EP2409005B1 - Method and apparatus for oiling rotating or oscillating components - Google Patents
Method and apparatus for oiling rotating or oscillating components Download PDFInfo
- Publication number
- EP2409005B1 EP2409005B1 EP10713597.2A EP10713597A EP2409005B1 EP 2409005 B1 EP2409005 B1 EP 2409005B1 EP 10713597 A EP10713597 A EP 10713597A EP 2409005 B1 EP2409005 B1 EP 2409005B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- oil
- exhaust gas
- valve
- heat exchanger
- line
- 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.)
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Classifications
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- 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
- F01M5/005—Controlling temperature of lubricant
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- 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
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- 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
- F01M5/002—Cooling
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
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- 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
- F01M11/0004—Oilsumps
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
Definitions
- the invention relates to a method for heating a lubrication system of rotating or oscillating components, in particular for an internal combustion engine or a transmission, with at least one ⁇ lsaugrohr, which is arranged in an oil sump and with the oil return bypass bypass line, wherein in the bypass line, a valve is arranged ,
- the DE 27 53 716 relates to a hot air-emitting heater for powered by an internal combustion engine motor vehicles, acted upon by atmospheric air heat exchanger for heat dissipation of a flowing in a conduit heat transfer medium and also in the line circuit turned on, the exhaust heat of the engine receiving and delivering to the heat carrier heat exchanger.
- the line circuit for the heat carrier of the heater is at least with the lubricating oil circuit Internal combustion engine in heat-conducting connection.
- a heat transfer to the lubricating oil in a dry sump is achieved in that heat is discharged through a flowing in a feed line heat transfer to the located in the dry sump tank lubricating oil.
- the GB 2 381 576 A discloses an exhaust heat recovery apparatus having a heat exchange conduit and a bypass conduit. In the region of the heat exchanger line, a heat exchanger is arranged. At least one valve device is provided in the heat exchanger line and / or the bypass line in order to influence an exhaust gas flow rate in the heat exchanger line. At least the heat exchanger line has a gradient in an exhaust gas flow direction in the installed position.
- the EP 0 885 758 B1 relates to a method for operating a heat exchanger in the exhaust gas stream of an internal combustion engine for motor vehicles, in which the exhaust gas stream is divisible into a main line and into a bypass line.
- the heat exchanger is arranged in the bypass line.
- a backflow can be generated in the main line, which causes a back pressure at the exhaust gas outlet of the internal combustion engine.
- the warm-up operation is divided into two phases, wherein in the first phase, a higher back pressure than in the second phase is generated.
- a first valve is disposed in the main conduit between the bypass conduit ports, with a second valve disposed in the bypass conduit downstream of the heat exchanger. In the first phase, both valves are closed, wherein in the second phase, the first valve is closed, but the second valve is open.
- the EP 0 202 344 describes a tank truck for transporting liquid goods, wherein a medium flowing along the outside of the tank releases heat to the tank contents.
- the medium is a heat transfer oil and flows through the circuit at least one of the hot exhaust gases of the internal combustion engine of the tank semitrailer traversed Heat exchanger.
- a catalyst through which the combustion gases flow is arranged in front of the heat exchanger.
- the DE 199 08 088 A1 relates to an internal combustion engine, in particular a diesel internal combustion engine, for a vehicle, with a passenger compartment heater, an exhaust pipe, a coolant line forming a cooling circuit with a first pump to which the internal combustion engine is connected, and an exhaust gas heat exchanger for transmitting exhaust gas heat to a heater core ,
- the exhaust gas heat exchanger is effective between the exhaust pipe and a circulation medium line, which forms a circulation circuit to which the heating heat exchanger is connected directly or indirectly.
- the DE 199 08 088 A1 but also relates to an internal combustion engine, in particular diesel internal combustion engine, wherein the internal combustion engine is connected to a branching off from the coolant line first bypass, in which a first thermostatic valve is arranged, which largely blocks the first bypass until reaching an average coolant temperature and opens above this coolant temperature , In a parallel to the first bypass extending second bypass, a second thermostatic valve is arranged, which largely blocks the second bypass above the average cooling temperature.
- the DE 100 47 810 A1 relates to a heating circuit with an auxiliary heater for motor vehicles with internal combustion engine, which is part of a separate short-circuit, which is switchable by means of a switching device in the heating circuit.
- auxiliary heater an exhaust system of the engine of the motor vehicle is used, from which the exhaust heat is transferred into the heating circuit.
- the exhaust heat supply is at a heat demand of the interior heating below exhaust gas exhaust heat supply by motorisehe Measures liftable.
- the DE 100 47 810 A1 but also relates to a method for operating a heating circuit with an auxiliary heater for motor vehicles with internal combustion engine, designed as exhaust gas heat exchanger through which the engine exhaust gas and coolant flow. To increase the heating power of the additional heater, the engine operating parameters can be influenced.
- the EP 1 094 214 A2 relates to a heat recovery system having a circulation line in which a heat transfer medium circulates through an engine cooling unit, and an exhaust gas heat exchanger for utilizing the exhaust gases of an engine and a conduit connecting an outlet side of the circulation line to an outlet of the heat exchanger.
- the exhaust gas heat exchanger is disposed across the circulation passage at a side upstream of the engine cooling unit.
- the heat transfer medium introduced into the exhaust gas heat exchanger is controlled to a lower temperature sufficient to lower a temperature of the water vapor contained in the exhaust gas stream from which heat is transferred to the heat transfer medium to lower its dew point.
- JP 2001 323808 A shows an oil lubrication system, in which from an oil suction pipe, which is arranged in an oil sump of a non-insulated oil tank, by means of an oil pump oil can be introduced into a lubrication system.
- the oil can be heated by means of an oil line and a heat exchanger through an exhaust system.
- the heated oil can be stored in a thermally insulated intermediate tank and returned by means of a supply line directly under a suction bell of the oil pump in the oil sump.
- a bypass line in an oil / exhaust gas heat exchanger wherein the heat exchanger for heating oil for lubrication in a warm-up phase by means of exhaust gas is used.
- the exhaust flow of the heat exchanger can be passed through a multi-way valve through an exhaust bypass to control further heating of the lubricating oil system.
- the US 4,393,824 relates to a heating method for lubricating oil, wherein by means of a high-pressure pump and a pressure reducing element, an additional heating of the total amount of lubricating oil can be achieved.
- JP 2005 299592 A discusses a generic oil lubrication system using heat from an EGR system to increase the viscosity of the lubricating oil.
- an oil cooler can be bypassed by means of an oil bypass. In any case, all the lubricating oil flows through the oil cooler or bypass and is returned to an oil reservoir. Even the D4 gives no indication of the missing features.
- a generic oil lubrication system goes out of the JP 60 185011 U ,
- the JP 60 185011 U concerns a generic type lubrication system.
- an oil suction pipe is arranged in an oil sump, and has a the oil recirculation umstructure oil bypass line.
- a valve is disposed in the oil bypass line, whereby the bypass line and / or at least one of the oil return can be connected to the suction line of an oil pump and the pressure line of a lubrication system.
- the nature of the installation of the oil bypass line is not chosen to be advantageous in order to allow accelerated heating.
- the JP 58 158 126 U considers an oil lubrication system for a turbocharged internal combustion engine in which an oil bypass line may lube-controlled oil pass through a portion of the turbocharger for faster heating.
- EP 0 123 620 A1 describes a lubricating system with oil bypass line for an internal combustion engine, wherein when an oil minimum pressure is exceeded, an exhaust valve is opened, so that oil flows through the bypass line and bypasses the oil return.
- a lubrication system with a cylinder head lubricant collection tank is known in which during a warm-up phase returning lubricating oil from the cylinder head in the cylinder head temporarily remains in the lubricant reservoir tank, heated and delayed concentrated in a suction of the oil pump in the oil sump can be returned.
- both an overflow return special connection is provided, which causes a return of the amount of oil used for the cylinder head lubrication with filled lubricant collection tank, as well as a switching valve that allows concentrated at reservoir already partially concentrated return.
- the switching valve can be opened as soon as the lubricant has reached the operating temperature, in the warm-up phase it remains closed, so that returning oil from the cylinder head is returned via the overflow line. Furthermore, an oil pressure filling pipe from the oil pump leads directly to the lubricant collecting tank, and is controlled by another switching valve so that the lubricant collecting tank can also be filled directly.
- JP S59183017 shows a lubrication system in which in a warm-up phase, the entire oil return can be passed through a manifold directly to the ⁇ lsaugrohr an oil pump to avoid mixing with the oil of the oil sump.
- the invention has for its object to improve an internal combustion engine or a transmission, in particular automatic transmission of the type mentioned with simple means to the extent that the engine oil is performed faster in the cold start phase or in the warm-up phase to operating temperature, so that both a reduced fuel consumption as well as reduced pollutant emissions are achieved, with overheating of the engine oil is to be avoided.
- a oil bypass umstructureden oil bypass line is connected to the suction of an oil pump and the pressure line of a lubrication system, wherein the oil bypass line of the internal combustion engine passes through at least one cylinder head, and that falls below a certain limit temperature and exceeding a certain minimum pressure of the lubricating oil in the pressure line the lubricating system, a bypass valve in the oil bypass line is at least partially opened, so that a partial flow of the lubricating oil in a warm-up phase of the lubrication system does not flow through the oil sump until either the minimum pressure or the limit temperature are reached, and that the lubricating oil mass flow through the oil bypass line (23) at least temporarily larger than the lubricating oil mass flow through the oil suction pipe (2).
- bypass line can pass through a turbocharger.
- the oil in the lubrication system heats up faster. Furthermore, the pressure loss of the lubrication system to be overcome decreases since the oil flowing back through the oil bypass line does not flow through the oil sump. Since the oil of the bypass line is preferably passed through the cylinder block and / or cylinder head, an increased oil volume flow at low temperatures can be achieved in an at least partial opening of the bypass valve, which can be arranged in or on the cylinder head or cylinder block, so that the oil more waste heat can record.
- the heating method of the lubricating system according to the invention can be used advantageously both in motor vehicles with automatic transmissions, as well as in motor vehicles with manual transmissions, and serve both for lubrication of the engine as an internal combustion engine and for lubricating the gear unit.
