WO2018188789A1 - Bielle réglable en longueur à unité cylindre-piston à dispositif anti-rotation - Google Patents

Bielle réglable en longueur à unité cylindre-piston à dispositif anti-rotation Download PDF

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Publication number
WO2018188789A1
WO2018188789A1 PCT/EP2018/000182 EP2018000182W WO2018188789A1 WO 2018188789 A1 WO2018188789 A1 WO 2018188789A1 EP 2018000182 W EP2018000182 W EP 2018000182W WO 2018188789 A1 WO2018188789 A1 WO 2018188789A1
Authority
WO
WIPO (PCT)
Prior art keywords
connecting rod
piston
cylinder
length
securing
Prior art date
Application number
PCT/EP2018/000182
Other languages
German (de)
English (en)
Inventor
Stefanie Rehm
Kai Arens
Maite HELLER
Zoltán Riba
Original Assignee
Iwis Motorsysteme Gmbh & Co. Kg
Avl List Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Iwis Motorsysteme Gmbh & Co. Kg, Avl List Gmbh filed Critical Iwis Motorsysteme Gmbh & Co. Kg
Priority to CN201880024271.7A priority Critical patent/CN110799739B/zh
Publication of WO2018188789A1 publication Critical patent/WO2018188789A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods

Definitions

  • the present invention relates to a length-adjustable connecting rod for an internal combustion engine having a first connecting rod, a second connecting rod and at least one cylinder-piston unit to adjust the first connecting rod relative to the second connecting rod
  • the cylinder-piston unit comprises a housing with a Cylinder bore, a longitudinally movably arranged in the cylinder bore adjusting piston, at least one provided in the cylinder bore pressure chamber and an anti-rotation comprises.
  • the invention relates to an internal combustion engine with such a length-adjustable connecting rod and the use of such a cylinder-piston unit for a length-adjustable connecting rod of an internal combustion engine.
  • the compression ratio can not be increased arbitrarily, since too high a compression ratio leads to unintentional spontaneous combustion of the combustion mixture due to pressure and temperature increase.
  • This early combustion not only leads to a troubled run and the so-called knocking in gasoline engines, but can also lead to component damage to the engine.
  • the risk of spontaneous combustion is lower, which, in addition to the influence of ambient temperature and pressure, also depends on the operating point of the engine. Accordingly, a higher compression ratio is possible in the partial load range. In the development of modern internal combustion engines, there are therefore efforts to adjust the compression ratio to the respective operating point of the engine.
  • VCR variable compression ratio
  • EP 1 426 584 A1 A discontinuous adjustment of the compression ratio for an internal combustion engine is shown in EP 1 426 584 A1, in which an eccentric connected to the piston pin makes it possible to adjust the compression ratio.
  • DE 10 2005 055 99 A1 likewise discloses the mode of operation of a length-variable connecting rod with which different compression ratios are made possible. The realization is also done here via an eccentric in the small connecting rod, which is fixed in position by two hydraulic cylinders with variable resistance.
  • WO 2013/092364 A1 describes a length-adjustable connecting rod for an internal combustion engine with two telescopically movable rod parts, wherein a rod part forms a cylinder and the second rod part forms a longitudinally displaceable piston element. Between the adjusting piston of the first rod part and the cylinder of the second rod part, a high-pressure space is formed, which is supplied via a hydraulic adjusting mechanism with an oil passage and an oil pressure-dependent valve with engine oil.
  • a similar length-adjustable connecting rod for an internal combustion engine with telescopically displaceable rod parts is shown in WO 2015/055582 A2.
  • the adjustable connecting rod length affects the compression volume in the combustion chamber, wherein the stroke volume is determined by the position of the crankshaft journal and the cylinder bore.
  • a short connecting rod leads to a lower compression ratio than a long connecting rod with otherwise identical geometrical dimensions, eg pistons, cylinder head, crankshaft, valve control etc.
  • the connecting rod length is hydraulically varied between two positions.
  • the entire connecting rod is made in several parts, wherein the change in length is effected by a telescopic mechanism which is adjustable by means of a double-acting hydraulic cylinder.
  • the small connecting rod eye is connected to a piston rod (telescopic rod part).
  • the associated adjusting piston is axially displaceably guided in a cylinder which is arranged in the connecting rod part with the large connecting rod eye, usually for receiving the crankshaft journal.
