EP2305975B1 - Combustion engine with pump for transporting engine oil and method for heating the engine oil of such a combustion engine - Google Patents
Combustion engine with pump for transporting engine oil and method for heating the engine oil of such a combustion engine Download PDFInfo
- Publication number
- EP2305975B1 EP2305975B1 EP10154681.0A EP10154681A EP2305975B1 EP 2305975 B1 EP2305975 B1 EP 2305975B1 EP 10154681 A EP10154681 A EP 10154681A EP 2305975 B1 EP2305975 B1 EP 2305975B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder head
- combustion engine
- internal combustion
- oil
- exhaust
- 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.)
- Active
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 84
- 239000010705 motor oil Substances 0.000 title claims description 39
- 238000010438 heat treatment Methods 0.000 title claims description 13
- 238000000034 method Methods 0.000 title claims description 10
- 239000003921 oil Substances 0.000 claims description 72
- 239000002826 coolant Substances 0.000 claims description 54
- 239000007789 gas Substances 0.000 claims description 36
- 238000001816 cooling Methods 0.000 claims description 20
- 238000011144 upstream manufacturing Methods 0.000 claims description 13
- 238000007599 discharging Methods 0.000 claims description 2
- 239000000446 fuel Substances 0.000 description 12
- 239000007788 liquid Substances 0.000 description 12
- 239000012634 fragment Substances 0.000 description 9
- 230000008901 benefit Effects 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 238000012546 transfer Methods 0.000 description 3
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 206010063493 Premature ageing Diseases 0.000 description 1
- 208000032038 Premature aging Diseases 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004939 coking Methods 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000004806 packaging method and process Methods 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000012805 post-processing Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000012858 resilient material Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- 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
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/02—Arrangements of lubricant conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/022—Chain drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
-
- 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
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
- F01M5/001—Heating
-
- 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
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
- F01M5/02—Conditioning lubricant for aiding engine starting, e.g. heating
-
- 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
- F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
- F01M9/10—Lubrication of valve gear or auxiliaries
- F01M9/102—Lubrication of valve gear or auxiliaries of camshaft bearings
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/005—Cooling of pump drives
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/14—Lubrication of pumps; Safety measures therefor
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/243—Cylinder heads and inlet or exhaust manifolds integrally cast together
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/26—Cylinder heads having cooling means
- F02F1/36—Cylinder heads having cooling means for liquid cooling
- F02F1/40—Cylinder heads having cooling means for liquid cooling cylinder heads with means for directing, guiding, or distributing liquid stream
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/02—Lubrication
Definitions
- the invention relates to a method for heating the engine oil of such an internal combustion engine.
- An internal combustion engine of the type mentioned above is in the JP 8 177440 A disclosed and used as a drive for motor vehicles.
- the term internal combustion engine includes diesel engines and gasoline engines, but also hybrid internal combustion engines.
- the JP 61 047437 U describes an internal combustion engine in which the supply line upstream of the main oil gallery supplies the bearing of an exhaust gas turbocharger with oil.
- the JP H06 40305 U describes a method for raising the oil temperature according to the prior art, wherein heat is introduced into the oil by means of fin arranged on the cylinder block.
- the heat of the cylinder block is also used to heat a silicone oil, which in turn can be used to heat the oil.
- the cylinder block has a corresponding number of cylinder bores for receiving the pistons or the cylinder tubes.
- the piston of each cylinder of an internal combustion engine is axially movably guided in a cylinder tube and limits together with the cylinder tube and the cylinder head the combustion chamber of a cylinder.
- the piston head forms a part of the combustion chamber inner wall and seals together with the piston rings the combustion chamber against the cylinder block or the crankcase, so that no combustion gases or combustion air enter the crankcase and no oil enters the combustion chamber.
- the piston serves to transfer the gas forces generated by the combustion to the crankshaft.
- the piston is articulated by means of a piston pin with a connecting rod, which in turn is movably mounted on the crankshaft.
- the crankshaft mounted in the crankcase receives the connecting rod forces, which are composed of the gas forces due to the fuel combustion in the combustion chamber and the mass forces due to the non-uniform movement of the engine parts.
- the oscillating stroke movement of the piston is transformed into a rotating rotational movement of the crankshaft.
- the crankshaft transmits the torque to the drive train. Part of the energy transferred to the crankshaft is used to drive auxiliary equipment such as the oil pump and the alternator, or to drive the camshaft and thus actuate the valvetrain.
- the upper crankcase half is formed by the cylinder block.
- the crankcase is supplemented by the lower half of the crankcase, which can be mounted on the upper crankcase half and serves as an oil sump.
- the upper crankcase half for receiving the oil pan, i. the lower crankcase half on a flange.
- a seal is provided in or on the flange surface for sealing the oil sump or the crankcase relative to the environment. The connection is often done by a screw.
- At least two bearings are provided in the crankcase, which are usually made in two parts and each include a bearing saddle and connectable to the bearing saddle bearing cap.
- the crankshaft is mounted in the region of the crankshaft journals which are arranged at a distance from one another along the crankshaft axis and are generally designed as thickened shaft shoulders.
- Bearing caps and bearing saddles can be used as separate components or in one piece with the crankcase, i. the crankcase halves are formed. Between the crankshaft and the bearings bearing shells can be arranged as intermediate elements.
- each bearing saddle When assembled, each bearing saddle is connected to the corresponding bearing cap.
- a bearing saddle and a bearing cap form - possibly in cooperation with bearing shells as intermediate elements - a bore for receiving a crankshaft journal.
- the holes are usually supplied with engine oil, ie lubricating oil, so that ideally forms between the inner surface of each hole and the associated crankshaft journal with rotating crankshaft - similar to a plain bearing - a viable lubricating film.
- a pump for the delivery of engine oil to the at least two bearings, wherein the pump supplied via the supply line, a main oil gallery, lead from the channels to the at least two camps, with engine oil.
- the supply line leads according to the prior art of the pump through the cylinder block to Hauptöl request.
- a main supply channel is often provided, which is aligned along the longitudinal axis of the crankshaft.
- the main supply channel can be arranged above or below the crankshaft in the crankcase or integrated into the crankshaft.
- the intended pump must have a sufficiently large flow, d. H. ensure a correspondingly high delivery volume and ensure a sufficiently high oil pressure in the supply system, in particular the main oil gallery.
- a permanent oil supply of at least two bearings is not required.
- a permanent supply of oil to the bearings may be detrimental to the pressure in the overall system.
- a merely regular but not continuous oil supply of the bearings can be advantageous.
- Another oil supply in the above sense for example, be the oil supply to a camshaft, which is usually stored in a two-piece so-called camshaft.
- the statements already made with regard to the crankshaft bearing apply analogously.
- the camshaft receptacle is usually supplied with lubricating oil, to which a supply channel is provided, which branches off in the prior art from the main oil gallery, passes through the cylinder block and extends in overhead camshafts into the cylinder head.
- the friction in the bearings of the crankshaft which depends largely on the viscosity and thus of the temperature of the oil used, contributes to the fuel consumption of the internal combustion engine.
- Another sub-task is to show a method for heating the engine oil of such an internal combustion engine.
- the supply line in the internal combustion engine according to the invention passes through the cylinder head before this line opens into the main oil gallery. Ie. the flow direction of the oil is reversed compared to conventional internal combustion engines. While the prior art engine oil flows from the main oil gallery to the cylinder head, according to the invention, it is directed from the cylinder head to the main oil gallery.
- the oil is heated as it passes the cylinder head, providing higher temperature oil to the downstream main gallery and thus to the downstream crankshaft bearings, reducing friction in the bearings and reducing fuel consumption.
- the cylinder head is thermally highly loaded, especially in comparison to the cylinder block is thermally loaded higher, so that the heating of the oil, d. H. the increase in the oil temperature at a flow through the cylinder head is more pronounced than when flowing through the cylinder block.
- the inventively designed engine proves to be particularly advantageous during the warm-up phase, in particular after a cold start.
- d. H After a stoppage of the vehicle, d. H.
- the oil first flows through the cylinder head, which heats up comparatively quickly as a result of the combustion processes taking place, in particular in comparison to the cylinder block.
- the oil provided for the lubrication of the crankshaft bearings is also heated faster if, according to the procedure according to the invention, it is first guided through the cylinder head.
- the engine oil can also be performed in the internal combustion engine according to the invention through the cylinder block, for example, when the supply line to the main oil gallery is passed from the cylinder head through the cylinder block.
- Heated oil of a higher temperature has a lower viscosity, which lowers the friction of the engine and improves the efficiency.
- the fuel consumption of the internal combustion engine is noticeably reduced, in particular after a cold start.
- At least one exhaust-gas turbocharger comprising a turbine, a compressor and a bearing is provided for charging the internal combustion engine.
- a compressor and a turbine are arranged on the same shaft.
- the shaft is received in a bearing which is located between the turbine and the compressor.
- the hot exhaust gas flow is supplied to the turbine and relaxes with energy release in this, whereby the shaft is rotated.
- the energy emitted by the exhaust gas flow to the turbine and finally to the shaft is used to drive the compressor, which is also arranged on the shaft.
- the compressor conveys and compresses the charge air supplied to it, whereby a charging of the cylinder is achieved.
- the charge is used primarily to increase the performance of the internal combustion engine.
- the air required for the combustion process is compressed, which allows each cylinder per working cycle, a larger air mass can be supplied. As a result, the fuel mass and thus the medium pressure can be increased.
- the charge is a suitable means to increase the capacity of an internal combustion engine with unchanged displacement or to reduce the displacement at the same power.
- the charging leads to an increase in space performance and a lower power mass. Under the same vehicle boundary conditions, the load spectrum can thus be shifted to higher loads, where the specific fuel consumption is lower. The latter is also referred to as downsizing.
- the charging thus supports the constant effort in the development of internal combustion engines to minimize fuel consumption, ie to improve the efficiency of the internal combustion engine.
- the advantage of the exhaust gas turbocharger compared to a mechanical supercharger is that there is no mechanical connection to the power transmission between the supercharger and the internal combustion engine or is required. While a mechanical supercharger obtains the energy required for its drive completely from the internal combustion engine and thus reduces the power provided and thus adversely affects the efficiency, the exhaust gas turbocharger uses the exhaust gas energy of the hot exhaust gases.
- the turbine has a housing for receiving an impeller and the supply line leads according to the invention upstream of the main oil gallery through this turbine housing.
- the turbine housing heats up particularly quickly after a cold start of the internal combustion engine due to the hot exhaust gas flow, so that the housing is suitable for a rapid heat input into the engine oil during the warm-up phase.
- the guided through the housing oil removes heat from the exhaust gas and thus reduces the temperature, d. H. the thermal load of the housing.
- the internal combustion engine according to the invention solves the problem underlying the invention, namely to provide an internal combustion engine, which is optimized in terms of friction.
- the section of the supply line which passes through the at least one cylinder head is preferably designed, ie designed, with regard to its primary function, namely the oil heating.
- Embodiments of the internal combustion engine in which an oil sump which can be mounted on the upper crankcase half and serves as a lower crankcase half for collecting the engine oil are provided, and the pump delivers oil from the sump via the supply line to the main oil gallery.
- the crankcase is formed in two parts, wherein the upper crankcase half is supplemented by an oil pan, in which the recirculated oil is collected.
- the oil pan can be equipped on the outside with cooling ribs or stiffening ribs and is preferably made of sheet metal by deep drawing, whereas the upper crankcase half is preferably a casting.
- crankcase In the design and construction of the crankcase, it is a fundamental goal to achieve the highest possible stiffness to vibration, d. H. Reduce vibrations and thus influence the noise and noise emission favorable.
- the modular crankcase should preferably be constructed in such a way that the processing of the mounting and sealing surfaces and the assembly can be done in the simplest possible way to reduce costs.
- Embodiments of the internal combustion engine in which the at least one cylinder head is equipped with a coolant jacket integrated at least partially in the cylinder head are advantageous.
- the heat released during combustion by the exothermic, chemical conversion of the fuel is partly dissipated via the walls delimiting the combustion chamber to the cylinder head and the cylinder block and partly via the exhaust gas flow to the adjacent components and the environment.
- a portion of the introduced into the cylinder head heat flow must be withdrawn from the cylinder head again.
- the liquid cooling, d. H. the formation of a liquid-cooled cylinder head requires the equipment of the cylinder head with a coolant jacket, d. H. the arrangement of the coolant through the cylinder head leading coolant channels, which causes a complex structure of the cylinder head construction.
- the mechanically and thermally highly stressed cylinder head is weakened by the introduction of the coolant channels on the one hand in its strength.
- the heat must not be directed to the cylinder head surface as in the air cooling, to be dissipated.
- the heat is already in the interior of the cylinder head to the coolant, usually mixed with additives added water.
- the coolant is conveyed by means of a pump arranged in the cooling circuit, so that it circulates in the coolant jacket. The heat given off to the coolant is removed in this way from the interior of the cylinder head and removed from the coolant in a heat exchanger again.
- Liquid cooling is particularly suitable for supercharged internal combustion engines, which require efficient and optimized cooling due to higher exhaust gas temperatures.
