Patent Application
20180128274
The present application claims priority to German Patent Application No. 102016211638.4, filed Nov. 4, 2016 and German Patent Application No. 102016221639.2, filed Nov. 4, 2016. The entire contents of the above-referenced applications are hereby incorporated by reference in their entirety for all purposes.
The present description relates generally to a turbocharger having a cooling arrangement to decrease a compressed air temperature.
An internal combustion engine of the type mentioned in the introduction may be used as a motor vehicle drive. Within the context of the present disclosure, the expression “internal combustion engine” encompasses diesel engines and Otto-cycle engines and also hybrid internal combustion engines, which utilize a hybrid combustion process, and hybrid drives which comprise not only the internal combustion engine but also an electric machine which can be connected in terms of drive to the internal combustion engine and which receives power from the internal combustion engine or which, as a switchable auxiliary drive, additionally outputs power.
In recent years, there has been a trend in development toward supercharged engines, wherein the economic significance of said engines for the automobile industry continues to steadily increase.
Supercharging is primarily a method for increasing power in which the air needed for the combustion process in the engine is compressed, as a result of which a greater air mass can be fed to each cylinder in each working cycle. In this way, the fuel mass and therefore the mean pressure can be increased.
Supercharging is a suitable means for increasing the power of an internal combustion engine while maintaining an unchanged swept volume, or for reducing the swept volume while maintaining the same power. In any case, supercharging leads to an increase in volumetric power output and a more expedient power-to-weight ratio. If the swept volume is reduced, it is thus possible to shift the load collective toward higher loads, at which the specific fuel consumption is lower. By means of supercharging in combination with a suitable transmission configuration, it is also possible to realize so-called downspeeding, with which it is likewise possible to achieve a lower specific fuel consumption.
Supercharging consequently assists in the constant efforts in the development of internal combustion engines to minimize fuel consumption, that is to say to improve the efficiency of the internal combustion engine.
For supercharging, use may made of an exhaust-gas turbocharger, in which a compressor and a turbine are arranged on the same shaft. The hot exhaust-gas flow is fed to the turbine and expands in the turbine with a release of energy, as a result of which the shaft is set in rotation. The energy released by the exhaust-gas flow to the turbine and ultimately to the shaft is used for driving the compressor which is likewise arranged on the shaft. The compressor conveys and compresses the charge air fed to it, as a result of which supercharging of the cylinders is obtained. A charge-air cooler may be arranged in the intake system downstream of the compressor, by means of which charge-air cooler the compressed charge air is cooled before it enters the at least one cylinder. The cooler lowers the temperature and thereby increases the density of the charge air, such that the cooler also contributes to improved charging of the cylinders, that is to say to a greater air mass. Additional compression by cooling may take place.
The difference between an exhaust-gas turbocharger in relation to a supercharger—which can be driven by means of an auxiliary drive—consists in that an exhaust-gas turbocharger utilizes the exhaust-gas energy of the hot exhaust gases, whereas a supercharger draws the energy needed for driving it directly or indirectly from the internal combustion engine and thus adversely affects, that is to say reduces, the efficiency, at least for as long as the drive energy does not originate from an energy recovery source. Thus, the efficiency and/or overall power output of the turbocharger may be greater than the supercharger.
If the supercharger is not one that can be driven by means of an electric machine, that is to say electrically, a mechanical or kinematic connection for power transmission is generally needed between the supercharger and the internal combustion engine, which also influences the packaging in the engine bay.
The benefit of a supercharger in relation to an exhaust-gas turbocharger consists in that the supercharger can generate, and make available, the desired charge pressure at a greater range of times, specifically regardless of the operating state of the internal combustion engine. This applies in particular to a supercharger which can be driven electrically by means of an electric machine, and is therefore independent of the rotational speed of the crankshaft. For example, the supercharger may provide charge pressure during transient conditions where the turbocharger may lag.
In previous examples, it is specifically the case that difficulties are encountered in achieving an increase in power in all engine speed ranges by means of exhaust-gas turbocharging. A relatively severe torque drop is observed in the event of a certain engine speed being undershot. Said torque drop is understandable if one takes into consideration that the charge pressure ratio is dependent on the turbine pressure ratio or the turbine power. If the engine speed is reduced, this leads to a smaller exhaust-gas mass flow and therefore to a lower turbine pressure ratio or a lower turbine power. Consequently, toward lower engine speeds, the charge pressure ratio likewise decreases. This equates to a torque drop.
The internal combustion engine to which the present disclosure relates has a compressor for supercharging purposes, wherein, in the context of the present disclosure, both a supercharger that can be driven by means of an auxiliary drive and a compressor of an exhaust-gas turbocharger can be subsumed under the expression “compressor”.
