich im Brennraum bewegenden Kolbens und/oder in Folge von Druckkräften in dem Brennraum. Dies bedeutet, dass aktive Stellglieder zum Drehen des Kolbenbolzens relativ zum Kolben nicht vorgesehen und nicht vonnöten sind. Die Drehung des Kolbenbolzens relativ zum Kolben erfolgt vielmehr passiv. Dies hält das Gewicht und die Komplexität der Verbrennungskraftmaschine gering, so dass dieser eine besonders hohe Funktionserfüllungssicherheit aufweist.According to the invention, for effecting the rotation, at least one locking element of the device held on the piston pin is moved from a blocking position preventing the rotation to a rotation enabling position relative to the piston pin and relative to the piston. As a result, the rotation of the piston pin takes place relative to the piston as a result of centrifugal and / or inertial forces of the piston moving in the combustion chamber and / or as a result of pressure forces in the combustion chamber. This means that active actuators for rotating the piston pin relative to the piston are not provided and are not required. The rotation of the piston pin relative to the piston is rather passive. This keeps the weight and complexity of the internal combustion engine low, so that it has a particularly high functional performance safety.

Um diese passive Verstellung des Kolbens relativ zum Pleuel und damit die Verstellung des Verdichtungsverhältnisses zu unterstützen, ist vorgesehen, dass ein dem Brennraum und dem Kolben zugeordneter Kurbelraum des Kurbelgehäuses mittels wenigstens eines Stellelements gegenüber wenigstens einen sich an den Kurbelraum anschließenden weiteren Raum, insbesondere Kurbelraum, des Kurbelgehäuses abgedichtet wird. Dies erfolgt derart, dass das Stellelement von einer ersten Stellung in eine den Kurbelraum im Vergleich zu der ersten Stellung gegen den weiteren Raum abdichtende zweite Stellung verstellt wird. Durch die Abdichtung des Kurbelraums gegen den weiteren Raum wird der in dem Kurbelraum herrschende Druck erhöht, welcher die Verstellung des Kolbens relativ zum Pleuel verursacht.In order to support this passive adjustment of the piston relative to the connecting rod and thus the adjustment of the compression ratio, it is provided that a crank chamber of the crankcase assigned to the combustion chamber and the piston by means of at least one actuating element opposite at least one further space adjoining the crank chamber, in particular crank space, the crankcase is sealed. This takes place in such a way that the actuating element is adjusted from a first position into a second position sealing the crank chamber in comparison to the first position against the further space. By sealing the Crank space against the other space of the pressure prevailing in the crank chamber pressure is increased, which causes the adjustment of the piston relative to the connecting rod.

Das Stellelement ist beispielsweise ein Schmierölabweiser in dem Kurbelraum. Der Schmierölabweiser ist schaltbar und zumindest im Wesentlichen gasdicht ausgeführt, so dass der Schmierölabweiser den Kurbelraum zumindest im Wesentlichen abdichten kann.The actuator is, for example, a Schmierölabweiser in the crankcase. The lubricating oil deflector is switchable and at least substantially gas-tight, so that the lubricating oil deflector can at least substantially seal the crank chamber.

Ferner kann vorgesehen sein, dass mittels des Stellelements wenigstens eine Ventilationsöffnung des Kurbelraums zumindest im Wesentlichen versperrbar und demgegenüber freigebbar ist. In der zweiten Stellung des Stellelements ist die Ventilationsöffnung gegenüber der ersten Stellung des Stellelements versperrt und somit zumindest im Wesentlichen gasdicht geschaltet, was zur Erhöhung des Drucks in dem Kurbelraum der ersten Stellung führt.Furthermore, it can be provided that at least one ventilation opening of the crank chamber can be at least essentially locked and, by contrast, released by means of the adjusting element. In the second position of the actuating element, the ventilation opening is blocked relative to the first position of the actuating element and thus connected at least substantially gas-tight, resulting in increasing the pressure in the crank chamber of the first position.

Bei einer weiteren Ausführungsform der Erfindung ist vorgesehen, dass sich das Stellelement selbstständig von der zweiten in die erste Stellung verstellt, wenn der Druck in dem Kurbelraum einen Schwellenwert überschreitet. Dadurch kann ein unerwünscht hoher Druckaufbau in dem Kurbelraum vermieden werden.In a further embodiment of the invention, it is provided that the adjusting element moves automatically from the second to the first position when the pressure in the crank chamber exceeds a threshold value. As a result, an undesirably high pressure build-up in the crankcase can be avoided.

Die selbstständige Verstellung des Stellelements ist beispielsweise derart realisiert, dass ein mit dem Stellelement zusammenwirkendes Federelement vorgesehen ist. Das Stellelement ist dabei unter Federkraftbeaufschlagung durch das Federelement in der zweiten Stellung gehalten. Erreicht oder überschreitet der Druck in dem Kurbelraum den vorgebbaren Schwellenwert, so wird das Stellelement durch den Druck entgegen der Federkraftbeaufschlagung durch das Federelement von der zweiten Stellung in die erste Stellung verstellt. In der ersten Stellung kann der Kurbelraum entlüftet werden, so dass der Druck in dem Kurbelraum abgebaut wird. So sinkt der Druck in dem Kurbelraum unter dem Schwellenwert, so wird das Stellelement unter Federkraftbeaufschlagung durch das Federelement wieder in seine Stellung verstellt, in welcher der Kurbelraum im Vergleich zu ersten Stellung gegen den weiteren Raum abgedichtet ist.The automatic adjustment of the actuating element is for example realized in such a way that a spring element cooperating with the actuating element is provided. The actuator is held under Federkraftbeaufschlagung by the spring element in the second position. If the pressure in the crank chamber reaches or exceeds the predefinable threshold value, then the actuating element is displaced from the second position into the first position by the pressure against the spring force application by the spring element. In the first position, the crank chamber can be vented, so that the pressure in the crank chamber is reduced. Thus, the pressure in the crank chamber drops below the threshold value, the actuator is adjusted under Federkraftbeaufschlagung by the spring element back into its position in which the crank chamber is sealed compared to the first position against the other room.

Durch die Verstellung des wenigstens einen Stellelements kann der Druck in dem Kurbelraum bedarfsgerecht für die Einstellung bzw. Verstellung des Verdichtungsverhältnisses angepasst und angesteuert, insbesondere geregelt werden.By adjusting the at least one actuating element, the pressure in the crank chamber can be adapted as required for the adjustment or adjustment of the compression ratio and controlled, in particular regulated.

