EP2409005A1 - Verfahren und vorrichtung zur ölschmierung von rotierenden oder oszillierenden bauteilen - Google Patents
Verfahren und vorrichtung zur ölschmierung von rotierenden oder oszillierenden bauteilenInfo
- Publication number
- EP2409005A1 EP2409005A1 EP10713597A EP10713597A EP2409005A1 EP 2409005 A1 EP2409005 A1 EP 2409005A1 EP 10713597 A EP10713597 A EP 10713597A EP 10713597 A EP10713597 A EP 10713597A EP 2409005 A1 EP2409005 A1 EP 2409005A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- oil
- valve
- heat exchanger
- exhaust gas
- 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.)
- Granted
Links
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
-
- 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
-
- 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
-
- 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 ,
- DE 27 53 716 relates to a warm air-emitting heater for powered by an internal combustion engine motor vehicles, acted upon by atmospheric air heat exchanger for a heat transfer flowing in a line circuit heat carrier and also in the line circuit turned on, exhaust heat of the engine receiving and emitting to the heat transfer 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 tank is achieved in that heat is discharged through a flowing in a flow line heat transfer to the befindaji in the dry sump tank Schmierö l.
- GB 2 381 576 A discloses an exhaust gas heat
- Recovery device with a heat exchanger line and a bypass line.
- a heat exchanger 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.
- 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 can be divided 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.
- 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 in the circuit through at least one of the hot exhaust gases of the internal combustion engine of the tank semitrailer. flowed heat exchangers.
- a catalyst through which the combustion gases flow is arranged in front of the heat exchanger.
- 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 heating device, an exhaust pipe, a coolant line forming a cooling circuit with a first pump to which the internal combustion engine is connected, and Exhaust gas heat exchanger for transferring exhaust heat to a heating heat exchanger.
- 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.
- DE 199 08 088 A1 also relates to an internal combustion engine, in particular a diesel internal combustion engine, the internal combustion engine being connected to a first bypass branching off from the coolant line, in which a first thermostatic valve is arranged, which moves the first bypass until it reaches a middle one Coolant temperature largely locks and opens above this coolant temperature.
- a second thermostatic valve is arranged, which largely blocks the second bypass above the average cooling temperature.
- DE 100 47 810 Al relates to a heating circuit with an auxiliary heating device 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 motori- see measures liftable.
- DE 100 47 810 A1 also relates to a method for operating a heating circuit with an auxiliary heating device for motor vehicles with an internal combustion engine, designed as an 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.
- EP 1 094 214 A2 relates to a heat recovery system having a circulation passage in which a heat transfer medium circulates through an engine cooling unit, and an exhaust heat exchanger for utilizing the exhaust gases of an engine and a passage connecting an outlet side of the circulation passage to an exit 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 brought 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 about its dew point to lower.
- fuel consumption during a NEDC tests in the cold state is about 10 to 15% higher than for the same test with an engine oil temperature at a start of approximately 90 0 C, the so-called NEDC -H sustaintest.
- this is due to the fact 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.
- measures are taken to heat the catalyst faster, these are z. As a retardation of the ignition, raising the idle speed and enrichment with Sekundär Kunststoffmaschinesung.
- the invention is based on the object of improving an internal combustion engine or a transmission, in particular an automatic transmission of the type mentioned at the outset, by simple means such that the engine oil is accelerated to operating temperature in the cold start phase or in the warmup phase, so that both a reduced
- Fuel consumption and reduced pollutant emissions are achieved, with overheating of the engine oil is to be avoided.
- an oil return line bypassing oil bypass line is connected to the suction line of an oil pump and the pressure line of a lubrication system, the oil bypass line in the case of an internal combustion engine preferably by at least one cylinder head and / or cylinder block and / or at least one Turbocharger and in the case of a transmission preferably by at least one heat exchanger of the internal combustion engine and / or at least one heating element runs, and that falls below a certain limit temperature and when exceeding a certain minimum pressure of the lubricating oil in the printing line tion of the lubrication 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.
- 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, at an at least partial opening of the bypass valve, which can be arranged in or on the cylinder head or cylinder block, an increased oil volume flow can be achieved at low temperatures, 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.
- waste heat from the electrical energy storage unit (rechargeable battery / battery) and / or the inverter can advantageously heat oil in the bypass line, thereby heating 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, via which additional heat is introduced into the transmission oil in the heating phase in order to reduce friction.
- the invention can be applied in 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 at least one of the devices to be lubricated are arranged, so that the back-flowing lubricating oil can additionally heat up. 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 heat conductivity of less than 1 W / (m * K) in order to reduce the heat transfer to the environment during the backflow, in particular there, where the oil bypass line is not passed through the device to be lubricated.
- At least one of the lubricating oil return lines 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 is.