An issue in the case of supercharging is that the charge air heats up during the compression in the compressor, whereby the efficiency of the compression deteriorates. The compressed hot charge air is duly generally cooled downstream of the compressor in a charge-air cooler of the intake system to ensure an improved cylinder charge. That is to say, compression by cooling may occur, thereby allowing more compressed air to flow to each cylinder of the engine if desired. However, owing to the operating principle, said charge-air cooling has no influence on the compression of the charge air in the compressor that is performed upstream.
To reduce or eliminate efficiency losses during the compression, compressors according to previous examples are cooled. In general, the compressor housing may be equipped with at least one coolant jacket to form the cooling arrangement. Either the housing is a cast part, wherein a coolant jacket is formed as an integral constituent part of a monolithic housing during the course of the casting process, or said housing is of modular construction, wherein during the course of the assembly process, a cavity is formed which serves as coolant jacket.
From the previous examples, concepts are known in which a coolant jacket is provided in the outlet region of the compressor, and concepts are also known in which the coolant jacket follows the contour of the impeller. Both concepts are unsuitable for effectively cooling the charge air during the compression in the compressor and for ensuring as isothermic a compression as possible and thereby improving the efficiency of the compression.
Consequently, further or other measures may be desired to improve the efficiency of the compression in a supercharged internal combustion engine.
In one example, the issues described above may be addressed by a supercharged internal combustion engine having an intake system for the supply of a charge-air flow, an exhaust-gas discharge system for the discharge of exhaust gas, at least one compressor arranged in the intake system, which compressor comprises at least one impeller which is mounted, in a compressor housing, on a rotatable shaft, and a bearing housing for the accommodation and mounting of the rotatable shaft of the at least one compressor, which internal combustion engine further comprises that the rotatable shaft of the at least one compressor is equipped with a ventilation system which comprises at least one duct which is formed so as to be open to the intake system upstream of the at least one compressor and from which at least one line branches off which emerges from the shaft between the at least one compressor and the bearing housing. In this way, heat transfer from the turbine to the compressor is reduced and cooling to the compressor blades is increased.
As one example, the compressor of the internal combustion engine according to the present disclosure is air-cooled and has at least one ventilation system which is suitable for dissipating heat from the compressor and from the charge air situated in the compressor. For this purpose, the rotatable shaft of the compressor is equipped with at least one duct which is connected or at least connectable to the intake system upstream of the compressor and from which at least one line branches off which emerges into the surroundings.
The ventilation system according to the present disclosure is supplied by the duct with air from the intake system upstream of the compressor, wherein the air passes into the surroundings via lines which branch off from the duct. As it flows through the ventilation system, the air cools the shaft of the compressor. Here, in particular, the convection between the rotating shaft and the air flow is utilized for the heat transfer and the heat dissipation.
The air which heats up during the compression is to be regarded as a heat source, wherein the temperature difference between the hot air and the relatively cool or cooled compressor shaft drives the heat dissipation. According to the present disclosure, the heat is extracted from the compressor and the shaft by means of air as said air flows through, and said heat is dissipated to the surroundings by the ventilation system.
By means of the approach according to the present disclosure, the charge air can be cooled during the compression, wherein an isothermic compression is sought, which is distinguished by particularly high efficiency.
The internal combustion engine according to the present disclosure may be a supercharged internal combustion engine which is improved in relation to previous examples with regard to the efficiency of the compression of the charge air in the compressor. The object on which the present disclosure is based is thereby achieved and air is cooled during compression more than in the previous examples utilizing coolant jackets in the compressor housing or the like.
The concept according to the present disclosure for cooling the charge air is also distinguished by the fact that it is suitable for retrofitting of compressors already on the market. Said another way, the cooling arrangement of the present disclosure is relatively simple to introduce to current turbocharging systems and turbocharging systems already in use. Thus, the manufacture of the cooling arrangement is relatively simple compared to, for example, arranging a cooling jacket in the compressor housing.
The at least one impeller of the compressor may be fastened rotationally conjointly to the shaft.
Additional embodiments of the supercharged internal combustion engine will be discussed below.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one duct opens into the intake system at a compressor-side end side of the shaft. Then, the at least one duct faces toward the charge-air inflow in the inlet region of the compressor, and the flow energy can be utilized for feeding air into the ventilation system and conveying said air through the ventilation system.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one duct is of rectilinear form. A rectilinear form of the duct facilitates the manufacture of the duct, for example by means of drilling.
In this context, embodiments of the supercharged internal combustion engine may comprise in which the at least one duct runs coaxially with respect to the shaft or with respect to the axis of rotation of the shaft. Thus, air from the intake system may readily flow into the ventilation system without turning or deviating from an original direction of flow.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one line is of rectilinear form. A rectilinear form of the line facilitates the manufacture of the line, for example by means of drilling.