In einer weiteren vorteilhaften Ausführungsform ist vorgesehen, dass eine Ausgleichswelle, insbesondere eines Lanchester-Massenausgleich, der Verbrennungskraftmaschine als Schaltwalze genutzt wird, um einen unerwünscht hohen Druck in dem Kurbelraum zu vermeiden. Auch dadurch ist die bedarfsgerechte Einstellung des Drucks in dem Kurbelraum ermöglicht.In a further advantageous embodiment, it is provided that a balance shaft, in particular a Lanchester mass balance, the Internal combustion engine is used as a shift drum to avoid an undesirably high pressure in the crankcase. This also allows the demand-based adjustment of the pressure in the crankcase.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels sowie anhand der Zeichnung. Die vorstehend in der Beschreibung genannten Merkmale und Merkmalskombinationen sowie die nachfolgend in der Figurenbeschreibung genannten und/oder in den Figuren alleine gezeigten Merkmale und Merkmalskombinationen sind nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar, ohne den Rahmen der Erfindung zu verlassen.Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the description of the figures and / or in the figures alone can be used not only in the respectively specified combination but also in other combinations or in isolation, without the scope of To leave invention.

Die Zeichnung zeigt in:

Fig. 1
eine schematische Perspektivansicht eines Kolbenbolzens mit einem Sperrelement und einer Kolbenbolzenbuchse einer in der Fig. 3 gezeigten Kolbenanordnung;
Fig. 2
eine schematische Perspektivansicht des Kolbenbolzens gemäß Fig. 1;
Fig. 3
ausschnittsweise eine schematische Seitenansicht einer Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Zylinder einer Hubkolben-Verbrennungskraftmaschine, mit einem transparent dargestellten Kolben, der über den Kolbenbolzen gemäß den Fig. 1 und 2 mit einem Pleuel der Kolbenanordnung gelenkig gekoppelt ist, wobei die Kolbenanordnung eine Einrichtung umfasst, mittels welcher das Kompressionsverhältnis einstellbar ist;
Fig. 4
eine schematische Seitenansicht des Kolbens gemäß Fig. 3, wobei sich ein Steuerelement der Einrichtung in seiner ersten Stellung befindet;
Fig. 5
eine weitere schematische Seitenansicht des Kolbens gemäß Fig. 4;
Fig. 6
eine weitere schematische Seitenansicht des Kolbens gemäß den Fig. 4 und 5, wobei sich das Steuerelement in seiner zweiten Stellung befindet;
Fig. 7
eine weitere schematische Seitenansicht des Kolbens gemäß Fig. 6;
Fig. 8a - e
jeweils eine schematische Seitenansicht der Kolbenanordnung gemäß Fig. 3 während einer Hubbewegung in dem Zylinder, wobei das Kompressionsverhältnis verstellt wird;
Fig. 9
ausschnittsweise eine schematische Perspektivansicht des Kolbens gemäß Fig. 3;
Fig. 10
ausschnittsweise eine weiteres schematische Perspektivansicht des Kolbens gemäß Fig. 9;
Fig. 11
eine schematische Perspektivansicht des Kolbens gemäß den Fig. 9 und 10, wobei der Kolben transparent dargestellt ist; und
Fig. 12
ausschnittsweise eine schematische Perspektivansicht des Kolbens gemäß Fig. 11, wobei der Kolben transparent dargestellt ist.
The drawing shows in:
Fig. 1
a schematic perspective view of a piston pin with a locking element and a piston pin bushing one in the Fig. 3 shown piston assembly;
Fig. 2
a schematic perspective view of the piston pin according to Fig. 1 ;
Fig. 3
a schematic side view of a piston assembly for a variable compression ratio having cylinder of a reciprocating internal combustion engine, with a piston shown in phantom, via the piston pin according to the Fig. 1 and 2 is pivotally coupled to a connecting rod of the piston assembly, the piston assembly comprising means by which the compression ratio is adjustable;
Fig. 4
a schematic side view of the piston according to Fig. 3 with a control of the device in its first position;
Fig. 5
a further schematic side view of the piston according to Fig. 4 ;
Fig. 6
a further schematic side view of the piston according to the 4 and 5 with the control in its second position;
Fig. 7
a further schematic side view of the piston according to Fig. 6 ;
Fig. 8a - e
each a schematic side view of the piston assembly according to Fig. 3 during a stroke in the cylinder, the compression ratio being adjusted;
Fig. 9
a schematic perspective view of the piston according to FIG Fig. 3 ;
Fig. 10
a detail of another schematic perspective view of the piston according to Fig. 9 ;
Fig. 11
a schematic perspective view of the piston according to the Fig. 9 and 10 wherein the piston is shown transparent; and
Fig. 12
a schematic perspective view of the piston according to FIG Fig. 11 , wherein the piston is shown transparent.

Die Fig. 1 und 2 zeigen einen Kolbenbolzen 10 einer Kolbenanordnung 12 (Fig. 3), über welchen ein Kolben 14 der Kolbenanordnung mit einem Pleuel 16 einer als Hubkolben-Verbrennungskraftmaschine ausgebildeten Verbrennungskraftmaschine gelenkig zu koppeln ist. Wie in Zusammenschau mit den Fig. 8a-e zu erkennen ist, umfasst die Verbrennungskraftmaschine eine Kurbelwelle 18, welche in einem Kurbelgehäuse um eine Drehachse 20 relativ zu dem Kurbelgehäuse drehbar gelagert ist. Die Kurbelwelle 18 umfasst einen Hubzapfen, an dem das Pleuel 16 über ein großes Pleuelauge gelenkig gelagert ist. Das Pleuel 16 umfasst ferner ein kleines Pleuelauge, in welchem der Kolbenbolzen 10 bereichsweise aufgenommen ist.The Fig. 1 and 2 show a piston pin 10 of a piston assembly 12 ( Fig. 3 ), via which a piston 14 of the piston assembly with a connecting rod 16 of a combustion engine designed as a reciprocating internal combustion engine is to be coupled articulated. As in synopsis with the Fig. 8a-e can be seen, the internal combustion engine comprises a crankshaft 18 which is rotatably mounted in a crankcase about an axis of rotation 20 relative to the crankcase. The crankshaft 18 includes a crank pin on which the connecting rod 16 is articulated via a large connecting rod. The connecting rod 16 further comprises a small connecting rod eye, in which the piston pin 10 is partially received.