- hybrid vehicles which include both an internal combustion engine and an electric drive unit
- the heating method can be used for rapid heating of an electric motor / generator unit, which achieve optimum efficiency only at elevated temperatures, and also lubricate the electromotive moving components. It can be advantageous in these cases Waste heat from the electrical energy storage unit (battery / battery) and / or the inverter heats oil in the bypass line, which in turn heat up the electric motor / generator unit or lubricate this and a downstream transmission improved.
- an oil bypass line can be arranged, which contains a heat exchanger, through which additional heat is introduced into the transmission oil in the heating phase so as to reduce the friction.
- the invention can be applied to all types of internal combustion engine driven equipment and vehicles such as cars, trucks, buses, motorcycles, construction machinery, ships, boats, aircraft and mobile and stationary work equipment and devices, power plants such as emergency generators and the like.
- the invention enables optimum lubrication to reduce friction between the moving parts, thus increasing the longevity of the machine, reducing the noise level, achieving higher efficiency, achieving higher power output, delivering lower exhaust emissions, and costs can be saved.
- the length of the oil line of the lubrication system from the output of the oil pump to the entry into the oil bypass line at least 80% of the maximum length of the oil line of the lubrication system from the output of the oil pump to the farthest to be lubricated device is.
- the lubricating oil flowing through the oil bypass line can heat better.
- the lubricating oil mass flow through the oil bypass line is at least temporarily greater than the lubricating oil mass flow through the oil suction pipe and the oil sump. In this case, the total mass flow flowing through the lubricating system is heated faster than without oil bypass line.
- the oil bypass line is arranged in the same housing, in which also at least one of the devices to be lubricated are arranged, so that the back-flowing lubricating oil can additionally heat. It is particularly advantageous if one or several of the oil returns are connected directly to the suction line of an oil pump.
- the oil bypass line consists of a heat insulating material with a thermal conductivity less than 1 W / (m * K) to reduce the heat transfer to the environment during the backflow, especially where the oil bypass line not is guided through the device to be lubricated.
- At least one of the lubricating oil return flows arranged downstream of the devices to be lubricated is connected to the oil bypass line, one of the lubricating oil return lines connected to the oil bypass line being part of an exhaust gas turbocharger.
- the lubricating oil flowing through the oil bypass line is heated by a heat exchanger.
- the heat exchanger for heating the lubricating oil is flowed through by the exhaust gas of an internal combustion engine downstream of a catalyst. At this time, the exhaust gas flowing through the heat exchanger flows upstream through a valve. This valve is closed as soon as a specified limit temperature of the Is exhaust gas is achieved to prevent coking of the lubricating oil in the heat exchanger.
- flowing through the heat exchanger exhaust flows as exhaust gas recirculation downstream in the sense of the invention through a valve in the intake manifold of an internal combustion engine, wherein the valve is at least partially closed as soon as a predetermined limit temperature of Is exhaust gas is reached or as soon as a predetermined volume flow of the exhaust gas recirculation is achieved.
- the exhaust gas is cooled by the heat exchanger, which has a further reduction in the combustion temperature result, so that it can be dispensed with the use of an additional cooler for exhaust gas recirculation.
- a further heat exchanger and a further valve is arranged downstream of the oil pump for cooling, wherein this valve is at least partially opened when a predetermined limit value for the lubricating oil temperature is exceeded or not reached.
- the heat exchanger is flowed through by a cooling medium, such as ambient air or cooling liquid, in order to cool the lubricating oil.
- this heat exchanger is flowed through by the exhaust gas of the internal combustion engine in order to heat the lubricating oil and reduce the friction.
- a further valve is arranged in the lubricating oil line parallel to the heat exchanger and the valve. This valve is at least partially closed when a predetermined limit for the lubricating oil temperature exceeded or fallen short of. It is expedient in this case also if this heat exchanger is arranged in the circuit for cabin heating or in the circuit for heating or cooling of an electric battery.
- a control unit controls the opening cross section of the various valves, and if sensors for detecting the lubricating oil pressure, the lubricating oil temperature, the exhaust gas temperature, the rotational speed, the load and / or the coolant temperature with the Control unit are connected.
- the lubrication system, the exhaust pipe and the intake manifold are part of an internal combustion engine.
- the exhaust gas heat exchanger is designed to be double-flow, so that the transmission oil and the engine oil can be heated simultaneously in parallel and the exhaust gas heat exchanger is connected to the exhaust pipe by a heat-insulating material which has a heat conductivity less than 1 W / (m * K) auf calendart.
- the sealing of the valves in the exhaust pipe has a particularly important meaning, since a high density on the one hand improves the effectiveness of the heating and on the other hand in the closed position avoids that the oil heats up unintentionally, for example, at high engine loads and speeds. This can then be dispensed with the use of an additional oil cooler.
- the second sealing surface is arranged on the opposite side of the valve disk, from which the valve stem leads away from the actuator. In the active state, the outermost end of the valve closes the exhaust gas bypass and in the passive state, the inner sealing surface of the plate closes the line to the heat exchanger.
- Fig. 1 shows an internal combustion engine 30 in a schematic diagram.
- the internal combustion engine 30 has an exhaust pipe 14, in which a catalyst 10 is arranged.
- the internal combustion engine 30 is shown as a four-cylinder engine, the four cylinder manifolds open into a common exhaust pipe 14.
- a heat exchanger 8 is arranged in the exhaust gas line 14 behind the catalytic converter 10, and a turbocharger 24 is arranged in front of the catalytic converter.
- the internal combustion engine 30 has a lubricating oil system 16.
- the lubricating oil system has an oil sump 1, an oil receiving line 2, an oil pump 3, devices to be lubricated 31 of a cylinder head 12 and a cylinder block 15 and a turbocharger 24, an oil pan 5, and an oil pressure relief valve 4.
- the lubricating oil system 16 is also assigned a bypass valve 17.
- the bypass valve 17 controls the flow of the engine oil through the lubricating oil bypass 23, so that the temperature and the pressure of the engine oil can be set to optimum values.
- the lubricating oil system 16 has a plurality of oil returns 19.
- the heat exchanger 8 at least upstream of the exhaust stream, an exhaust valve or exhaust gas recirculation valve 20, 21, 41, advantageously an EGR control valve upstream, which regulates the exhaust gas flow through the heat exchanger 8 and thus indirectly controls the oil temperature.
- the heat exchanger 8 is integrated in the lubricating oil system 16, so that the oil is heated in a warm-up phase of the internal combustion engine 30 by means of the exhaust heat.
- an exhaust / oil heat exchanger for heating the oil in the bypass line.
- an exhaust valve 13 is additionally arranged in the exhaust pipe 14 parallel to the heat exchanger 8, which controls the exhaust gas flow through the heat exchanger 8 bypassing exhaust gas bypass 38.
- a valve 29 and a heat exchanger 26 with a supply line 27 and a discharge line 28 is arranged for controlling the oil temperature and the oil pressure.
- a valve 25 for regulating the oil pressure and the oil temperature is further arranged.
- the heat exchanger 26 can serve as an oil cooler for heating a cabin interior of a vehicle.
- a control unit 18 For regulating oil pressure and oil temperature, a control unit 18 is connected to the valves 13, 17, 20, 21, 25, 29 and 41, and at least with sensors for detecting the lubricating oil pressure 32, the lubricating oil temperature 33, the exhaust gas temperature 34, the rotational speed 35, the load 36 and the coolant temperature 37 connected.
- a throttle valve 7 is arranged, which is connected to a turbocharger 24 which opens downstream into an intake manifold 9.
- the intake manifold is connected to the exhaust gas recirculation exhaust pipe 14 via an exhaust gas recirculation valve 21, which may be configured as an EGR control valve, the connection being located downstream of the heat exchanger 8.
- the heat exchanger 8 may be an EGR heat exchanger. In this way harmful nitric oxide emissions are reduced
- the engine oil is heated faster 30 in a warm-up phase of the internal combustion engine.
- Parallel to the heat exchanger 8 is controlled via the second exhaust valve 13 exhaust bypass 38 is guided so that overheating of the engine oil is avoided in the heat exchanger.
- the heat exchanger 8 is preferred sufficiently dimensioned in the counterflow principle, so that the engine oil is heated as quickly as possible, the exhaust gas is cooled down as much as possible.
- Fig. 2 shows an advantageous embodiment of the invention.
- the exhaust outlet of the heat exchanger 8 is connected only to the intake manifold 9, so that the exhaust valve 13 and the exhaust gas recirculation valve 20 are not required.
- the heat exchanger has a dual function.
- the heat exchanger 8 heats up the engine oil during the warm-up phase due to the exhaust gas temperature in order to avoid high combustion temperatures.
- the heat exchanger 8 acts as a cooler of the exhaust gas recirculation 22 by the exhaust gas recirculated into the intake manifold 9 is cooled by the lubricating oil. This can be dispensed with an additional cooler for exhaust gas recirculation and additional valves to control the exhaust gas flow rate.
- Fig. 3 shows an embodiment of an oil lubricating device in a cold state, eg shortly after starting a motor vehicle.
- the main oil flow through the bypass valve 17 is shown in bold.
- the oil flows from the cylinder head 12 into the turbocharger 24.
- a bypass line leads to the opened bypass valve 17 through which the oil continues to flow and is combined with the oil return line 19 from the turbocharger.
- the oil continues to flow through the heat exchanger 8 in which it is heated by the hot exhaust gas.
- the oil is returned through the oil pan where the return line 23 is connected to the ⁇ lansaugrohr 2, so that the heated oil can be sucked directly further from the oil pump 3.
- the flow of the exhaust gas through the heat exchanger 8 is also shown in bold.
- the hot exhaust gas flows from the catalyst 10 into the exhaust pipe 14 and thence through the opened exhaust gas recirculation valve 21 into the heat exchanger 8 where it heats the cold oil the exhaust gas cools down. From there, the cold exhaust gas flows through the exhaust gas recirculation line 22 back into the intake manifold.
- the oil bypass valve 17 is completely or at least partially closed, so that the oil pressure in the internal combustion engine 30 can rise again.