In this context, embodiments of the supercharged internal combustion engine may comprise in which the at least one line runs perpendicular to the at least one duct. Then, when the shaft is in rotation, the centrifugal force acting on the air situated in the ventilation system can be utilized without hindrance for conveying the air in the ventilation system or out of the ventilation system. This is supplemented by a pump effect which results from the pressure gradient across the ventilation system. The higher the air throughput and thus the flow speed of the air in the ventilation system, the greater the amount of heat that is dissipated.
In this context, embodiments of the supercharged internal combustion engine may further comprise in which the at least one line is oriented radially outward. In one example, the at least one line functions as an outlet, expelling air out of the ventilation system and into a space in the turbocharger housing.
Embodiments of the supercharged internal combustion engine may comprise in which at least two lines are provided.
Embodiments of the supercharged internal combustion engine may comprise in which multiple lines are provided, but only one duct.
Embodiments of the supercharged internal combustion engine may comprise in which, furthermore, at least one disk-shaped element is arranged on the shaft, preferably at the compressor side. A disk-shaped element has a relatively large surface in contact with the surroundings, whereby the heat dissipation to the surroundings is increased or improved.
When the compressor is in operation, the disk-shaped element rotates with the rotating shaft, whereby the heat transfer from the disk to the surroundings may be assisted by convection.
Embodiments of the supercharged internal combustion engine may comprise in which the shaft has, at the impeller side, a thickened shaft end for accommodating the at least one impeller.
The thickened shaft end facilitates the introduction of heat or heat transfer from the impeller into the shaft and thus the heat dissipation from the charge air situated in the compressor. Furthermore, the thickened shaft end increases the strength of the shaft and allows for the fact that, according to the present disclosure, the shaft is equipped with a ventilation system, that is to say with cavities.
Embodiments of the supercharged internal combustion engine may comprise in which at least one compressor which can be driven by means of an auxiliary drive is arranged in the intake system.
A compressor which can be driven via an auxiliary drive, that is to say a supercharger, can generate and make available the desired charge pressure at a wide range of engine operating parameters, specifically independently of the operating state of the internal combustion engine. This applies in particular to a supercharger which can be driven electrically by means of an electric machine, and is therefore independent of the rotational speed of the crankshaft. For example, the supercharger may provide the desired boost during transient conditions where engine exhaust gas output may be too low to sufficiently drive a turbine.
In this context, embodiments of the supercharged internal combustion engine may comprise in which the at least one compressor of the internal combustion engine is a compressor which can be driven by means of an auxiliary drive.
Embodiments of the supercharged internal combustion engine may further comprise in which at least one exhaust-gas turbocharger is provided, which comprises a turbine arranged in the exhaust-gas discharge system and a compressor arranged in the intake system.
In this context, embodiments of the supercharged internal combustion engine may comprise in which the at least one compressor is the compressor of the at least one exhaust-gas turbocharger.
To be able to counteract a torque drop at low engine speeds, embodiments of the internal combustion engine may comprise in which at least two exhaust-gas turbochargers are provided. Specifically, if the engine speed is reduced, this leads to a smaller exhaust-gas mass flow and therefore to a lower charge-pressure ratio.
Through the use of multiple exhaust-gas turbochargers, for example multiple exhaust-gas turbochargers connected in series or parallel, the torque characteristic of a supercharged internal combustion engine may be increased.
To improve the torque characteristic, it is also possible, in addition to the at least one exhaust-gas turbocharger, for a further compressor, that is to say a compressor which can be driven by means of an auxiliary drive, to be provided.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one impeller has a multiplicity of impeller blades to improve the heat dissipation.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one compressor is a radial compressor. This embodiment permits dense packaging with regard to the supercharging arrangement. The compressor housing may be configured as a spiral or worm housing. In the case of an exhaust-gas turbocharger, the diversion of the charge-air flow in the compressor of the exhaust-gas turbocharger may be utilized for conducting the compressed charge air on the shortest path from the outlet side, on which the turbine of the exhaust-gas turbocharger is commonly arranged, to the inlet side.
In this connection, embodiments may comprise in which the turbine of the at least one exhaust-gas turbocharger is a radial turbine. This embodiment likewise permits dense packaging of the exhaust-gas turbocharger and thus of the supercharging arrangement as a whole.
By contrast to turbines, compressors are defined in terms of their exit flow. A radial compressor is thus a compressor whose flow exiting the rotor blades runs substantially radially. In the context of the present disclosure, “substantially radially” means that the speed component in the radial direction is greater than the axial speed component.
Embodiments of the supercharged internal combustion engine may further comprise in which the at least one compressor is of axial type of construction. The flow exiting the impeller blades of an axial compressor runs substantially axially.
Embodiments of the supercharged internal combustion engine may comprise in which the at least one compressor has an inlet region which runs coaxially with respect to the shaft of the at least one impeller and which is designed such that the flow of charge air approaching the at least one impeller runs substantially axially.