- Embodiments of the internal combustion engine in which the supply line comprises at least two partial supply lines along a section passing through the at least one cylinder head are advantageous.
- the supply line forks into at least two partial supply lines, i. H. fanned out into several partial supply lines.
- This increases the overall surface area of the supply line along a portion passing through the at least one cylinder head, thereby assisting heat transfer between the cylinder head and the engine oil contained in the supply line, i. H. is increased.
- the supply line is optimized according to the embodiment in question at least along a section with respect to their primary function in the cylinder head, namely in terms of their function as a heat exchanger.
- the heat transfer between the cylinder head and the motor oil present in the supply line can affect both the heat input of the hot exhaust gas stream into the engine oil and - in liquid-cooled cylinder heads - the heat input or heat removal of the coolant in or out of the engine oil.
- the supply line can split in the cylinder head in two or more partial supply lines, but also outside, d. H. upstream of the cylinder head. Likewise, the merging of the individual partial supply lines can be made to a common supply line in the cylinder head or downstream of the cylinder head.
- Embodiments of the internal combustion engine in which the coolant jacket integrated in the at least one cylinder head also extends at least partially between the at least two partial supply lines are advantageous.
- the coolant jacket also extends between the at least two partial supply lines. This includes in particular embodiments in which the coolant jacket passes through an imaginary envelope, ie envelope, placed around the at least two partial supply lines, ie, cuts.
- the coolant jacket or the coolant passed through the cooling channels counteracts overheating and thus premature aging of the engine oil and prevents coking of the oil and the formation of deposits in the supply line, which would reduce the flow cross-section or lead to a closure of the line.
- Embodiments of the internal combustion engine in which the at least one cylinder head comprises at least two cylinders are advantageous, wherein each cylinder has at least one outlet opening for discharging the exhaust gases from the cylinder and an exhaust pipe connects to each outlet opening, the exhaust pipes of at least two cylinders forming a integrated exhaust manifold merge within the at least one cylinder head to form an overall exhaust gas line.
- exhaust manifold The combination of exhaust pipes to an overall exhaust line is generally and in the context of the present invention referred to as exhaust manifold.
- the exhaust gases Downstream of a manifold, the exhaust gases are often supplied to the turbine of an exhaust gas turbocharger and / or one or more exhaust aftertreatment systems. It is on the one hand endeavored to arrange the exhaust gas turbocharger or the closest possible to the outlet of the engine to optimally use in this way the exhaust enthalpy of the hot exhaust gases, which is largely determined by the exhaust pressure and the exhaust gas temperature, and a quick response of the turbocharger to ensure.
- the way the hot exhaust gases to the various exhaust aftertreatment systems should be as short as possible, so that the exhaust gases are given little time to cool and the exhaust aftertreatment systems reach their operating temperature or light-off as soon as possible, especially after a cold start of the engine.
- the exhaust pipes are preferably merged within the cylinder head. This measure also allows the densest possible packaging of the drive unit.
- Embodiments of the cylinder head with, for example, four cylinders arranged in series, in which the exhaust pipes of the outer cylinder and the exhaust pipes of the inner cylinder are each combined to form an overall exhaust line, can also be used to form an internal combustion engine of the type in question.
- a cylinder head with integrated exhaust manifold is thermally loaded higher than a conventional cylinder head, which is equipped with an external manifold, and therefore makes increased demands on the cooling, which is why liquid cooling is particularly advantageous in a cylinder head with integrated exhaust manifold.
- the integration of the manifold helps to further reduce the friction of the internal combustion engine. Because especially in the warm-up phase after a cold start of the internal combustion engine reaches a cylinder head with integrated manifold faster higher temperatures than a conventional cylinder head with an external manifold.
- Liquid cooling of the cylinder head advantageously serves to limit the temperature increase of the oil upwards and may possibly assist the heating of the oil in the warm-up phase.
- Embodiments in which the coolant jacket integrated in the at least one cylinder head extends at least partially between the integrated exhaust manifold and the at least one supply line are advantageous. This arrangement of coolant jacket, manifold and conduit ensures that the engine oil does not overheat.
- the coolant jacket acts as a thermal barrier at high exhaust gas temperatures.
- the coolant jacket also extends between the integrated exhaust manifold and the at least one supply line. This includes in particular embodiments in which the coolant jacket passes through an imaginary envelope which encloses the manifold and the supply line.
- Embodiments in which the supply line for supplying engine oil is connected to a camshaft receptacle are advantageous.
- valves which are movable along their longitudinal axis between a valve-closed position and a valve-open position are generally used for the charge exchange as control members in order to release or obstruct an inlet or outlet opening.
- valve spring means are provided to bias the valve in the direction of valve closing position, and on the other hand valve actuators used to open the valve against the biasing force of the valve spring means.
- the valve actuator comprises in the present case a camshaft on which a plurality of cams is arranged and which - for example by means of a chain drive - is rotated by the crankshaft in such a way that the cam shaft rotates at half the crankshaft speed.
- camshafts which are arranged above the mounting surface between the cylinder head and cylinder block and stored in the cylinder head.
- Overhead camshafts are stored for example in two-piece so-called camshaft shots.
- the camshaft has at least two bearing points, which are usually designed as thickened shaft shoulders.
- the camshaft receiving comprises a lower part and an upper part, in which the bearing saddles or bearing caps are arranged.
- the camshaft is received and stored with their bearings in the bearing saddles and bearing caps.
- the bearings are supplied with engine oil, so that a revolving camshaft - similar to a plain bearing - forms a viable lubricating film.
- the supply line with the camshaft receptacle in combination.
- the supply of the camshaft bearing via supply line with heated engine oil reduces the friction in the bearings of the camshaft and further reduces the friction of the engine. This applies to both the camshaft of the intake valves, d. H. the inlet side as well as for the camshaft of the exhaust valves, d. H. the outlet side.
- the supply line upstream of the main oil gallery supplies the bearing of the exhaust gas turbocharger with oil.
- the bearing of the shaft must always be supplied with oil, so that it is advantageous to use the supply line for this purpose, ie to lead the line to the camp or to pass through the bearing housing.
- the supply line can lead through the turbine housing or lead directly from the cylinder head to the camp.
- Embodiments in which the turbine is provided with a coolant jacket to form a liquid cooling system are advantageous, wherein the coolant jacket is preferably integrated in the turbine housing.
- the thermal load of the turbine housing is comparatively high.
- the cooling of the turbine allows a production of the housing made of sheet metal or thermally less resilient materials, which offers cost advantages.
- the use of cost-intensive - often nickel-containing - materials is no longer necessary or is greatly reduced.
- Embodiments in which the turbine housing is at least partially made of aluminum are advantageous. This brings cost benefits compared to the use of conventional materials. In addition, the use of aluminum for the manufacture of the turbine housing leads to a lower weight.
- the second sub-problem underlying the invention namely to show a method for heating the engine oil for an internal combustion engine of the aforementioned type, is achieved by a method which is characterized in that the engine oil is passed through the at least one cylinder head upstream of the at least two bearings ,
- FIG. 1 schematically shows the fragment of a cylinder head 1 of a first embodiment of the internal combustion engine in a perspective view and in a section perpendicular to the longitudinal axis of the cylinder head first
- the cylinder head 1 has a plurality of cylinders 14 arranged in series.
- the combustion chamber 13 of each cylinder 14 is supplied with fresh mixture or fresh air via two inlet channels 12.
- Two outlet openings per cylinder 14 serve to discharge the exhaust gases, wherein an exhaust pipe 4 connects to each outlet opening.
- the exhaust pipes 4 of all cylinders 14 lead together to form an integrated exhaust manifold 5 within the cylinder head 1 to form an overall exhaust gas line 6.
- the in FIG. 1 shown cylinder head 1 is liquid-cooled.
- the cylinder head 1 is equipped with an integrated coolant jacket 7, which passes coolant 8 through the cylinder head 1.
- the coolant jacket 7 comprises a coolant jacket 7 arranged above the exhaust manifold 5, ie arranged on the side of the manifold 5 facing away from the cylinder block, and a coolant jacket 7 arranged below the exhaust manifold 5, ie on the side of the manifold 5 facing the cylinder block Cylinder block passes.
- a supply line 2 leads along the longitudinal axis of the cylinder head 1 through the cylinder head 1 therethrough.
- the line 2 serves to supply the bearings of a crank shaft received in the crankcase with engine oil 3 (not shown) and extends above the coolant jacket 7, i. the line 2 is arranged on the side facing away from the exhaust manifold 5 side of the coolant jacket 7.
- each bearing 10 comprises a bearing saddle 11 and a bearing cap.
- the supply line 2 is in communication with the camshaft receptacle 9 (not shown).
- the supply of the camshaft bearing 10 via supply line 2 with heated engine oil 3 reduces the friction in the bearings 10 of the camshaft.
- FIG. 2 schematically shows the fragment of a cylinder head 1 of a second embodiment of the internal combustion engine in a perspective view and in a section perpendicular to the longitudinal axis of the cylinder head first
- FIG. 1 It should be the differences to the in FIG. 1 Otherwise, reference will be made to FIG. 1 , The same reference numerals have been used for the same components.
- the integrated for forming a liquid cooling in the cylinder head 1 coolant jacket 7 is disposed substantially above the exhaust manifold 5, i. on the side facing away from the cylinder block (not shown) of the manifold 5 and leads around the manifold 5 to the bottom of the manifold 5.
- the coolant jacket 7 is interrupted on the underside of the manifold 5 from the supply line 2, i. the coolant jacket 7 extends on both sides of the line 2 and has an opening 16 which is provided adjacent to the entire exhaust line 6 on a longitudinal side of the cylinder head 1 and is closed in the mounted state of the head 1.
- the introduction of the opening 16 is made for manufacturing reasons and is used for post-processing of the coolant jacket 7. Nevertheless, the opening 16 for removing coolant also remain open, for example, to supply a liquid-cooled turbocharger with coolant.
- the supply line 2 runs at the in FIG. 2 illustrated embodiment on the cylinder block (not shown) facing side of the manifold 5, ie on the underside of the manifold 5, wherein - in the illustrated section - no portion of the coolant jacket between the manifold 5 and the supply line 2 extends, so that heat from Exhaust flow can pass on the engine oil 3 unhindered.
- FIG. 3 schematically shows the fragment of a cylinder head 1 of a third embodiment of the internal combustion engine in a perspective view and in a section perpendicular to the longitudinal axis of the cylinder head 1 and in the direction of the longitudinal axis.
- FIGS. 1 and 2 It should only the differences to those in the FIGS. 1 and 2 Otherwise, reference will be made to FIGS FIGS. 1 and 2 , The same reference numerals have been used for the same components.
- the supply line 2 runs at the in FIG. 3 shown cylinder head 1 - as in the in FIG. 2 illustrated embodiment - on the cylinder block (not shown) facing side of the manifold 5, ie on the underside of the manifold 5 along the longitudinal axis of the cylinder head 1.
- the manifold 5 and the supply line 2 are - in the illustrated section - not separated by a coolant jacket.
- the supply line 2 comes from the cylinder block coming on the underside of the head 1, ie the mounting end face in the cylinder head 1 and leaves the cylinder head 1 at the other end of the line 2 again at the bottom, where it enters the block again (indicated by arrows made).
- coolant jacket 7 extends both above the exhaust manifold 5, ie on the cylinder block (not shown) side facing away from the manifold 5 and on the underside of the manifold 5.
- the coolant jacket 7 is on the underside of the manifold 5 - as in FIG. 2 - interrupted by the supply line 2, ie the coolant jacket 7 extends on both sides of the line second
- each bearing 10 comprises a bearing saddle 11 and a bearing cap (not shown).
- the camshaft receptacle 9 is arranged for the camshaft of the intake valves, which is also supplied via a further line 15 with lubricating oil.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Description
Die Erfindung betrifft eine Brennkraftmaschine mit
- mindestens einem Zylinderkopf,
- mindestens einem mit dem mindestens einen Zylinderkopf verbindbaren und als obere Kurbelgehäusehälfte dienenden Zylinderblock zur Aufnahme einer Kurbelwelle in mindestens zwei Lagern, und
- einer Pumpe zur Förderung von Motoröl zu den mindestens zwei Lagern, wobei die Pumpe via Versorgungsleitung eine Hauptölgalerie mit Motoröl versorgt, von der Kanäle zu den mindestens zwei Lagern führen, und
- die Versorgungsleitung stromaufwärts der Hauptölgalerie durch den Zylinderkopf hindurchführt.
- at least one cylinder head,
- at least one cylinder block connectable to the at least one cylinder head and serving as the upper crankcase half for receiving a crankshaft in at least two bearings, and
- a pump for delivering engine oil to the at least two bearings, the pump supplying via the supply line a main oil gallery with engine oil, leading from the channels to the at least two bearings, and
- Pass the supply line upstream of the main oil gallery through the cylinder head.
Des Weiteren betrifft die Erfindung ein Verfahren zur Erwärmung des Motoröls einer derartigen Brennkraftmaschine.Furthermore, the invention relates to a method for heating the engine oil of such an internal combustion engine.