- the oil bypass valve 17 is completely or at least partially closed when exceeding a maximum oil temperature, while then the exhaust gas recirculation valve 21 is closed or alternatively the in Fig. 4 shown EGR bypass flap 39, opened.
- Fig. 4 shows the system in a simplified version in the warm state.
- the bypass valve 17 is completely or at least partially closed, so that only a very small volume of oil flow through the heat exchanger 8 flows.
- the majority of the lubricating oil - shown in bold here - then flows through the bearings 31, eg crankshaft main bearings, connecting rod bearings, camshaft bearings, piston injectors, camshaft adjuster, camshaft plunger, etc. either through return lines 19 or directly back into the oil pan 1.
- the exhaust gas recirculation valve 21 can either be closed or be open. If the exhaust gas recirculation valve 21 is open, it is advantageous if the exhaust gas is guided back into the exhaust gas recirculation line 22 and the intake manifold 9 via a further EGR bypass flap 39.
- Fig. 5 The exhaust gas flows from an internal combustion engine (not shown) through a catalytic converter 10 into a 3-way valve 41. In the cold state, the exhaust gas flows through a heat exchanger 8 and heats the transmission oil passing through a bypass valve 17 is released. In the warm state, the exhaust gas does not flow through the heat exchanger 8 but through the bypass 38 and the bypass valve 17 is completely or at least partially closed.
- the volume flow of the oil pump 3 decreases more or less linear, this occurs especially at low oil temperatures.
- the heat transfer coefficient between oil and cylinder head 12 or cylinder block 15 decreases so that the oil can absorb only a small amount of heat from the cylinder head 12 or cylinder block 15.
- a pressure relief valve 4 opens. This reduces the oil volume flow flowing through the cylinder head 12 and block 15, so that the mechanical pumping power of the oil pump 3 is reduced. This reduces the heat transfer coefficient between oil and metal of the cylinder block 15 or head 12.
- An increase in the heat transfer coefficient at low temperatures can be achieved by an embodiment of the invention in that the volume flow through the cylinder block 15 and in particular through the cylinder head 12 is increased at low temperatures. This is achieved by at least partial opening of the (bypass) valve 17, for example as a function of temperature, pressure, engine speed and / or load. Supporting this is also conceivable, the volume flow rate of the oil pump 3 to increase mechanically or by a manual transmission or increase by moving conveyor wheels.
- the oil contained in the oil passages of an internal combustion engine 30 is only a fraction, usually only 10% of the total volume of oil.
- the entire oil volume is uniformly heated in known methods.
- Core idea of the invention is a targeted rapid heating of the lubricating oil located in the oil passages, this being achieved by connecting the oil passage of the cylinder heads 12 by means of a bypass line 23 with the suction side of the oil pump, wherein at the end of the bypass line 23, a negative pressure is applied to the Do not let oil flow back into the sump 1 but back into the oil channel.
- the generation of a negative pressure at the end of the bypass line 23 can be achieved by direct connection of the bypass line 23 with the suction side of the oil pump 3 and with a direct connection to the oil suction pipe 2.
- the bypass line 23 can be at least partially integrated in a plastic oil pan with integrated oil suction 2, which leads to improved insulation and less heat loss.
- the mouth of the bypass line 23 can be positioned in the oil sump 1 in close proximity to the opening of the ⁇ lsaugrohres 2, so that the opening of the bypass line end in the direction of the opening of the ⁇ lansaugrohres 2 shows and forms an angle of 0 to 45 °, which is also facilitates installation and the option of retrofitting later.
- additional active heat sources may be introduced into the bypass line 23, eg electrical heating rods or heating elements, preferably, one or more PTC heating rods, EGR oil cooler (exhaust gas recirculation cooler), full flow oil cooler or the like may be arranged to quickly heat the oil in the oil passages in the warm-up phase.
- EGR oil cooler exhaust gas recirculation cooler
- a motor control in the warm-up phase at least a small part of the heat exchanger 8 to control the heating of the oil in the bypass line 23, and after some time shut off the oil flow through the bypass line 23 to prevent coking in the exhaust gas heat exchanger 8
- Control variables for the control can be the higher the required oil pressure as a function of speed and load, and the desired oil temperature as a lower priority.
- the use of thermal insulation of the bypass line 23 and / or the EGR bypass (exhaust gas recirculation) upstream of the valve 17 by using a ceramic tube is advantageously conceivable to limit the temperature of the exhaust gas heat exchanger 8 and the exhaust gas recirculation valve 21 when the exhaust gas recirculation valve 21 is closed.
- an oil pan with line in front of the oil suction 2 in an oil pan, not shown, of the oil sump 1 are integrated to absorb the oil that exits from the bearings in the head and crankshaft while it is also warmed up, and feed directly to the oil pump, without the oil sump heat.
- the valve 17 may in this case also be integrated in the oil sump after merging the bypass line 23 and the line of the oil sump, wherein a check valve must be present in the line of the oil sump, so that the oil does not flow from the bypass line 23 back into the oil sump can.
- a combination of oil pan with spray nozzles which are arranged in the connecting rod for cooling the piston to increase the flow rate of the oil flow, wherein the spray nozzles are not turned off in the cold start.
- the exhaust gas flow for heating the oil in the bypass line 23 can in principle be diverted as desired from the normal exhaust gas flow.
- the exhaust gas before a turbocharger by means of a conventional EGR valve exhaust gas recirculation valve
- the high mass flow of the exhaust gas can be achieved in a small size and independent of the EGR calibration.
- a warm-up of the oil can be achieved without affecting the combustion temperature and thus also the exhaust gas.
- the EGR cooler assembly has a vertical gas guide with an angle up to 40 degrees to the vertical, so that condensation water can be discharged into an exhaust.
- an additional flap in the main exhaust gas flow can produce a pressure difference and thus conduct an increased volume flow through the heat exchanger 8.
- the invention is not limited to the illustrated embodiments. It is conceivable that the heat exchanger 26 is connected to the exhaust pipe 14 in order to effect a faster heating of the lubricating oil.
- the arrangement of the valves may vary, the valves may be arranged upstream and downstream of the various heat exchangers and vice versa.
- the invention may be used to lubricate engine parts, transmission parts or other moving components of a vehicle.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Description
Die Erfindung betrifft ein Verfahren zur Aufheizung eines Schmiersystem von rotierenden oder oszillierenden Bauteilen, insbesondere für eine Verbrennungskraftmaschine oder ein Getriebe, mit zumindest einem Ölsaugrohr, das in einem Ölsumpf angeordnet ist und mit einer den Ölrücklauf umführenden Bypassleitung, wobei in der Bypassleitung ein Ventil angeordnet ist.The invention relates to a method for heating a lubrication system of rotating or oscillating components, in particular for an internal combustion engine or a transmission, with at least one Ölsaugrohr, which is arranged in an oil sump and with the oil return bypass bypass line, wherein in the bypass line, a valve is arranged ,
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In einem Verbrennungsmotor ist ein Kraftstoffverbrauch während eines NEDC-Tests im kalten Zustand (Starttemperatur ca. 24 °C) ca. 10 bis 15 % höher als bei demselben Test mit einer Motoröltemperatur bei einem Start von ca. 90°C, dem so genannten NEDC-Heißtest. Dies liegt unter anderem daran, dass das Schmieröl bei niedrigeren Temperaturen eine höhere Zähigkeit aufweist und dass der Kraftstoff an Zylinderwänden kondensiert und in das Motoröl eingetragen wird. Zudem werden Maßnahmen ergriffen, um den Katalysator schneller aufzuheizen, dies sind z. B. eine Spätverstellung der Zündung, eine Anhebung der Leerlaufdrehzahl sowie eine Anfettung mit Sekundärlufteinblasung. Zudem entsteht der Großteil der emittierten Abgasemissionen während der Kaltstartphase des Verbrennungsmotors, wenn der Katalysator noch nicht die erforderliche Betriebstemperatur erreicht hat. Gleichzeitig wird ein Großteil der zugeführten Energie ungenutzt als Abgasenthalpie abgeführt. Dies sind insgesamt ca. 30 bis 40 % der Energie des zugeführten Kraftstoffes.In a combustion engine, fuel consumption during a cold NEDC test (starting temperature about 24 ° C) is about 10 to 15% higher than in the same test with an engine oil temperature starting at about 90 ° C, the so-called NEDC -Heißtest. One of the reasons for this is that the lubricating oil has a higher toughness at lower temperatures and that the fuel is condensed on cylinder walls and introduced into the engine oil. In addition, measures are taken to heat the catalyst faster, these are z. As a retardation of the ignition, raising the idle speed and enrichment with Sekundärlufteinblasung. In addition, the majority of the emitted exhaust emissions during the cold start phase of the internal combustion engine, if the catalyst has not yet reached the required operating temperature. At the same time, a Most of the energy supplied unused as exhaust enthalpy dissipated. This is a total of about 30 to 40% of the energy of the fuel supplied.
Bekannt ist, die Aufwärmphase des Motors zu verbessern, indem Abgaswärmetauscher eingesetzt werden, die in komplizierter Weise das Motoröl aufheizen und den Öldruck reduzieren. Auf der anderen Seite ist es ein Problem, den Motor, insbesondere das Motoröl bei dieser Aufheizung vor Überhitzung zu schützen. Daher werden zusätzliche Hochleistungsölkühler verwendet. Die bekannten Lösungen sind sehr aufwändig und führen nur zu einer relativ geringen Reduzierung des Kraftstoffverbrauches, so dass aus wirtschaftlichen Gründen die praktische Umsetzung meist nicht realisiert wird.It is known to improve the warm-up phase of the engine by using exhaust gas heat exchangers which in a complicated manner heat up the engine oil and reduce the oil pressure. On the other hand, it is a problem to protect the engine, in particular the engine oil in this heating from overheating. Therefore, additional high performance oil coolers are used. The known solutions are very complex and only lead to a relatively small reduction in fuel consumption, so that for economic reasons, the practical implementation is usually not realized.