In the case of an axial inflow to the compressor, a diversion or change in direction of the charge-air flow in the intake system upstream of the at least one impeller is often omitted, whereby unnecessary pressure losses in the charge-air flow owing to flow diversion are avoided, and the pressure of the charge air at the inlet into the compressor is increased.
Embodiments of the supercharged internal combustion engine may comprise in which the ventilation system is equipped with a shut-off element which in the open state opens up, that is to say activates, the ventilation system and which in the closed state shuts off, that is to say deactivates, the ventilation system.
It should be understood that the summary above is provided to introduce in simplified form a selection of concepts that are further described in the detailed description. It is not meant to identify key or essential features of the claimed subject matter, the scope of which is defined uniquely by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that solve any disadvantages noted above or in any part of this disclosure.
The following description relates to systems and methods for a turbocharging system. The system comprises a compressor arranged in an intake system and a turbine arranged in an exhaust system. The compressor and turbine are rotatably coupled via a shaft extending therebetween. The shaft, compressor and turbine are shown in
A ventilation system may be arranged along the shaft, as shown in
The shaft may additionally comprise a fan, such as the fan illustrated in
One or more heat conductors may be arranged along the compressor impeller, as shown in
Note that
Turning now to
For the supply of the charge air to the cylinders, the internal combustion engine has an intake system 1. An exhaust-gas discharge system 6 serves for the discharge of the exhaust gases from engine cylinders.
For the supercharging of the internal combustion engine, an exhaust-gas turbocharger is provided which comprises a turbine 5 arranged in the exhaust-gas discharge system 6 and a compressor 2 arranged in the intake system 1, which turbine and compressor are arranged on the same shaft 2d. A bearing housing 3 arranged between turbine 5 and compressor 2 serves for the accommodation and mounting of the rotatable shaft 2d of the exhaust-gas turbocharger or compressor 2.
The compressor 2 may be a radial compressor, which comprises an impeller 2e mounted on the rotatable shaft 2d, which impeller is arranged in a compressor housing 2c and rotates during the operation of the compressor 2. The shaft 2d lies in the plane of the drawing of
The compressor 2 of the exhaust-gas turbocharger has an inlet region 2a which runs, and is formed, coaxially with respect to the shaft 2d of the compressor 2, such that the section of the intake system 1 upstream of the compressor 2 does not exhibit any changes in direction, and the flow of charge air approaching the compressor 2 of the exhaust-gas turbocharger, or the impeller 2e thereof, runs substantially axially. Thus, ambient air may readily flow toward the impeller 2e without any turns or adjustments from its original direction of travel, parallel to the central axis 8.
The rotatable shaft 2d of the compressor 2 is equipped with a ventilation system 4 which comprises a duct 4a which opens into the intake system 1 at the compressor-side end side of the shaft 2d and is thereby connected to the intake system 1 upstream of the compressor 2, such that air from the intake system 1 can be fed into the duct 4a and the rest of the ventilation system 4.
The duct 4a is of rectilinear form and runs coaxially with respect to the shaft 2d of the compressor 2, that is to say with respect to the axis of rotation (e.g., central axis 8) of the compressor 2.
Two lines 4b branch off from the duct 4a, which lines are likewise of rectilinear form. In the present case, the lines 4b run perpendicular to the duct 4a and are oriented radially outward, whereby the conveyance of air via the ventilation system 4 is intensified via centrifugal forces created by air flowing out of the duct 4a via the lines 4b during rotation of the shaft 2d and locomotion of a vehicle.
The lines 4b emerge from the shaft 2d, and open into the surroundings, between the compressor 2 and the bearing housing 3.
As it flows through the ventilation system 4, the air cools the shaft 2d of the compressor 2, wherein the temperature difference between the hot air in the impeller 2e and the relatively cool compressor shaft 2d forces the dissipation of heat from the charge air. It is sought to achieve as isothermic a compression as possible with high efficiency.
Said another way, each of the compressor 2 and the turbine 5 may be rotatably coupled to the shaft 2d. The turbine 6 may receive exhaust gases, where a turbine impeller rotates, translating to rotation of the shaft 2d and the compressor impeller 2e. As ambient air flows toward the compressor impeller 2e via the inlet region 2a, a first portion of ambient air which contacts the impeller may be compressed. A second portion of ambient air, which flows toward the compressor impeller 2e, but does not contact the impeller 2e, flows into the duct 4a of the ventilation system 4. The second portion of ambient air may be less than the first portion. The duct 4a may be arranged along geometric centers of the compressor impeller 2e and the shaft 2d, aligned with the central axis 8. The duct 4a may fluidly couple the ventilation system 4 to the intake system 1. Specifically, the duct 4a may fluidly couple an interior of the shaft 2d to the intake system 1. The duct 4a may extend to a portion of the shaft 2d upstream of the bearings 3 such that the duct 4a does not contact nor is surrounded by the bearings 3.
