EP4453402A1 - Moteur diesel à injection haute pression et suralimentation et piston d'un moteur diesel - Google Patents

Moteur diesel à injection haute pression et suralimentation et piston d'un moteur diesel

Info

Publication number
EP4453402A1
EP4453402A1 EP22843806.5A EP22843806A EP4453402A1 EP 4453402 A1 EP4453402 A1 EP 4453402A1 EP 22843806 A EP22843806 A EP 22843806A EP 4453402 A1 EP4453402 A1 EP 4453402A1
Authority
EP
European Patent Office
Prior art keywords
piston
connecting rod
diesel engine
connection
less
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.)
Pending
Application number
EP22843806.5A
Other languages
German (de)
English (en)
Inventor
Stephan GESCHKE
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.)
Newgreen Ag
Newgreen American Inc
Original Assignee
Newgreen Ag
Newgreen American Inc
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 Newgreen Ag, Newgreen American Inc filed Critical Newgreen Ag
Publication of EP4453402A1 publication Critical patent/EP4453402A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/02—Pistons  having means for accommodating or controlling heat expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F01M2001/062—Crankshaft with passageways
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F01M2001/066—Connecting rod with passageways

Definitions

  • the invention relates to a diesel engine with high-pressure injection and supercharging and/or a compression temperature of more than 700° C. and/or a combustion temperature of more than 1 . 200 °C, one or more cylinders with a respective cylinder bore, a connecting rod associated with each respective cylinder and a piston arranged in the respective cylinder bore and having a top, a bottom and a peripheral surface with a nominal diameter, the top for receiving of compressive forces of a gas within the respective cylinder, the underside has a connecting rod receptacle with an undercut that acts in a tension and a compression direction, so that the connecting rod receptacle is set up for receiving a thickened portion of the respective connecting rod that corresponds to the receptacle and is pivotable about a pivot axis and the peripheral surface is designed for guiding the piston in the respective cylinder bore along a movement axis and with a seat for a piston ring for sealing the piston relative to the respective cylinder bore and a peripheral collar
  • the present invention relates to a corresponding piston of a diesel engine.
  • Combustion engines based on the diesel principle have undergone extensive development . Modern diesel engines are now operated using high-pressure fuel injection and charging using a compressor or turbocharger, for example, so that correspondingly high compression and combustion temperatures are achieved and the power output of the respective diesel engine has increased significantly compared to the fuel consumption. It also reduces emissions.
  • diesel engines are reaching their technical limits, for example with regard to heat management in the crank mechanism, in particular a piston. Heat generated during combustion cannot be dissipated completely or not quickly enough, so that pistons in modern diesel engines must have appropriate measures with regard to thermal expansion, such as ovality, and often a pronounced so-called top land, i.e.
  • the object of the invention is to improve the state of the art .
  • the task is solved by a diesel engine with high-pressure injection and supercharging and/or a compression temperature of more than 700 °C and/or a compression combustion temperature of more than 1 . 200 ° C, one or more cylinders with a respective cylinder bore, a connecting rod associated with each respective cylinder and a piston arranged in the respective cylinder bore and having a top, a bottom and a peripheral surface with a nominal diameter, the top for receiving of compressive forces of a gas within the respective cylinder, the underside has a connecting rod receptacle with an undercut that acts in a tension and a compression direction, so that the connecting rod receptacle is set up for receiving a thickened portion of the respective connecting rod that corresponds to the receptacle and is pivotable about a pivot axis and the peripheral surface is designed for guiding the piston in the respective cylinder bore along a movement axis and with a seat for a piston ring for sealing the piston relative to the respective cylinder bore and a peripheral collar
  • Such a diesel engine has a piston, which manages with a circumferential collar that is almost the same size or the same size in relation to the nominal diameter of the circumferential surface, since in the embodiment described a pronounced top land is no longer necessary in order to nagement of the diesel engine within tolerable limits.
  • a “diesel engine” is an internal combustion engine, in particular a reciprocating internal combustion engine, with so-called compression ignition.