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Der Erfindung liegt die Aufgabe zugrunde, eine Verbrennungskraftmaschine oder ein Getriebe, insbesondere Automatikgetriebe der eingangs genannten Art mit einfachen Mitteln dahin gehend zu verbessern, dass das Motoröl in der Kaltstartphase bzw. in der Warmlaufphase schneller auf Betriebstemperatur geführt wird, so dass sowohl ein verringerter Kraftstoffverbrauch als auch verringerte Schadstoffemissionen erreicht werden, wobei eine Überhitzung des Motoröls vermieden werden soll.The invention has for its object to improve an internal combustion engine or a transmission, in particular automatic transmission of the type mentioned with simple means to the extent that the engine oil is performed faster in the cold start phase or in the warm-up phase to operating temperature, so that both a reduced fuel consumption as well as reduced pollutant emissions are achieved, with overheating of the engine oil is to be avoided.
Erfindungsgemäß wird die Aufgabe dadurch gelöst, dass eine den Ölrücklauf umführenden Ölbypassleitung mit der Saugleitung einer Ölpumpe und der Druckleitung eines Schmiersystems verbunden ist, wobei die Ölbypassleitung der Verbrennungskraftmaschine durch zumindest einen Zylinderkopf verläuft, und dass bei Unterschreitung einer bestimmten Grenztemperatur und bei Überschreitung eines bestimmten Mindestdruckes des Schmieröls in der Druckleitung des Schmiersystems ein Bypassventil in der Ölbypassleitung zumindest teilweise geöffnet wird, so dass ein Teilstrom des Schmieröls in einer Warmlaufphase des Schmiersystems nicht durch den Ölsumpf strömt, bis entweder der Mindestdruck oder die Grenztemperatur erreicht sind, und dass der Schmierölmassenstrom durch die Ölbypassleitung (23) zumindest zeitweise größer ist als der Schmierölmassenstrom durch das Ölsaugrohr (2).According to the invention the object is achieved in that a oil bypass umführenden oil bypass line is connected to the suction of an oil pump and the pressure line of a lubrication system, wherein the oil bypass line of the internal combustion engine passes through at least one cylinder head, and that falls below a certain limit temperature and exceeding a certain minimum pressure of the lubricating oil in the pressure line the lubricating system, a bypass valve in the oil bypass line is at least partially opened, so that a partial flow of the lubricating oil in a warm-up phase of the lubrication system does not flow through the oil sump until either the minimum pressure or the limit temperature are reached, and that the lubricating oil mass flow through the oil bypass line (23) at least temporarily larger than the lubricating oil mass flow through the oil suction pipe (2).
Vorteilhafterweise kann die Bypassleitung durch einen Turbolader verlaufen.Advantageously, the bypass line can pass through a turbocharger.
Indem das Schmieröl direkt in die Ölpumpe zurückgeführt wird, erwärmt sich das Öl im Schmiersystem schneller. Des Weiteren sinkt der zu überwindende Druckverlust des Schmiersystems, da das durch die Ölbypassleitung rückströmende Öl nicht durch den Ölsumpf strömt. Da bevorzugt das Öl der Bypassleitung durch Zylinderblock und/oder Zylinderkopf geleitet wird, kann bei einem zumindest teilweisen Öffnen des Bypassventils, dass in oder am Zylinderkopf oder Zylinderblock angeordnet sein kann, ein erhöhter Ölvolumenstrom bei niedrigen Temperaturen erreicht werden, so dass das Öl mehr Abwärme aufnehmen kann.By returning the lubricating oil directly to the oil pump, the oil in the lubrication system heats up faster. Furthermore, the pressure loss of the lubrication system to be overcome decreases since the oil flowing back through the oil bypass line does not flow through the oil sump. Since the oil of the bypass line is preferably passed through the cylinder block and / or cylinder head, an increased oil volume flow at low temperatures can be achieved in an at least partial opening of the bypass valve, which can be arranged in or on the cylinder head or cylinder block, so that the oil more waste heat can record.
Hierdurch wird in der Warmlaufphase eine verminderte Reibung erreicht, da das Schmieröl schneller auf Betriebstemperatur geführt wird und die Druckverluste reduziert werden.As a result, a reduced friction is achieved in the warm-up phase, since the lubricating oil is led faster to operating temperature and the pressure losses are reduced.
Das erfindungsgemäße Aufheizverfahren des Schmiersystems kann vorteilhaft sowohl in Kraftfahrzeugen mit Automatikgetrieben, als auch in Kraftfahrzeugen mit Schaltgetrieben eingesetzt werden, und sowohl zur Schmierung des Motors als Verbrennungskraftmaschine als auch zur Schmierung der Getriebeeinheit dienen. In Hybridfahrzeugen, die sowohl eine Verbrennungskraftmaschine als auch eine Elektroantriebseinheit umfassen, kann das Aufheizverfahren zur schnellen Erwärmung einer Elektromotor/Generatoreinheit verwendet werden, die erst bei erhöhten Temperaturen einen optimalen Wirkungsgrad erreichen, und ebenfalls die elektromotorisch bewegten Komponenten schmieren. Dabei kann in diesen Fällen vorteilhafterweise Abwärme der elektrischen Energiespeichereinheit (Akku/Batterie) und/oder des Inverters Öl in der Bypassleitung erwärmen, die hierdurch Elektromotor/Generatoreinheit erwärmen
bzw. diese und ein nachgeschaltetes Getriebe verbessert schmieren können. Bei Automatikgetrieben kann ebenso wie im Verbrennungsmotor eine Ölbypassleitung angeordnet werden, die einen Wärmetauscher beinhaltet, über den in der Aufheizphase zusätzlich Wärme in das Getriebeöl eingebracht wird, um so die Reibung zu reduzieren.The heating method of the lubricating system according to the invention can be used advantageously both in motor vehicles with automatic transmissions, as well as in motor vehicles with manual transmissions, and serve both for lubrication of the engine as an internal combustion engine and for lubricating the gear unit. In hybrid vehicles, which include both an internal combustion engine and an electric drive unit, the heating method can be used for rapid heating of an electric motor / generator unit, which achieve optimum efficiency only at elevated temperatures, and also lubricate the electromotive moving components. It can be advantageous in these cases Waste heat from the electrical energy storage unit (battery / battery) and / or the inverter heats oil in the bypass line, which in turn heat up the electric motor / generator unit
or lubricate this and a downstream transmission improved. In automatic transmissions, as well as in the internal combustion engine, an oil bypass line can be arranged, which contains a heat exchanger, through which additional heat is introduced into the transmission oil in the heating phase so as to reduce the friction.
Die Erfindung kann in allen Arten von Verbrennungskraftmaschinen angetriebenen Anlagen und Fahrzeugen wie beispielsweise PKW, LKW, Omnibus, Motorrad, Baumaschinen, Schiffen, Booten, Flugzeugen sowie mobilen und stationären Arbeitsgeräten und -vorrichtungen, Energieerzeugungsanlagen wie Notstromaggregaten und dergleichen angewendet werden. Insbesondere bei kurzfristigem Einsatz und bei variierenden Arbeitsbelastungen ermöglicht die Erfindung eine optimale Schmierung zur Verringerung der Reibung zwischen den bewegten Teilen, so dass die Langlebigkeit der Maschine erhöht, der Geräuschpegel reduziert, ein höherer Wirkungsgrad erreicht, eine höhere Leistungsausbeute erzielt, niedrigere Abgasemission abgegeben und Kosten gespart werden können.The invention can be applied to all types of internal combustion engine driven equipment and vehicles such as cars, trucks, buses, motorcycles, construction machinery, ships, boats, aircraft and mobile and stationary work equipment and devices, power plants such as emergency generators and the like. In particular, in short-term use and with varying workloads, the invention enables optimum lubrication to reduce friction between the moving parts, thus increasing the longevity of the machine, reducing the noise level, achieving higher efficiency, achieving higher power output, delivering lower exhaust emissions, and costs can be saved.
Günstig im Sinne der Erfindung ist es, wenn die Länge der Ölleitung des Schmiersystems von dem Ausgang der Ölpumpe bis zu dem Eintritt in die Ölbypassleitung mindestens 80% von der maximalen Länge der Ölleitung des Schmiersystems von dem Ausgang der Ölpumpe bis zur weitest entfernten zu schmierenden Einrichtung beträgt. Dadurch kann sich das durch die Ölbypassleitung strömende Schmieröl besser erwärmen. Besonders vorteilhaft ist, dass der Schmierölmassenstrom durch die Ölbypassleitung zumindest zeitweise größer ist als der Schmierölmassenstrom durch das Ölsaugrohr und den Ölsumpf. In diesem Fall wird der durch das Schmiersystem strömende Gesamtmassenstrom schneller aufgeheizt als ohne Ölbypassleitung.Favorable in the context of the invention, it is when the length of the oil line of the lubrication system from the output of the oil pump to the entry into the oil bypass line at least 80% of the maximum length of the oil line of the lubrication system from the output of the oil pump to the farthest to be lubricated device is. As a result, the lubricating oil flowing through the oil bypass line can heat better. It is particularly advantageous that the lubricating oil mass flow through the oil bypass line is at least temporarily greater than the lubricating oil mass flow through the oil suction pipe and the oil sump. In this case, the total mass flow flowing through the lubricating system is heated faster than without oil bypass line.
Zweckmäßig ist auch, wenn die Ölbypassleitung in dem selben Gehäuse angeordnet ist, in dem auch mindestens eine der zu schmierenden Einrichtungen angeordnet sind, so dass sich das rückströmende Schmieröl zusätzlich erwärmen kann. Besonders vorteilhaft ist es wenn ein oder mehrere der Ölrückläufe direkt mit der Saugleitung einer Ölpumpe verbunden sind.It is also expedient if the oil bypass line is arranged in the same housing, in which also at least one of the devices to be lubricated are arranged, so that the back-flowing lubricating oil can additionally heat. It is particularly advantageous if one or several of the oil returns are connected directly to the suction line of an oil pump.