Der Kolbenbolzen 10 ist mit dem Kolben 14 über jeweilige Verbindungsbereiche 22 gekoppelt. Die Verbindungsbereiche 22 des Kolbenbolzens 10 sind durch eine außenumfangsseitige Mantelfläche des Kolbenbolzens 10 gebildet, wobei die Verbindungsbereiche zumindest im Wesentlichen in Form eines geraden Kreiszylinders ausgebildet sind. Zum Koppeln des Kolbenbolzens 10 mit dem Kolben 14 sind die Verbindungsbereiche 22 zumindest bereichsweise in jeweiligen, vorliegend als Durchgangsöffnungen ausgebildeten Aufnahmeöffnungen 26 des Kolbens14 aufgenommen.The piston pin 10 is coupled to the piston 14 via respective connection portions 22. The connecting regions 22 of the piston pin 10 are formed by an outer peripheral surface of the piston pin 10, wherein the connecting portions are formed at least substantially in the form of a right circular cylinder. For coupling the piston pin 10 with the piston 14, the connecting regions 22 are accommodated at least in regions in respective receiving openings 26 of the piston 14, which are designed as passage openings in the present case.

Über den - bezogen auf die Bildebene der Fig. 2 - rechten Verbindungsbereich 22 des Kolbenbolzens 10 ist der Kolbenbolzen 10 mittelbar mit dem Kolben 14 verbunden. Wie anhand der Fig. 1 erkennbar ist, umfasst die Kolbenanordnung 12 eine Kolbenbolzenbuchse 28, in welcher der rechte Verbindungsbereich 22 des Kolbenbolzens 10 angeordnet ist. Die Kolbenbolzenbuchse 28 ist in der korrespondierenden Aufnahmeöffnung 26 aufgenommen. Die Kolbenbolzenbuchse 28 fungiert dabei als Anschlag für den Kolbenbolzen 10 und ermöglicht eine einfache Montage des Kolbenbolzens 10 am bzw. im Kolben 14.
Der Kolbenbolzen 10 weist ein Exzenterelement 23 auf, welches zumindest im Wesentlichen in Form eines geraden Kreiszylinders ausgebildet und bezogen auf die Verbindungsbereiche 22 exzentrisch angeordnet ist. Dies bedeutet, dass die Längsmittelachse des Exzenterelements senkrecht zu den jeweiligen, koaxial zueinander angeordneten Längsmittelachsen der Verbindungsbereiche 22 versetzt ist. Über das Exzenterelement 23, welches in dem kleinen Pleuelauge des Pleuels 16 zumindest bereichsweise aufgenommen ist, ist der Kolbenbolzen 10 mit dem Pleuel 16 gelenkig verbunden. Somit ist der der Kolben 14 gelenkig mit dem Pleuel 16 gekoppelt. Infolge dieser gelenkigen Kopplung können translatorische Relativbewegungen des in einem Zylinder der Verbrennungskraftmaschine aufgenommenen Kolben s14 relativ zu dem Zylinder in eine rotatorische Bewegung der Kurbelwelle 18 um die Drehachse umgewandelt werden.About - related to the image level of Fig. 2 Right connecting portion 22 of the piston pin 10, the piston pin 10 is indirectly connected to the piston 14. As based on the Fig. 1 can be seen, the piston assembly 12 comprises a piston pin bushing 28, in which the right connection portion 22 of the piston pin 10 is arranged. The piston pin bushing 28 is received in the corresponding receiving opening 26. The piston pin bushing 28 acts as a stop for the piston pin 10 and allows easy mounting of the piston pin 10 on or in the piston 14th
The piston pin 10 has an eccentric element 23, which is formed at least substantially in the form of a straight circular cylinder and is arranged eccentrically relative to the connecting regions 22. This means that the longitudinal central axis of the eccentric element is offset perpendicularly to the respective, coaxially arranged longitudinal central axes of the connecting regions 22. About the eccentric element 23, which is at least partially received in the small connecting rod eye of the connecting rod 16, the piston pin 10 is pivotally connected to the connecting rod 16. Thus, the piston 14 is pivotally coupled to the connecting rod 16. As a result of this articulated coupling, translational relative movements of the piston s14 received in a cylinder of the internal combustion engine relative to the cylinder can be converted into a rotational movement of the crankshaft 18 about the axis of rotation.

Wie insbesondere der Fig. 2 zu entnehmen ist, weist der eine durch einen Richtungspfeil 30 angedeutete Längserstreckung aufweisenden Kolbenbolzen 10 eine Aufnahmeöffnung 32 auf, welche beispielsweise als Durchgangsöffnung ausgebildet ist. Die Aufnahmeöffnung 32 erstreckt sich dabei zumindest im Wesentlichen senkrecht zur Längserstreckung (Richtungspfeil 30) des Kolbenbolzens 10.How the particular Fig. 2 can be seen, the one indicated by a direction arrow 30 longitudinal extension piston pin 10 has a receiving opening 32 which is formed for example as a passage opening. The receiving opening 32 extends at least substantially perpendicular to the longitudinal extent (direction arrow 30) of the piston pin 10th

In der Aufnahmeöffnung 32 ist ein Sperrelement in Form eines Verriegelungsbolzens 34 aufgenommen. Der Verriegelungsbolzen 34 ist in der Aufnahmeöffnung 32 geführt senkrecht zur Längserstreckung des Kolbenbolzens 10 relativ zum Kolbenbolzen 10 verschiebbar. In Zusammenschau mit der Fig. 3 ist es ersichtlich, dass zumindest der Kolbenbolzen 10 und der Verriegelungsbolzen 34 einer Einrichtung 36 der Kolbenanordnung 12 zugeordnet sind. Mittels der Einrichtung 36 ist es möglich, das Kompressionsverhältnis des der Kolbenanordnung 12 zugeordneten Zylinders der Verbrennungskraftmaschine variabel einstellen zu können.In the receiving opening 32, a locking element in the form of a locking bolt 34 is received. The locking pin 34 is guided in the receiving opening 32 perpendicular to the longitudinal extent of the piston pin 10 relative to the piston pin 10 slidably. In conjunction with the Fig. 3 It can be seen that at least the piston pin 10 and the locking pin 34 of a device 36 of the piston assembly 12 are assigned. By means of the device 36, it is possible to adjust the compression ratio of the piston assembly 12 associated cylinder of the internal combustion engine variable.

Dazu umfasst die Einrichtung 36 auch ein Steuerelement in Form eines Steuerschiebers 38. Der Steuerschieber 38 ist an dem Kolben 14 gehalten und relativ zu dem Kolben 14 sowie relativ zu dem Kolbenbolzen 10 zwischen zwei Stellungen verschiebbar. Der Steuerschieber 38 ist dabei ausschließlich zwischen den beiden Stellungen verschiebbar. Bei dem Steuerschieber 38 handelt es sich somit um einen sogenannten bistabilen Steuerkolben.For this purpose, the device 36 also includes a control in the form of a spool 38. The spool 38 is held on the piston 14 and displaceable relative to the piston 14 and relative to the piston pin 10 between two positions. The spool 38 is displaceable only between the two positions. In the spool 38 is thus a so-called bistable control piston.