  • injected fuel for example a mineral oil product known as diesel fuel
  • diesel fuel is injected into a combustion chamber within a cylinder, in particular when a compression temperature is exceeded a compression of an air volume within the cylinder by means of a piston is already greatly increased. This leads to self-ignition of the mostly finely atomized fuel within the cylinder.
  • the internal combustion engine known as the so-called diesel petrol engine which works according to a mixed principle, is also to be understood between the diesel principle and the Otto principle with external ignition of, for example, over 1 . 000 bar is injected into the combustion chamber.
  • such a diesel engine can have a “supercharger”, with this supercharger being achieved by means of a compressor or a turbocharger, which in each case or in combination with one another presses air into the cylinder so that a higher degree of filling and thus a higher power output can be achieved.
  • a “compression temperature” is the temperature inside the cylinder that is reached when a piston of the crank mechanism of such a diesel engine compresses intake air and prepares it for the combustion cycle. Such a compression process usually takes place directly before the combustion cycle
  • a “combustion temperature” is a temperature that occurs when fuel is then injected and the resulting combustion occurs.
  • a "cylinder bore” can be, for example, a cast and/or drilled bore and then further refined, for example by honing, within an engine block of an internal combustion engine, with which a "cylinder” is created. Furthermore, however, such a cylinder bore can also be a round or substantially round non-closed cavity of a steam engine, an expansion drive or another form of prime mover. The piston closes off the cylinder bore to a last open side, so that pressure forces within the cylinder bore then allow forces to act on the piston.
  • a " connecting rod " is used in a so - called “ crank mechanism " to mechanically establish a connection between a crankshaft and the reciprocating piston within the cylinder .
  • the connecting rod is connected to the piston with a "head area”, with a “foot area” being connected to the head area via a “middle area” and ensuring the connection to an eccentric crank pin of the crankshaft.
  • the head area has the connection with the thickened portion and the foot area has a second connection for receiving the crankshaft.
  • a “piston” is a movable component which, together with a surrounding housing, in the case of a “cylinder” engine, forms a closed cavity, with a volume of the cavity changing by movement of the piston in the cylinder.
  • a reciprocating piston that can be moved up and down is referred to within a prismatic cylinder.
  • An "upper side" of such a piston is, for example, the piston roof or also the area of the piston referred to as the piston crown, which in an internal combustion engine faces the combustion chamber, for example Gas mixture and thus carries the forces necessary for the operation of the crank mechanism to the connecting rod and thus to the crankshaft.
  • a "bottom" is the side of the piston facing the connecting rod or the connecting rod, ie in particular the side of the piston which has the connecting rod receptacle.
  • a "circumferential area" is the area of the piston 12 that faces the cylinder bore in the case of an internal combustion engine 12, for example Specifications relate to the usual design of a cylindrical piston, which is therefore designed similar to a round disc, and the associated essentially round cylinder bore. Likewise, a correspondingly different form of piston and a different form of cylinder bore can also be implemented, if technically sensible.
  • the peripheral surface can also typically be referred to as the piston skirt.
  • This peripheral surface has a so-called “nominal diameter”, which describes, for example, the desired diameter of the peripheral surface of the piston.
  • a "gas” that exerts compressive forces can be either a simple compressed gas, such as compressed air, or a gas produced by phase transition, such as superheated steam, or a gas mixture of, for example, ambient air and petrol or diesel or another fuel be f, which exerts compressive forces by ignition, for example in a gasoline or diesel engine.
  • a "connecting rod receptacle" on the underside of the piston serves to hold a connecting rod in a tension-resistant and pivoting manner, so that the piston together with the connecting rod form a non-positive connection in a so-called crank mechanism, i.e., for example, in the case of a connecting rod placed on a crankshaft of the piston with the crankshaft is made in such a way that the piston is non-positively connected to the connecting rod receptacle with the connecting rod.