- 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 catalytic converter. 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 reached exhaust gas 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 oil 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. 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 value 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 Regular 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 is a circuit diagram of a first embodiment of the invention in an internal combustion engine
- Fig. 2 is a circuit diagram of a second embodiment of the invention in an internal combustion engine
- Fig. 3 is a circuit diagram of another embodiment of the invention in a cold state
- FIG. 4 is a circuit diagram of the embodiment of FIG. 3 in a warm condition
- Fig. 5 is a circuit diagram of an embodiment of the invention in an automatic transmission
- 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 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 intake line 2, an oil pump 3, devices 31 to be lubricated of a cylinder head 12 and a cylinder block 15 and a turbocharger 24, an oil sump 5, and an oil overpressure 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 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 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 gas outlet of the heat exchanger 8 is connected only to the intake manifold 9, so that the exhaust gas 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 makes it possible to dispense with an additional cooler for the exhaust gas recirculation and with additional valves for controlling the exhaust gas volume flow.
- Fig. 3 shows an embodiment of an oil lubricating device in a cold state, for example, 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, then the exhaust gas recirculation valve 21 is then closed or alternatively the EGR bypass valve 39 shown in FIG. 4, 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, e.g. Crankshaft main bearing, connecting rod bearings, camshaft bearings, piston injectors, camshaft adjuster, camshaft rams, etc. either through return lines 19 or directly back into the oil pan 1.
- the exhaust gas recirculation valve 21 may be either closed or open. If the exhaust gas recirculation valve 21 is open, it is advantageous if the exhaust gas is led back into the exhaust gas recirculation line 22 and the intake manifold 9 via a further EGR bypass flap 39.
- FIG. 5 shows the system in combination with an automatic transmission 40.
- the exhaust gas flows from an internal combustion engine (not shown) through a catalytic converter 10 into a 3-way valve 41.
- an internal combustion engine not shown
- a catalytic converter 10 into a 3-way valve 41.
- the exhaust gas flows through a heat exchanger 8 and heats the transmission oil, which is released by a bypass valve 17.
- 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 by 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.
- 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.
- 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 channels in the warm-up phase.
- EGR oil cooler exhaust gas recirculation cooler
- engine control in the warm-up phase can initially regulate at least a small portion of the heat exchanger 8 for heating the oil in the bypass line 23, and after some time switch off the oil flow through the bypass line 23 to allow coking in the exhaust gas heat exchanger 8 to avoid.
- 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 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 pipe 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 is not returned from the bypass line 23 in the Can flow oil pan.
- 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 generate 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.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200910013943 DE102009013943A1 (de) | 2009-03-19 | 2009-03-19 | Ölschmiersystem |
PCT/EP2010/053643 WO2010106179A1 (de) | 2009-03-19 | 2010-03-19 | Verfahren und vorrichtung zur ölschmierung von rotierenden oder oszillierenden bauteilen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2409005A1 true EP2409005A1 (de) | 2012-01-25 |
EP2409005B1 EP2409005B1 (de) | 2018-08-15 |
Family
ID=42269705
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10713597.2A Not-in-force EP2409005B1 (de) | 2009-03-19 | 2010-03-19 | Verfahren und vorrichtung zur ölschmierung von rotierenden oder oszillierenden bauteilen |
Country Status (7)
Country | Link |
---|---|
US (1) | US8978613B2 (de) |
EP (1) | EP2409005B1 (de) |
JP (1) | JP5656970B2 (de) |
CN (1) | CN102356217B (de) |
AU (1) | AU2010224799B2 (de) |
DE (1) | DE102009013943A1 (de) |
WO (1) | WO2010106179A1 (de) |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
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- 2009-03-19 DE DE200910013943 patent/DE102009013943A1/de not_active Withdrawn
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- 2010-03-19 AU AU2010224799A patent/AU2010224799B2/en not_active Ceased
- 2010-03-19 CN CN201080012734.1A patent/CN102356217B/zh not_active Expired - Fee Related
- 2010-03-19 WO PCT/EP2010/053643 patent/WO2010106179A1/de active Application Filing
- 2010-03-19 JP JP2012500273A patent/JP5656970B2/ja not_active Expired - Fee Related
- 2010-03-19 EP EP10713597.2A patent/EP2409005B1/de not_active Not-in-force
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Title |
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See references of WO2010106179A1 * |
Also Published As
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WO2010106179A1 (de) | 2010-09-23 |
CN102356217A (zh) | 2012-02-15 |
CN102356217B (zh) | 2013-12-25 |
US20120006622A1 (en) | 2012-01-12 |
JP2012520965A (ja) | 2012-09-10 |
US8978613B2 (en) | 2015-03-17 |
AU2010224799B2 (en) | 2014-10-02 |
DE102009013943A1 (de) | 2010-09-23 |
EP2409005B1 (de) | 2018-08-15 |
AU2010224799A1 (en) | 2011-09-29 |
JP5656970B2 (ja) | 2015-01-21 |
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