In einer insbesondere in den Fig. 4 und 5 gezeigten ersten Stellung des Steuerschiebers 38 ist dieser mittels eines ersten Magneten gehalten. Der erste Magnet ist dabei an dem Kolben 14 angeordnet. In der insbesondere in den Fig. 3, 6 und 7 gezeigten zweiten Stellung ist der Steuerschieber 38 mittels eines zweiten Magneten gehalten, wobei auch der zweite Magnet an dem Kolben 14 gehalten ist. Insbesondere in der Fig. 9 ist eine Hülse 44 der Einrichtung 36 zu erkennen, in welcher der Steuerschieber 38 verschiebbar aufgenommen ist.In a particular in the 4 and 5 shown first position of the spool 38 this is held by a first magnet. The first magnet is arranged on the piston 14. In particular in the Fig. 3 . 6 and 7 shown second position, the spool 38 is held by a second magnet, wherein the second magnet is held on the piston 14. Especially in the Fig. 9 is a sleeve 44 of the device 36 can be seen, in which the spool 38 is slidably received.

Durch Verschieben des Steuerschiebers 38 zumindest im Wesentlichen senkrecht zur Längserstreckung des Kolbenbolzens 10 zwischen seinen zwei Stellungen kann eine Bewegung des Verriegelungsbolzens 34 zwischen einer Freigabestellung und einer Sperrstellung des Verriegelungsbolzens 34 bewirkt oder verhindert bzw. verriegelt werden. Das Verschieben des Steuerschiebers 38 zwischen seinen beiden Stellungen kann wiederum mittels eines Stellglieds, beispielsweise eines Elektromagneten oder mittels Öldruck erfolgen. Vorliegend wird der Steuerschieber 38 mittels Öldruck verschoben.By moving the spool 38 at least substantially perpendicular to the longitudinal extent of the piston pin 10 between its two positions, a movement of the locking bolt 34 between a release position and a locking position of the locking bolt 34 can be effected or prevented or locked. The displacement of the spool 38 between its two positions can in turn be done by means of an actuator, such as an electromagnet or by means of oil pressure. In the present case, the spool 38 is moved by means of oil pressure.

Wie anhand der Fig. 9 bis 12 erkennbar ist, weist der Kolben 14 in seinem Kolbenhemd 40 zwei einander gegenüberliegende Durchgangsöffnungen 42 auf. Die Durchgangsöffnungen 42 durchsetzen das Kolbenhemd 40 und damit eine außenumfangseitige Mantelfläche des Kolbens 14 vollständig. An die Durchgangsöffnungen schließen sich Nuten 43 an, welche in axialer Richtung des Kolbens 14 verlaufen und welche mit den Durchgangsöffnungen 42 verbunden sind. Mit anderen Worten münden die Nuten 43 in die Durchgangsöffnungen.As based on the Fig. 9 to 12 can be seen, the piston 14 in its piston skirt 40 two opposing through holes 42. The through holes 42 pass through the piston skirt 40 and thus an outer peripheral side surface of the piston 14 completely. The passage openings are followed by grooves 43 which extend in the axial direction of the piston 14 and which are connected to the passage openings 42. In other words, the grooves 43 open into the passage openings.

Die Verstellung des Kompressionsverhältnisses ist insbesondere anhand der Fig. 8a - e zu erkennen. Über ein Beaufschlagungselement 46, beispielsweise eine Ölspritzdüse, wird Schmieröl der Verbrennungskraftmaschine in die Nuten 43 und in die Durchgangsöffnungen 42 eingespritzt, während sich der Kolben 14 im Zylinder bewegt. Dadurch wird der Steuerschieber 38 von einer seiner Stirnseiten her mit Schmieröl beaufschlagt, insbesondere druckbeaufschlagt. Die Ansteuerung mit dem Schmieröl erfolgt dabei über 150° Kurbelwinkel der Kurbelwelle 18, wobei die Beaufschlagung, d.h. die Ansteuerungen des Steuerschiebers 38 bei einer Drehstellung der Kurbelwelle 18 gemäß Fig. 8b beginnt und bei einer weiteren Drehstellung der Kurbelwelle 18 gemäß Fig. 8e endet. Die der jeweils mit Schmieröl beaufschlagten Stirnseite gegenüberliegende andere entsprechend Stirnseite des Steuerschiebers 38 wird nicht mit Schmieröl beaufschlagt, was beispielsweise durch gegenseitig verriegelte Schaltventile sichergestellt ist. Durch Beaufschlagen der einen Stirnseite des Steuerschiebers 38 wird der Steuerschieber 38 in Richtung der anderen Stirnseite verschoben, welche nicht mit Schmieröl beaufschlagt wird. In den Fig. 8a-e ist auch eine Ölspritzdüse 47 erkennbar, mittels welcher der Kolben 14 mit Schmieröl bespritzt und somit gekühlt werden kann.The adjustment of the compression ratio is in particular based on the Fig. 8a - e to recognize. Lubricating oil of the internal combustion engine is injected into the grooves 43 and into the through-holes 42 via an impingement element 46, for example an oil-injection nozzle, while the piston 14 moves in the cylinder. Thereby, the spool 38 from one of its end faces with lubricating oil acted upon, in particular pressurized. The control with the lubricating oil is carried out over 150 ° crank angle of the crankshaft 18, wherein the application, ie the activations of the spool 38 at a rotational position of the crankshaft 18 according to Fig. 8b begins and at a further rotational position of the crankshaft 18 according to Fig. 8e ends. The each acted upon with lubricating oil end opposite other corresponding end face of the spool 38 is not acted upon by lubricating oil, which is ensured for example by mutually locked switching valves. By applying the one end face of the spool 38, the spool 38 is displaced in the direction of the other end face, which is not acted upon by lubricating oil. In the Fig. 8a-e also an oil spray nozzle 47 can be seen, by means of which the piston 14 is sprayed with lubricating oil and thus can be cooled.

Das Beaufschlagungselement 46 ist dabei in der Zylinderlaufbahn des Zylinders angeordnet. Mit anderen Worten erfolgt die Beaufschlagung bzw. die Ansteuerung des Steuerschiebers 38 von außerhalb des Kolbens 14 über die Zylinderlaufbahn und somit von außerhalb des Kolbens 14 her.The biasing element 46 is arranged in the cylinder bore of the cylinder. In other words, the application or the control of the spool 38 takes place from outside the piston 14 via the cylinder bore and thus from outside the piston 14 ago.