  • An "undercut” refers to such a configuration of a receptacle or part of a receptacle in which a component or an area or partial area in the direction of force prevents pulling out in a form-fitting manner or enables the transmission of forces in a form-fitting manner.
  • Such an undercut can be a surface formed by a projection, which is then used by a component mounted or attached behind this undercut for the transmission of forces.
  • a "pivot axis" is, for example, the axis about which the connecting rod is rotatably or pivotally mounted on the piston. This pivot axis corresponds, for example, to the axis of the piston pin in the prior art.
  • a "bulge" of the connecting rod is such a region which has a larger or wider cross-section or a larger or wider diameter than a part of the connecting rod lying in front of it.
  • a thickening can serve, together with the undercut, in particular form a form-fitting, tension- or pressure-resistant connection with the surfaces formed by the undercut .
  • a "axis of motion” describes an axis along which the piston is moved during rotation of a crankshaft, for example.
  • this axis of motion runs parallel to a central axis of a cylinder bore of the cylinder, with no mathematical exact axis, but a corresponding direction with technically caused deviations is indicated.
  • a "piston ring” is a ring that is usually inserted into a circumferential ring groove of the respective piston and acts as a sealing element between the piston and the cylinder bore Position towards the top is meant compression ring which is in direct contact with the combustion chamber in the cylinder.
  • This piston ring serves to "seal" the piston, ie to prevent combustion gases in particular from escaping past the piston in the cylinder bore in the direction of a crank mechanism of the internal combustion engine, in particular the diesel engine.
  • a "circumferential collar” is a part of the circumferential surface or a part of the circumferential surface that is offset from the circumferential surface between the upper side and a receptacle, for example an annular groove, for the piston ring.
  • This circumferential collar is usually also referred to as "Feuersteg” known .
  • the "diameter" of the peripheral collar is measured, for example, by an average radius of the peripheral collar, i.e. a radius of all points of the peripheral collar in relation to the axis of movement, for example, averaged using statistical methods.
  • the nominal diameter of the peripheral surface can also be calculated in this way. It comes at the core of the invention that this scope collar, i.e. the top land, in the best case has no radius difference compared to the peripheral surface that goes beyond deviations caused by production technology, i.e. it can be produced in one go and one clamping, for example.
  • the diameter of the peripheral collar is more than 99%, more than 99.5%, in particular more than 99.8% of the nominal diameter of the peripheral surface.
  • the diameter of the peripheral collar is equal to the nominal diameter of the peripheral surface.
  • the height of the circumferential collar along the axis of movement is less than 5%, less than 3%, less than 2%, in particular less than 1%, a height of the pistons.
  • the "height" of the piston and a related "height of the peripheral collar” describes an expansion of the piston or the peripheral collar along the axis of movement.
  • the height of the peripheral collar is defined by measuring the distance between, for example, an upper peripheral edge of the piston around the top and a topmost piston ring.
  • the height of the piston describes in particular the height between the upper side and the underside, it being possible for further parts of the piston, such as a piston skirt, to protrude beyond the underside.
  • a radius of the circumferential surface, a radius of the circumferential collar, a radius of a nominal contour of the circumferential surface and/or a radius of the nominal contour of the circumferential collar deviates from a mean radius of the circumferential surface, mean radius of the circumferential collar, a mean radius of the Nominal contour of the peripheral surface and/or an average radius of the nominal contour of the peripheral collar of less than 1%, less than 0.5%, in particular less than 1 k».
  • the piston is shaped in such a way that a radially arranged, essentially planar first cross-sectional area running through the movement axis and a radially arranged, essentially planar second cross-sectional area running through the movement axis are one less of each other than 10%, less than 7%, less than 5%, in particular less than 2%, differ in size.
  • a corresponding "cross-sectional area” refers to an essentially flat surface, which results from an imaginary cutting of the piston with a cutting path along the axis of movement.
  • This cross-sectional area is specified as a surface area, which is what matters in the core of the invention that precisely this cross-sectional area is the same or similar with respect to a further cross-section rotated at a rotation angle about the axis of movement.