Vorteilhaft im Sinne der Erfindung ist ebenfalls, wenn die Ölbypassleitung aus einem Wärme isolierenden Material besteht mit einer Wärmeleitzahl kleiner als 1 W/(m*K), um die Wärmeübertragung an die Umgebung während dem Rückströmen zu reduzieren, insbesondere dort, wo die Ölbypassleitung nicht durch die zu schmierende Einrichtung geführt ist.Advantageous in the context of the invention is also, if the oil bypass line consists of a heat insulating material with a thermal conductivity less than 1 W / (m * K) to reduce the heat transfer to the environment during the backflow, especially where the oil bypass line not is guided through the device to be lubricated.
Um das Aufwärmen des Öles weiter zu Beschleunigen und den Druckverlust des Schmiersystems weiter zu reduzieren ist es günstig, wenn zumindest einer der von den zu schmierenden Einrichtungen stromabwärts angeordneten Schmierölrückläufe mit der Ölbypassleitung verbunden ist wobei einer der mit der Ölbypassleitung verbundenen Schmierölrückläufe Teil eines Abgasturboladers ist.In order to further accelerate the warming up of the oil and to further reduce the pressure loss of the lubricating system, it is favorable if at least one of the lubricating oil return flows arranged downstream of the devices to be lubricated is connected to the oil bypass line, one of the lubricating oil return lines connected to the oil bypass line being part of an exhaust gas turbocharger.
Da bei verschiedenen Belastungen und Drehzahlen unterschiedliche Schmieröldrücke erforderlich sind, um eine ausreichende Schmierung zu gewährleisten und Schäden an den zu schmierenden Bauteilen zu vermeiden, ist es günstig im Sinne der Erfindung, wenn das Bypassventil in der Ölbypassleitung geschlossen wird, sobald eine vorgegebene Drehzahl oder eine Geschwindigkeit oder ein Drehmoment oder eine Kraft der zu schmierenden Bauteile einen vorgegebenen Grenzwert überschreitet.Since at different loads and speeds different lubricating oil pressures are required to ensure adequate lubrication and to avoid damage to the components to be lubricated, it is favorable in the context of the invention, when the bypass valve is closed in the oil bypass line as soon as a predetermined speed or a Speed or torque or force of the components to be lubricated exceeds a predetermined limit.
In einer vorteilhaften Ausgestaltung der Erfindung wird das durch die Ölbypassleitung strömende Schmieröl durch einen Wärmetauscher erwärmt. Um die Erwärmung des Schmieröls zusätzlich zu beschleunigen, ist es vorteilhaft, wenn der Wärmetauscher zur Erwärmung des Schmieröles von dem Abgas einer Verbrennungskraftmaschine stromabwärts eines Katalysators durchströmt wird. Dabei strömt das durch den Wärmetauscher strömende Abgas stromaufwärts durch ein Ventil. Dieses Ventil wird geschlossen, sobald eine vorgegebene Grenztemperatur des Abgases erreicht wird, um ein Verkoken des Schmieröls im Wärmetauscher zu vermeiden.In an advantageous embodiment of the invention, the lubricating oil flowing through the oil bypass line is heated by a heat exchanger. In order to accelerate the heating of the lubricating oil in addition, it is advantageous if the heat exchanger for heating the lubricating oil is flowed through by the exhaust gas of an internal combustion engine downstream of a catalyst. At this time, the exhaust gas flowing through the heat exchanger flows upstream through a valve. This valve is closed as soon as a specified limit temperature of the Is exhaust gas is achieved to prevent coking of the lubricating oil in the heat exchanger.
Um die Verbrennungstemperatur und damit auch die Stickoxydemissionen der Verbrennungskraftmaschine zu reduzieren, strömt das durch den Wärmetauscher strömende Abgas als Abgasrückführung günstig im Sinne der Erfindung stromabwärts durch ein Ventil in den Ansaugkrümmer einer Verbrennungskraftmaschine, wobei das Ventil zumindest teilweise geschlossen wird, sobald eine vorgegebene Grenztemperatur des Abgases erreicht wird oder sobald ein vorgegebener Volumenstrom der Abgasrückführung erreicht wird. Dabei wird das Abgas durch den Wärmetauscher abgekühlt, was eine weitere Reduzierung der Verbrennungstemperatur zur Folge hat, so dass auf die Verwendung eines zusätzlichen Kühlers für die Abgasrückführung verzichtet werden kann.In order to reduce the combustion temperature and thus also the nitrogen oxide emissions of the internal combustion engine, flowing through the heat exchanger exhaust flows as exhaust gas recirculation downstream in the sense of the invention through a valve in the intake manifold of an internal combustion engine, wherein the valve is at least partially closed as soon as a predetermined limit temperature of Is exhaust gas is reached or as soon as a predetermined volume flow of the exhaust gas recirculation is achieved. In this case, the exhaust gas is cooled by the heat exchanger, which has a further reduction in the combustion temperature result, so that it can be dispensed with the use of an additional cooler for exhaust gas recirculation.
Zweckmäßig im Sinne der Erfindung ist, wenn das parallel zu dem Wärmetauscher strömende Abgas der Verbrennungsmaschine durch ein weiteres Ventil strömt und dass dieses Ventil zeitweise zumindest teilweise geschlossen wird, um den Abgasstrom und somit auch den Wärmeübergang im Wärmetauscher zu erhöhen.It is expedient for the purposes of the invention if the exhaust gas flowing parallel to the heat exchanger of the internal combustion engine flows through another valve and that this valve is at least partially closed at times to increase the exhaust gas flow and thus the heat transfer in the heat exchanger.
In einer weiteren vorteilhaften Ausgestaltung der Erfindung ist nach der Ölpumpe stromabwärts zur Abkühlung ein weiterer Wärmetauscher und ein weiteres Ventil angeordnet, wobei dieses Ventil zumindest teilweise geöffnet wird, wenn ein vorgegebener Grenzwert für die Schmieröltemperatur überschritten oder unterschritten wird. Der Wärmetauscher wird dazu in einer Ausführungsform von einem Kühlmedium wie Umgebungsluft oder Kühlflüssigkeit durchströmt, um das Schmieröl zu kühlen. In einer anderen Ausführungsform wird dieser Wärmetauscher von dem Abgas der Verbrennungskraftmaschine durchströmt, um das Schmieröl zu erwärmen und die Reibung zu reduzieren. Günstig ist dabei, wenn in der Schmierölleitung parallel zu dem Wärmetauscher und dem Ventil ein weiteres Ventil angeordnet ist. Dieses Ventil wird zumindest teilweise geschlossen, wenn ein vorgegebener Grenzwert für die Schmieröltemperatur überschritten oder unterschritten wird. Zweckmäßig ist es hierbei auch, wenn dieser Wärmetauscher in dem Kreislauf zur Kabinenheizung oder in dem Kreislauf zur Heizung oder Kühlung einer elektrischen Batterie angeordnet ist.In a further advantageous embodiment of the invention, a further heat exchanger and a further valve is arranged downstream of the oil pump for cooling, wherein this valve is at least partially opened when a predetermined limit value for the lubricating oil temperature is exceeded or not reached. In one embodiment, the heat exchanger is flowed through by a cooling medium, such as ambient air or cooling liquid, in order to cool the lubricating oil. In another embodiment, this heat exchanger is flowed through by the exhaust gas of the internal combustion engine in order to heat the lubricating oil and reduce the friction. It is advantageous if a further valve is arranged in the lubricating oil line parallel to the heat exchanger and the valve. This valve is at least partially closed when a predetermined limit for the lubricating oil temperature exceeded or fallen short of. It is expedient in this case also if this heat exchanger is arranged in the circuit for cabin heating or in the circuit for heating or cooling of an electric battery.
Zur Regelung von Öldruck und Öltemperatur ist es günstig im Sinne der Erfindung, wenn eine Regeleinheit den Öffnungsquerschnitt der verschiedenen Ventile steuert, und wenn Sensoren zur Erfassung des Schmieröldruckes, der Schmieröltemperatur, der Abgastemperatur, der Drehzahl, der Last und/oder der Kühlmitteltemperatur mit der Regeleinheit verbunden sind.For controlling oil pressure and oil temperature, it is favorable in the context of the invention, when a control unit controls the opening cross section of the various valves, and if sensors for detecting the lubricating oil pressure, the lubricating oil temperature, the exhaust gas temperature, the rotational speed, the load and / or the coolant temperature with the Control unit are connected.
In einer vorteilhaften Ausgestaltung der Erfindung sind das Schmiersystem, die Abgasleitung und der Ansaugkrümmer Teil einer Verbrennungskraftmaschine.In an advantageous embodiment of the invention, the lubrication system, the exhaust pipe and the intake manifold are part of an internal combustion engine.
Günstig im Sinne der Erfindung ist auch, wenn zumindest ein Teil des Schmiersystems in einem Getriebe angeordnet ist, das mit der Verbrennungskraftmaschine verbunden ist und die Verbrennungskraftmaschine sowie das Getriebe Bestandteil eines Kraftfahrzeuges sind. Dabei ist besonders vorteilhaft, wenn der Abgaswärmetauscher zweiflutig ausgeführt ist, so dass das Getriebeöl und das Motoröl gleichzeitig parallel erwärmt werden können und das der Abgaswärmetauscher mit der Abgasleitung durch ein wärmeisolierendes Material verbunden ist welches eine Wärmeleitzahl kleiner als 1 W/(m*K) aufweißt.Favorable for the purposes of the invention is also when at least a part of the lubrication system is arranged in a transmission which is connected to the internal combustion engine and the internal combustion engine and the transmission are part of a motor vehicle. It is particularly advantageous if the exhaust gas heat exchanger is designed to be double-flow, so that the transmission oil and the engine oil can be heated simultaneously in parallel and the exhaust gas heat exchanger is connected to the exhaust pipe by a heat-insulating material which has a heat conductivity less than 1 W / (m * K) aufweißt.