  • the adjusting piston separates the cylinder into two pressure chambers, an upper and a lower pressure chamber. These two pressure chambers are supplied via a hydraulic adjusting mechanism with engine oil, wherein its supply of engine oil via the lubricating oil supply of the connecting rod bearing takes place. For this purpose, an oil passage from the crankshaft journal over the connecting rod bearing to the connecting rod and there via the check valves of the adjusting mechanism in the pressure chambers is required.
  • the connecting rod is in the long position, there is no engine oil in the upper pressure chamber.
  • the lower pressure chamber is completely filled with engine oil.
  • the connecting rod is loaded alternately due to the gas and inertial forces on train and pressure.
  • a tensile force is absorbed by the mechanical contact with an upper stop of the adjusting piston.
  • the connecting rod length does not change as a result.
  • An applied compressive force is transmitted via the piston surface to the oil-filled lower pressure chamber. Since the check valve of this chamber prevents the oil return, the oil pressure increases, which can result in the lower pressure chamber very high dynamic pressures of well over 1,000 bar.
  • the connecting rod length does not change.
  • the connecting rod is hydraulically locked in this direction by the system pressure.
  • the lower pressure chamber is empty, the upper pressure chamber is filled with engine oil.
  • a tensile force causes a pressure increase in the upper pressure chamber.
  • a compressive force is absorbed by a mechanical stop.
  • the connecting rod length can be adjusted in two stages by emptying one of the two pressure chambers.
  • one of the two non-return valves in the inlet is bridged by the adjusting mechanism or an associated return channel is opened. Due to these return passages, engine oil can flow into the crankcase independently of the pressure difference between the pressure chamber and the supply device.
  • the respective check valve loses its effect accordingly.
  • the two return channels are opened and closed by a control valve, always exactly one return channel open, the other is closed.
  • the actuator for switching the two return channels is controlled hydraulically by the supply pressure here.
  • the patent AT 516 387 B1 relates to a length-adjustable connecting rod for an internal combustion engine with two telescopically movable rod parts.
  • the pressure chambers formed by the cylinder-piston unit are here at least partially formed by two bellows, which are each connected to one of the rod parts.
  • an anti-rotation is further provided here, which defines the angular position of the axis of the piston rod arranged in the small connecting rod to the axis of the large crankpin arranged in the crankshaft journal, these axes are usually parallel to each other.
  • the rotation is formed as a screw which engages through a hole in the housing of the cylinder-piston unit and the mounting sleeve of the upper bellows through into a slot of the first telescopic connecting rod and this thus ensures against rotation.
  • the locking screw thus extends through the housing into the cylinder bore and must be sealed depending on the design of the pressure chambers in the region of the housing in order to withstand the extremely high pressures.
  • the present invention is therefore an object of the invention to provide a length-adjustable connecting rod with a cylinder-piston unit, which allows a simple and secure rotation of the rotational angle positions of the piston pin and crankshaft journal.
  • the anti-rotation has a disc-like securing profile and at least one arranged on the disc-like securing profile securing arm, wherein the disc-like securing profile rotatably disposed on the first connecting rod and the securing arm extends in the longitudinal direction of the length-adjustable connecting rod displaceable along a guide on the second connecting rod ,
  • Such an anti-rotation device not only avoids an opening in the housing of the cylinder-piston unit and a correspondingly necessary sealing of the housing bore, but also avoids complex special cross-sectional profiles of the cylinder bore of the adjusting piston.
  • the adjusting piston and the cylinder bore can thus be produced in a cost-effective cylindrical manner despite an intended rotation lock.
  • the disc-like securing profile can be manufactured inexpensively separately from the other components of the cylinder-piston unit and fastened with a correspondingly simple construction, for example a positive arrangement, on the first connecting rod part.
  • the securing arm arranged on the securing profile can thereby extend along a guide on the second connecting rod part in the longitudinal direction, i. the telescoping direction of the mutually movable first and second connecting rod parts, while being prevented by the guide at a relative rotation.
  • at least two securing arms may be provided on the disc-like securing profile in order to minimize the remaining play of the angular position of the piston pin to the crankshaft journal.
  • the securing arms are arranged as evenly as possible on the circumference of the disc-like securing profile.
  • the at least one securing arm is resiliently connected to the disk-shaped securing profile, preferably in one piece with the disk-shaped securing profile.