Eine Brennkraftmaschine der oben genannten Art wird in der
Die
Die
Brennkraftmaschinen verfügen über einen Zylinderblock und einen Zylinderkopf, die zur Ausbildung der einzelnen Zylinder, d. h. Brennräume miteinander verbindbar bzw. verbunden sind. Auf die einzelnen Bauteile wird im Folgenden kurz eingegangen.Internal combustion engines have a cylinder block and a cylinder head, which are used to form the individual cylinders, d. H. Combustion chambers are interconnected or connected. The individual components will be briefly discussed below.
Der Zylinderblock weist zur Aufnahme der Kolben bzw. der Zylinderrohre eine entsprechende Anzahl an Zylinderbohrungen auf. Der Kolben jedes Zylinders einer Brennkraftmaschine wird axial beweglich in einem Zylinderrohr geführt und begrenzt zusammen mit dem Zylinderrohr und dem Zylinderkopf den Brennraum eines Zylinders. Der Kolbenboden bildet dabei einen Teil der Brennrauminnenwand und dichtet zusammen mit den Kolbenringen den Brennraum gegen den Zylinderblock bzw. das Kurbelgehäuse ab, so dass keine Verbrennungsgase bzw. keine Verbrennungsluft in das Kurbelgehäuse gelangen und kein Öl in den Brennraum gelangt.The cylinder block has a corresponding number of cylinder bores for receiving the pistons or the cylinder tubes. The piston of each cylinder of an internal combustion engine is axially movably guided in a cylinder tube and limits together with the cylinder tube and the cylinder head the combustion chamber of a cylinder. The piston head forms a part of the combustion chamber inner wall and seals together with the piston rings the combustion chamber against the cylinder block or the crankcase, so that no combustion gases or combustion air enter the crankcase and no oil enters the combustion chamber.
Der Kolben dient der Übertragung der durch die Verbrennung generierten Gaskräfte auf die Kurbelwelle. Hierzu ist der Kolben mittels eines Kolbenbolzens mit einer Pleuelstange gelenkig verbunden, die wiederum an der Kurbelwelle beweglich gelagert ist.The piston serves to transfer the gas forces generated by the combustion to the crankshaft. For this purpose, the piston is articulated by means of a piston pin with a connecting rod, which in turn is movably mounted on the crankshaft.
Die im Kurbelgehäuse gelagerte Kurbelwelle nimmt die Pleuelstangenkräfte auf, die sich aus den Gaskräften infolge der Kraftstoffverbrennung im Brennraum und den Massenkräften infolge der ungleichförmigen Bewegung der Triebwerksteile zusammensetzen. Dabei wird die oszillierende Hubbewegung der Kolben in eine rotierende Drehbewegung der Kurbelwelle transformiert. Die Kurbelwelle überträgt dabei das Drehmoment an den Antriebsstrang. Ein Teil der auf die Kurbelwelle übertragenen Energie wird zum Antrieb von Hilfsaggregaten wie der Ölpumpe und der Lichtmaschine verwendet oder dient dem Antrieb der Nockenwelle und damit der Betätigung des Ventiltriebes.The crankshaft mounted in the crankcase receives the connecting rod forces, which are composed of the gas forces due to the fuel combustion in the combustion chamber and the mass forces due to the non-uniform movement of the engine parts. In this case, the oscillating stroke movement of the piston is transformed into a rotating rotational movement of the crankshaft. The crankshaft transmits the torque to the drive train. Part of the energy transferred to the crankshaft is used to drive auxiliary equipment such as the oil pump and the alternator, or to drive the camshaft and thus actuate the valvetrain.
Im Allgemeinen und im Rahmen der vorliegenden Erfindung wird die obere Kurbelgehäusehälfte durch den Zylinderblock gebildet. Ergänzt wird das Kurbelgehäuse durch die an die obere Kurbelgehäusehälfte montierbare und als Ölwanne dienende untere Kurbelgehäusehälfte. Dabei weist die obere Kurbelgehäusehälfte zur Aufnahme der Ölwanne, d.h. der unteren Kurbelgehäusehälfte eine Flanschfläche auf. In der Regel wird zur Abdichtung der Ölwanne bzw. des Kurbelgehäuses gegenüber der Umgebung eine Dichtung in der bzw. an der Flanschfläche vorgesehen. Die Verbindung erfolgt häufig durch eine Verschraubung.In general, and in the context of the present invention, the upper crankcase half is formed by the cylinder block. The crankcase is supplemented by the lower half of the crankcase, which can be mounted on the upper crankcase half and serves as an oil sump. In this case, the upper crankcase half for receiving the oil pan, i. the lower crankcase half on a flange. As a rule, a seal is provided in or on the flange surface for sealing the oil sump or the crankcase relative to the environment. The connection is often done by a screw.
Zur Aufnahme und Lagerung der Kurbelwelle sind mindestens zwei Lager im Kurbelgehäuse vorgesehen, die in der Regel zweiteilig ausgeführt sind und jeweils einen Lagersattel und einen mit dem Lagersattel verbindbaren Lagerdeckel umfassen. Die Kurbelwelle wird im Bereich der Kurbelwellenzapfen, die entlang der Kurbelwellenachse beabstandet zueinander angeordnet und in der Regel als verdickte Wellenabsätze ausgebildet sind, gelagert. Dabei können Lagerdeckel und Lagersättel als separate Bauteile oder einteilig mit dem Kurbelgehäuse, d.h. den Kurbelgehäusehälften ausgebildet werden. Zwischen der Kurbelwelle und den Lagern können Lagerschalen als Zwischenelemente angeordnet werden.For receiving and supporting the crankshaft at least two bearings are provided in the crankcase, which are usually made in two parts and each include a bearing saddle and connectable to the bearing saddle bearing cap. The crankshaft is mounted in the region of the crankshaft journals which are arranged at a distance from one another along the crankshaft axis and are generally designed as thickened shaft shoulders. Bearing caps and bearing saddles can be used as separate components or in one piece with the crankcase, i. the crankcase halves are formed. Between the crankshaft and the bearings bearing shells can be arranged as intermediate elements.
Im montierten Zustand ist jeder Lagersattel mit dem korrespondierenden Lagerdeckel verbunden. Jeweils ein Lagersattel und ein Lagerdeckel bilden - gegebenenfalls im Zusammenwirken mit Lagerschalen als Zwischenelemente - eine Bohrung zur Aufnahme eines Kurbelwellenzapfens. Die Bohrungen werden üblicherweise mit Motoröl, d. h. Schmieröl versorgt, so dass sich idealerweise zwischen der Innenfläche jeder Bohrung und dem dazugehörigen Kurbelwellenzapfen bei umlaufender Kurbelwelle - ähnlich einem Gleitlager - ein tragfähiger Schmierfilm ausbildet.When assembled, each bearing saddle is connected to the corresponding bearing cap. In each case a bearing saddle and a bearing cap form - possibly in cooperation with bearing shells as intermediate elements - a bore for receiving a crankshaft journal. The holes are usually supplied with engine oil, ie lubricating oil, so that ideally forms between the inner surface of each hole and the associated crankshaft journal with rotating crankshaft - similar to a plain bearing - a viable lubricating film.
Zur Versorgung der Lager mit Öl ist eine Pumpe zur Förderung von Motoröl zu den mindestens zwei Lagern vorgesehen, wobei die Pumpe via Versorgungsleitung eine Hauptölgalerie, von der Kanäle zu den mindestens zwei Lagern führen, mit Motoröl versorgt. Dabei führt die Versorgungsleitung nach dem Stand der Technik von der Pumpe durch den Zylinderblock zur Hauptölgalerie. Zur Ausbildung der sogenannten Hauptölgalerie wird häufig ein Hauptversorgungskanal vorgesehen, der entlang der Längsachse der Kurbelwelle ausgerichtet ist. Der Hauptversorgungskanal kann oberhalb oder unterhalb der Kurbelwelle im Kurbelgehäuse angeordnet sein oder auch in die Kurbelwelle integriert werden.To supply the bearings with oil, a pump is provided for the delivery of engine oil to the at least two bearings, wherein the pump supplied via the supply line, a main oil gallery, lead from the channels to the at least two camps, with engine oil. The supply line leads according to the prior art of the pump through the cylinder block to Hauptölgalerie. To form the so-called Hauptölgalerie a main supply channel is often provided, which is aligned along the longitudinal axis of the crankshaft. The main supply channel can be arranged above or below the crankshaft in the crankcase or integrated into the crankshaft.
Die vorgesehene Pumpe muß einen ausreichend großen Förderstrom, d. h. ein entsprechend hohes Fördervolumen sicherstellen und für einen ausreichend hohen Öldruck im Versorgungssystem, insbesondere der Hauptölgalerie, sorgen. Gegebenenfalls ist eine dauerhafte Ölversorgung der mindestens zwei Lager nicht erforderlich. Insbesondere wenn die Ölversorgung der Lager mit einer weiteren Ölversorgung beispielsweise via Hauptölgalerie in Verbindung, d. h. in Wechselwirkung steht, kann eine dauerhafte Ölversorgung der Lager nachteilig hinsichtlich des Drucks im Gesamtsystem sein. Insofern kann auch eine lediglich regelmäßige, aber nicht kontinuierliche Ölversorgung der Lager vorteilhaft sein.The intended pump must have a sufficiently large flow, d. H. ensure a correspondingly high delivery volume and ensure a sufficiently high oil pressure in the supply system, in particular the main oil gallery. Optionally, a permanent oil supply of at least two bearings is not required. In particular, when the oil supply of the bearings with another oil supply, for example via Hauptölgalerie in conjunction, d. H. interacts, a permanent supply of oil to the bearings may be detrimental to the pressure in the overall system. In this respect, a merely regular but not continuous oil supply of the bearings can be advantageous.
Eine weitere Ölversorgung im vorstehend genannten Sinn kann beispielsweise die Ölversorgung einer Nockenwelle sein, welche in der Regel in einer zweiteiligen sogenannten Nockenwellenaufnahme gelagert ist. Die bereits hinsichtlich der Kurbelwellenlagerung gemachten Ausführungen gelten in analoger Weise. Auch die Nockenwellenaufnahme wird üblicherweise mit Schmieröl versorgt, wozu ein Versorgungskanal vorgesehen wird, der nach dem Stand der Technik von der Hauptölgalerie abzweigt, durch den Zylinderblock hindurchführt und bei obenliegenden Nockenwellen bis in den Zylinderkopf reicht.Another oil supply in the above sense, for example, be the oil supply to a camshaft, which is usually stored in a two-piece so-called camshaft. The statements already made with regard to the crankshaft bearing apply analogously. The camshaft receptacle is usually supplied with lubricating oil, to which a supply channel is provided, which branches off in the prior art from the main oil gallery, passes through the cylinder block and extends in overhead camshafts into the cylinder head.
Die Reibung in den Lagern der Kurbelwelle, die maßgeblich von der Viskosität und damit von der Temperatur des verwendeten Öls abhängt, trägt zum Kraftstoffverbrauch der Brennkraftmaschine bei.The friction in the bearings of the crankshaft, which depends largely on the viscosity and thus of the temperature of the oil used, contributes to the fuel consumption of the internal combustion engine.
Aufgrund der begrenzten Vorkommen an Mineralöl für die Gewinnung von Kraftstoff, ist man bei der Entwicklung von Brennkraftmaschinen grundsätzlich bemüht, den Kraftstoffverbrauch zu minimieren. Neben einer verbesserten, d. h. effektiveren Verbrennung steht dabei auch die Reduzierung der Reibleistung im Vordergrund der Bemühungen. Ein verminderter Kraftstoffverbrauch trägt auch zu einer Reduzierung der Schadstoffemissionen bei.Due to the limited occurrence of mineral oil for the production of fuel, it is always endeavored in the development of internal combustion engines to minimize fuel consumption. In addition to an improved, d. H. more effective combustion is also the reduction of friction in the foreground of the efforts. A reduced fuel consumption also contributes to a reduction of pollutant emissions.
Vor dem Hintergrund des oben Gesagten ist es eine Aufgabe der vorliegenden Erfindung, eine Brennkraftmaschine gemäß dem Oberbegriff des Anspruches 1 bereitzustellen, die hinsichtlich der Reibleistung optimiert ist.In light of the above, it is an object of the present invention to provide an internal combustion engine according to the preamble of claim 1 which is optimized in terms of friction performance.
Eine weitere Teilaufgabe besteht darin, ein Verfahren zur Erwärmung des Motoröls einer derartigen Brennkraftmaschine aufzuzeigen.Another sub-task is to show a method for heating the engine oil of such an internal combustion engine.