  • the piston is shaped in such a way that a radially arranged, essentially flat, first cross-sectional area running through the movement axis and a radially arranged, essentially planar, second cross-sectional area running through the movement axis have a differ in size from one another by less than 7%, less than 5% and/or less than 2%.
  • a first cross-sectional area and a second cross-sectional area each denote any desired cross-sectional area
  • two cross-sectional areas in different reference axes, for example perpendicular to one another are configured identically or similarly, so that thermal deformation behavior of the piston in the two main directions is controlled, for example.
  • the respective cross-sectional areas can run at any desired angles to one another, so that in particular a comparison of any cross-sectional areas around a circumference of the piston stands up to the correspondingly mentioned criteria.
  • a piston skirt running from the top to the bottom and/or beyond the bottom is arranged on the peripheral surface, with the piston skirt in particular having a radial thickness of less than 10%, less than 5% and/or or less than 2% of a diameter of the piston.
  • a corresponding compensating volume or corresponding compensating volumes can be arranged in such a way that material of the piston is applied at a point where this is not absolutely necessary from a technical point of view, so that the criteria for the size of different cross-sectional areas are met in relation to one another.
  • a vent volume and/or several vent volumes can be removed on the upper side and/or on the underside, with the vent volume and/or the vent volumes being used to compensate for the respective cross-sectional area Volume sections of the piston is created fen.
  • a "compensation volume” describes an increase in volume, namely an additional material applied, whereas a “deduction volume” designates a correspondingly non-existent or removed material.
  • an additional volume can be provided in the mold with respect to a corresponding deduction volume, with a corresponding volume being removed from the mold with respect to a compensating volume is taken out.
  • corresponding compensating volumes or also deduction volumes can be provided directly, for example in a CNC milling program.
  • the head area of the connecting rod has a first connection with a thickened area for connecting a piston, rotatable about the pivot axis, to a connecting rod receptacle of the piston that has an undercut that corresponds to the thickened area, and the foot area has a second connection for accommodating a crankshaft and
  • the head area is connected to the base area via the central area, with the connecting rod having a lubricant guide that connects the second connection to the first connection in a fluid-conducting manner, so that a lubricant introduced into the lubricant guide at the second connection in the area of the crankshaft passes through the lubricant guide to the first Connection is performed and the lubricant for lubricating and / or cooling the first connection is present.
  • Lubricant guide along the connecting rod sure that the first connection between the connecting rod and the piston is reliably lubricated and/or cooled.
  • the lubricant guide runs in the form of a lubricant channel, with the lubricant channel running in particular along the middle region.
  • a lubricant channel can be, for example, a bore running along the middle area of the connecting rod, whereby ideally only material runs in a neutral axis of the middle area designed against bending and therefore no or only an insignificant weakening of the connecting rod occurs overall through the lubricant channel.
  • the lubricant guide runs from a crankshaft boss assigned to the second connection to the thickened area, in particular from an inner surface of the crankshaft boss to the thickened area.
  • a quantity of oil that is already present within a hollow crankshaft and is in particular under pressure for lubricating bearing points of the crankshaft in an engine housing can be used to be introduced into the respective crankshaft boss.
  • a corresponding bore or hole can be present in the crankshaft boss or in a bearing shell inserted in the crankshaft boss, so that engine oil escaping at a crankshaft boss corresponding to the crankshaft boss is introduced with excess pressure into the lubricant guide and thickened can be spent, so ultimately by means of the pressurized amount of engine oil, the thickening and thus the first connection between the connecting rod and the piston is reliably lubricated and cooled.
  • the lubricant guide is introduced into the connecting rod by means of spark erosion and/or deep drilling.
  • Such "radio erosion”, which is also briefly described as “eroding”, can be used for high-precision material processing.
  • the electrically conductive workpiece to be machined is placed in a dielectric and machined; a tool that is also electrically conductive is brought close to the material and a voltage difference between the tool and the workpiece is used to generate sparks by means of local discharge between the tool and the workpiece and primarily to remove material from the workpiece.