  • a resilient securing arm facilitates in particular a simple and quick installation of the rotation, but also avoids damage to the rotation by static and dynamic loads of length-adjustable connecting rod in the • internal combustion engine.
  • the at least one securing arm itself may be resilient and / or resiliently connected to the disc-shaped securing profile.
  • the disk-shaped securing profile has a profiled opening, wherein the profiled opening engages in a complemantäres profile on the first connecting rod.
  • Such a profiled opening for example, with a non-circular, angular or toothed contour, in addition to a cost-effective production also allows a simple arrangement of the disc-shaped securing profile on a complementary profile on the first connecting rod and the inclusion of higher torsional forces.
  • the profiled opening on the disk-shaped securing profile can be open on one side. This allows a very quick subsequent assembly of the securing profile on the complementary profile of the first connecting rod part following the final assembly of the connecting rod.
  • the profiled opening may be formed closed to improve the anti-rotation arrangement, however, this requires during installation of the disc-shaped securing profile, a passage of the first connecting rod part through the profiled opening.
  • the first connecting rod part has a piston rod, wherein the piston rod has an at least one side, preferably two-sided, flattened groove in which the profiled opening of the disc-shaped securing profile is arranged rotationally fixed.
  • the piston rod which is arranged on an end face of the adjusting piston and extends through a pressure chamber of the cylinder-piston unit and through a rod bore in the housing cover into the crankcase of the internal combustion engine, allows a simple transmission of the movement of the adjusting piston in the cylinder bore for relative length adjustment between the first and second connecting rod part.
  • the piston rod allows the simple production of a complementary profile for the arrangement of the profiled opening of the disc-shaped securing profile, but also a passage of the piston rod through a closed-shaped opening. At the same time such a piston rod allows a secure sealing of the pressure chamber by means of a rod seal between the piston rod and the rod bore in the housing cover.
  • the disk-shaped securing profile can be formed as a stamped and bent part.
  • Such a stamped and bent part is a very cost-effective production of relatively thin, disk-shaped profiles, wherein the securing profile can be both annular or flange-shaped and also the corresponding securing arms in the punch-bending process can be formed and molded simultaneously with.
  • the guide is formed on the second connecting rod as a longitudinally extending groove.
  • Such an outside of the housing of the cylinder Piston unit lying groove can be both retrospectively bring in and provide without undercuts in the manufacture of the housing.
  • the guide may be provided as a bore in the housing or merely as a flattening on the housing.
  • the cylinder-piston unit has a cover which covers the cylinder bore, wherein arranged on the disc-like securing profile at least one securing arm laterally surrounds the lid in the longitudinal direction and extends along the guide provided on the housing.
  • the sealing of the cylinder bore of the lid also limits the adjacent pressure chamber in the cylinder bore. Since the at least one locking of the anti-rotation lock laterally engages the housing cover, one can dispense with a corresponding recess for the arrangement of the securing arm, so that the lid must be designed and manufactured only on its function to seal the cylinder bore and receiving a piston rod.
  • a preferred embodiment of the length-adjustable connecting rod provides that a sealing device is provided between the outer wall of the adjusting piston and the inner wall of the cylinder bore. This sealing device prevents even at high system pressures engagement of the adjusting piston in the respective filled with engine oil first or second pressure chamber, thus enabling the function of a length-adjustable connecting rod according to the invention safely and permanently implement.
  • the sealing device between the outer wall of the adjusting and the inner wall of the cylinder bore prevents engagement of the adjusting piston in the respective pressure chamber, even with a large force on the adjusting piston, especially in the compression and combustion process in the respective cylinder of the engine, thereby allowing a variable compression ratio in the cylinders and the achieved improvement in the efficiency of the internal combustion engine is not reduced by an engagement of the adjusting piston in the respective pressure chamber again.
  • a sealing device can both gap seals that constructively have a certain leakage, but also touching piston seals are used, which virtually prevent leakage, but are structurally complex and functionally more prone.
  • the gap of a gap seal should be at most 20 m, in particular at most 10 ⁇ , preferably even less.
  • an oil filter and / or a ⁇ labstreifer should be provided, the entry of large soot particles and chips from the engine oil in the pressure chambers and from there into the gap of the gap seal or between the sealing surfaces of Prevent piston seals. This can prevent that the particles present in the engine oil due to the high system pressures and the movement of the adjusting piston in the cylinder bore in the Seal device are registered.