Gelöst wird die erste Teilaufgabe durch eine Brennkraftmaschine mit
- mindestens einem Zylinderkopf,
- mindestens einem mit dem mindestens einen Zylinderkopf verbindbaren und als obere Kurbelgehäusehälfte dienenden Zylinderblock zur Aufnahme einer Kurbelwelle in mindestens zwei Lagern, und
- einer Pumpe zur Förderung von Motoröl zu den mindestens zwei Lagern, wobei die Pumpe via Versorgungsleitung eine Hauptölgalerie mit Motoröl versorgt, von der Kanäle zu den mindestens zwei Lagern führen, und
- die Versorgungsleitung stromaufwärts der Hauptölgalerie durch den Zylinderkopf hindurchführt,
- mindestens ein Abgasturbolader zur Aufladung der Brennkraftmaschine vorgesehen ist, der eine Turbine, einen Verdichter und ein Lager umfasst, wobei die Turbine ein Gehäuse zur Aufnahme eines Laufrades aufweist und die Versorgungsleitung stromaufwärts der Hauptölgalerie durch dieses Turbinengehäuse hindurchführt.
- at least one cylinder head,
- at least one cylinder block connectable to the at least one cylinder head and serving as the upper crankcase half for receiving a crankshaft in at least two bearings, and
- a pump for delivering engine oil to the at least two bearings, the pump supplying via the supply line a main oil gallery with engine oil, leading from the channels to the at least two bearings, and
- the supply line passes through the cylinder head upstream of the main oil gallery,
- at least one exhaust gas turbocharger for charging the internal combustion engine is provided, which comprises a turbine, a compressor and a bearing, wherein the turbine has a housing for receiving an impeller and the Supply line upstream of the main oil gallery passes through this turbine housing.
Im Gegensatz zum Stand der Technik führt die Versorgungsleitung bei der erfindungsgemäßen Brennkraftmaschine durch den Zylinderkopf hindurch, bevor diese Leitung in die Hauptölgalerie mündet. D. h. die Strömungsrichtung des Öls ist gegenüber herkömmlichen Brennkraftmaschinen umgekehrt. Während das Motoröl nach dem Stand der Technik von der Hauptölgalerie zum Zylinderkopf strömt, wird es erfindungsgemäß vom Zylinderkopf zur Hauptölgalerie geleitet.In contrast to the prior art, the supply line in the internal combustion engine according to the invention passes through the cylinder head before this line opens into the main oil gallery. Ie. the flow direction of the oil is reversed compared to conventional internal combustion engines. While the prior art engine oil flows from the main oil gallery to the cylinder head, according to the invention, it is directed from the cylinder head to the main oil gallery.
Das Öl wird beim Passieren des Zylinderkopfes erwärmt, wodurch der stromabwärts angeordneten Hauptölgalerie und damit den stromabwärts gelegenen Lagern der Kurbelwelle ein Öl höherer Temperatur bereitgestellt wird, was die Reibung in den Lagern vermindert und den Kraftstoffverbrauch reduziert.The oil is heated as it passes the cylinder head, providing higher temperature oil to the downstream main gallery and thus to the downstream crankshaft bearings, reducing friction in the bearings and reducing fuel consumption.
Zu berücksichtigen ist dabei, dass der Zylinderkopf thermisch hoch belastet ist, insbesondere im Vergleich zu dem Zylinderblock thermisch höher belastet ist, so dass die Erwärmung des Öls, d. h. der Anstieg der Öltemperatur bei einem Durchströmen des Zylinderkopfes deutlicher ausfällt als beim Durchströmen des Zylinderblocks.It should be noted that the cylinder head is thermally highly loaded, especially in comparison to the cylinder block is thermally loaded higher, so that the heating of the oil, d. H. the increase in the oil temperature at a flow through the cylinder head is more pronounced than when flowing through the cylinder block.
Die erfindungsgemäß ausgestaltete Brennkraftmaschine erweist sich während der Warmlaufphase, insbesondere nach einem Kaltstart, als besonders vorteilhaft. Nach einem Stillstand des Fahrzeuges, d. h. bei einem Neustart der Brennkraftmaschine durchströmt das Öl zunächst den Zylinderkopf, der sich vergleichsweise schnell infolge der ablaufenden Verbrennungsprozesse erwärmt, insbesondere im Vergleich zum Zylinderblock. Insofern wird auch das für die Schmierung der Kurbelwellenlager bereitgestellte Öl schneller erwärmt, wenn es gemäß der erfindungsgemäßen Vorgehensweise zunächst durch den Zylinderkopf geführt wird.The inventively designed engine proves to be particularly advantageous during the warm-up phase, in particular after a cold start. After a stoppage of the vehicle, d. H. When the internal combustion engine is restarted, the oil first flows through the cylinder head, which heats up comparatively quickly as a result of the combustion processes taking place, in particular in comparison to the cylinder block. In this respect, the oil provided for the lubrication of the crankshaft bearings is also heated faster if, according to the procedure according to the invention, it is first guided through the cylinder head.
Es sei angemerkt, dass das Motoröl auch bei der erfindungsgemäßen Brennkraftmaschine durch den Zylinderblock geführt werden kann, beispielsweise wenn die Versorgungsleitung zur Hauptölgalerie vom Zylinderkopf durch den Zylinderblock hindurchgeführt wird.It should be noted that the engine oil can also be performed in the internal combustion engine according to the invention through the cylinder block, for example, when the supply line to the main oil gallery is passed from the cylinder head through the cylinder block.
Erwärmtes Öl bzw. Öl von einer höheren Temperatur weist eine geringere Viskosität auf, was die Reibleistung der Brennkraftmaschine senkt und den Wirkungsgrad verbessert. Infolgedessen wird durch das Erwärmen des Öls der Kraftstoffverbrauch der Brennkraftmaschine spürbar reduziert, insbesondere nach einem Kaltstart.Heated oil of a higher temperature has a lower viscosity, which lowers the friction of the engine and improves the efficiency. As a result, by heating the oil, the fuel consumption of the internal combustion engine is noticeably reduced, in particular after a cold start.
Erfindungsgemäß ist mindestens ein Abgasturbolader, der eine Turbine, einen Verdichter und ein Lager umfasst, zur Aufladung der Brennkraftmaschine vorgesehen.According to the invention, at least one exhaust-gas turbocharger comprising a turbine, a compressor and a bearing is provided for charging the internal combustion engine.
Bei einem Abgasturbolader sind ein Verdichter und eine Turbine auf derselben Welle angeordnet. Die Welle wird in einem Lager aufgenommen, welches zwischen der Turbine und dem Verdichter angeordnet ist. Der heiße Abgasstrom wird der Turbine zugeführt und entspannt sich unter Energieabgabe in dieser, wodurch die Welle in Drehung versetzt wird. Die vom Abgasstrom an die Turbine und schließlich an die Welle abgegebene Energie wird für den Antrieb des ebenfalls auf der Welle angeordneten Verdichters genutzt. Der Verdichter fördert und komprimiert die ihm zugeführte Ladeluft, wodurch eine Aufladung der Zylinder erreicht wird.In an exhaust gas turbocharger, a compressor and a turbine are arranged on the same shaft. The shaft is received in a bearing which is located between the turbine and the compressor. The hot exhaust gas flow is supplied to the turbine and relaxes with energy release in this, whereby the shaft is rotated. The energy emitted by the exhaust gas flow to the turbine and finally to the shaft is used to drive the compressor, which is also arranged on the shaft. The compressor conveys and compresses the charge air supplied to it, whereby a charging of the cylinder is achieved.
Die Aufladung dient in erster Linie der Leistungssteigerung der Brennkraftmaschine. Die für den Verbrennungsprozess benötigte Luft wird dabei verdichtet, wodurch jedem Zylinder pro Arbeitsspiel eine größere Luftmasse zugeführt werden kann. Dadurch können die Kraftstoffmasse und damit der Mitteldruck gesteigert werden.The charge is used primarily to increase the performance of the internal combustion engine. The air required for the combustion process is compressed, which allows each cylinder per working cycle, a larger air mass can be supplied. As a result, the fuel mass and thus the medium pressure can be increased.
Die Aufladung ist ein geeignetes Mittel, bei unverändertem Hubraum die Leistung einer Brennkraftmaschine zu steigern oder bei gleicher Leistung den Hubraum zu reduzieren. In jedem Fall führt die Aufladung zu einer Erhöhung der Bauraumleistung und einer günstigeren Leistungsmasse. Bei gleichen Fahrzeugrandbedingungen lässt sich so das Lastkollektiv zu höheren Lasten hin verschieben, wo der spezifische Kraftstoffverbrauch niedriger ist. Letzteres wird auch als Downsizing bezeichnet.The charge is a suitable means to increase the capacity of an internal combustion engine with unchanged displacement or to reduce the displacement at the same power. In any case, the charging leads to an increase in space performance and a lower power mass. Under the same vehicle boundary conditions, the load spectrum can thus be shifted to higher loads, where the specific fuel consumption is lower. The latter is also referred to as downsizing.
Die Aufladung unterstützt folglich das ständige Bemühen in der Entwicklung von Verbrennungsmotoren, den Kraftstoffverbrauch zu minimieren, d. h. den Wirkungsgrad der Brennkraftmaschine zu verbessern.The charging thus supports the constant effort in the development of internal combustion engines to minimize fuel consumption, ie to improve the efficiency of the internal combustion engine.
Der Vorteil des Abgasturboladers im Vergleich zu einem mechanischen Lader besteht darin, dass keine mechanische Verbindung zur Leistungsübertragung zwischen Lader und Brennkraftmaschine besteht bzw. erforderlich ist. Während ein mechanischer Lader die für seinen Antrieb benötigte Energie vollständig von der Brennkraftmaschine bezieht und somit die bereitgestellte Leistung mindert und auf diese Weise den Wirkungsgrad nachteilig beeinflusst, nutzt der Abgasturbolader die Abgasenergie der heißen Abgase.The advantage of the exhaust gas turbocharger compared to a mechanical supercharger is that there is no mechanical connection to the power transmission between the supercharger and the internal combustion engine or is required. While a mechanical supercharger obtains the energy required for its drive completely from the internal combustion engine and thus reduces the power provided and thus adversely affects the efficiency, the exhaust gas turbocharger uses the exhaust gas energy of the hot exhaust gases.
Die Turbine weist ein Gehäuse zur Aufnahme eines Laufrades auf und die Versorgungsleitung führt erfindungsgemäß stromaufwärts der Hauptölgalerie durch dieses Turbinengehäuse hindurch. Das Turbinengehäuse erwärmt sich nach einem Kaltstart der Brennkraftmaschine aufgrund des heißen Abgasstromes besonders schnell, so dass sich das Gehäuse für einen zügigen Wärmeeintrag in das Motorenöl während der Warmlaufphase eignet. Das durch das Gehäuse hindurch geführte Öl entzieht dem Abgas dabei Wärme und mindert auf diese Weise die Temperatur, d. h. die thermische Belastung des Gehäuses.The turbine has a housing for receiving an impeller and the supply line leads according to the invention upstream of the main oil gallery through this turbine housing. The turbine housing heats up particularly quickly after a cold start of the internal combustion engine due to the hot exhaust gas flow, so that the housing is suitable for a rapid heat input into the engine oil during the warm-up phase. The guided through the housing oil removes heat from the exhaust gas and thus reduces the temperature, d. H. the thermal load of the housing.
Die erfindungsgemäße Brennkraftmaschine löst die der Erfindung zugrundeliegende Aufgabe, nämlich eine Brennkraftmaschine bereitzustellen, die hinsichtlich der Reibleistung optimiert ist.The internal combustion engine according to the invention solves the problem underlying the invention, namely to provide an internal combustion engine, which is optimized in terms of friction.
Der wesentliche Vorteil der erfindungsgemäßen Vorgehensweise gegenüber Konzepten, bei denen das Öl mittels Heizvorrichtung aktiv erwärmt wird, besteht in dem vergleichsweise einfachen Aufbau der erfindungsgemäßen Ölerwärmung. Es sind grundsätzlich keine zusätzlichen Bauteile erforderlich, insbesondere keine externe Heizvorrichtung, die in einer Gesamtbilanz im Hinblick auf den Kraftstoffeinsatz als zusätzlicher Verbraucher auftreten würde. Dies würde einer Lösung der hier zugrundeliegenden Aufgabe entgegenstehen. Ausgehend vom Stand der Technik kann es zur Ausbildung einer erfindungsgemäßen Brennkraftmaschine bereits genügen, die Strömungsrichtung zwischen Hauptölgalerie und Zylinderkopf umzukehren, wobei gegebenenfalls zusätzliche Leitungen bzw. Kanäle zur Ausbildung eines Ölkreislaufs vorzusehen sind.The essential advantage of the procedure according to the invention over concepts in which the oil is actively heated by means of a heating device consists in the comparatively simple construction of the oil heating according to the invention. There are basically no additional components required, in particular no external heating device, which would occur in an overall balance in terms of fuel use as an additional consumer. This would be contrary to a solution of the underlying problem. Based on the prior art, it may already be sufficient for the embodiment of an internal combustion engine according to the invention to reverse the flow direction between the main oil gallery and the cylinder head, wherein additional lines or channels may be provided to form an oil circuit.
Das Teilstück der Versorgungsleitung, welches durch den mindestens einen Zylinderkopf hindurchführt, wird vorzugsweise hinsichtlich seiner primären Funktion, nämlich der Ölerwärmung, ausgelegt, d. h. ausgebildet.The section of the supply line which passes through the at least one cylinder head is preferably designed, ie designed, with regard to its primary function, namely the oil heating.