Die Abdichtung der Ventile in der Abgasleitung hat eine besonders wichtige Bedeutung, da eine hohe Dichtigkeit zum einen die Effektivität der Aufheizung verbessert und zum anderen bei geschlossener Stellung vermeidet, dass sich das Öl ungewollt aufheizt, zum Beispiel bei hohen Motorlasten und Drehzahlen. Dadurch kann dann auf die Verwendung eines zusätzlichen Ölkühlers verzichtet werden. Dadurch erweißt sich vorteilhaft im Sinne der Erfindung, wenn die Ventile in der Abgasleitung einteilig als Dreiwegeventil ausgebildet sind und dass diese Ventile als doppeltseitig wirkendes Tellerventil ausgeführt sind, wobei der Teller zwei Dichtflächen aufweist. Davon ist eine Dichtfläche am äußersten Ende des Ventiles angeordnet, wie bei einem Ausslassventil im Zylinderkopf einer Verbrennungskraftmaschine. Die zweite Dichtfläche ist auf der gegenüberliegenden Seite des Ventiltellers angeordnet, von der der Ventilschaft zur Betätigungseinrichtung wegführt. Im aktiven Zustand verschließt das äußerste Ende des Ventiles den Abgasbypass und im passiven Zustand verschließt die innere Dichtfläche des Tellers die Leitung zum Wärmetauscher.The sealing of the valves in the exhaust pipe has a particularly important meaning, since a high density on the one hand improves the effectiveness of the heating and on the other hand in the closed position avoids that the oil heats up unintentionally, for example, at high engine loads and speeds. This can then be dispensed with the use of an additional oil cooler. This makes it advantageous in the sense of the invention, when the valves are integrally formed in the exhaust pipe as a three-way valve and that these valves as Double-acting poppet valve are executed, wherein the plate has two sealing surfaces. Of which a sealing surface at the outermost end of the valve is arranged, as in an outlet valve in the cylinder head of an internal combustion engine. The second sealing surface is arranged on the opposite side of the valve disk, from which the valve stem leads away from the actuator. In the active state, the outermost end of the valve closes the exhaust gas bypass and in the passive state, the inner sealing surface of the plate closes the line to the heat exchanger.
Weitere vorteilhafte Ausgestaltungen sind in den Unteransprüchen und der folgenden Figurenbeschreibung offenbart.Further advantageous embodiments are disclosed in the subclaims and the following description of the figures.
Es zeigen:
- Fig. 1
- ein Schaltbild einer ersten Ausführung der Erfindung in einer Verbrennungskraftmaschine;
- Fig. 2
- ein Schaltbild einer zweiten Ausführung der Erfindung in einer Verbrennungskraftmaschine;
- Fig. 3
- ein Schaltbild einer weiteren Ausführungsform der Erfindung in einem kalten Zustand;
- Fig. 4
- ein Schaltbild der Ausführungsform der
Fig. 3 in einem warmen Zustand; - Fig. 5
- ein Schaltbild einer Ausführungsform der Erfindung in einem Automatikgetriebe;
- Fig. 1
- a circuit diagram of a first embodiment of the invention in an internal combustion engine;
- Fig. 2
- a circuit diagram of a second embodiment of the invention in an internal combustion engine;
- Fig. 3
- a circuit diagram of another embodiment of the invention in a cold state;
- Fig. 4
- a circuit diagram of the embodiment of the
Fig. 3 in a warm state; - Fig. 5
- a circuit diagram of an embodiment of the invention in an automatic transmission;
In den unterschiedlichen Figuren sind gleiche Teile stets mit denselben Bezugszeichen versehen, so dass diese in der Regel nur einmal beschrieben werden.In the different figures, the same parts are always provided with the same reference numerals, so that they are usually described only once.
In Abgasstromrichtung des Abgases gesehen ist in der Abgasleitung 14 hinter dem Katalysator 10 ein Wärmetauscher 8 angeordnet und vor dem Katalysator ist ein Turbolader 24 angeordnet. Die Verbrennungskraftmaschine 30 weist ein Schmierölsystem 16 auf. Das Schmierölsystem weist einen Ölsumpf 1, eine Ölaufnahmeleitung 2, eine Ölpumpe 3, zu schmierende Einrichtungen 31 eines Zylinderkopfes 12 und eines Zylinderblockes 15 und eines Turboladers 24, einer Ölwanne 5, sowie ein Ölüberdruckventil 4 auf.Viewed in the exhaust gas flow direction of the exhaust gas, a
Dem Schmierölsystem 16 ist zudem ein Bypassventil 17 zugeordnet. Das Bypassventil 17 steuert die Strömung des Motoröls durch den Schmierölbypass 23, so dass die Temperatur und der Druck des Motoröls auf optimale Werte eingestellt werden können. Weiter weist das Schmierölsystem 16 mehrere Ölrückläufe 19 auf.The lubricating
Dem Wärmetauscher 8 ist zumindest stromaufwärts des Abgasstromes ein Abgasventil oder Abgasrückführungsventil 20, 21, 41, vorteilhaft ein AGR-Regelventil vorgeschaltet, welches den Abgasstrom durch den Wärmetauscher 8 regelt und damit auch indirekt die Öltemperatur regelt. Der Wärmetauscher 8 ist in das Schmierölsystem 16 integriert, so dass das Öl in einer Warmlaufphase der Verbrennungskraftmaschine 30 mittels der Abgaswärme aufgeheizt wird. Alternativ zu einem Wärmetauscher 8 kann ein oder mehrere elektrische Heizelemente, insbesondere Heizstäbe eingesetzt werden, die ebenfalls den Zweck erfüllen, das Öl innerhalb der Bypassleitung aufzuheizen. Insbesondere bei Anwendung in einem Automatikgetriebe bietet es sich an, einen Abgas/Öl-Wärmetauscher zur Erwärmung des Öls in der Bypassleitung einzusetzen.The
In dem dargestellten Ausführungsbeispiel ist in der Abgasleitung 14 parallel zum Wärmetauscher 8 zusätzlich ein Abgasventil 13 angeordnet, welches den Abgasstrom durch den Wärmetauscher 8 umführenden Abgasbypass 38 regelt.In the illustrated embodiment, an
In dem Schmierölsystem 16 ist stromabwärts der Ölpumpe 3 ein Ventil 29 und ein Wärmetauscher 26 mit einer Zuleitung 27 und einer Ableitung 28 angeordnet zur Regelung der Öltemperatur und des Öldruckes. In einem den Wärmetauscher 26 umführenden weiteren Ölbypass ist weiterhin ein Ventil 25 zur Regelung des Öldruckes und der Öltemperatur angeordnet. Der Wärmetauscher 26 kann als Ölkühler zur Aufheizung eines Kabineninnenraums eines Fahrzeugs dienen.In the
Zur Regelung von Öldruck und Öltemperatur wird eine Regeleinheit 18 mit den Ventilen 13, 17, 20, 21, 25, 29 und 41 verbunden, sowie zumindest mit Sensoren zur Erfassung des Schmieröldruckes 32, der Schmieröltemperatur 33, der Abgastemperatur 34, der Drehzahl 35, der Last 36 und der Kühlmitteltemperatur 37 verbunden.For regulating oil pressure and oil temperature, a
In dem Ansaugsystem 6 der Verbrennungskraftmaschine 30 ist eine Drosselklappe 7 angeordnet, die mit einem Turbolader 24 verbunden ist der stromabwärts in einen Ansaugkrümmer 9 mündet. Zur Verringerung der Verbrennungstemperatur ist der Ansaugkrümmer über ein Abgasrückführungsventil 21, das als AGR-Regelventil ausgestaltet sein kann, mit der Abgasleitung 14 zur Abgasrückführung verbunden, wobei die Verbindung stromabwärts vom Wärmetauscher 8 angeordnet ist. In diesem Fall kann der Wärmetauscher 8 ein AGR-Wärmetauscher sein. Auf diese Weise werden schädliche Stickoxydemissionen reduziertIn the
Durch die in
In dieser vorteilhaften Ausgestaltung der Erfindung kommt dem Wärmetauscher eine Doppelfunktion zu. Zum einen heizt der Wärmetauscher 8 durch die Abgastemperatur das Motoröl während der Warmlaufphase auf, um hohe Verbrennungstemperaturen zu vermeiden. Zum anderen wirkt der Wärmetauscher 8 als Kühler der Abgasrückführung 22, indem das in den Ansaugkrümmer 9 zurückgeführte Abgas von dem Schmieröl gekühlt wird. Damit kann auf einen zusätzlichen Kühler für die Abgasrückführung und auf zusätzliche Ventile zur Regelung des Abgasvolumenstromes verzichtet werden.In this advantageous embodiment of the invention, the heat exchanger has a dual function. On the one hand, the
Der Hauptölfluss durch das Bypassventil 17 ist fett dargestellt. Das Öl strömt aus dem Zylinderkopf 12 in den Turbolader 24. Von dem Turbolader 24 führt eine Bypassleitung zu dem geöffneten Bypassventil 17 durch die das Öl weiterströmt und mit der Ölrückführungsleitung 19 aus dem Turbolader zusammengeführt wird. Von dort fließt das Öl weiter durch den Wärmetauscher 8 in dem es vom heißen Abgas erwärmt wird. Danach wird das Öl durch die Ölwanne zurückgeführt wo die Rückführleitung 23 mit dem Ölansaugrohr 2 verbunden ist, so dass das erwärmte Öl direkt weiter von der Ölpumpe 3 angesaugt werden kann.
Der Fluss des Abgases durch den Wärmetauscher 8 ist ebenfalls fett dargestellt. Das heiße Abgas strömt aus dem Katalysator 10 in die Abgasleitung 14 und von dort durch das geöffnete Abgasrückführungsventil 21 in den Wärmetauscher 8 in dem es das kalte Öl erwärmt wobei sich das Abgas dabei abkühlt. Von dort fließt das kalte Abgas durch die Abgasrückführungsleitung 22 zurück in den Ansaugkrümmer 9.
The main oil flow through the
The flow of the exhaust gas through the
Sobald ein bestimmter Grenzwert für den Öldruck unterschritten ist, wird das Ölbypassventil 17 ganz oder zumindest teilweise geschlossen, so dass der Öldruck in der Verbrennungskraftmaschine 30 wieder steigen kann.