  • wear on the inner wall of the cylinder bore and the outer wall of the adjusting or on the sealing surfaces of one or more piston seals can be prevented or significantly reduced, to ultimately prevent damage and failure of the cylinder-piston unit.
  • the adjusting piston of the cylinder-piston unit may be formed as a double-acting adjusting piston, wherein the adjusting piston arranged longitudinally movably in the cylinder bore limits the first pressure chamber on the first end side and on a second end side of the second pressure chamber.
  • a two-way adjusting piston allows the fixing of the piston rod both in the direction of a larger compression ratio and in the direction of a lower compression ratio with a single cylinder-piston unit. So it is the same adjusting, unlike in DE 10 2005 055 199 A1, used for bidirectional adjustment of the piston stroke, or the compression ratio.
  • a stepped piston can be used, by means of which the larger end face is held in its extended position with a corresponding pressurization, the connecting rod. Due to the prevailing force conditions in an internal combustion engine, the smaller end face usually suffices for fixing in the opposite direction.
  • the first connecting rod part can be connected to the adjusting piston of the cylinder-piston unit and the second connecting rod part can have the cylinder bore of the cylinder-piston unit.
  • the invention relates to the use of a cylinder-piston unit with anti-rotation for a length-adjustable connecting rod of an internal combustion engine with a first connecting rod and a second connecting rod, which are adjustable by means of the cylinder-piston unit comprising the cylinder-piston unit a housing with a cylinder bore, a piston arranged longitudinally movably adjusting and at least a first pressure chamber and a second pressure chamber in the cylinder bore for receiving engine oil, which are bounded on one side by the longitudinally movable adjusting piston, and a lid for sealing the cylinder bore.
  • a cylinder-piston unit for a length-adjustable connecting rod of an internal combustion engine allows the use of engine oil in the hydraulic adjusting mechanism despite the very small size of the cylinder-piston unit and the extremely high system pressure.
  • a disk-like securing profile and laterally extending securing arms allow the use of rotationally symmetrical components for the cylinder Piston unit and the entire length-adjustable connecting rod with corresponding advantages in view of the small available space and the material and production costs.
  • the invention relates to an internal combustion engine having at least one reciprocating piston and having at least one adjustable compression ratio in a cylinder and a length-adjustable connecting rod connected to the reciprocating piston according to the above-described embodiments.
  • all the reciprocating piston of an internal combustion engine are equipped with such a length-adjustable connecting rod, but this is not required.
  • the fuel economy of such an internal combustion engine can be considerable if the compression ratio is set in accordance with the respective operating state.
  • the cylinder-piston unit of the length-adjustable connecting rod can be connected to the engine oil of the internal combustion engine.
  • the pressures present in the engine oil circuit can be used to control a hydraulic adjusting mechanism.
  • soot particles and chips are present in the engine oil, which require insensitivity of the hydraulic adjusting mechanism and an associated sealing device.
  • the use of an anti-rotation device with a disc-like securing profile and at least one securing arm enables the proper function of the length-adjustable connecting rod by the secure parallel arrangement of the axes of the piston pin and the crankshaft journal.
  • a further modification provides that the system pressure of the engine oil in the first or second pressure chamber of the cylinder-piston unit is between 1,000 bar and 3,000 bar, preferably between 2,000 bar and 2,500 bar.
  • the limitation of the system pressure allows the safe structural design of the inner diameter of the cylinder bore and the wall thickness of the cylinder, and thus allows a safe structural design of the length-adjustable connecting rod according to the invention.
  • a control drive can be provided with at least one timing chain, a tensioning and / or guide rail, and / or a chain tensioner, which connects the crankshaft to the at least one camshaft of the internal combustion engine.
  • the timing drive is important because it can have a significant influence on the dynamic load of the engine and thus also on the length-adjustable connecting rod. Preferably, this is designed so that no excessive dynamic forces on the control be initiated.
  • a control drive can also be formed with a spur gear or a drive belt, for example a toothed belt, which is prestressed by means of a tensioning device with tensioning roller.