  • a channel-like, eroded bore is produced in the so-called countersinking or drilling EDM using a rod-shaped tool.
  • deep drilling can be used as a special machining of a drilling, with deep drilling being characterized in that a drilling depth e is many times larger than the diameter.
  • the lubricant guide has a lubricant reservoir at the thickened area, where is introduced in the lubricant reservoir in particular in an outer surface of the thickening and / or assigned to the connecting rod receptacle.
  • a corresponding retention of lubricant i.e. an additionally available amount of lubricant, can be kept available in the area of the thickening and can also be used, for example, as a hydraulic cushion to prevent direct workpiece contact between an inner surface of the undercut and the outer surface of the thickening.
  • a "lubricant reservoir” can be provided, for example, as a depression in a surface of the thickened area.
  • a valve device can also be assigned to this lubricant reservoir or to another area of the thickened portion .
  • This valve device serves to control a lubricant flow introduced into the lubricant guide at the second connection in the area of the crankshaft and guided through the lubricant guide to the first connection by pivoting the thickened portion about the pivot axis.
  • valve device depending on an angular position of the pivoting of the thickened area about the pivot axis, so that, for example, lubricating oil can only flow off when the connection between the piston and connecting rod is unloaded or only slightly loaded.
  • valve device on the connecting rod can be designed analogously to the described valve device on the connecting rod alternatively or additionally as a valve device of a piston on the inner surface of the undercut with the same effect according to a further aspect of the invention, so that a corresponding recess as a valve device, for example in this inner surface of the piston is introduced.
  • Figure 1 is a schematic representation of a crank unit with a piston and a connecting rod in an isometric view
  • FIG. 2a shows the piston of the crank unit of FIG. 1 in a schematic side view
  • FIG. 2b shows the piston in a schematic view from below
  • Figure 2c shows the piston of Figure 2b in a sectional view A-A
  • FIG. 2d shows the piston in a view from below with different sectional planes
  • FIG. 3a shows the connecting rod of FIG. 1 in a schematic side view
  • Figure 3b the connecting rod in an isometric
  • Figure 4 in a side view, partially sectioned, from an exemplary embodiment of a crank mechanism with a piston according to the invention
  • Figure 5 in a perspective view, partially sectioned, from an exemplary embodiment of a reciprocating internal combustion engine with a piston according to the invention.
  • a crank unit 101 has a piston 201 and a connecting rod 301 .
  • the crank unit 101 is part of a diesel engine (not shown), wherein the corresponding diesel engine can have, for example, four, six or eight of these crank units, the respective pistons 201 being movably accommodated along a movement axis 281 within corresponding cylinders.
  • the connecting rod 301 is held about a crank axis 185 on respective crank pins of a crankshaft 401 designed according to the number of cylinders.
  • the diesel engine is designed, for example, as an in-line four-cylinder, in-line six-cylinder or V-eight engine.
  • Each is a diesel engine with high-pressure injection for diesel fuel and turbo and/or compressor charging, which results in high combustion temperatures in each cylinder.
  • Other designs are can of course also be represented in the corresponding number by means of the crank unit 101 .
  • the piston 101 is formed from an aluminum alloy.
  • the respective connecting rod 301 is forged from steel and machined and arranged to be pivotable about a pivot axis 183 relative to the piston 201 , so that when the crankshaft rotates completely (not shown), the crank axis 185 is guided in a circular motion, the piston 201 is moved up and down in the cylinder by means of the connecting rod 301 and thus completes a complete revolution of the crankshaft without mechanical obstacles.
  • the injected diesel fuel is ignited by the compression of intake air in the cylinder, the compression temperature is over 700 °C and the resulting combustion temperature is over 1 . 200°C .
  • the thermal influences on the piston 201 are correspondingly high.
  • the piston 201 has a peripheral surface 205 and an underside 207 .
  • a combustion chamber 241 with a cone-like cap 243 is arranged inside the upper side concentrically to the movement axis 281 , which enlarges the combustion chamber of the cylinder in the piston 201 .