Das Ölbypassventil 17 wird ganz oder zumindest teilweise geschlossen bei Überschreitung einer maximalen Öltemperatur, dabei wird dann auch das Abgasrückführungsventil 21 geschlossen oder alternativ die in
The
Mit steigendem Öldruck sinkt der Volumenstrom der Ölpumpe 3 mehr oder wenig linear, dies tritt insbesondere bei niedrigen Öltemperaturen auf. Mit sinkendem Volumenstrom sinkt allerdings der Wärmeübergangskoeffizient zwischen Öl und Zylinderkopf 12 bzw. Zylinderblock 15, so dass das Öl nur wenig Wärme aus dem Zylinderkopf 12 bzw. Zylinderblock 15 aufnehmen kann. Bei sehr hohen Drücken öffnet sich ein Überdruckventil 4. Dadurch sinkt der Ölvolumenstrom, der durch Zylinderkopf 12 und -block 15 fließt, so dass die mechanische Pumpleistung der Ölpumpe 3 verringert wird. Hierdurch sinkt der Wärmeübergangskoeffizient zwischen Öl und Metal des Zylinderblocks 15 bzw. -kopfs 12.With increasing oil pressure, the volume flow of the
Eine Erhöhung des Wärmeübergangskoeffizienten bei niedrigen Temperaturen kann durch eine Ausführungsform der Erfindung dadurch erreicht werden, dass der Volumenstrom durch den Zylinderblock 15 und insbesondere durch den Zylinderkopf 12 bei niedrigen Temperaturen erhöht wird. Dies wird durch zumindest teilweises Öffnen des (Bypass)-Ventils 17 beispielsweise in Abhängigkeit von Temperatur, Druck, Motordrehzahl und/oder Last erreicht. Unterstützend hierzu ist des Weiteren denkbar, die Volumenförderleistung der Ölpumpe 3 elektrisch oder durch ein Schaltgetriebe mechanisch zu erhöhen oder durch Verschieben von Förderrädern zu erhöhen.An increase in the heat transfer coefficient at low temperatures can be achieved by an embodiment of the invention in that the volume flow through the
Des Weiteren ist unterstützend denkbar, die Ölgalerie im Zylinderkopf 12 in Reihe anstatt parallel, d.h. im Gegenstromprinzip vom Öl durchfließen zu lassen. Hierzu kann es vorteilhaft sein, den Ölfluss zunächst durch eine Hauptgalerie eines Zylinderkopf 12 fließen zu lassen, danach am auslasseitigen Ende mittels eines Ventils durch eine weitere Hauptgalerie eines Zylinderkopfs 12 in Gegenrichtung zurückfließen zu lassen, so dass der Flussweg des Öls durch den Zylinderkopf 12 erhöht wird. Das Ventil kann auch auf der anderen Seite der Bypassleitung 23 in der Ölwanne angeordnet sein.Furthermore, it is supportive conceivable to flow through the oil gallery in the
Das in den Ölkanälen einer Verbrennungskraftmaschine 30 befindliche Öl beträgt nur einen Bruchteil, in der Regel nur 10% des Gesamtölvolumens. In der Aufwärmphase wird bei bekannten Verfahren das gesamte Ölvolumen gleichmäßig erwärmt. Kerngedanke der Erfindung ist eine gezielte schnelle Erwärmung des in den Ölkanälen befindlichen Schmieröls, wobei dies durch Verbindung des Ölkanals des oder der Zylinderköpfe 12 mittels einer Bypassleitung 23 mit der Saugseite der Ölpumpe erreicht wird, wobei am Ende der Bypassleitung 23 ein Unterdruck anliegt, um das Öl nicht zurück in den Ölsumpf 1 sondern zurück in den Ölkanal fließen zu lassen. Somit wird in der Aufwärmphase des Motors nur ein geringer, schnell zu erwärmender Teil des Gesamtöls zur Schmierung verwendet.The oil contained in the oil passages of an
Die Erzeugung eines Unterdrucks am Ende der Bypassleitung 23 kann durch direkte Verbindung der Bypassleitung 23 mit der Saugseite der Ölpumpe 3 sowie mit einer direkten Verbindung mit dem Ölsaugrohr 2 erreicht werden. Hierzu kann die Bypassleitung 23 zumindest zum Teil in eine Kunststoffölwanne mit integrierter Ölsaugleitung 2 integriert werden, wobei dies zu einer verbesserten Isolierung und zu geringerem Wärmeverlust führt. Des weiteren kann die Mündung der Bypassleitung 23 im Ölsumpf 1 in unmittelbarer Nähe zur Öffnung des Ölsaugrohres 2 positioniert werden, so dass die Öffnung des Bypassleitungsendes in Richtung der Öffnung des Ölansaugrohres 2 zeigt und mit diesem einen Winkel von 0 bis 45° bildet, wodurch sich auch eine erleichterte Montagemöglichkeit und die Option einer späteren Nachrüstbarkeit ergibt.The generation of a negative pressure at the end of the
Denkbar ist zur Verbesserung der Wärmeübertragung des Öls im Zylinderkopf der Einsatz von Rippenkörpern in den Ölgalerien, beispielsweise durch eine raue Oberflächengestaltung der Ölkanäle im Zylinderblock 15 bzw. -kopf 12 - insbesondere durch Einarbeitung eines Gewindes - wodurch eine Verringerung der durchfließbaren Ölmenge erreicht wird.It is conceivable to improve the heat transfer of the oil in the cylinder head, the use of ribbed bodies in the oil galleries, for example by a rough surface design of the oil passages in the
Daneben können zusätzliche aktive Wärmequellen in der Bypassleitung 23 eingebracht sein, z.B. elektrische Heizstäbe oder Heizelemente, bevorzugt ein oder mehrere PTC-Heizstäbe, AGR-Ölkühler (Abgasrückführungs-Kühler), Vollstromölkühler oder vergleichbares angeordnet werden, um das Öl in den Ölkanälen in der Aufwärmphase schnell zu erwärmen.In addition, additional active heat sources may be introduced into the
Des Weiteren ist zusätzlich denkbar, die Abgasleitung 14 über ein weiteres Ventil zumindest in der Aufwärmphase direkt durch oder benachbart zum Ölsumpf 1 oder in die Bypassleitung 23 zu leiten, wobei eine Erhöhung der Wärmeübertragung um ein Vielfaches ermöglicht wird, und auf einen Wärmetauscher 8 gegebenenfalls verzichtet werden kann.Furthermore, it is additionally conceivable to direct the
Des Weiteren kann eine Motorregelung in der Aufwärmphase zumindest einen kleinen Teil des Abgasstroms zunächst durch den Wärmetauscher 8 gezielt zur Aufwärmung des Öls in der Bypassleitung 23 regeln, und nach einiger Zeit den Öldurchfluss durch die Bypassleitung 23 abschalten, um eine Verkokung im Abgaswärmetauscher 8 zu vermeiden. Führungsgrößen für die Regelung können als höhere Priorität der erforderliche Öldruck in Abhängigkeit von Drehzahl und Last sein, sowie als niedrigere Priorität die gewünschte Öltemperatur sein.Furthermore, a motor control in the warm-up phase at least a small part of the
Des Weiteren ist denkbar, den Höhenpotentialunterschied zwischen Zylinderkopf 12 und Ölsaugleitung 2 zur Verbesserung des Ölfließverhaltens in der Byplassleitung 23 auszunutzen, bzw. dieses Höhenpotential konstruktiv möglichst groß zu gestalten.Furthermore, it is conceivable to exploit the difference in height potential between the
Daneben ist der Einsatz einer Wärmeisolierung der Bypassleitung 23 und/oder des AGR-Bypasses (Abgasrückführung) abgasseitig stromaufwärts vor dem Ventil 17 durch Verwendung eines Keramikrohres vorteilhaft denkbar, um bei geschlossenem Abgasrückführungsventil 21 die Temperatur des Abgaswärmetauschers 8 und des Abgasrückführungsventil 21 zu begrenzen.In addition, the use of thermal insulation of the
Bevorzugt kann eine Ölauffangwanne mit Leitung vor der Ölsaugleitung 2 in eine nicht dargestellte Ölwanne des Ölsumpfs 1 integriert werden, um das Öl, das aus den Lagerstellen im Kopf und Kurbelwelle austritt und dabei auch aufgewärmt wird, aufzufangen und direkt der Ölpumpe zuzuführen, ohne den Ölsumpf aufzuheizen. Das Ventil 17 kann in diesem Fall ebenfalls in der Ölwanne nach Zusammenführung der Bypassleitung 23 und der Leitung der Ölauffangwanne integriert sein, wobei ein Rückschlagventil in der Leitung der Ölauffangwanne vorhanden sein muss, so dass das Öl nicht von der Bypassleitung 23 zurück in die Ölauffangwanne fließen kann.Preferably, an oil pan with line in front of the
Vorteilhaft kann eine Kombination der Ölauffangwanne mit Spritzdüsen sein, die in den Pleuel zur Kühlung der Kolben angeordnet sind, um den Volumenstrom des Ölflusses zu erhöhen, wobei die Spritzdüsen im Kaltstart nicht abgeschaltet werden.Advantageously, a combination of oil pan with spray nozzles, which are arranged in the connecting rod for cooling the piston to increase the flow rate of the oil flow, wherein the spray nozzles are not turned off in the cold start.