The air in the duct 4a may cool the shaft 2d. The shaft 2d may be heated due to high exhaust gas temperatures from the turbine 5. For example, the turbine 5 may be approximately 1000° C. and the compressor 2 may be approximately 100° C. Thus, the shaft 2d may transfer heat from the turbine 5 to parts of the compressor 2. For example, the shaft 2d may heat the compressor housing 2c and the compressor impeller 2e, thereby decreasing a compression efficiency. By flowing ambient air into the shaft 2d via the duct 4a, the ambient air may both reduce heat transfer from the turbine 5 to the compressor 2 and cool the compressor housing. The ambient air in the duct 4a, which is not compressed and comprises a pressure and temperature substantially equal to ambient air (e.g., 20-40° C.), may exit the duct 4a via lines in radially outward directions normal to the central axis 8 and contact the compressor housing 2c. Herein, lines 4b may be referred to as outlets 4b. Although only 2 outlets 4b are shown, there may be three or more outlets 4b. As shown, there are no other inlets or additional outlets of the ventilation arrangement than the duct 4a and the outlets 4b.
The outlets 4b may allow ambient air in the duct 4a to exit the shaft 2d and enter a space 15 in a turbocharger housing 11, in which the ambient air may contact the compressor housing 2c, contact oil passages 9 configured to cool the bearings 3, and/or flow through a bleed passage 4c arranged in the turbocharger housing. The bleed passage may flow the ambient air to an ambient atmosphere. In this way, there is space for air to flow between the shaft 2d and the turbocharger housing 11.
Turning now to
In the embodiment shown, the duct 4a and the outlets 4b are arranged along a portion of the shaft 2d upstream of the bearings 3. As shown, the outlets 4b are positioned such that they direct air from out of the duct 4a to a housing (e.g., housing 11 of
Ambient air, shown via arrows 13a and 13b, flows from the intake system 1 toward the impeller 2e. Black head arrows 13a indicate ambient air flow flowing directly toward the impeller 2e and white head arrows 13b indicate ambient air flow flowing directly toward the duct 4a. As shown, the arrows 13a are distal to the central axis 8 and the arrows 13b are proximal to the central axis 8. In this way, black head arrows 13a may be compressed and white head arrows 13b may not be compressed. In one example, ambient air flowing into the duct 4a is not compressed and ambient air flowing to the impeller 2e, and not into the duct 4a, is compressed.
The duct 4a may rotate proportionally to a rotation of the shaft 2d as it receive ambient air (arrows 13b). The ambient air may flow directly into the duct 4a without turning or other form of protuberance to its original flow. The ambient air may continue to flow directly along the central axis 8 while in the duct 4a until it reaches outlets 4b. As the outlets 4b, the ambient air in the duct 4a may flow in a radially outward direction perpendicular to the central axis 8. This may be promoted via centrifugal forces generated during rotation of the shaft 2d. Thus, a vacuum effect may occur at an inlet of the duct 4a, near the intake system 1, such that air flow into the duct 4a is promoted. A combination of the air flowing into the duct 4a, which may reduce heat transfer between the shaft 2d and the impeller 2e, and the air flowing out of the outlets 4b, which may reduce an impeller temperature and temperatures of other components, may reduce an overall temperature of compressed air 13a.
In addition to cooling the compressed air, the ambient air flowing out of the duct 4b may further cool a fluid used to cool the bearings 3. For example, the air may come into contact with surfaces housing the fluid and may cool the fluid as the air flows across the surfaces. In this way, a temperature of the bearings 3 may also be decreased.
The embodiment 200 further comprises a shut-off element 4c arranged in the duct 4a upstream of the outlets 4b. The shut-off element 4c may be configured to actuate in response to instructions sent by a controller (e.g., controller 12 of
Turning now to
The rotatable shaft 2d of the compressor 2 is equipped with a fan wheel 17 which is mounted on the shaft 2d and which rotates when the compressor 2 is in operation and the shaft 2d is in rotation.
The fan wheel 17 has a multiplicity of vanes 17a and is arranged at the compressor side between the compressor housing 2c and the bearing housing 3. An air flow generated by the rotating fan wheel 17 is conducted over the housing 2c, wherein the air flow is indicated in
The temperature difference between the hot charge air in the impeller 2e and the relatively cool fan wheel 4 also ensures an increased dissipation of heat from the charge air via impeller 2e, shaft 2d and fan wheel 17. It is sought to achieve as isothermic a compression as possible with high efficiency.
Turning now to
The impeller 2e of the compressor 2 is equipped with multiple heat conductors 19 which are arranged in the manner of a spider and which run in stellate fashion from the edges of the impeller blades toward the shaft 2d. Said heat conductors 19 serve for the improved dissipation of heat from the impeller 2e and from the charge air that flows through the impeller 2e during the course of the compression. It is sought to achieve as isothermic a compression as possible with high efficiency.