  • Fig. 1 shows a schematic cross section through an internal combustion engine
  • FIG. 2 is a schematic representation of the length-adjustable connecting rod of FIG. 1 in a partially sectioned illustration
  • FIG. 3a is a perspective view of a section of the length-adjustable connecting rod of FIG. 2 with anti-rotation
  • FIG. 3b shows a perspective view of the disc-like securing profile of the anti-twist device from FIG. 3a, FIG.
  • FIG. 4a is a perspective view of a section of the length-adjustable connecting rod of FIG. 2 with another embodiment of the anti-rotation device of FIG. 3a,
  • FIG. 4b is a perspective view of the disc-like securing profile of the rotation of Fig. 4a,
  • FIG. 5a is a perspective view of a section of the length-adjustable connecting rod of FIG. 2 with a further anti-rotation
  • FIG. 5b is a perspective view of the disc-like securing profile of the rotation of Fig. 5a
  • Fig. 6a is a perspective view of a section of the length-adjustable connecting rod of Fig. 2 with another embodiment of the anti-rotation of Fig. 5a and
  • Fig. 6b is a perspective view of the disc-like securing profile of the rotation of Fig. 6a.
  • a combustion engine (gasoline engine) 1 is shown in a schematic representation.
  • the internal combustion engine 1 has three cylinders 2.1, 2.2 and 2.3, in each of which a reciprocating piston 3.1, 3.2, 3.3 moves up and down.
  • the internal combustion engine 1 comprises a crankshaft 4, which is rotatably mounted by means of crankshaft bearings 5.1, 5.2, 5.3 and 5.4.
  • the crankshaft 4 is by means of the connecting rods 6.1, 6.2 and 6.3 respectively with the associated reciprocating piston 3.1, 3.2 and 3.3 connected.
  • the crankshaft 4 has an eccentrically arranged crankshaft journals 7.1, 7.2 and 7.3.
  • the large connecting rod 8.1, 8.2, and 8.3 is each mounted on the associated crankshaft journal 7.1, 7.2 and 7.3.
  • the small connecting rod 9.1, 9.2 and 9.3 are each mounted on a piston pin 10.1, 10.2 and 10.3 and so pivotally connected to the associated reciprocating 3.1, 3.2 and 3.3.
  • the terms small connecting rod 9.1, 9.2 and 9.3 and large connecting rod 8.1, 8.2 and 8.3 neither an absolute nor relative size assignment refer to, but they are only used to distinguish the components and assignment to the engine shown in Fig. 1. Accordingly, the dimensions of the diameter of the small connecting rods 9.1, 9.2 and 9.3 may be smaller, equal to or greater than the dimensions of the diameter of the large connecting rods 8.1, 8.2 and 8.3.
  • the crankshaft 4 is provided with a crankshaft sprocket 1 1 and coupled by means of a timing chain 12 with a Nockenwellenkettenrad 13.
  • the camshaft sprocket 13 drives a camshaft 14 with its associated cams for actuating the intake and exhaust valves (not shown in detail) of each cylinder 2.1, 2.2 and 2.3.
  • the slack side of the timing chain 12 is tensioned by means of a pivotally mounted clamping rail 15 which is pressed by means of a chain tensioner 16 to this.
  • the Switzerlandtrum the timing chain 12 can slide along a guide rail. The essential operation of this control drive including the fuel injection and ignition by spark plug is not explained in detail and assumed to be known.
  • the eccentricity of the crankshaft journals 7.1, 7.2 and 7.3 are significantly the stroke H «, especially if, as in the present case, the crankshaft 4 is arranged exactly centrally below the cylinders 2.1, 2.2 and 2.3.
  • the reciprocating piston 3.1 is shown in Fig. 1 in its lowermost position, while the reciprocating piston 3.2 is shown in its uppermost position. The difference results in the present case the stroke ⁇ .
  • the remaining height Hc gives the remaining compression height in cylinder 2.2.
  • the stroke volume V h and from the remaining compression height Hc is calculated, the compression volume V c .
  • the compression volume V c significantly depends on the design of the cylinder cover. From these volumes Vh and V c results in the compression ratio ⁇ .
  • the compression ratio ⁇ is calculated from the sum of the stroke volume V h and the compression volume V c divided by the compression volume V c .
  • Today's values for gasoline engines are between 10 and 14 for ⁇ .
  • the compression ratio ⁇ can be adjusted according to the invention, the connecting rods 6.1, 6.2 and 6.3 designed adjustable in their length. As a result, can be driven in the partial load range with a higher compression ratio than in the full load range.