Die Nuten 43, welche auch als Langlöcher ausgebildet sein können dienen dabei zur Aufnahme des Schmieröls über die Drehung der Kurbelwelle 18 und damit über die translatorische Bewegung des Kolbens 14 in dem Zylinder hinweg und leiten das Schmieröl zu den Durchgangsöffnungen 42 und darüber zu dem Steuerschieber 38.The grooves 43, which may also be formed as elongated holes serve to receive the lubricating oil via the rotation of the crankshaft 18 and thus over the translational movement of the piston 14 in the cylinder and guide the lubricating oil to the through holes 42 and over to the spool 38th ,

Der Steuerschieber 38 dient dabei zur sogenannten Vorsteuerung von Schmieröl der Verbrennungskraftmaschine, mittels welchem der Verriegelungsbolzen 34 zwischen wenigstens einer Freigabestellung und wenigstens einer Sperrstellung des Verriegelungsbolzens 34 bewegt wird.The spool 38 serves for the so-called pilot control of lubricating oil of the internal combustion engine, by means of which the locking bolt 34 is moved between at least one release position and at least one locking position of the locking bolt 34.

Das Schmieröl zum Verstellen des Verriegelungsbolzens 34 wird über Lagerstellen der Kurbelwelle 18 an dem Kurbelgehäuse an die Kurbelwelle 18 und über entsprechende Kanäle weiter an das Pleuel 16 übergeben. Von dem Pleuel 16 strömt das Schmieröl zu einer außenumfangseitig in Umfangsrichtung vollständig umlaufenden ersten Nut 48 des Kolbenbolzens 10. Von der ersten Nut 48 strömt das Schmieröl über wenigstens einen entsprechenden Verbindungskanal zu einer zweiten Nut 50 des Kolbenbolzens 10, welche in Umfangsrichtung des Kolbenbolzens 10 außenumfangseitig ebenso vollständig umlaufend verläuft. Von der zweiten Nut 50 kann das Schmieröl an entsprechende Kanäle 56, 58 in dem Kolben 14 überströmen. Je nach Stellung des Steuerschiebers 38 kann das Schmieröl den ersten Kanal 56 oder den zweiten Kanal 58 durchströmen, zu dem Verriegelungsbolzen 34 gelangen, und diesen bewegen. Die Kanäle 56, 58 sind dabei direkt in den Kolben 14 integriert, das heißt durch Wandungen des Kolbens 14 gebildet bzw. begrenzt. Das am Steuerschieber 38 aus der Durchgangsöffnung 42 beim Umschalten austretende Öl kann zur Kühlung eingesetzt werden. Der Verbindungskanal der Nuten 48, 50 muss den Druckaufbau hinter den Verriegelungsbolzen gewährleisten und sollte deswegen keine unnötige Leckage nach außen aufweisen.The lubricating oil for adjusting the locking bolt 34 is transferred via bearings of the crankshaft 18 on the crankcase to the crankshaft 18 and via appropriate channels on to the connecting rod 16. From the connecting rod 16, the lubricating oil flows to an outer circumferential side circumferentially completely circumferential first groove 48 of the piston pin 10. From the first groove 48, the lubricating oil flows through at least one corresponding connecting channel to a second groove 50 of the piston pin 10, which in the circumferential direction of the piston pin 10 on the outer circumference just as completely revolving. From the second groove 50, the lubricating oil can flow to corresponding channels 56, 58 in the piston 14. Depending on the position of the spool 38, the lubricating oil can flow through the first channel 56 or the second channel 58, too get the locking pin 34, and move it. The channels 56, 58 are integrated directly into the piston 14, that is formed by walls of the piston 14 and limited. The exiting at the spool 38 from the passage opening 42 when switching oil can be used for cooling. The connecting channel of the grooves 48, 50 must ensure the pressure build-up behind the locking bolt and should therefore have no unnecessary leakage to the outside.

Die Fig. 5 zeigt den Steuerschieber 38 in seiner ersten Stellung. Der Verriegelungsbolzen 34 befindet sich zunächst in seiner Sperrstellung, in der er auf Seiten der - bezogen auf die Bildebene der Fig. 5 - rechten Nut 43 mit dem Kolben 14 zusammenwirkt und eine Drehung des Kolbenbolzens 10 relativ zu dem Kolben 14 verhindert. Das heißt, dass der Kolbenbolzen 10 lediglich im kleinen Pleuelauge des Pleuels 16 um die Längsmittelachse des Exzenterelements 23 relativ zum Pleuel 16 gedreht werden kann, so dass der Kolben 14 über den Kolbenbolzen 10 gelenkig mit dem Pleuel 16 gekoppelt ist. Dazu ist der Verriegelungsbolzen 34 bereichsweise in der Aufnahmeöffnung 32 und bereichsweise in einer auf Seiten der rechten Nut 43 angeordneten ersten Aufnahme im Kolben 14 aufgenommen.The Fig. 5 shows the spool 38 in its first position. The locking pin 34 is initially in its blocking position in which he on the side of - based on the image plane of Fig. 5 - Right groove 43 cooperates with the piston 14 and prevents rotation of the piston pin 10 relative to the piston 14. This means that the piston pin 10 can only be rotated in the small connecting rod eye of the connecting rod 16 about the longitudinal central axis of the eccentric element 23 relative to the connecting rod 16, so that the piston 14 is pivotally coupled via the piston pin 10 to the connecting rod 16. For this purpose, the locking pin 34 is partially received in the receiving opening 32 and partially in a arranged on the side of the right groove 43 first receptacle in the piston 14.

In der ersten Stellung des Steuerschiebers 38 kann der erste Kanal 56 im Kolben 14 mit Schmieröl versorgt werden. Eine Versorgung des zweiten Kanals 58 im Kolben 14 mit Schmieröl ist durch den Steuerschieber 38 verhindert. Wie der Fig. 5 zu entnehmen ist, strömt das Schmieröl in der ersten Stellung des Steuerschiebers 38 vom Pleuel 16 über die Nuten 48, 50 in den rechten ersten Kanal 56 und von dort weiter zu einer in dieser Stellung des Kolbenbolzens 10 rechten ersten Stirnseite 52 des Verriegelungsbolzens 34. Dies bedeutet, dass die erste Stirnseite 52 von dem Schmieröl beaufschlagt wird. Das Schmieröl drückt nun den Verriegelungsbolzen 34 in radialer Richtung des Kolbenbolzens 10 in die Aufnahmeöffnung 32 hinein und so von seiner Sperrstellung in seine Freigabestellung.In the first position of the spool 38, the first channel 56 in the piston 14 can be supplied with lubricating oil. A supply of the second channel 58 in the piston 14 with lubricating oil is prevented by the spool 38. Again Fig. 5 can be seen, the lubricating oil flows in the first position of the spool 38 from the connecting rod 16 via the grooves 48, 50 in the right first channel 56 and from there to a right in this position, the piston pin 10 first end face 52 of the locking bolt 34th Dies means that the first end face 52 is acted upon by the lubricating oil. The lubricating oil now presses the locking pin 34 in the radial direction of the piston pin 10 in the receiving opening 32 and so from its blocking position to its release position.