Mit Hinblick auf Konzepte, bei denen im Betrieb erwärmtes Motoröl in einem isolierten Behältnis gespeichert und bei einem erneuten Start der Brennkraftmaschine zur Schmierung der Lager genutzt wird, muß berücksichtigt werden, dass das im Betrieb erwärmte Öl zeitlich nicht unbegrenzt auf hoher Temperatur gehalten werden kann, weshalb ein Erwärmen des Öls in der Regel während des Betriebs der Brennkraftmaschine erfolgen muß.With regard to concepts in which engine oil warmed up in operation is stored in an insulated container and used to lubricate the bearings when the engine is restarted, it must be taken into account that the oil heated during operation can not be kept indefinitely at high temperature, why a heating of the oil must usually be done during operation of the internal combustion engine.
Weitere vorteilhafte Ausführungsformen der erfindungsgemäßen Brennkraftmaschine werden im Zusammenhang mit den Unteransprüchen erörtert.Further advantageous embodiments of the internal combustion engine according to the invention are discussed in connection with the subclaims.
Vorteilhaft sind Ausführungsformen der Brennkraftmaschine, bei denen eine an die obere Kurbelgehäusehälfte montierbare und als untere Kurbelgehäusehälfte dienende Ölwanne zum Sammeln des Motoröls vorgesehen ist, und die Pumpe aus der Ölwanne stammendes Motoröl via Versorgungsleitung zu der Hauptölgalerie fördert.Embodiments of the internal combustion engine in which an oil sump which can be mounted on the upper crankcase half and serves as a lower crankcase half for collecting the engine oil are provided, and the pump delivers oil from the sump via the supply line to the main oil gallery.
Gemäß dieser Ausführungsform ist das Kurbelgehäuse zweiteilig ausgebildet, wobei die obere Kurbelgehäusehälfte durch eine Ölwanne ergänzt wird, in der das rückgeführte Öl gesammelt wird. Die Ölwanne kann an der Außenseite mit Kühlrippen bzw. Versteifungsrippen ausgestattet sein und wird vorzugsweise aus Blech im Tiefziehverfahren hergestellt, wohingegen die obere Kurbelgehäusehälfte vorzugsweise ein Gußteil ist.According to this embodiment, the crankcase is formed in two parts, wherein the upper crankcase half is supplemented by an oil pan, in which the recirculated oil is collected. The oil pan can be equipped on the outside with cooling ribs or stiffening ribs and is preferably made of sheet metal by deep drawing, whereas the upper crankcase half is preferably a casting.
Bei der Auslegung und Konstruktion des Kurbelgehäuses ist es ein grundsätzliches Ziel, eine möglichst hohe Steifigkeit zu erzielen, um Vibrationen, d. h. Schwingungen zu mindern und auf diese Weise die Geräuschentwicklung und Geräuschemission günstig zu beeinflussen.In the design and construction of the crankcase, it is a fundamental goal to achieve the highest possible stiffness to vibration, d. H. Reduce vibrations and thus influence the noise and noise emission favorable.
Des Weiteren soll das modular aufgebaute Kurbelgehäuse vorzugsweise in der Art aufgebaut sein, dass die Bearbeitung der Montage- und Dichtflächen sowie die Montage in möglichst einfacher Weise erfolgen kann, um die Kosten zu senken.Furthermore, the modular crankcase should preferably be constructed in such a way that the processing of the mounting and sealing surfaces and the assembly can be done in the simplest possible way to reduce costs.
Vorteilhaft sind Ausführungsformen der Brennkraftmaschine, bei denen der mindestens eine Zylinderkopf mit einem zumindest teilweise im Zylinderkopf integrierten Kühlmittelmantel ausgestattet ist.Embodiments of the internal combustion engine in which the at least one cylinder head is equipped with a coolant jacket integrated at least partially in the cylinder head are advantageous.
Die bei der Verbrennung durch die exotherme, chemische Umwandlung des Kraftstoffes freigesetzte Wärme wird teilweise über die den Brennraum begrenzenden Wandungen an den Zylinderkopf und den Zylinderblock und teilweise über den Abgasstrom an die angrenzenden Bauteile und die Umgebung abgeführt. Um die thermische Belastung des Zylinderkopfes in Grenzen zu halten, muß ein Teil des in den Zylinderkopf eingeleiteten Wärmestromes dem Zylinderkopf wieder entzogen werden.The heat released during combustion by the exothermic, chemical conversion of the fuel is partly dissipated via the walls delimiting the combustion chamber to the cylinder head and the cylinder block and partly via the exhaust gas flow to the adjacent components and the environment. In order to keep the thermal load of the cylinder head within limits, a portion of the introduced into the cylinder head heat flow must be withdrawn from the cylinder head again.
Aufgrund der wesentlich höheren Wärmekapazität von Flüssigkeiten gegenüber Luft können mit einer Flüssigkeitskühlung wesentlich größere Wärmemengen abgeführt werden als mit einer Luftkühlung, weshalb die vorstehend genannte Ausführungsform, bei der in dem mindestens einen Zylinderkopf zur Ausbildung einer Flüssigkeitskühlung mindestens ein Kühlmittelmantel integriert wird, vorteilhaft ist.Due to the significantly higher heat capacity of liquids compared to air can be dissipated with a liquid cooling much larger amounts of heat than with air cooling, which is why the above embodiment, in which at least one cylinder head to form a liquid cooling at least one coolant jacket is integrated, is advantageous.
Die Flüssigkeitskühlung, d. h. die Ausbildung eines flüssigkeitsgekühlten Zylinderkopfes erfordert die Ausstattung des Zylinderkopfes mit einem Kühlmittelmantel, d. h. die Anordnung von das Kühlmittel durch den Zylinderkopf führenden Kühlmittelkanälen, was eine komplexe Struktur der Zylinderkopfkonstruktion bedingt. Dabei wird der mechanisch und thermisch hochbelastete Zylinderkopf durch das Einbringen der Kühlmittelkanäle einerseits in seiner Festigkeit geschwächt. Andererseits muß die Wärme nicht wie bei der Luftkühlung erst an die Zylinderkopfoberfläche geleitet werden, um abgeführt zu werden. Die Wärme wird bereits im Inneren des Zylinderkopfes an das Kühlmittel, in der Regel mit Additiven versetztes Wasser, abgegeben. Das Kühlmittel wird dabei mittels einer im Kühlkreislauf angeordneten Pumpe gefördert, so dass es im Kühlmittelmantel zirkuliert. Die an das Kühlmittel abgegebene Wärme wird auf diese Weise aus dem Inneren des Zylinderkopfes abgeführt und in einem Wärmetauscher dem Kühlmittel wieder entzogen.The liquid cooling, d. H. the formation of a liquid-cooled cylinder head requires the equipment of the cylinder head with a coolant jacket, d. H. the arrangement of the coolant through the cylinder head leading coolant channels, which causes a complex structure of the cylinder head construction. In this case, the mechanically and thermally highly stressed cylinder head is weakened by the introduction of the coolant channels on the one hand in its strength. On the other hand, the heat must not be directed to the cylinder head surface as in the air cooling, to be dissipated. The heat is already in the interior of the cylinder head to the coolant, usually mixed with additives added water. The coolant is conveyed by means of a pump arranged in the cooling circuit, so that it circulates in the coolant jacket. The heat given off to the coolant is removed in this way from the interior of the cylinder head and removed from the coolant in a heat exchanger again.
Eine Flüssigkeitskühlung eignet sich insbesondere für aufgeladene Brennkraftmaschinen, die aufgrund höherer Abgastemperaturen eine effiziente und optimierte Kühlung erfordern.Liquid cooling is particularly suitable for supercharged internal combustion engines, which require efficient and optimized cooling due to higher exhaust gas temperatures.
Vorteilhaft sind Ausführungsformen der Brennkraftmaschine, bei denen die Versorgungsleitung entlang eines durch den mindestens einen Zylinderkopf hindurchführenden Teilstücks mindestens zwei Teilversorgungsleitungen umfaßt.Embodiments of the internal combustion engine in which the supply line comprises at least two partial supply lines along a section passing through the at least one cylinder head are advantageous.
Bei dieser Ausführungsform gabelt sich die Versorgungsleitung in mindestens zwei Teilversorgungsleitungen, d. h. fächert sich in mehrere Teilversorgungsleitungen auf. Dies vergrößert die Gesamtoberfläche der Versorgungsleitung entlang eines durch den mindestens einen Zylinderkopf hindurchführenden Teilstücks, wodurch der Wärmeübergang zwischen dem Zylinderkopf und dem in der Versorgungsleitung befindlichen Motoröl unterstützt, d. h. erhöht wird. Damit ist die Versorgungsleitung gemäß der in Rede stehenden Ausführungsform zumindest entlang eines Teilstücks hinsichtlich ihrer primären Funktion im Zylinderkopf optimiert, nämlich hinsichtlich ihrer Funktion als Wärmetauscher.In this embodiment, the supply line forks into at least two partial supply lines, i. H. fanned out into several partial supply lines. This increases the overall surface area of the supply line along a portion passing through the at least one cylinder head, thereby assisting heat transfer between the cylinder head and the engine oil contained in the supply line, i. H. is increased. Thus, the supply line is optimized according to the embodiment in question at least along a section with respect to their primary function in the cylinder head, namely in terms of their function as a heat exchanger.
Der Wärmeübergang zwischen dem Zylinderkopf und dem in der Versorgungsleitung befindlichem Motoröl kann dabei sowohl den Wärmeintrag des heißen Abgasstroms in das Motoröl betreffen als auch - bei flüssigkeitsgekühlten Zylinderköpfen - den Wärmeeintrag bzw. Wärmeentzug des Kühlmittels in das bzw. aus dem Motoröl.The heat transfer between the cylinder head and the motor oil present in the supply line can affect both the heat input of the hot exhaust gas stream into the engine oil and - in liquid-cooled cylinder heads - the heat input or heat removal of the coolant in or out of the engine oil.
Die Versorgungsleitung kann sich dabei im Zylinderkopf in zwei oder mehrere Teilversorgungsleitungen aufspalten, aber auch außerhalb, d. h. stromaufwärts des Zylinderkopfes. Ebenso kann das Zusammenführen der einzelnen Teilversorgungsleitungen zu einer gemeinsamen Versorgungsleitung im Zylinderkopf oder stromabwärts des Zylinderkopfes erfolgen.The supply line can split in the cylinder head in two or more partial supply lines, but also outside, d. H. upstream of the cylinder head. Likewise, the merging of the individual partial supply lines can be made to a common supply line in the cylinder head or downstream of the cylinder head.
Vorteilhaft sind in diesem Zusammenhang Ausführungsformen der Brennkraftmaschine, bei denen die mindestens zwei Teilversorgungsleitungen zumindest streckenweise parallel zueinander verlaufen.In this connection, embodiments of the internal combustion engine in which the at least two partial supply lines run parallel to one another, at least in parts, are advantageous.
Vorteilhaft sind Ausführungsformen der Brennkraftmaschine bei denen sich der in dem mindestens einen Zylinderkopf integrierte Kühlmittelmantel zumindest teilweise auch zwischen den mindestens zwei Teilversorgungsleitungen erstreckt.Embodiments of the internal combustion engine in which the coolant jacket integrated in the at least one cylinder head also extends at least partially between the at least two partial supply lines are advantageous.
Gemäß dieser Ausführungsform erstreckt sich der Kühlmittelmantel auch zwischen den mindestens zwei Teilversorgungsleitungen. Dies schließt insbesondere Ausführungsformen ein, bei denen der Kühlmittelmantel eine gedachte um die mindestens zwei Teilversorgungsleitungen gelegte Einhüllende, d. h. Umhüllende durchtritt, d. h. schneidet.According to this embodiment, the coolant jacket also extends between the at least two partial supply lines. This includes in particular embodiments in which the coolant jacket passes through an imaginary envelope, ie envelope, placed around the at least two partial supply lines, ie, cuts.
Der Kühlmittelmantel bzw. das durch die Kühlkanäle hindurchgeführte Kühlmittel wirkt einer Überhitzung und damit einer vorzeitigen Alterung des Motoröls entgegen und verhindert eine Verkokung des Öls sowie die Bildung von Ablagerungen in der Versorgungsleitung, welche den Strömungsquerschnitt vermindern würden oder zu einem Verschluß der Leitung führen können.The coolant jacket or the coolant passed through the cooling channels counteracts overheating and thus premature aging of the engine oil and prevents coking of the oil and the formation of deposits in the supply line, which would reduce the flow cross-section or lead to a closure of the line.