Thus,
Cylinder 14 can receive intake air via a series of intake air passages 142, 144, and 146. Intake air passage 146 can communicate with other cylinders of engine 10 in addition to cylinder 14.
Exhaust passage 148 can receive exhaust gases from other cylinders of engine 10 in addition to cylinder 14. Exhaust gas sensor 128 is shown coupled to exhaust passage 148 upstream of emission control device 178. Sensor 128 may be selected from among various suitable sensors for providing an indication of exhaust gas air/fuel ratio such as a linear oxygen sensor or UEGO (universal or wide-range exhaust gas oxygen), a two-state oxygen sensor or EGO (as depicted), a HEGO (heated EGO), a NOx, HC, or CO sensor, for example. Emission control device 178 may be a three way catalyst (TWC), NOx trap, various other emission control devices, or combinations thereof.
Each cylinder of engine 10 may include one or more intake valves and one or more exhaust valves. For example, cylinder 14 is shown including at least one intake poppet valve 150 and at least one exhaust poppet valve 156 located at an upper region of cylinder 14. In some examples, each cylinder of engine 10, including cylinder 14, may include at least two intake poppet valves and at least two exhaust poppet valves located at an upper region of the cylinder.
Intake valve 150 may be controlled by controller 12 via actuator 152. Similarly, exhaust valve 156 may be controlled by controller 12 via actuator 154. During some conditions, controller 12 may vary the signals provided to actuators 152 and 154 to control the opening and closing of the respective intake and exhaust valves. The position of intake valve 150 and exhaust valve 156 may be determined by respective valve position sensors (not shown). The valve actuators may be of the electric valve actuation type or cam actuation type, or a combination thereof. The intake and exhaust valve timing may be controlled concurrently or any of a possibility of variable intake cam timing, variable exhaust cam timing, dual independent variable cam timing or fixed cam timing may be used. Each cam actuation system may include one or more cams and may utilize one or more of cam profile switching (CPS), variable cam timing (VCT), variable valve timing (VVT) and/or variable valve lift (VVL) systems that may be operated by controller 12 to vary valve operation. For example, cylinder 14 may alternatively include an intake valve controlled via electric valve actuation and an exhaust valve controlled via cam actuation including CPS and/or VCT. In other examples, the intake and exhaust valves may be controlled by a common valve actuator or actuation system, or a variable valve timing actuator or actuation system.
Cylinder 14 can have a compression ratio, which is the ratio of volumes when piston 138 is at bottom center to top center. In one example, the compression ratio is in the range of 9:1 to 10:1. However, in some examples where different fuels are used, the compression ratio may be increased. This may happen, for example, when higher octane fuels or fuels with higher latent enthalpy of vaporization are used. The compression ratio may also be increased if direct injection is used due to its effect on engine knock.
In some examples, each cylinder of engine 10 may include a spark plug 192 for initiating combustion. Ignition system 190 can provide an ignition spark to cylinder 14 via spark plug 192 in response to spark advance signal SA from controller 12, under select operating modes. However, in some embodiments, spark plug 192 may be omitted, such as where engine 10 may initiate combustion by auto-ignition or by injection of fuel as may be the case with some diesel engines.
In some examples, each cylinder of engine 10 may be configured with one or more fuel injectors for providing fuel thereto. As a non-limiting example, cylinder 14 is shown including two fuel injectors 166 and 170. Fuel injectors 166 and 170 may be configured to deliver fuel received from fuel system 508. Fuel system 508 may include one or more fuel tanks, fuel pumps, and fuel rails. Fuel injector 166 is shown coupled directly to cylinder 14 for injecting fuel directly therein in proportion to the pulse width of signal FPW-1 received from controller 12 via electronic driver 168. In this manner, fuel injector 166 provides what is known as direct injection (hereafter referred to as “DI”) of fuel into combustion cylinder 14. While
Fuel injector 170 is shown arranged in intake passage 146, rather than in cylinder 14, in a configuration that provides what is known as port fuel injection (hereafter referred to as “PFI”) into the intake port upstream of cylinder 14. Fuel injector 170 may inject fuel, received from fuel system 508, in proportion to the pulse width of signal FPW-2 received from controller 12 via electronic driver 171. Note that a single driver 168 or 171 may be used for both fuel injection systems, or multiple drivers, for example driver 168 for fuel injector 166 and driver 171 for fuel injector 170, may be used, as depicted.
In an alternate example, each of fuel injectors 166 and 170 may be configured as direct fuel injectors for injecting fuel directly into cylinder 14. In still another example, each of fuel injectors 166 and 170 may be configured as port fuel injectors for injecting fuel upstream of intake valve 150. In yet other examples, cylinder 14 may include only a single fuel injector that is configured to receive different fuels from the fuel systems in varying relative amounts as a fuel mixture, and is further configured to inject this fuel mixture either directly into the cylinder as a direct fuel injector or upstream of the intake valves as a port fuel injector.