In der Aufnahmeöffnung 32 kann ein Federelement angeordnet sein, über das der Verriegelungsbolzen 34 an dem Kolbenbolzen 10 unter Federkraftbeaufschlagung abgestützt ist. Die Federkraft ist dabei in radialer Richtung des Kolbenbolzens 10 nach außen gerichtet. Das heißt, dass dann das Schmieröl den Verriegelungsbolzens 34 entgegen der Federkraft in die Aufnahmeöffnung 32 hinein- und aus der ersten Aufnahme herausdrückt. Ist der Verriegelungsbolzen 34 vollständig aus der ersten Aufnahme bewegt, so befindet er sich in seiner Freigabestellung. In der Freigabestellung kann der Verriegelungsbolzen 34 eine Relativdrehung des Kolbenbolzens 10 zum Kolben 14 nicht mehr verhindern. Der Kolbenbolzen 10 kann dann im kleinen Pleuelauge des Pleuels 16 um die Längsmittelachse des Exzenterelements 23 relativ zum Pleuel 16 sowie in den Aufnahmeöffnungen 26 um die jeweiligen Längsmittelachsen der Verbindungsbereiche 22 relativ zum Kolben 14 gedreht werden.In the receiving opening 32, a spring element may be arranged, via which the locking pin 34 is supported on the piston pin 10 under Federkraftbeaufschlagung. The spring force is directed in the radial direction of the piston pin 10 to the outside. This means that then the lubricating oil pushes the locking bolt 34 against the spring force into the receiving opening 32 and out of the first receptacle. If the locking pin 34 is completely moved out of the first receptacle, it is in its release position. In the release position, the locking pin 34, a relative rotation of the piston pin 10 to the piston 14 is not prevent more. The piston pin 10 can then be rotated in the small connecting rod eye of the connecting rod 16 about the longitudinal center axis of the eccentric element 23 relative to the connecting rod 16 and in the receiving openings 26 about the respective longitudinal center axes of the connecting portions 22 relative to the piston 14.

Eine solche Relativdrehung wird beispielsweise durch Massen- und/oder Flieh- und/oder in dem Zylinder herrschende und auf den Kolben 14 wirkende Druckkräfte infolge der exzentrischen Anordnung des Exzenterelements 23 relativ zu den Verbindungsbereichen 22 bewirkt. Beim Verdichtungstakt des Kolbens 14 wird der Kolben 14 in Richtung der Drehachse 20 gedrückt. Aufgrund der exzentrischen Anordnung des Exzenterelements 23 relativ zu den Verbindungsbereichen 22 wird der Abstand zwischen dem Kolben 14 und der Drehachse verkleinert bzw. der Abstand zwischen dem Kolben 14 und einem Brennraumdach des Zylinders vergrößert, wodurch das Kompressionsverhältnis (ε) verringert wird. Während des Ansaugtrakts wird der Abstand zwischen dem Kolben 14 und der Drehachse 20 vergrößert, indem der Kolben 14 von der Drehachse weggezogen wird. Dadurch wird ein demgegenüber höheres Kompressionsverhältnis eingestellt. Das Drücken und Ziehen des Kolbens 14 bewirkt dabei über seine Kopplung mit dem Kolbenbolzen 10 das Drehen des Kolbenbolzens 10 relativ zum Kolben 14 bzw. relativ zum Pleuel 16, wenn sich der Verriegelungsbolzen 34 in seiner Freigabestellung befindet.Such a relative rotation is effected for example by mass and / or centrifugal and / or prevailing in the cylinder and acting on the piston 14 compressive forces due to the eccentric arrangement of the eccentric element 23 relative to the connecting portions 22. During the compression stroke of the piston 14, the piston 14 is pressed in the direction of the axis of rotation 20. Due to the eccentric arrangement of the eccentric element 23 relative to the connecting regions 22, the distance between the piston 14 and the axis of rotation is reduced or the distance between the piston 14 and a combustion chamber roof of the cylinder is increased, whereby the compression ratio (ε) is reduced. During the intake tract, the distance between the piston 14 and the rotation axis 20 is increased by pulling the piston 14 away from the rotation axis. This sets a higher compression ratio. The pressing and pulling of the piston 14 causes via its coupling with the piston pin 10, the rotation of the piston pin 10 relative to the piston 14 and relative to the connecting rod 16 when the locking pin 34 is in its release position.

Vorliegend dreht sich der Kolbenbolzen 10 um 180 Grad - bezogen auf die Bildebene der Fig. 5 - nach links, also entgegen dem Uhrzeigersinn. Ist die Aufnahmeöffnung 32 als Durchgangsöffnung ausgebildet, so wirkt dann das Schmieröl über den ersten rechten Kanal 56 auf eine der ersten Stirnseite 52 abgewandte zweite Stirnseite 54 des Verriegelungsbolzens 34 und drückt den Verriegelungsbolzen 34 zusammen mit der Federkraft des Federelements in radialer Richtung nach außen aus der Aufnahmeöffnung 32 hinaus. Der Verriegelungsbolzen 34 wird somit von seiner Freigabestellung wieder in seine Sperrstellung bewegt. Dann wirkt der Verriegelungsbolzen 34 auf Seiten der - bezogen auf die Bildebene der Fig. 5 - linken Nut 43 mit dem Kolben 14 zusammen, so dass dann wieder ein Verdrehen des Kolbenbolzens 10 relativ zum Kolben 14 verhindert ist. Der Kolbenbolzen 10 ist verriegelt.In the present case, the piston pin 10 rotates by 180 degrees - with respect to the image plane of Fig. 5 - to the left, ie counterclockwise. If the receiving opening 32 is formed as a passage opening, the lubricating oil then acts on the first right side channel 56 on a first end face 52 facing away from the second end face 54 of the locking bolt 34 and pushes the locking pin 34 together with the spring force of the spring element in the radial direction out of the Receiving opening 32 addition. The locking pin 34 is thus moved from its release position back to its blocking position. Then, the locking pin 34 acts on the side of - relative to the image plane of Fig. 5 - Left groove 43 with the piston 14 together, so that then again a rotation of the piston pin 10 is prevented relative to the piston 14. The piston pin 10 is locked.