  • the connecting rod 6.1 has a connecting rod head 17.1 with the said small connecting-rod eye 9.1, a first connecting rod part 18.1, which is guided telescopically in a second connecting rod part 19.1.
  • the relative movement of the first connecting rod part 18.1 in the longitudinal direction to the second connecting rod part 19.1 takes place by means of a cylinder-piston unit 20.1 with an adjusting piston 21.1. and a cylinder bore 22.1 and a sealing device 23.1 between the adjusting piston 21.1 and the cylinder bore 22.1.
  • a lower bearing shell 19b.1 is arranged, which surrounds the large connecting rod eye 8.1 together with the lower region of the second connecting rod part 19.1.
  • the lower bearing shell 19b.1 and the second Pleuelteil 19.1 are usually connected to each other by means of fastening means.
  • the piston rod 18a.1 at the lower end of the first connecting rod part 18.1 is connected to the adjusting piston 21.1, which is guided displaceably in the cylinder bore 22.1 of the second connecting rod part 19.1.
  • the second connecting rod part 19.1 has a cover 19a.1, through which the piston rod 18a.1 of the first connecting rod part 18.1 is guided and sealed.
  • the cover 19a.1 seals the cylinder bore 22.1 in total.
  • the adjusting piston 21.1 is designed as a stepped piston. Below the adjusting piston 21.1, a first pressure chamber 24.1 is formed with a circular cross-section and above the adjusting piston 21.1, an annular second pressure chamber 25.1 is formed. To change the connecting rod length by means of the movement of the adjusting piston 21.1 in the cylinder bore 22.1, a hydraulic adjusting mechanism 26.1 is provided. To the adjusting mechanism 26.1 includes a hydraulic circuit described in detail below, which provides correspondingly for an inlet and outlet of the engine oil in and out of the pressure chambers 24.1 and 25.1 and thus for a fixation of the actuated by means of the connecting rod 6.1 forces adjusting piston 21.1 ,
  • Other geometric dimensions are conceivable. Accordingly, here the wall thickness Dw of the housing in the region of the cylinder bore 22.1 results from the associated outer radius r a of the upper section of the second connecting rod part 19.1 minus the inner radius n of the cylinder bore 22.1.
  • the wall thickness Dw over the circumference of the second connecting rod 19.1 uniformly thick and the stresses in the material of the second Pleuelteils 19.1 evenly low, so that due to a relatively large piston diameter for the adjusting 21.1 occurring in the connecting rod 6.1 maximum system pressure within controllable limits remains.
  • the adjusting piston 21.1 of the cylinder-piston unit 20.1 is designed as a double-acting piston. Under a double-acting piston is generally understood a piston with differently oriented active surfaces.
  • a first end face 27.1 is annular and assigned to the first pressure chamber 24.1.
  • a second end face 28.1 is also annular in shape and associated with the second pressure chamber 25.1, wherein the first end face 27.1 and the second end face 28.1 may have the same or different surfaces.
  • the cylinder-piston unit 20.1 is operated with engine oil.
  • an oil supply channel 29.1 is connected to the large connecting rod eye 8.1 in connection, whereby engine oil can be supplied to the hydraulic adjusting mechanism 26.1 or, if appropriate, can also flow out of this in an alternative circuit.
  • a control valve 30.1 is provided to the oil supply channel 29.1 .
  • the engine oil conveyed by means of the gas and mass forces of the internal combustion engine 1 acting on the connecting rods 18.1, 19.1 passes into the first pressure chamber 24.1 via a first oil channel 31.1 and into the second pressure chamber 25.1 via a second oil channel 32.1.
  • a check valve and optionally an oil filter is provided in the first oil passage 31.1 before the first oil passage 31.1 opens into the first pressure chamber 24.1.
  • the outlet channel is equipped with a drain valve, which is closed when the engine oil flows in via the first oil passage 31.1 into the first pressure chamber 24.1.
  • the second oil channel 32.1 is constructed in accordance with the first oil channel 31.1 and has in the inflow direction of the engine oil in the second pressure chamber 25.1 after the control valve 30.1 a check valve, the branch of an outlet channel with drain valve (not shown) and then optionally an oil filter before the second oil channel 32.1 opens into the second pressure chamber 25.1.