  • a predominant part of the peripheral surface 205 forms a piston skirt which runs cylindrically in the direction of the underside 207 and is thin-walled.
  • the piston 201 has a narrow peripheral collar 221 which forms a distance from the top 203 to a first annular groove 223 .
  • a piston ring for sealing against the cylinder is arranged within this first annular groove 223 .
  • a ring groove 225 and a ring groove 227 are arranged further in the direction of the underside 207, with a further piston ring being inserted in the ring groove 225 as a sealing ring, and in the ring groove 227 a piston ring functioning as an oil scraper ring (piston rings not shown in each case).
  • Additional bores 229 are arranged on the annular groove 227 , which facilitate the draining of engine oil.
  • the peripheral collar 221 is known in diesel engines according to the prior art as a so-called "fire bridge" and is designed in these engines in the prior art with a significantly smaller diameter than the peripheral surface of a piston.
  • the peripheral collar 221, on the other hand, has a radius 282 , this radius 282 being, within technical tolerances, identical to a radius 284 of the peripheral surface 205.
  • the piston 201 can therefore be manufactured with regard to its cylindrical shape in a single clamping and with a single setting on a lathe.
  • the peripheral collar 221 can be designed in this form because the usual function of a "fire bridge" of the prior art, namely additional heat dissipation via this top land can be eliminated by a thinner diameter and thus access for the combustion gases in the piston 201. More detailed explanations on this are given below.
  • the piston 201 has a receptacle 210 for the connecting rod 301 .
  • the receptacle 210 is essentially formed by an undercut 211 which has an inner surface 213 arranged concentrically around the pivot axis 183 and is delimited by a respective edge 217 .
  • the piston skirt 219 has a cutout 220 on both sides along the pivot axis 183 . Through this cutout 220, both the connecting rod 301 can be pushed into the piston 201, and during the previous production of the piston 201, a corresponding tool for fine machining the inner surface 213 can be introduced without obstacles.
  • the piston 201 has different volumes.
  • the piston 201 has a respective symmetrical to the movement axis 281 arranged thickenings 231, also arranged symmetrically to the movement axis 281 pockets 233 and additional, Thickened portions 235 arranged symmetrically to the movement axis 281 and in the direction of the pivot axis 183 .
  • the corresponding volumes of the thickenings 231, the pocket 233 and the thickenings 235 are selected in such a way that any cut surfaces formed by the movement axis 281, namely, for example, cut surfaces formed along a cutting plane 271, a cutting plane 273 or a cutting plane 275 (also compare FIG. 2d) , are each equal in area with a tolerance of, for example, 2% in relation to a smallest sectional area of the respective comparison.
  • This geometric configuration ensures that the thermal expansion behavior of the piston 201 is almost identical or even identical in different polar positions about the movement axis 281 .
  • material is applied to the thickened portion 231 , material is removed from the pocket 233 and material is applied to the thickened portion 235 .
  • a respective thickening 235 also serves, for example, to at least partially equalize the missing material in the piston skirt 219 at the cutout 220 to form corresponding cross-sectional areas.
  • other components are compensated analogously by subtracting or adding corresponding volumes of the material of the piston 201 .
  • annular grooves 215 are introduced along the pivot axis 183 on both sides symmetrically to the movement axis 281 , these annular grooves due to the shape of the rear cutting 211 are formed as partial annular grooves 215.
  • the respective annular groove 215 has a cross section starting from a diameter 216 of the inner surface 213 up to a diameter 218 .
  • the connecting rod 301 has a connecting rod head 303 , a central area 305 and a crankshaft connection 307 .
  • the connecting rod head is designed as a thickened area with a cylindrical outer surface 311 .
  • the outer surface 311 corresponds to the diameter 216 of the inner surface 213 of the piston 201, taking into account the necessary tolerances.
  • chamfers 312 are arranged in the end regions of the thickening in the direction of the pivot axis 183 .