Dazu ist der Verriegelungsbolzen 34 zum Beispiel bereichsweise in der Aufnahmeöffnung 32 und bereichsweise in einer auf Seiten der linken Nut 43 angeordneten zweiten Aufnahme im Kolben 14 aufgenommen. Das Schmieröl wird nicht nur zum bewegen des Verriegelungsbolzens 34 sondern auch zum Arretieren dieses in der Sperrstellung genutzt und erfüllt somit auch eine Arretierungsfunktion.For this purpose, the locking pin 34 is for example partially received in the receiving opening 32 and partially in a arranged on the side of the left groove 43 second receptacle in the piston 14. The lubricating oil is not only used to move the locking bolt 34 but also to lock this in the locked position and thus also fulfills a locking function.

Wird dann - davon ausgehend - der Steuerschieber 38 in seine zweite Stellung bewegt (verschoben), wird die Versorgung des rechten ersten Kanals 56 mit Schmieröl beendet. Dann wird der linke zweite Kanal 58 mit Schmieröl versorgt. Das Schmieröl kann dann von dem Pleuel 16 über die Nuten 48, 50 in den linken zweiten Kanal 58 und von dort weiter zu der in der jetzigen Stellung des Kolbenbolzens linken ersten Stirnseite 52 strömen. Dies bedeutet, dass nun wieder die erste Stirnseite 52 (nicht mehr die zweite Stirnseite 54) mit Schmieröl beaufschlagt wird. Das Schmieröl drückt den Verriegelungsbolzen 34 wieder in seine Freigabestellung.If the control slide 38 is then moved (shifted) to its second position (starting from this), the supply of the right-hand first channel 56 is ended with lubricating oil. Then, the left second passage 58 is supplied with lubricating oil. The lubricating oil can then flow from the connecting rod 16 via the grooves 48, 50 in the left second channel 58 and from there to the left in the current position of the piston pin first end face 52. This means that now again the first end face 52 (not the second end face 54) is acted upon by lubricating oil. The lubricating oil pushes the locking pin 34 back into its release position.

Nun kann sich der Kolbenbolzen wieder um 180 Grad drehen, nur diesmal nach rechts, also im Uhrzeigersinn. Dies wird wiederum nicht durch ein aktives Stellelement sondern im Wesentlichen passiv durch die Flieh- und/oder Massen- und/oder Druckkräfte bewirkt.Now, the piston pin can turn 180 degrees again, only this time to the right, so clockwise. This in turn is not caused by an active actuator but essentially passive by the centrifugal and / or mass and / or pressure forces.

Wie der Fig. 7 zu entnehmen ist, wird dann - nach der Drehung nach rechts - wieder die zweite Stirnseite 54 mit Schmieröl beaufschlagt, nur diesmal über den zweiten Kanal 58. Dadurch wird der Verriegelungsbolzen 34 zusammen mit der Federkraft in seine Sperrstellung auf Seiten der rechten Nut 43 gedrückt und mittels des Schmieröls arretiert. Der Kolbenbolzen 10 ist wieder verriegelt.Again Fig. 7 can be seen, then - after turning to the right - again the second end face 54 is acted upon by lubricating oil, only this time on the second channel 58. As a result, the locking pin 34 is pressed together with the spring force in its blocking position on the side of the right groove 43 and locked by means of the lubricating oil. The piston pin 10 is locked again.

Dies bedeutet, dass je nach Stellung des Steuerschiebers 38 und Drehstellung des Kolbenbolzens 10 in den Aufnahmeöffnungen 26 entweder die erste Stirnseite 52 oder die zweite Stirnseite 54 mit Schmieröl beaufschlagt und der Verriegelungsbolzen 34 entsprechend bewegt (verstellt) werden kann oder der Verriegelungsbolzen 34 wird arretiert, wodurch der Kolbenbolzen 10 in den Totpunkten des Kolbens 14 verriegelt wird.This means that depending on the position of the spool 38 and rotational position of the piston pin 10 in the receiving openings 26, either the first end face 52 or the second end face 54 loaded with lubricating oil and the locking pin 34 moves accordingly (adjusted) or the locking pin 34 is locked, whereby the piston pin 10 is locked in the dead centers of the piston 14.

Es ist ersichtlich, dass mittels des einen Steuerschiebers 38 zwei Stellungen des Kolbenbolzens 10 und somit zwei voneinander unterschiedliche Kompressionsverhältnisse (Verdichtungsverhältnisse) des Zylinders mittels der Kolbenanordnung 12 darstellbar sind. Es kann wenigstens ein weiterer Steuerschieber wie der Steuerschieber 38 vorgesehen sein, so dass mittels des weiteren Steuerschiebers zwei weitere Stellungen des Kolbenbolzens 10 und somit zwei weitere Kompressionsverhältnisse darstellbar sind. Zur Darstellung der zwei weiteren Kompressionsverhältnisse ist der Kolbenbolzen 10 zum Beispiel über seine zwei Verbindungsbereiche 22 unter Vermittlung jeweiliger Exzenterbuchsen mit dem Kolben gekoppelt. Dies bedeutet, dass der Kolben 14 über die Exzenterbuchsen an dem Kolbenbolzen 10 gelagert ist. Analog zu der Drehung des Kolbenbolzens 10 relativ zu dem Kolben 14 durch Verschieben des Steuerschiebers 38 können dann Relativdrehungen der Exzenterbuchsen zu dem Kolben 14 mittels des weiteren Steuerschiebers bewirkt werden, so dass dadurch der Kolben 14 relativ zur Drehachse 20 und relativ zum Brennraumdach verstellt wird.It can be seen that by means of the one spool 38 two positions of the piston pin 10 and thus two different compression ratios (compression ratios) of the cylinder by means of the piston assembly 12 can be displayed. It can be provided at least one further spool as the spool 38, so that by means of the further spool two other positions of the piston pin 10 and thus two further compression ratios can be displayed. To illustrate the two other compression ratios of the piston pin 10 is coupled, for example, via its two connecting portions 22 through the intermediary of respective eccentric bushings with the piston. This means that the piston 14 is mounted on the eccentric bushes on the piston pin 10. Analogous to the rotation of the piston pin 10 relative to Relative rotation of the eccentric bushings to the piston 14 by means of the further control spool can then be effected to the piston 14 by displacing the spool 38, thereby displacing the piston 14 relative to the axis of rotation 20 and relative to the combustion chamber roof.