  • the entire inflowing engine oil can be injected via an oil filter. be headed, in which larger soot particles and chips are filtered out of the engine oil and held.
  • the engine oil flowing into the pressure chambers 24.1 and 25.1 of the cylinder bore 22.1 is only slightly contaminated with contaminants, so that the sealing device 23.1 is exposed only slightly to wear between the outer wall of the adjusting piston 21.1 and the inner wall of the cylinder bore 22.1.
  • both the risk of severe damage to the surface of the sealing device 23.1 can be prevented, as well as improve the necessary life of the length-adjustable connecting rods 6.1.
  • the control valve 30.1 of the hydraulic adjusting mechanism 26.1 of the length-adjustable connecting rod 6.1 actively controls the exhaust valves associated with the first oil passage 31.1 and the second oil passage 32.1 in the branching exhaust passages to fix the position of the length-adjustable connecting rod 6.1, while the gas and mass-force driven intake of engine oil in the first oil passage 31.1 and the second oil passage 32.1 only passively via the control valve 30.1.
  • the drain valve in the other branch of the hydraulic adjusting mechanism 26.1 i.
  • control valve 30.1 preferably takes place with the pressure of the engine oil applied to the oil supply channel 29.1, whereby other, alternatively however also possible, electric, electronic, magnetic or mechanical activations of the control valve 30.1 or the drain valves can be avoided.
  • a rotation 33.1 is further provided, which is connected against rotation with the piston rod 18a.1 of the first connecting rod 18.1.
  • the rotation 33.1 comprises a disc-like securing profile 34.1, with which the anti-rotation 33.1 sits on the piston rod 18a.1, and two securing arms 35.1 extending from the disc-like securing profile 34.1 in the longitudinal direction of the connecting rod 6.1, ie axially parallel to the longitudinal axis of the connecting rod 6.1, in the direction extend the second connecting rod 19.1.
  • the two securing arms 35.1 abut against or engage in suitable guides 36.1 which extend in the longitudinal direction of the connecting rod 6.1 corresponding to the securing arms 35.1 in order to twist the large connecting rod 8.1 to the small connecting rod eye via the anti-rotation device 33.1 9.1, according to the rotational angle position of the piston pin 10.1 to the crankshaft journal 7.1, in a longitudinal movement of the first Connecting rod 18.1 against the second connecting rod 19.1 to prevent.
  • the arranged in the disc-like securing profile 34.1 securing arms 35.1 in the longitudinal direction laterally past the lid 19a.1 of the cylinder-piston unit 20.1, without cutting the maximum radial contour of the lid 19a.1.
  • the perspective partial view of the length-adjustable connecting rod 6.1 in Fig. 3a shows an embodiment of an anti-rotation 33.1 in a retracted position of the connecting rod 6.1.
  • this securing profile 34.1 is formed like a flange and provided with two holes 37.1 for attaching the two bolt-shaped securing arms 35.1.
  • the two arranged at the outer tips of the flange-shaped securing profile 34.1 securing arms 35.1 are received in a groove-shaped guide 36.1 on the outer circumference of the second connecting rod 19.1 and overlap in the longitudinal direction of the lid 19a.1.
  • This opening 38.1 is formed closed and is accordingly threaded before the final assembly of the connecting rod 6.1 on the piston rod 18a.1 and fixed.
  • the bolt-shaped securing arms 35.1 need only be fixed in the final assembly of the connecting rod 6.1 in the holes 37.1 of the securing profile 34.1, for example by gluing, welding or pressing.
  • the opening 38.1 is formed in this embodiment with two flattened sides, but can also be polygonal or hexagonal shapes of the opening 38.1 apply. By profiling the opening 38.1, the anti-rotation 33.1 is rotatably connected to the piston rod 18a.1.
  • the anti-rotation device 33.1 in the perspective view of part of the connecting rod 6.1 in FIG. 4a shows a variant of the flange-shaped securing profile 34.1 from FIGS. 3a and 3b.
  • the disk-like securing profile 34.1 is provided with a profile opening 38.1 which is open towards one side.
  • this opening is 38.1 again provided with two flattened sides.
  • this profile opening 38.1 which is open towards one side, can be attached after a final assembly of the first connecting rod part 18.1 and the second connecting rod part 19.1 in a final assembly step.