Vorteilhaft sind Ausführungsformen der Brennkraftmaschine, bei denen der mindestens eine Zylinderkopf mindestens zwei Zylinder umfaßt, wobei jeder Zylinder mindestens eine Auslaßöffnung zum Abführen der Abgase aus dem Zylinder aufweist und sich an jede Auslaßöffnung eine Abgasleitung anschließt, wobei die Abgasleitungen von mindestens zwei Zylindern unter Ausbildung eines integrierten Abgaskrümmers innerhalb des mindestens einen Zylinderkopfes zu einer Gesamtabgasleitung zusammenführen.Embodiments of the internal combustion engine in which the at least one cylinder head comprises at least two cylinders are advantageous, wherein each cylinder has at least one outlet opening for discharging the exhaust gases from the cylinder and an exhaust pipe connects to each outlet opening, the exhaust pipes of at least two cylinders forming a integrated exhaust manifold merge within the at least one cylinder head to form an overall exhaust gas line.
Die Zusammenführung von Abgasleitungen zu einer Gesamtabgasleitung wird im Allgemeinen und im Rahmen der vorliegenden Erfindung als Abgaskrümmer bezeichnet.The combination of exhaust pipes to an overall exhaust line is generally and in the context of the present invention referred to as exhaust manifold.
Ein im Zylinderkopf integrierter Abgaskrümmer hat mehrere Vorteile, auf die im Folgenden kurz eingegangen wird.An integrated in the cylinder head exhaust manifold has several advantages, which will be discussed briefly below.
Stromabwärts eines Krümmers werden die Abgase häufig der Turbine eines Abgasturboladers und/oder einem oder mehreren Abgasnachbehandlungssystemen zugeführt. Dabei ist man zum einen bemüht, den bzw. die Abgasturbolader möglichst nahe am Auslaß der Brennkraftmaschine anzuordnen, um auf diese Weise die Abgasenthalpie der heißen Abgase, die maßgeblich vom Abgasdruck und der Abgastemperatur bestimmt wird, optimal nutzen zu können und ein schnelles Ansprechverhalten des Turboladers zu gewährleisten. Zum anderen soll auch der Weg der heißen Abgase zu den verschiedenen Abgasnachbehandlungssystemen möglichst kurz sein, damit den Abgasen wenig Zeit zur Abkühlung eingeräumt wird und die Abgasnachbehandlungssysteme möglichst schnell ihre Betriebstemperatur bzw. Anspringtemperatur erreichen, insbesondere nach einem Kaltstart der Brennkraftmaschine.Downstream of a manifold, the exhaust gases are often supplied to the turbine of an exhaust gas turbocharger and / or one or more exhaust aftertreatment systems. It is on the one hand endeavored to arrange the exhaust gas turbocharger or the closest possible to the outlet of the engine to optimally use in this way the exhaust enthalpy of the hot exhaust gases, which is largely determined by the exhaust pressure and the exhaust gas temperature, and a quick response of the turbocharger to ensure. On the other hand, the way the hot exhaust gases to the various exhaust aftertreatment systems should be as short as possible, so that the exhaust gases are given little time to cool and the exhaust aftertreatment systems reach their operating temperature or light-off as soon as possible, especially after a cold start of the engine.
Aus den zuvor genannten Gründen ist man daher grundsätzlich bemüht, die thermische Trägheit des Teilstücks der Abgasleitung zwischen Auslaßöffnung am Zylinder und Abgasnachbehandlungssystem bzw. zwischen Auslaßöffnung am Zylinder und Abgasturbolader bzw. Turbine zu minimieren, was durch Reduzierung der Masse und der Länge dieses Teilstückes erreicht werden kann.For the reasons mentioned above, therefore, there is a fundamental effort, the thermal inertia of the section of the exhaust pipe between the exhaust port on the cylinder and the exhaust aftertreatment system or between exhaust port on the cylinder and To minimize turbocharger or turbine, which can be achieved by reducing the mass and the length of this section.
Um die zuvor genannten Ziele zu erreichen, werden die Abgasleitungen vorzugsweise innerhalb des Zylinderkopfes zusammengeführt. Diese Maßnahme gestattet darüber hinaus ein möglichst dichtes Packaging der Antriebseinheit.In order to achieve the aforementioned objects, the exhaust pipes are preferably merged within the cylinder head. This measure also allows the densest possible packaging of the drive unit.
Ausführungsformen des Zylinderkopfes mit beispielsweise vier in Reihe angeordneten Zylindern, bei denen die Abgasleitungen der außenliegenden Zylinder und die Abgasleitungen der innenliegenden Zylinder jeweils zu einer Gesamtabgasleitung zusammengeführt werden, können auch zur Ausbildung einer erfindungsgemäßen Brennkraftmaschine der in Rede stehenden Art verwendet werden. Gleiches gilt für Zylinderköpfe mit drei oder mehr Zylindern, bei denen nur die Abgasleitungen von zwei Zylindern zu einer Gesamtabgasleitung zusammenführen.Embodiments of the cylinder head with, for example, four cylinders arranged in series, in which the exhaust pipes of the outer cylinder and the exhaust pipes of the inner cylinder are each combined to form an overall exhaust line, can also be used to form an internal combustion engine of the type in question. The same applies to cylinder heads with three or more cylinders, in which only the exhaust pipes from two cylinders merge to form an overall exhaust gas line.
Vorteilhaft sind auch Ausführungsformen, bei denen die Abgasleitungen sämtlicher Zylinder des mindestens einen Zylinderkopfes innerhalb des Zylinderkopfes zu einer einzigen, d. h. gemeinsamen Gesamtabgasleitung zusammenführen.Also advantageous are embodiments in which the exhaust pipes of all cylinders of the at least one cylinder head within the cylinder head to a single, d. H. merge together overall exhaust gas line.
Ein Zylinderkopf mit integriertem Abgaskrümmer ist thermisch höher belastet als ein herkömmlicher Zylinderkopf, der mit einem externen Krümmer ausgestattet ist, und stellt daher erhöhte Anforderungen an die Kühlung, weshalb insbesondere bei einem Zylinderkopf mit integriertem Abgaskrümmer eine Flüssigkeitskühlung vorteilhaft ist.A cylinder head with integrated exhaust manifold is thermally loaded higher than a conventional cylinder head, which is equipped with an external manifold, and therefore makes increased demands on the cooling, which is why liquid cooling is particularly advantageous in a cylinder head with integrated exhaust manifold.
Andererseits trägt die Integration des Krümmers dazu bei, die Reibleistung der Brennkraftmaschine weiter zu reduzieren. Denn insbesondere in der Warmlaufphase nach einem Kaltstart der Brennkraftmaschine erreicht ein Zylinderkopf mit integriertem Krümmer schneller höhere Temperaturen als ein konventioneller Zylinderkopf mit einem externen Krümmer.On the other hand, the integration of the manifold helps to further reduce the friction of the internal combustion engine. Because especially in the warm-up phase after a cold start of the internal combustion engine reaches a cylinder head with integrated manifold faster higher temperatures than a conventional cylinder head with an external manifold.
Folglich ist es vorteilhaft, den Krümmer in den Zylinderkopf zu integrieren, um das durch den Zylinderkopf hindurchgeführte Motoröl nach einem Kaltstart möglichst schnell zu erwärmen.Consequently, it is advantageous to integrate the manifold in the cylinder head to heat the engine oil passed through the cylinder head after a cold start as quickly as possible.
Eine Flüssigkeitskühlung des Zylinderkopfes dient vorteilhafterweise zur Begrenzung der Temperaturanhebung des Öls nach oben und kann die Erwärmung des Öls in der Warmlaufphase gegebenenfalls unterstützen.Liquid cooling of the cylinder head advantageously serves to limit the temperature increase of the oil upwards and may possibly assist the heating of the oil in the warm-up phase.
Vorteilhaft sind Ausführungsformen, bei denen der in dem mindestens einen Zylinderkopf integrierte Kühlmittelmantel sich zumindest teilweise auch zwischen dem integrierten Abgaskrümmer und der mindestens einen Versorgungsleitung erstreckt. Diese Anordnung von Kühlmittelmantel, Krümmer und Leitung stellt sicher, dass das Motoröl nicht überhitzt. Der Kühlmittelmantel fungiert bei hohen Abgastemperaturen als Wärmebarriere.Embodiments in which the coolant jacket integrated in the at least one cylinder head extends at least partially between the integrated exhaust manifold and the at least one supply line are advantageous. This arrangement of coolant jacket, manifold and conduit ensures that the engine oil does not overheat. The coolant jacket acts as a thermal barrier at high exhaust gas temperatures.
Gemäß dieser Ausführungsform erstreckt sich der Kühlmittelmantel auch zwischen dem integrierten Abgaskrümmer und der mindestens einen Versorgungsleitung. Dies schließt insbesondere Ausführungsformen ein, bei denen der Kühlmittelmantel eine gedachte Einhüllende durchtritt, welche den Krümmer und die Versorgungsleitung umschließt.According to this embodiment, the coolant jacket also extends between the integrated exhaust manifold and the at least one supply line. This includes in particular embodiments in which the coolant jacket passes through an imaginary envelope which encloses the manifold and the supply line.
Vorteilhaft sind Ausführungsformen, bei denen die Versorgungsleitung zur Versorgung mit Motoröl mit einer Nockenwellenaufnahme in Verbindung steht.Embodiments in which the supply line for supplying engine oil is connected to a camshaft receptacle are advantageous.
Nach dem Stand der Technik werden für den Ladungswechsel als Steuerorgane in der Regel Ventile verwendet, die entlang ihrer Längsachse zwischen einer Ventilschließstellung und einer Ventiloffenstellung bewegbar sind, um eine Einlaß- oder Auslaßöffnung freizugeben bzw. zu versperren. Zur Betätigung des Ventils werden einerseits Ventilfedermittel vorgesehen, um das Ventil in Richtung Ventilschließstellung vorzuspannen, und andererseits Ventilbetätigungseinrichtungen eingesetzt, um das Ventil entgegen der Vorspannkraft der Ventilfedermittel zu öffnen.According to the state of the art, valves which are movable along their longitudinal axis between a valve-closed position and a valve-open position are generally used for the charge exchange as control members in order to release or obstruct an inlet or outlet opening. For actuation of the valve on the one hand valve spring means are provided to bias the valve in the direction of valve closing position, and on the other hand valve actuators used to open the valve against the biasing force of the valve spring means.
Die Ventilbetätigungseinrichtung umfaßt vorliegend eine Nockenwelle, auf der eine Vielzahl von Nocken angeordnet ist und die - beispielsweise mittels eines Kettenantriebes - von der Kurbelwelle in der Art in Drehung versetzt wird, dass die Nockenwelle mit der halben Kurbelwellendrehzahl umläuft.The valve actuator comprises in the present case a camshaft on which a plurality of cams is arranged and which - for example by means of a chain drive - is rotated by the crankshaft in such a way that the cam shaft rotates at half the crankshaft speed.
Häufig werden obenliegende Nockenwellen eingesetzt, d. h. Nockenwellen, die oberhalb der Montagefläche zwischen Zylinderkopf und Zylinderblock angeordnet und im Zylinderkopf gelagert sind.Often overhead camshafts are used, i. H. Camshafts, which are arranged above the mounting surface between the cylinder head and cylinder block and stored in the cylinder head.
Obenliegende Nockenwellen werden beispielsweise in zweiteiligen sogenannten Nockenwellenaufnahmen gelagert. Hierzu verfügt die Nockenwelle über mindestens zwei Lagerstellen, die in der Regel als verdickte Wellenabsätze ausgebildet sind. Die Nockenwellenaufnahme umfaßt einen unteren Teil und einen oberen Teil, in denen die Lagersättel bzw. Lagerdeckel angeordnet sind. Die Nockenwelle wird mit ihren Lagerstellen in den Lagersätteln und Lagerdeckeln aufgenommen und gelagert. Die Lager werden dabei mit Motoröl versorgt, so dass sich bei umlaufender Nockenwelle - ähnlich einem Gleitlager - ein tragfähiger Schmierfilm ausbildet.Overhead camshafts are stored for example in two-piece so-called camshaft shots. For this purpose, the camshaft has at least two bearing points, which are usually designed as thickened shaft shoulders. The camshaft receiving comprises a lower part and an upper part, in which the bearing saddles or bearing caps are arranged. The camshaft is received and stored with their bearings in the bearing saddles and bearing caps. The bearings are supplied with engine oil, so that a revolving camshaft - similar to a plain bearing - forms a viable lubricating film.
Zur Versorgung der Nockenwellenlager mit Öl steht gemäß der in Rede stehenden Ausführungsform die Versorgungsleitung mit der Nockenwellenaufnahme in Verbindung. Die Versorgung der Nockenwellenlager via Versorgungsleitung mit erwärmtem Motoröl verringert die Reibung in den Lagern der Nockenwelle und reduziert die Reibleistung der Brennkraftmaschine weiter. Dies gilt sowohl für die Nockenwelle der Einlaßventile, d. h. der Einlaßseite als auch für die Nockenwelle der Auslaßventile, d. h. der Auslaßseite.To supply the camshaft bearing with oil is in accordance with the present embodiment, the supply line with the camshaft receptacle in combination. The supply of the camshaft bearing via supply line with heated engine oil reduces the friction in the bearings of the camshaft and further reduces the friction of the engine. This applies to both the camshaft of the intake valves, d. H. the inlet side as well as for the camshaft of the exhaust valves, d. H. the outlet side.