Claims (4)

  1. Method for the variable adjustment of a compression ratio of a combustion chamber, in particular of a cylinder, of an internal combustion engine, wherein the compression ratio is adjusted by means of a device (36) of a piston (14) assigned to the combustion chamber, which piston (14) is coupled to a piston pin (10) via respective connecting regions (22, 24) for connecting the piston (14) to a connecting rod (16) of the internal combustion engine, wherein, for the adjustment of the compression ratio, a rotation of the piston pin (10), which is assigned to the device (36) and which comprises at least one eccentric element (23) arranged eccentrically relative to the connecting region (22) of the piston pin (10) for connecting the piston pins (10) to the connecting rod (16), is caused relative to the piston and wherein, for causing the rotation, at least one locking element (34) of the device (36), which is held on the piston pin (10) or on the piston, is moved from a locking position preventing the rotation into a release position allowing the rotation relative to the piston pin (10) and the piston (14), whereby the rotation of the piston pin (10) relative to the piston (14) is effected by centrifugal and/or inertial forces of the piston (14) moving in the combustion chamber and/or by compressive forces in the combustion chamber,
    characterised in that
    a crank chamber of a crankcase, which crank chamber is assigned to the combustion chamber and the piston (14) and in which at least some sections of a crankshaft of the internal combustion engine are located, is sealed against at least one further chamber of the crankcase, which adjoins the crank chamber, by means of at least one positioning element by moving the positioning element from a first position into a second position, in which the crank chamber is sealed against the further chamber relative to the first position.
  2. Method according to claim 1,
    characterised in that
    a lubricating oil deflector in the crank chamber is adjusted to act as the positioning element.
  3. Method according to claim 1 or 2,
    characterised in that
    a valve element which in the first position opens at least some sections of a vent opening of the crank chamber and in the second position closes at least some sections of the vent opening relative to the first position is adjusted.
  4. Method according to any of claims 1 to 3,
    characterised in that
    the positioning element automatically, in particular if subjected to a spring force by means of at least one spring element, moves from the second position into the first position if the pressure in the crank chamber exceeds a threshold value.
EP20120756109 2011-10-08 2012-09-04 Method for the variable adjustment of a compression ratio of a combustion chamber of an internal combustion engine Not-in-force EP2764228B1 (en)

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DE102011115415A DE102011115415A1 (en) 2011-10-08 2011-10-08 Method for variably setting a compression ratio of a combustion chamber of an internal combustion engine
PCT/EP2012/003698 WO2013050098A1 (en) 2011-10-08 2012-09-04 Method for the variable adjustment of a compression ratio of a combustion chamber of an internal combustion engine

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EP2764228B1 true EP2764228B1 (en) 2015-04-29

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Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103790717B (en) * 2014-01-26 2016-08-24 梁荣光 A kind of internal-combustion engine variable compression ratio device with self-locking structure
DE102014101929B4 (en) * 2014-02-17 2022-02-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft connecting rod and internal combustion engine
DE102014009484A1 (en) 2014-06-26 2015-12-31 Daimler Ag Actuator for variably adjusting at least one compression ratio of a cylinder of a reciprocating engine
DE102015014887A1 (en) 2015-11-17 2016-07-21 Daimler Ag Piston arrangement for a variable compression ratio having combustion chamber of an internal combustion engine
DE102015015882A1 (en) 2015-12-08 2016-08-11 Daimler Ag Piston arrangement for a variable compression ratio having combustion chamber of an internal combustion engine
DE102015015884A1 (en) 2015-12-08 2016-08-11 Daimler Ag Piston arrangement for a variable compression ratio having combustion chamber of an internal combustion engine
US10247093B2 (en) 2016-01-21 2019-04-02 Tenneco Inc. Variable compression ratio connecting rod
DE102016005950A1 (en) 2016-05-13 2017-02-16 Daimler Ag Piston assembly for a variable compression ratio having cylinder in the reciprocating engine
DE102016005973A1 (en) 2016-05-13 2017-02-16 Daimler Ag Piston assembly for a variable compression ratio cylinder having a reciprocating engine
KR20190126504A (en) * 2018-05-02 2019-11-12 현대자동차주식회사 Variable compression ratio engine
CN115234399B (en) * 2022-06-30 2024-03-22 中国第一汽车股份有限公司 Variable compression ratio mechanism, engine and vehicle

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0639912B2 (en) * 1983-12-29 1994-05-25 本田技研工業株式会社 Variable compression ratio control device for internal combustion engine for vehicle
CN85102778A (en) * 1985-04-01 1986-09-10 李文华 Automatically adjust the eccentric stiffener of compression ratio of internal-combustion engine
JPS61291736A (en) * 1985-06-20 1986-12-22 Toyota Motor Corp Eccentric bearing lock mechanism of compression ratio varying mechanism
JPH0216008Y2 (en) * 1985-07-05 1990-05-01
JPH0338424Y2 (en) * 1985-10-25 1991-08-14
US4864977A (en) * 1987-07-03 1989-09-12 Honda Giken Kogyo Kabushiki Kaisha Compression ratio-changing device for internal combustion engines
JPH01110845A (en) * 1987-07-03 1989-04-27 Honda Motor Co Ltd Variable compression ratio mechanism for internal combustion engine
US4864975A (en) * 1987-07-03 1989-09-12 Honda Giken Kogyo Kabushiki Kaisha Compression ratio-changing device for internal combustion engines
DE3807244C1 (en) * 1988-03-05 1989-03-23 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
JPH02163428A (en) * 1988-12-15 1990-06-22 Mazda Motor Corp Variable compression ratio mechanism for reciprocating engine
DE4041637C1 (en) * 1990-12-22 1992-04-09 Mtu Friedrichshafen Gmbh
CA2089815A1 (en) * 1993-02-18 1994-08-19 John F. E. Beattie Variable compression piston
EP1327753B1 (en) * 2001-12-24 2004-10-13 Visteon Global Technologies, Inc. Crank case ventilation system
DE102005055199B4 (en) * 2005-11-19 2019-01-31 FEV Europe GmbH Reciprocating internal combustion engine with adjustable variable compression ratio
JP4430654B2 (en) * 2005-12-28 2010-03-10 本田技研工業株式会社 Variable compression ratio device for internal combustion engine
JP4748591B2 (en) * 2006-03-29 2011-08-17 本田技研工業株式会社 Engine with breather device
US7546820B2 (en) * 2007-10-31 2009-06-16 Ford Global Technologies, Llc Variable compression ratio engine with lost motion coupling
JP2010038146A (en) * 2008-08-08 2010-02-18 Toyota Motor Corp Engine lubricating device
AT506470B1 (en) * 2009-04-29 2010-12-15 Avl List Gmbh DEVICE FOR MODIFYING THE PISTON KINEMATICS OF AN INTERNAL COMBUSTION ENGINE
DE102009045172B4 (en) 2009-09-30 2013-11-28 Faurecia Innenraum Systeme Gmbh Cable drive and window lift
KR101114378B1 (en) * 2009-10-06 2012-02-15 현대자동차주식회사 Variable compression ratio device

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DE102011115415A1 (en) 2013-04-11
WO2013050098A1 (en) 2013-04-11
US20150040870A1 (en) 2015-02-12
EP2764228A1 (en) 2014-08-13
CN103874836A (en) 2014-06-18

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