  • the disk-like securing profile 34.1 with the opening 38.1 open to one side is laterally pushed onto a profile groove 39.1 of the piston rod 18a.1 and arranged correspondingly secured against rotation.
  • the bolt-shaped securing arms 35.1 are fixed in the holes 37.1 of the securing profile 34.1, whereby by means of the guide of the securing arms 35.1 in the groove-like guides 36.1 on the second connecting rod part 19.1 and the securing profile 34.1 captive on the piston rod 18a.1 is arranged.
  • the perspective view of a part of the connecting rod 6.1 in Fig. 5a shows another embodiment of the anti-rotation 33.1 for a length-adjustable connecting rod 6.1 according to the invention.
  • the securing profile 34.1 and the two lateral securing arms 35.1 are integrally formed as a stamped and bent part.
  • the disk-like securing profile 34.1 is substantially annular in shape with two laterally arranged bent securing arms 35.1 which engage in a corresponding guide 36.1 on the outer circumference of the second connecting rod part 19.1 or rest on the guide 36.1.
  • the securing arms may be formed resiliently 35.1 to easily overlap laterally over the lid 19a.1 at a mounting of the first connecting rod 18.1 with the second connecting rod 19.1 and can be safely guided by the guide 36.1.
  • the profiled opening 38.1 of this securing profile 34.1 shown in detail in FIG. 5b is again closed and formed with two flattened sides. Accordingly, this securing profile 34.1 is also arranged on the piston rod 18a.1 prior to the final assembly and connected with it against rotation.
  • the profile opening 38.1 of the securing profile 34.1 of FIG. 5b may be open towards one side, see FIG. 6b.
  • This securing profile 34.1 can in turn be pushed after the final assembly of the connecting rod 6.1 to a corresponding profile 39.1 on the piston rod 18a.1, see also Fig. 6a.
  • the integrally formed with the securing profile 34.1 securing arms 35.1 have to be easily bent to the arrangement on the guides 36.1 on the outer circumference of the second connecting rod 19.1 and positioned accordingly.
  • the anti-rotation device 33.1 may also have a second securing profile 34.1, which is arranged in opposite directions to a first securing profile 34.1 on the profile groove 39.1 of the piston rod 18a.1 and preferably connected to the first disk-like securing profile 34.1.

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

Abstract

La présente invention concerne une bielle réglable en longueur, destinée à un moteur à combustion interne, comprenant une première partie de bielle, une deuxième partie de bielle et au moins une unité cylindre-piston pour régler la première partie de bielle par rapport à la deuxième partie de bielle. L'unité cylindre-piston comprend un boîtier pourvu d'un alésage de cylindre, un piston disposé dans l'alésage du cylindre de manière à pouvoir se déplacer longitudinalement et au moins une chambre de pression prévue dans l'alésage de cylindre et un dispositif anti-rotation. Le dispositif anti-rotation destiné à fixer la position angulaire en rotation de l'axe de piston par rapport au tourillon de vilebrequin est disposé au niveau de la première partie de bielle et s'étend avec au moins un bras de fixation dans la direction longitudinale le long d'un guide au niveau de la deuxième partie de bielle. En outre, l'invention concerne un moteur à combustion interne équipé d'une telle bielle réglable en longueur et l'utilisation d'une telle unité cylindre-piston pour une bielle réglable en longueur d'un moteur à combustion interne.
PCT/EP2018/000182 2017-04-10 2018-04-10 Bielle réglable en longueur à unité cylindre-piston à dispositif anti-rotation WO2018188789A1 (fr)

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CN201880024271.7A CN110799739B (zh) 2017-04-10 2018-04-10 具有带防扭转部的缸-活塞单元的长度能调节的连杆

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DE102017107706.5 2017-04-10
DE102017107706.5A DE102017107706A1 (de) 2017-04-10 2017-04-10 Längenverstellbare Pleuelstange mit einer Zylinder-Kolben-Einheit mit Verdrehsicherung

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AT522976B1 (de) * 2020-03-13 2021-04-15 Avl List Gmbh GROß-BRENNKRAFTMASCHINE

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AT519799A3 (de) 2019-02-15
AT519799B1 (de) 2019-08-15
CN110799739A (zh) 2020-02-14
DE102017107706A1 (de) 2018-10-11
CN110799739B (zh) 2021-08-31
AT519799A2 (de) 2018-10-15

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