Fuel may be delivered by both injectors to the cylinder during a single cycle of the cylinder. For example, each injector may deliver a portion of a total fuel injection that is combusted in cylinder 14. Further, the distribution and/or relative amount of fuel delivered from each injector may vary with operating conditions, such as engine load, knock, and exhaust temperature, such as described herein below. The port injected fuel may be delivered during an open intake valve event, closed intake valve event (e.g., substantially before the intake stroke), as well as during both open and closed intake valve operation. Similarly, directly injected fuel may be delivered during an intake stroke, as well as partly during a previous exhaust stroke, during the intake stroke, and partly during the compression stroke, for example. As such, even for a single combustion event, injected fuel may be injected at different timings from the port and direct injector. Furthermore, for a single combustion event, multiple injections of the delivered fuel may be performed per cycle. The multiple injections may be performed during the compression stroke, intake stroke, or any appropriate combination thereof.
Fuel injectors 166 and 170 may have different characteristics. These include differences in size, for example, one injector may have a larger injection hole than the other. Other differences include, but are not limited to, different spray angles, different operating temperatures, different targeting, different injection timing, different spray characteristics, different locations etc. Moreover, depending on the distribution ratio of injected fuel among injectors 170 and 166, different effects may be achieved.
Fuel tanks in fuel system 508 may hold fuels of different fuel types, such as fuels with different fuel qualities and different fuel compositions. The differences may include different alcohol content, different water content, different octane, different heats of vaporization, different fuel blends, and/or combinations thereof etc. One example of fuels with different heats of vaporization could include gasoline as a first fuel type with a lower heat of vaporization and ethanol as a second fuel type with a greater heat of vaporization. In another example, the engine may use gasoline as a first fuel type and an alcohol containing fuel blend such as E85 (which is approximately 85% ethanol and 15% gasoline) or M85 (which is approximately 85% methanol and 15% gasoline) as a second fuel type. Other feasible substances include water, methanol, a mixture of alcohol and water, a mixture of water and methanol, a mixture of alcohols, etc.
Controller 12 is shown in
As described above,
In some examples, vehicle 505 may be a hybrid vehicle with multiple sources of torque available to one or more vehicle wheels 55. In other examples, vehicle 505 is a conventional vehicle with only an engine. In the example shown, vehicle 505 includes engine 10 and an electric machine 52. Electric machine 52 may be a motor or a motor/generator. Crankshaft 140 of engine 10 and electric machine 52 are connected via a transmission 54 to vehicle wheels 55 when one or more clutches 56 are engaged. In the depicted example, a first clutch 56 is provided between crankshaft 140 and electric machine 52, and a second clutch 56 is provided between electric machine 52 and transmission 54. Controller 12 may send a signal to an actuator of each clutch 56 to engage or disengage the clutch, so as to connect or disconnect crankshaft 140 from electric machine 52 and the components connected thereto, and/or connect or disconnect electric machine 52 from transmission 54 and the components connected thereto. Transmission 54 may be a gearbox, a planetary gear system, or another type of transmission. The powertrain may be configured in various manners including as a parallel, a series, or a series-parallel hybrid vehicle.
Electric machine 52 receives electrical power from a traction battery 58 to provide torque to vehicle wheels 55. Electric machine 52 may also be operated as a generator to provide electrical power to charge battery 58, for example during a braking operation.
In this way, the compressor shaft may comprise a duct configured to allow ambient air into the shaft to decrease a temperature of the compressor. The duct may mitigate heat transfer along the shaft from the turbine to the compressor. Outlets of the duct may be oriented to direct air out of the duct toward the compressor housing. The technical effect of including the duct in the shaft is to decrease compression temperatures to increase engine power output and increase compression efficiency.
A supercharged internal combustion engine comprises an intake system for the supply of a charge-air flow, an exhaust-gas discharge system for the discharge of exhaust gas, at least one compressor arranged in the intake system, which compressor comprises at least one impeller which is mounted, in a compressor housing, on a rotatable shaft, and a bearing housing for the accommodation and mounting of the rotatable shaft of the at least one compressor, and where the rotatable shaft of the at least one compressor is equipped with a ventilation system which comprises at least one duct which is formed so as to be open to the intake system upstream of the at least one compressor and from which at least one line branches off which emerges from the shaft between the at least one compressor and the bearing housing. A first example of the engine further includes where the at least one duct opens out into the intake system at a compressor-side end side of the shaft. A second example of the engine, optionally including the first example, further includes where the at least one duct is of rectilinear form and is coaxial with the shaft. A third example of the engine, optionally including the first and/or second examples, further includes where the at least one line is of rectilinear form and extends in a radially outward direction perpendicular to the duct and the shaft. A fourth example of the engine, optionally including one or more of the first through third examples, further includes where the shaft has, at the impeller side, a thickened shaft end for accommodating the at least one impeller. A fifth example of the engine, optionally including one or more of the first through fourth examples, further includes where the at least one compressor which can be driven by means of an auxiliary drive is arranged in the intake system. A sixth example of the engine, optionally including one or more of the first through fifth examples, further includes where the at least one compressor is included in an exhaust-gas turbocharger provided with a turbine arranged in the exhaust-gas discharge system and the compressor being arranged in the intake system. A seventh example of the engine, optionally including one or more of the first through sixth examples, further includes where the ventilation system is equipped with a shut-off element.