  • the connecting rod head 303 can thus be pushed into the piston 201 along the pivot axis 183 so that a pivot joint with freedom of movement about the pivot axis 183 is formed.
  • the middle area 305 connects the connecting rod head 303 to the crankshaft connection 307 and has a depression 306 on both sides along its extension between the connecting rod head 303 and the crankshaft connection 307, so that overall a rigid cross-section of the middle area 305 according to a double T-beam is formed .
  • webs 315 with recesses 316 formed in relation to the central region 305 are arranged in such a way that the central region 305 is additionally rigidly connected with respect to the crankshaft connection 307 and yet is as light as possible.
  • crankshaft connection 307 consists of a part of the connecting rod 301 and a so-called cover 308, with the crankshaft boss 309 is formed, which is arranged concentrically around the crank axis 185 .
  • the crankshaft boss 309 is provided with a bearing shell 321 in order to produce a low-friction, wear-resistant connection to the crankshaft that is able to run in an emergency.
  • the bearing shell is arranged in the crankshaft boss 309 so that it cannot rotate, so that the position of the bearing shell 321 in relation to the connecting rod 301 is rotationally fixed.
  • the connecting rod 301 has a valve groove 341 on the outer surface 311 of the connecting rod head 303 , which is connected to an outlet opening 343 .
  • the outlet opening 343 is part of an oil channel 345 which runs between the outlet opening 343 and an inlet opening 347 arranged inside the crankshaft boss 309 .
  • the oil channel 345 is arranged in the neutral fiber of the middle area 305 so that the oil channel 345 weakens the middle area 305 as little as possible, in particular against bending.
  • the connecting rod head 303 is pushed into the undercut 211 along the pivot axis 183 .
  • An elastic locking ring with a round wire cross-section is inserted inside the annular groove 215 in such a way that a part of the locking ring (not shown) extends into the cross-section of the undercut 211 formed by the inner surface 213 .
  • This circlip is then pushed back into the annular groove by means of the chamfer 312 on the connecting rod head 303 , the cross section of the circlip being selected such that it can be positioned completely between the diameter 216 and the diameter 218 .
  • the chamfer 312 thus facilitates the insertion of the connecting rod head 303 into the piston 201 . If the connecting rod head 303 is pushed in completely symmetrically, a corresponding locking ring springs back into its initial position and secures the connecting rod 301 on the connecting rod head 303 against unintentional removal along the pivot axis 183 .
  • crank unit 101 The function of the crank unit 101 with regard to the lubrication of the connection between the connecting rod head and the piston 201 in the undercut 211 is explained as follows:
  • crankshaft Inside the crankshaft (not shown ) , an oil duct running inside the crankshaft with corresponding outlet bores at the bearing points is provided for lubricating corresponding bearing points of the crankshaft .
  • the crankshaft also has corresponding outlet bores for pressurized engine oil on the crank pins, which accommodate the respective connecting rod 301 around the crank axis 185 .
  • the engine oil is then held in a circumferential annular groove on the crankshaft and forces its way through the inlet opening 347 into the oil channel 345 to the outlet opening 343 . With the outlet opening 343 and the valve groove 341, an oil reservoir is created, in which pressurized engine oil is available for lubricating the undercut 311.
  • valve groove 341 serves to control the oil flow depending on a position of the crankshaft and a resulting position of the connecting rod 301 and the piston 201 .
  • the piston 201 arrived at a top dead center or a bottom dead center, so is the Connecting rod 301 substantially perpendicular within cylinder bore along axis of motion 281 .
  • the valve groove 341 is completely surrounded by the inner surface 213 of the undercut 211, so that no oil can escape through the valve groove 341.
  • the oil cushion in the oil reservoir also prevents direct material contact.
  • Figure 4 shows a side view, partially in section, of an exemplary embodiment of a crank mechanism according to the invention, the crank mechanism comprising a piston 201 according to one of the exemplary embodiments described above and a corresponding connecting rod 301 - i.e. a crank unit 101 - and a crankshaft 401.