Vorteilhaft sind ebenfalls Ausführungsformen, bei denen die Versorgungsleitung stromaufwärts der Hauptölgalerie das Lager des Abgasturboladers mit Öl versorgt. Das Lager der Welle muß grundsätzlich mit Öl versorgt werden, so dass es vorteilhaft ist, die Versorgungsleitung hierfür zu nutzen, d. h. die Leitung zum Lager zu führen bzw. durch das Lagergehäuse hindurch zu führen. Stromaufwärts des Lagers kann die Versorgungsleitung durch das Turbinengehäuse führen oder aber direkt vom Zylinderkopf kommend zum Lager führen.Also advantageous are embodiments in which the supply line upstream of the main oil gallery supplies the bearing of the exhaust gas turbocharger with oil. The bearing of the shaft must always be supplied with oil, so that it is advantageous to use the supply line for this purpose, ie to lead the line to the camp or to pass through the bearing housing. Upstream of the bearing, the supply line can lead through the turbine housing or lead directly from the cylinder head to the camp.
Vorteilhaft sind Ausführungsformen, bei denen die Turbine zur Ausbildung einer Flüssigkeitskühlung mit einem Kühlmittelmantel ausgestattet ist, wobei der Kühlmittelmantel vorzugsweise im Turbinengehäuse integriert ist. Die thermische Belastung des Turbinengehäuses ist vergleichsweise hoch. Die Kühlung der Turbine gestattet eine Fertigung des Gehäuses aus Blech bzw. aus thermisch weniger belastbaren Werkstoffen, was Kostenvorteile bietet. Der Einsatz kostenintensiver - häufig nickelhaltiger - Werkstoffe ist nicht mehr erforderlich bzw. wird stark reduziert.Embodiments in which the turbine is provided with a coolant jacket to form a liquid cooling system are advantageous, wherein the coolant jacket is preferably integrated in the turbine housing. The thermal load of the turbine housing is comparatively high. The cooling of the turbine allows a production of the housing made of sheet metal or thermally less resilient materials, which offers cost advantages. The use of cost-intensive - often nickel-containing - materials is no longer necessary or is greatly reduced.
Vorteilhaft sind Ausführungsformen, bei denen das Turbinengehäuse zumindest teilweise aus Aluminium gefertigt ist. Dies bringt gegenüber der Verwendung üblicher Werkstoffe Kostenvorteile mit sich. Darüber hinaus führt der Einsatz von Aluminium zur Herstellung des Turbinengehäuses zu einem geringeren Gewicht.Embodiments in which the turbine housing is at least partially made of aluminum are advantageous. This brings cost benefits compared to the use of conventional materials. In addition, the use of aluminum for the manufacture of the turbine housing leads to a lower weight.
Bei Brennkraftmaschinen, bei denen der mindestens eine Zylinderkopf flüssigkeitsgekühlt ist, insbesondere mit einem zumindest teilweise im Zylinderkopf integrierten Kühlmittelmantel ausgestattet ist, sind Ausführungsformen vorteilhaft, bei denen der Kühlmittelmantel der Turbine mit der Flüssigkeitskühlung des Zylinderkopfes, d.h. mit dem im Zylinderkopf integrierten Kühlmittelmantel, verbunden ist.In internal combustion engines in which the at least one cylinder head is liquid-cooled, in particular equipped with a coolant jacket integrated at least partially in the cylinder head, embodiments are advantageous in which the coolant jacket of the turbine is connected to the liquid cooling of the cylinder head, ie to the coolant jacket integrated in the cylinder head ,
Die zweite der Erfindung zugrunde liegende Teilaufgabe, nämlich ein Verfahren zur Erwärmung des Motoröls für eine Brennkraftmaschine einer zuvor genannten Art aufzuzeigen, wird gelöst durch ein Verfahren, das dadurch gekennzeichnet ist, dass das Motoröl stromaufwärts der mindestens zwei Lager durch den mindestens einen Zylinderkopf hindurchgeführt wird.The second sub-problem underlying the invention, namely to show a method for heating the engine oil for an internal combustion engine of the aforementioned type, is achieved by a method which is characterized in that the engine oil is passed through the at least one cylinder head upstream of the at least two bearings ,
Das im Zusammenhang mit der erfindungsgemäßen Brennkraftmaschine Gesagte gilt ebenfalls für das erfindungsgemäße Verfahren.The comments made in connection with the internal combustion engine according to the invention also apply to the inventive method.
Im Folgenden wird die Erfindung anhand von drei Ausführungsbeispielen der Brennkraftmaschine gemäß den
- Fig. 1
- schematisch das Fragment eines Zylinderkopfes einer ersten Ausführungsform der Brennkraftmaschine in einer perspektivischen Darstellung im Querschnitt,
- Fig. 2
- schematisch das Fragment eines Zylinderkopfes einer zweiten Ausführungsform der Brennkraftmaschine in einer perspektivischen Darstellung im Querschnitt, und
- Fig. 3
- schematisch das Fragment eines Zylinderkopfes einer dritten Ausführungsform der Brennkraftmaschine in einer perspektivischen Darstellung im Querschnitt bzw. Längsschnitt.
- Fig. 1
- 1 is a schematic cross-sectional view of the fragment of a cylinder head of a first embodiment of the internal combustion engine;
- Fig. 2
- schematically the fragment of a cylinder head of a second embodiment of the internal combustion engine in a perspective view in cross section, and
- Fig. 3
- schematically the fragment of a cylinder head of a third embodiment of the internal combustion engine in a perspective view in cross section and longitudinal section.
Der Zylinderkopf 1 verfügt über mehrere in Reihe angeordnete Zylinder 14. Der Brennraum 13 jedes Zylinders 14 wird über zwei Einlaßkanäle 12 mit Frischgemisch bzw. Frischluft versorgt. Zwei Auslaßöffnungen je Zylinder 14 dienen zum Abführen der Abgase, wobei sich an jede Auslaßöffnung eine Abgasleitung 4 anschließt. Die Abgasleitungen 4 sämtlicher Zylinder 14 führen unter Ausbildung eines integrierten Abgaskrümmers 5 innerhalb des Zylinderkopfes 1 zu einer Gesamtabgasleitung 6 zusammen.The cylinder head 1 has a plurality of cylinders 14 arranged in series. The combustion chamber 13 of each cylinder 14 is supplied with fresh mixture or fresh air via two
Der in
Eine Versorgungsleitung 2 führt entlang der Längsachse des Zylinderkopfes 1 durch den Zylinderkopf 1 hindurch. Die Leitung 2 dient der Versorgung der Lager einer im Kurbelgehäuse aufgenommenen Kurbelwelle mit Motoröl 3 (nicht dargestellt) und verläuft oberhalb des Kühlmittelmantels 7, d.h. die Leitung 2 ist auf der dem Abgaskrümmer 5 abgewandten Seite des Kühlmittelmantels 7 angeordnet.A supply line 2 leads along the longitudinal axis of the cylinder head 1 through the cylinder head 1 therethrough. The line 2 serves to supply the bearings of a crank shaft received in the crankcase with engine oil 3 (not shown) and extends above the
Bei dem in
Hierzu steht die Versorgungsleitung 2 mit der Nockenwellenaufnahme 9 in Verbindung (nicht dargestellt). Die Versorgung der Nockenwellenlager 10 via Versorgungsleitung 2 mit erwärmtem Motoröl 3 verringert die Reibung in den Lagern 10 der Nockenwelle. Gleiches gilt in analoger Weise für die Lager der Kurbelwelle.For this purpose, the supply line 2 is in communication with the camshaft receptacle 9 (not shown). The supply of the camshaft bearing 10 via supply line 2 with heated engine oil 3 reduces the friction in the bearings 10 of the camshaft. The same applies analogously to the bearings of the crankshaft.
Zu erkennen ist auch die Nockenwellenaufnahme für die Nockenwelle der Einlaßventile, sowie eine weitere Leitung 15, welche entlang der Langsachse des Zylinderkopfes 1 verläuft und die Nockenwellenlager auf der Einlaßseite mit Schmieröl versorgt.Evident is also the camshaft receptacle for the camshaft of the intake valves, and a
Es sollen die Unterschiede zu der in
Der zur Ausbildung einer Flüssigkeitskühlung im Zylinderkopf 1 integrierte Kühlmittelmantel 7 ist im Wesentlichen oberhalb des Abgaskrümmers 5 angeordnet, d.h. auf der dem Zylinderblock (nicht dargestellt) abgewandten Seite des Krümmers 5 und führt um den Krümmer 5 herum bis hin zur Unterseite des Krümmers 5. Der Kühlmittelmantel 7 wird auf der Unterseite des Krümmers 5 von der Versorgungsleitung 2 unterbrochen, d.h. der Kühlmittelmantel 7 verläuft beidseitig der Leitung 2 und verfügt über eine Öffnung 16, die benachbart zur Gesamtabgasleitung 6 an einer Längsseite des Zylinderkopfes 1 vorgesehen und im montierten Zustand des Kopfes 1 verschlossen ist. Das Einbringen der Öffnung 16 erfolgt aus fertigungstechnischen Gründen und dient der Nachbearbeitung des Kühlmittelmantels 7. Nichtsdestotrotz kann die Öffnung 16 zur Entnahme von Kühlmittel auch geöffnet bleiben, beispielsweise zur Versorgung eines flüssigkeitsgekühlten Turboladers mit Kühlmittel.The integrated for forming a liquid cooling in the cylinder head 1
Die Versorgungsleitung 2 verläuft bei der in
Es sollen nur die Unterschiede zu den in den
Die Versorgungsleitung 2 verläuft bei dem in
Der zur Ausbildung einer Flüssigkeitskühlung im Zylinderkopf 1 integrierte Kühlmittelmantel 7 verläuft sowohl oberhalb des Abgaskrümmers 5, d. h. auf der dem Zylinderblock (nicht dargestellt) abgewandten Seite des Krümmers 5 als auch auf der Unterseite des Krümmers 5. Der Kühlmittelmantel 7 wird auf der Unterseite des Krümmers 5 - wie in
Auf der dem Zylinderblock abgewandten Seite des Krümmers 5 ist die Nockenwellenaufnahme 9 für die Auslaßnockenwelle angeordnet. Eine weitere Leitung 15 dient der Versorgung der Nockenwellenlager 10 mit Schmieröl. Jedes Lager 10 umfaßt einen Lagersattel 11 und einen Lagerdeckel (nicht dargestellt).On the side facing away from the cylinder block of the
Gegenüberliegend, d. h. auf der Einlaßseite ist die Nockenwellenaufnahme 9 für die Nockenwelle der Einlaßventile angeordnet, welche ebenfalls über eine weitere Leitung 15 mit Schmieröl versorgt wird.Opposite, ie on the inlet side, the
- 11
- Zylinderkopfcylinder head
- 22
- Versorgungsleitungsupply line
- 33
- MotorölEngine oil
- 44
- Abgasleitungexhaust pipe
- 55
- Abgaskrümmerexhaust manifold
- 66
- GesamtabgasleitungTotal exhaust pipe
- 77
- KühlmittelmantelCoolant jacket
- 88th
- Kühlmittelcoolant
- 99
- Nockenwellenaufnahmecamshaft mount
- 1010
- Lagerstelledepository
- 1111
- Lagersattelbearing saddle
- 1212
- Einlaßkanalintake port
- 1313
- Brennraumcombustion chamber
- 1414
- Zylindercylinder
- 1515
- weitere Leitunganother line
- 1616
- Öffnungopening
Claims (13)
- Internal combustion engine having- at least one cylinder head (1),- at least one cylinder block, which can be connected to the at least one cylinder head (1) and which serves as an upper crankcase half, for holding a crankshaft in at least two bearings, and- a pump for feeding engine oil (3) to the at least two bearings, with the pump supplying engine oil (3) via a supply line (2) to a main oil gallery from which ducts lead to the at least two bearings, and- upstream of the main oil gallery, the supply line (2) extends through the cylinder head (1), characterized in that- at least one exhaust-gas turbocharger is provided for the purposes of supercharging the internal combustion engine, which at least one exhaust-gas turbocharger comprises a turbine, a compressor and a bearing, wherein the turbine has a housing for accommodating an impeller, and, upstream of the main oil gallery, the supply line (2) leads through said turbine housing.
- Internal combustion engine according to Claim 1, characterized in that- an oil pan which can be mounted on the upper crankcase half and which serves as a lower crankcase half is provided for collecting the engine oil (3), and the pump feeds engine oil (3) originating from the oil pan via a supply line (2) to the main oil gallery.
- Internal combustion engine according to Claim 1 or 2, characterized in that the at least one cylinder head (1) is equipped with a coolant jacket (7) which is at least partially integrated in the cylinder head (1).
- Internal combustion engine according to one of the preceding claims, characterized in that the supply line (2) comprises at least two partial supply lines along a part which extends through the at least one cylinder head (1).
- Internal combustion engine according to Claim 4, characterized in that the at least two partial supply lines run parallel to one another at least in sections.
- Internal combustion engine according to Claim 4 or 5, characterized in that the coolant jacket (7) which is integrated in the at least one cylinder head (1) also extends at least partially between the at least two partial supply lines.