Der Abgasstrom zur Erwärmung des Öls in der Bypassleitung 23 kann grundsätzlich beliebig vom normalen Abgasstrom abgezweigt werden. Besonders vorteilhaft kann das Abgas vor einem Turbolader mittels eines herkömmlichen AGR-Ventils (Abgasrückführungs-Ventil) in einem großen Abstand vom Turbolader abgezweigt werden, wobei der hohe Massenstrom des Abgases bei niedriger Baugröße und unabhängig von der AGR-Kalibrierung erreicht werden kann. Somit kann eine Aufwärmung des Öls erreicht werden, ohne die Verbrennungstemperatur und damit auch die Abgasbildung zu beeinflussen. Im Rahmen des Einsatzes einer Abgasrückführung kann es vorteilhaft sein, falls die AGR-Kühleranordnung eine vertikale Gasführung mit einem Winkel bis zu 40 Grad Neigung zur Vertikalen aufweist, so dass Kondensationswasser in einen Auspuff abgeleitet werden kann.The exhaust gas flow for heating the oil in the
Weist die Verbrennungskraftmaschine 30 keinen Turbolader oder keine Abgasrückführung auf, so kann eine zusätzliche Klappe im Hauptabgasstrom einen Druckunterschied erzeugen und somit einen erhöhten Volumenstrom durch den Wärmetauscher 8 leiten.If the
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt. Denkbar ist, dass der Wärmetauscher 26 mit der Abgasleitung 14 verbunden ist, um eine schnellere Erwärmung des Schmieröls zu bewirken. Auch die Anordnung der Ventile kann variieren, wobei die Ventile statt stromaufwärts auch stromabwärts der verschiedenen Wärmetauscher angeordnet sein können und umgekehrt. Die Erfindung kann zur Schmierung von Motorenteile, Getriebeteile oder anderen bewegten Komponenten eines Fahrzeugs verwendet werden.The invention is not limited to the illustrated embodiments. It is conceivable that the
Claims (16)
- A method for heating a lubricating system (16) for rotating or oscillating components, for an internal combustion engine (30) having at least one oil suction pipe (2) which is arranged in an oil sump (1) and having an oil bypass line (23) which bypasses the oil returns (19), a valve (17) being arranged in the oil bypass line (23),
the bypass line (23) being connected to the suction line of an oil pump (3) and the length of the oil line of the lubricating system (16) from the outlet of the oil pump (3) to the inlet into the oil bypass line (23) preferably amounting to at least 80% of the maximum length of the oil line of the lubricating system (16) from the outlet of the oil pump (3) to the most distant device (31) to be lubricated,
characterised in that
the bypass line (23) extends through at least one cylinder head (12) and, in the event of the temperature falling below a specific limit temperature and the pressure of the lubricating oil in the pressure line of the lubricating system (16) exceeding a specific minimum pressure, the bypass valve (17) is at least partially opened, such that in a warming-up phase of the lubricating system (16) at least a sub-stream of the lubricating oil does not flow through the oil sump (1) until either the minimum pressure or the limit temperature is achieved, and in that the lubricating oil mass flow rate through the oil bypass line (23) is at least temporarily greater than the lubricating oil mass flow rate through the oil suction pipe (2). - A method according to claim 1,
characterised in that
the bypass line (23) extends through a turbocharger (24). - A method according to claim 1 or 2,
characterised in that
the bypass valve (17) is closed as soon as a specified rotational speed or speed or torque or force of the components to be lubricated exceeds a specified limit value and/or in that, below a specified rotational speed or speed or torque or force, the delivery capacity of the oil pump (3) is raised in particular during the warming-up phase in order to generate an increased pump volumetric flow rate within the oil line. - A method according to one of the preceding claims,
characterised in that
the lubricating oil flowing through the oil bypass line (23) and/or at least one of the oil returns (19) is heated by a heat exchanger (8). - A method according to claim 4,
characterised in that
the exhaust gas from an internal combustion engine (30) is passed through the heat exchanger (8) to heat the lubricating oil, and in that the exhaust gas flowing through the heat exchanger (8) flows upstream through an exhaust gas valve/exhaust gas recirculation valve (20, 21, 41), and in that the exhaust gas valve/exhaust gas recirculation valve (20, 21, 41) is closed as soon as a specified limit temperature of the exhaust gas or the lubricating oil is reached, and/or in that at least some of the exhaust gas is passed via a controllable valve directly over or beside the oil sump (1), into or through an oil pan (5) or into the bypass line (23) in order to increase heat transfer. - A method according to claim 4 or 5,
characterised in that
the exhaust gas flowing through the heat exchanger (8) flows through an exhaust gas recirculation valve (21) and is connected downstream as exhaust gas recirculation (22) to the intake manifold (9) of an internal combustion engine (30), and in that the exhaust gas recirculation valve (21) is at least partially closed as soon as a specified limit temperature of the exhaust gas is reached or a specified volumetric flow rate of the exhaust gas recirculation is reached. - A method according to one of claims 4 to 6,
characterised in that
the exhaust gas from the internal combustion engine (30) flowing parallel to the heat exchanger (8) flows through an exhaust gas valve (13) and in that the second exhaust gas valve (13) is temporarily at least partially closed in order to increase exhaust gas flow and thus also heat transfer in the heat exchanger (8). - A method according to one of the preceding claims,
characterised in that
a heat exchanger (26) and a valve (29) for cooling are arranged downstream of the oil pump (3), and in that the valve (29) is at least partially opened if the lubricating oil temperature exceeds or falls below a specified limit value or the coolant inlet temperature (27) or coolant outlet temperature (28) falls below a specified limit value, a valve (25) preferably being arranged in the lubricating oil line parallel to the heat exchanger (26) and valve (29), and in that the valve (25) is at least partially closed if the lubricating oil temperature exceeds or falls below a specified limit value. - An apparatus for heating a lubricating system (16) for rotating or oscillating components for an internal combustion engine (30) for carrying out a method according to one of claims 1 to 8, having at least one oil suction pipe (2) which is arranged in an oil sump (1) and having an oil bypass line (23) which bypasses the oil return (19), a bypass valve (17) being arranged in the oil bypass line (23), and
the oil bypass line (23) being connected to the suction line of an oil pump (3) and the pressure line of a lubricating system (16),
characterised in that
the oil bypass line (23) extends through at least one cylinder head (12);
and at least one sensor for detecting the lubricating oil pressure (32) and the lubricating oil temperature (33) is provided,
such that at least in a warming-up phase of the lubricating system (16) at least a sub-stream of the lubricating oil does not flow through the oil sump (1) until either a limit oil pressure or a limit oil temperature is reached, and in that the lubricating oil mass flow rate through the oil bypass line (23) is at least temporarily greater than the lubricating oil mass flow rate through the oil suction pipe (2). - An apparatus according to claim 9,
characterised in that
the oil bypass line extends through a turbocharger (24). - An apparatus according to claim 9 or 10,
characterised in that
the length of the oil line of the lubricant system (16) from the outlet of the oil pump (3) to the inlet into the oil bypass line (23) amounts to at least 80% of the maximum length of the oil line of the lubricating system (16) from the outlet of the oil pump (3) to the most distant device (31) to be lubricated. - An apparatus according to one of claims 9 to 11,
characterised in that
the oil bypass line (23) and/or at least one of the oil returns (19) is connected to a heat exchanger (8) and the heat exchanger (8) for heating the lubricating oil is arranged downstream of the catalytic converter (10) in the exhaust gas system of an internal combustion engine (30), and in that an exhaust gas valve/exhaust gas recirculation valve (20, 41) is arranged upstream of the heat exchanger (8), which valve modifies throughflow as a function of at least the oil temperature or exhaust gas temperature, an exhaust gas recirculation valve (21) preferably being arranged downstream of the heat exchanger (8) and the first exhaust gas recirculation valve (21) being connected downstream to the intake manifold (9) of an internal combustion engine. - An apparatus according to claim 12,
characterised in that
an exhaust gas valve (13) is arranged parallel to the heat exchanger (8) in an exhaust gas bypass line (38) which bypasses the heat exchanger (8) in order at least temporarily to increase exhaust gas flow and thus also heat transfer in the heat exchanger (8). - An apparatus according to one of claims 12 or 13,
characterised in that
the heat exchanger (8) is arranged within an exhaust gas line (14) and is connected to this exhaust gas line (14) by a thermally insulating material which has a coefficient of thermal conductivity of less than 1 W/(m*K), and in that the heat exchanger (8) is of two-part construction and connected to the lubricating system of an internal combustion engine (30) and/or the lubricating system of a transmission, and in that both the internal combustion engine (30) and the transmission are part of a motor vehicle. - An apparatus according to one of claims 9 to 14,
characterised in that
the oil bypass line (23) is arranged in the same housing (15) in which at least one of the devices (31) to be lubricated is also arranged, a further part of the oil bypass line (23) being integrated in one piece in the oil pan (5), the end of the oil bypass line (23) preferably being arranged in the immediate vicinity of the opening of the oil suction line (2) and pointing towards the opening of the oil suction line (2), the two ends in particular adopting an angle of 0° to 45° to one another. - An apparatus according to one of claims 9 to 15,
characterised in that
at least one of the coolant lines (27) and (28) is connected to a heat exchanger (26) for passenger compartment heating and/or to a heat exchanger for a battery heating and cooling system.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE200910013943 DE102009013943A1 (en) | 2009-03-19 | 2009-03-19 | Oil lubrication system |
PCT/EP2010/053643 WO2010106179A1 (en) | 2009-03-19 | 2010-03-19 | Method and apparatus for oiling rotating or oscillating components |
Publications (2)
Publication Number | Publication Date |
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EP2409005A1 EP2409005A1 (en) | 2012-01-25 |
EP2409005B1 true EP2409005B1 (en) | 2018-08-15 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP10713597.2A Not-in-force EP2409005B1 (en) | 2009-03-19 | 2010-03-19 | Method and apparatus for oiling rotating or oscillating components |
Country Status (7)
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US (1) | US8978613B2 (en) |
EP (1) | EP2409005B1 (en) |
JP (1) | JP5656970B2 (en) |
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AU (1) | AU2010224799B2 (en) |
DE (1) | DE102009013943A1 (en) |
WO (1) | WO2010106179A1 (en) |
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-
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- 2010-03-19 US US13/256,611 patent/US8978613B2/en not_active Expired - Fee Related
- 2010-03-19 JP JP2012500273A patent/JP5656970B2/en not_active Expired - Fee Related
- 2010-03-19 AU AU2010224799A patent/AU2010224799B2/en not_active Ceased
- 2010-03-19 EP EP10713597.2A patent/EP2409005B1/en not_active Not-in-force
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Also Published As
Publication number | Publication date |
---|---|
US20120006622A1 (en) | 2012-01-12 |
CN102356217B (en) | 2013-12-25 |
DE102009013943A1 (en) | 2010-09-23 |
WO2010106179A1 (en) | 2010-09-23 |
CN102356217A (en) | 2012-02-15 |
AU2010224799B2 (en) | 2014-10-02 |
JP5656970B2 (en) | 2015-01-21 |
AU2010224799A1 (en) | 2011-09-29 |
EP2409005A1 (en) | 2012-01-25 |
US8978613B2 (en) | 2015-03-17 |
JP2012520965A (en) | 2012-09-10 |
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