  • the connecting rod 301 is coupled to the crankshaft 401 in a conventional manner.
  • the piston 201 can be moved in a cylinder arrangement 501 along a movement axis 281 .
  • Figure 5 shows a perspective and partially sectioned view - in detail - of an exemplary embodiment of a reciprocating internal combustion engine 601 in the form of a diesel engine with a cylinder arrangement 501 with four cylinders to form an in-line four-cylinder engine and with pistons 201 and connecting rods 301 according to one of the above exemplary embodiments.
  • a col- Ben 201 and a connecting rod 301 a crank unit 101 .
  • the connecting rod 301 is coupled to a crankshaft 401 .
  • the diesel engine can be operated with high combustion temperatures and thus low-emission and efficient combustion, because of the geometry of the piston 201, the compact design and central dissipation of heat into the connecting rod 301 and the controlled oil flow of the engine oil good heat management is ensured.
  • the combination of piston 201 and connecting rod 301 according to the invention therefore has a very low weight and thus reduced moving masses. It should be noted that this type of col- Ben 201 and connecting rod 301 was shown in the present example for a diesel engine with high-pressure injection and a supercharger, but the corresponding arrangement of piston 201 and connecting rod 301 is also suitable for other reciprocating machines, such as gasoline engines, compressors or diesel engines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

L'invention concerne un moteur diesel à injection haute pression et à suralimentation [question à inventeurs : quels composants définissent un "moteur diesel" ayant les caractéristiques correspondantes ? ] et/ou ayant une température de compression supérieure à 700°C et/ou une température de combustion supérieure à 1200°C, un cylindre ou plusieurs cylindres comportant un alésage de cylindre respectif, une tige de bielle associée à un cylindre respectif et un piston, disposé dans l'alésage de cylindre respectif, ledit piston comportant une face supérieure, une face inférieure et une face périphérique ayant un diamètre nominal, la face supérieure étant conçue de manière à absorber des forces de pression d'un gaz à l'intérieur du cylindre respectif, la face inférieure présentant une cavité de réception de tige de bielle comportant une contre-dépouille agissant dans une direction de traction et une direction de compression, de telle sorte que la cavité de réception de tige de bielle est agencée de manière à recevoir une surépaisseur correspondante de la bielle respective, par complémentarité de forme et par pivotement autour d'un axe de pivotement, et la face périphérique étant conçue de manière à guider le piston dans l'alésage de cylindre respectif le long d'un axe de déplacement, et un logement pour un segment de piston destiné à rendre étanche le piston par rapport à l'alésage de cylindre respectif et présentant une collerette périphérique partant de la face supérieure avec une hauteur agencée entre la face supérieure et le logement pour le segment de piston. En outre, l'invention concerne un piston correspondant d'un moteur diesel.
EP22843806.5A 2021-12-23 2022-12-22 Moteur diesel à injection haute pression et suralimentation et piston d'un moteur diesel Pending EP4453402A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021134521.9A DE102021134521A1 (de) 2021-12-23 2021-12-23 Dieselmotor mit Hochdruck-Einspritzung und Aufladung
PCT/EP2022/087654 WO2023118534A1 (fr) 2021-12-23 2022-12-22 Moteur diesel à injection haute pression et suralimentation et piston d'un moteur diesel

Publications (1)

Publication Number Publication Date
EP4453402A1 true EP4453402A1 (fr) 2024-10-30

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP22843806.5A Pending EP4453402A1 (fr) 2021-12-23 2022-12-22 Moteur diesel à injection haute pression et suralimentation et piston d'un moteur diesel

Country Status (4)

Country Link
US (1) US20250020089A1 (fr)
EP (1) EP4453402A1 (fr)
DE (1) DE102021134521A1 (fr)
WO (1) WO2023118534A1 (fr)

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Publication number Publication date
US20250020089A1 (en) 2025-01-16
WO2023118534A1 (fr) 2023-06-29
DE102021134521A1 (de) 2023-06-29

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