A system comprises a turbocharger comprising a compressor and a turbine rotatably coupled to a shaft, and where the shaft further comprises a ventilation system comprising a duct configured to allow air to enter an interior of the shaft. A first example of the system further includes where the compressor is arranged in an intake system, and where the duct receives ambient air from upstream of an impeller of the compressor relative to a direction of ambient air flow. A second example of the system, optionally including the first example, further includes where the duct extends along a central axis of the compressor and the shaft, and where the duct extends through an impeller of the compressor. A third example of the system, optionally including the first and/or second examples, further includes where air in the duct is not compressed. A fourth example of the system, optionally including one or more of the first through third examples, further includes where a bearing housing being arranged on the shaft, and where the duct is arranged between the compressor and the bearings. A fifth example of the system, optionally including one or more of the first through fourth examples, further includes where a plurality of outlets configured to expel air from the duct and a space within the turbocharger housing, wherein the outlets are arranged upstream of the bearings. A sixth example of the system, optionally including one or more of the first through fifth examples, further includes where air inside the ventilation system does not contact and mix with air compressed by the impeller.
A turbocharging system comprises a compressor arranged in an intake system and a turbine arranged in an exhaust system, the compressor and the turbine being mechanically coupled via a rotatable shaft and a ventilation system arranged in a compressor side of the shaft configured to admit air from the intake system to an interior portion of the shaft, upstream of a bearing housing relative to a direction of air flow. A first example of the turbocharging system further includes where the ventilation system comprises a duct arranged along a central axis of the shaft, the duct further arranged along a central portion of a compressor impeller, where the duct is configured to admit air flowing proximally to the central axis of the shaft. A second example of the turbocharging system, optionally including the first example, further includes where the ventilation system comprises one or more outlets arranged between the compressor and the bearing housing, the outlets extending in radially outward directions, and where the outlets are configured to discharge air to a space within a turbocharger housing such that the air may contact a compressor housing and an oil passage housing, where the oil passage housing surrounds the bearing housing. A third example of the turbocharging system, optionally including the first and/or second examples, further includes where the turbocharger housing further comprises a bleed passage to expel air from the space to an ambient atmosphere. A fourth example of the turbocharging system, optionally including one or more of the first through third examples, further includes where there are no additional inlets or outlets to the ventilation system other than the duct and the one or more outlets.
Note that the example control and estimation routines included herein can be used with various engine and/or vehicle system configurations. The control methods and routines disclosed herein may be stored as executable instructions in non-transitory memory and may be carried out by the control system including the controller in combination with the various sensors, actuators, and other engine hardware. The specific routines described herein may represent one or more of any number of processing strategies such as event-driven, interrupt-driven, multi-tasking, multi-threading, and the like. As such, various actions, operations, and/or functions illustrated may be performed in the sequence illustrated, in parallel, or in some cases omitted. Likewise, the order of processing is not necessarily required to achieve the features and advantages of the example embodiments described herein, but is provided for ease of illustration and description. One or more of the illustrated actions, operations and/or functions may be repeatedly performed depending on the particular strategy being used. Further, the described actions, operations and/or functions may graphically represent code to be programmed into non-transitory memory of the computer readable storage medium in the engine control system, where the described actions are carried out by executing the instructions in a system including the various engine hardware components in combination with the electronic controller.
It will be appreciated that the configurations and routines disclosed herein are exemplary in nature, and that these specific embodiments are not to be considered in a limiting sense, because numerous variations are possible. For example, the above technology can be applied to V-6, I-4, I-6, V-12, opposed 4, and other engine types. The subject matter of the present disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, and other features, functions, and/or properties disclosed herein.
The following claims particularly point out certain combinations and sub-combinations regarded as novel and non-obvious. These claims may refer to “an” element or “a first” element or the equivalent thereof. Such claims should be understood to include incorporation of one or more such elements, neither requiring nor excluding two or more such elements. Other combinations and sub-combinations of the disclosed features, functions, elements, and/or properties may be claimed through amendment of the present claims or through presentation of new claims in this or a related application. Such claims, whether broader, narrower, equal, or different in scope to the original claims, also are regarded as included within the subject matter of the present disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102016221638.4 | Nov 2016 | DE | national |
| 102016221639.2 | Nov 2016 | DE | national |