- Internal combustion engine according to one of the preceding claims, characterized in that the at least one cylinder head (1) comprises at least two cylinders (14), with each cylinder (14) having at least one outlet opening for discharging the exhaust gases out of the cylinder (14) and with each outlet opening being adjoined by an exhaust line (4), with the exhaust lines (4) of at least two cylinders (14) merging to form an overall exhaust line (6) within the at least one cylinder head (1), so as to form an integrated exhaust manifold (5).
- Internal combustion engine according to one of Claims 3 to 7, characterized in that the coolant jacket (7) which is integrated in the at least one cylinder head (1) also extends at least partially between the integrated exhaust manifold (5) and the at least one supply line (2) .
- Internal combustion engine according to one of the preceding claims, characterized in that the supply line (2) is connected to a camshaft receptacle (9) in order to supply engine oil (3) .
- Internal combustion engine according to one of the preceding claims, characterized in that, upstream of the main oil gallery, the supply line (2) supplies oil to the bearing of the exhaust-gas turbocharger.
- Internal combustion engine according to one of the preceding claims, characterized in that the turbine is equipped with a coolant jacket for the purposes of forming a liquid-type cooling arrangement.
- Internal combustion engine according to Claim 11, in which the at least one cylinder head (1) is equipped with a coolant jacket (7) at least partially integrated in the cylinder head (1), characterized in that the coolant jacket of the turbine is connected to the coolant jacket (7) integrated in the cylinder head (1).
- Method for heating the engine oil (3) using an internal combustion engine according to one of the preceding claims, characterized in that, upstream of the at least two bearings, the engine oil (3) is conducted through the at least one cylinder head (1).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009045320A DE102009045320A1 (en) | 2009-10-05 | 2009-10-05 | Internal combustion engine with pump for pumping engine oil and method for heating the engine oil of such an internal combustion engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2305975A2 EP2305975A2 (en) | 2011-04-06 |
EP2305975A3 EP2305975A3 (en) | 2011-05-11 |
EP2305975B1 true EP2305975B1 (en) | 2018-09-12 |
Family
ID=43125482
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10154681.0A Active EP2305975B1 (en) | 2009-10-05 | 2010-02-25 | Combustion engine with pump for transporting engine oil and method for heating the engine oil of such a combustion engine |
Country Status (4)
Country | Link |
---|---|
US (1) | US7992535B2 (en) |
EP (1) | EP2305975B1 (en) |
CN (1) | CN201924987U (en) |
DE (1) | DE102009045320A1 (en) |
Families Citing this family (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007060397A1 (en) * | 2007-12-14 | 2009-06-18 | GM Global Technology Operations, Inc., Detroit | Turbocharger and cylinder head |
DE102009029289B4 (en) * | 2009-09-09 | 2013-08-08 | Ford Global Technologies, Llc | Cylinder head with oil return |
DE102010024319B4 (en) * | 2010-06-18 | 2016-03-03 | Audi Ag | Internal combustion engine with coolant busbar for after-running and / or warm-up cooling |
DE102011075666B4 (en) * | 2011-05-11 | 2018-07-12 | Ford Global Technologies, Llc | Method for heating the engine oil of an internal combustion engine and internal combustion engine for carrying out such a method |
DE102011114305A1 (en) * | 2011-09-23 | 2013-03-28 | Audi Ag | Internal combustion engine and method for operating an internal combustion engine |
CN102644494A (en) * | 2012-05-12 | 2012-08-22 | 中国兵器工业集团第七0研究所 | Novel lubricating oil circuit for valve mechanism of diesel engine |
GB201208935D0 (en) | 2012-05-21 | 2012-07-04 | Ford Global Tech Llc | An engine system |
US9169801B2 (en) * | 2012-07-31 | 2015-10-27 | Ford Global Technologies, Llc | Internal combustion engine with oil-cooled cylinder block and method for operating an internal combustion engine of said type |
GB2511136B (en) * | 2013-02-26 | 2019-12-04 | Mclaren Automotive Ltd | Engine cooling |
JP6225505B2 (en) * | 2013-06-24 | 2017-11-08 | トヨタ自動車株式会社 | cylinder head |
US9261044B2 (en) | 2014-01-13 | 2016-02-16 | Ford Global Technologies, Llc | Cylinder gasket having oil drainback constraint feature for use with internal combustion engine |
GB2525863B (en) * | 2014-05-06 | 2020-08-05 | Ford Global Tech Llc | An engine block |
US9810113B2 (en) | 2015-03-09 | 2017-11-07 | The Boeing Company | Engine lubrication heating system |
US9784175B2 (en) * | 2015-06-01 | 2017-10-10 | Ford Global Technologies, Llc | Internal combustion engine and coolant pump |
DE102016201414B4 (en) * | 2016-01-29 | 2017-10-05 | Ford Global Technologies, Llc | Internal combustion engine with oil circuit |
US10781731B2 (en) * | 2016-07-28 | 2020-09-22 | Ford Global Technologies, Llc | Method and assembly for heating an engine fluid |
US10550754B2 (en) * | 2017-05-15 | 2020-02-04 | Polaris Industries Inc. | Engine |
US10639985B2 (en) | 2017-05-15 | 2020-05-05 | Polaris Industries Inc. | Three-wheeled vehicle |
US10428705B2 (en) | 2017-05-15 | 2019-10-01 | Polaris Industries Inc. | Engine |
US10576817B2 (en) | 2017-05-15 | 2020-03-03 | Polaris Industries Inc. | Three-wheeled vehicle |
JP6939485B2 (en) * | 2017-12-04 | 2021-09-22 | トヨタ自動車株式会社 | cylinder head |
CN108894886B (en) * | 2018-08-14 | 2024-05-14 | 重庆万虎机电有限责任公司 | Engine of motor tricycle, cylinder head and cooling system thereof |
USD904227S1 (en) | 2018-10-26 | 2020-12-08 | Polaris Industries Inc. | Headlight of a three-wheeled vehicle |
DE112019006640T5 (en) * | 2019-01-10 | 2021-10-07 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | MOTOR AND INVERTER INTEGRATED ROTATING ELECTRIC MACHINE |
CN109915274A (en) * | 2019-03-05 | 2019-06-21 | 广西玉柴机器股份有限公司 | A kind of braided channel cylinder head of anti-carbonization of oil |
FR3105649B1 (en) * | 2019-12-19 | 2021-11-26 | Valeo Equip Electr Moteur | Cooled rotating electric machine |
JP7279650B2 (en) * | 2020-01-20 | 2023-05-23 | トヨタ自動車株式会社 | internal combustion engine |
JP7065901B2 (en) * | 2020-03-18 | 2022-05-12 | 本田技研工業株式会社 | Cylinder head of multi-cylinder engine |
JP7509048B2 (en) * | 2021-02-02 | 2024-07-02 | トヨタ自動車株式会社 | Electric vehicles |
US20240077073A1 (en) * | 2022-09-01 | 2024-03-07 | EKU Power Drives Inc. | Reservoir for dual loop lubrication and thermal management system for pumps |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0640305U (en) * | 1992-11-09 | 1994-05-27 | 日産自動車株式会社 | Oil temperature raising device for internal combustion engine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2252705A1 (en) * | 1972-10-27 | 1974-05-02 | Daimler Benz Ag | MOUNTING OF AN EXHAUST TURBOCHARGER TO A COMBUSTION ENGINE |
JPS6147437U (en) * | 1984-08-31 | 1986-03-29 | 日産ディーゼル工業株式会社 | Turbo gear lubrication system for internal combustion engines |
JPS61135911A (en) * | 1984-12-06 | 1986-06-23 | Mitsubishi Heavy Ind Ltd | Lubricant oil heating device for internal combustion engine |
JP2709815B2 (en) * | 1988-01-11 | 1998-02-04 | ヤマハ発動機株式会社 | Cylinder head structure of turbocharged engine |
JP3447782B2 (en) * | 1993-01-19 | 2003-09-16 | トヨタ自動車株式会社 | Internal combustion engine lubrication system |
JPH08177440A (en) * | 1994-12-26 | 1996-07-09 | Nissan Motor Co Ltd | Lubricating device of internal combustion engine |
DE10235189A1 (en) * | 2002-07-26 | 2004-02-12 | Weber Motor Ag | Turbine housing for a turbocharger internal combustion engine, turbocharger internal combustion engine and method for cooling a turbocharger internal combustion engine |
DE102007060397A1 (en) * | 2007-12-14 | 2009-06-18 | GM Global Technology Operations, Inc., Detroit | Turbocharger and cylinder head |
-
2009
- 2009-10-05 DE DE102009045320A patent/DE102009045320A1/en not_active Ceased
-
2010
- 2010-02-25 EP EP10154681.0A patent/EP2305975B1/en active Active
- 2010-09-28 US US12/892,184 patent/US7992535B2/en active Active
- 2010-10-08 CN CN2010205543942U patent/CN201924987U/en not_active Expired - Lifetime
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0640305U (en) * | 1992-11-09 | 1994-05-27 | 日産自動車株式会社 | Oil temperature raising device for internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
DE102009045320A1 (en) | 2011-04-28 |
EP2305975A3 (en) | 2011-05-11 |
CN201924987U (en) | 2011-08-10 |
EP2305975A2 (en) | 2011-04-06 |
US7992535B2 (en) | 2011-08-09 |
US20110079187A1 (en) | 2011-04-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2305975B1 (en) | Combustion engine with pump for transporting engine oil and method for heating the engine oil of such a combustion engine | |
DE102010027816B4 (en) | Internal combustion engine with oil circuit and method for heating the engine oil of such an internal combustion engine | |
EP2385229B1 (en) | Internal combustion engine with liquid cooling system | |
DE102012210320B3 (en) | Liquid-cooled combustion engine for vehicle, has steering valve arranged in connecting line between pump and vent tank and providing enlarged passage area as result of reduced pressure refrigerant in work position | |
DE102011075666B4 (en) | Method for heating the engine oil of an internal combustion engine and internal combustion engine for carrying out such a method | |
EP2503125B1 (en) | Internal combustion engine equipped with two turbochargers and method to operate such an engine | |
DE102014218587B4 (en) | Supercharged internal combustion engine with a liquid-coolable turbine and method for controlling the cooling of this turbine | |
DE102008035957B4 (en) | Cylinder head for an internal combustion engine | |
DE102013214865A1 (en) | Internal combustion engine with oil-cooled cylinder block and method for operating such an internal combustion engine | |
DE102017202154A1 (en) | Charged liquid-cooled internal combustion engine | |
DE102016222184B4 (en) | A liquid-cooled internal combustion engine comprising a cylinder block and a method for manufacturing an associated cylinder block | |
DE102011002562B4 (en) | Supercharged liquid-cooled internal combustion engine | |
EP2143898A1 (en) | Arrangement with cylinder head and cylinder block | |
DE102009029289B4 (en) | Cylinder head with oil return | |
DE202010005708U1 (en) | Internal combustion engine with cylinder head and turbine | |
EP1709307B1 (en) | Coolant pump arrangement for an internal combustion engine | |
DE202013103704U1 (en) | Cylinder head with an axial turbine | |
DE102010037969B4 (en) | Internal combustion engine with liquid-cooled turbine and method for cooling the turbine | |
DE102013216112A1 (en) | Cylinder head with an axial turbine | |
DE102018206391A1 (en) | Internal combustion engine with oil circuit and method for need-based conditioning of the engine oil of such an internal combustion engine | |
DE102020200039B4 (en) | Internal combustion engine with at least one liquid-cooled cylinder tube | |
DE202014101338U1 (en) | Internal combustion engine with pump for pumping engine oil | |
DE102014205352A1 (en) | Internal combustion engine with pump for pumping engine oil and method for operating such an internal combustion engine | |
DE102015203329B4 (en) | Externally ignited internal combustion engine with a pump for delivering engine oil and a method for operating such an internal combustion engine | |
DE102016200269A1 (en) | Method for operating a liquid-cooled four-stroke internal combustion engine and four-stroke internal combustion engine for carrying out such a method |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F01M 5/00 20060101ALI20110406BHEP Ipc: F01M 11/02 20060101AFI20101130BHEP Ipc: F02B 39/00 20060101ALI20110406BHEP Ipc: F01M 9/10 20060101ALI20110406BHEP Ipc: F01M 5/02 20060101ALI20110406BHEP Ipc: F01N 13/00 20100101ALI20110406BHEP |
|
17P | Request for examination filed |
Effective date: 20111111 |
|
17Q | First examination report despatched |
Effective date: 20161018 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20180507 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502010015350 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1040841 Country of ref document: AT Kind code of ref document: T Effective date: 20181015 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20180912 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181213 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181212 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20181212 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190112 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20190112 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502010015350 Country of ref document: DE |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
26N | No opposition filed |
Effective date: 20190613 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190225 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20190228 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190228 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 1040841 Country of ref document: AT Kind code of ref document: T Effective date: 20190225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190225 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20200130 Year of fee payment: 11 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20200124 Year of fee payment: 11 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20100225 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20210225 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210225 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20180912 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230620 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240109 Year of fee payment: 15 |