DE102019108222A1 - Internal combustion engine for a motor vehicle and motor vehicle - Google Patents

Abstract

The invention relates to an internal combustion engine (1) for a motor vehicle, with at least one exhaust gas turbocharger (4), which has at least one housing (5), at least one rotor and at least one bearing by means of which the rotor is rotatably mounted on the housing (5) , with at least one line (6) through which a lubricant can flow, via which the bearing can be supplied with the lubricant for lubricating the bearing, and with at least one valve device (8) arranged in the line (6), by means of which a Flow cross-section (S), via which the bearing can be supplied with the lubricant, is adjustable, the valve device comprising: at least one valve element (9) which can be moved along a direction of movement (10) into different positions relative to a stop (11) , whereby the flow cross section (S) is adjustable; - at least one along the direction of movement (10) on the one hand to at least indirectly on the stop (11) and on the other hand at least indirectly on the valve element (9) supported or supportable spring element (15); and- at least one expansion element (19) which automatically deforms as a function of its temperature, whereby the stop (11) can be moved along the direction of movement (10).

Description

The invention relates to an internal combustion engine for a motor vehicle according to the preamble of patent claim 1. The invention also relates to a motor vehicle.

The DE 10 2013 203 042 A1 discloses a turbocharger for an internal combustion engine, with an oil-lubricated bearing, a feed line for the oil, a flow limiter for the oil and a control unit for controlling the flow limiter. It is provided that the control unit is designed to open the flow limiter completely when the internal combustion engine is cold started and to close the flow limiter at least partially after a predetermined period of time.

In addition, the DE 10 2011 103 657 A1 a lubricant supply device for an internal combustion engine, with at least one lubricant circuit which has at least one lubricant pump. By means of the lubricant pump, at least one component of the internal combustion engine can be supplied with lubricant from a lubricant reservoir via at least one lubricant line of the lubricant circuit. It is provided that the lubricant pump is variably adjustable with regard to its delivery rate.

The object of the present invention is to create an internal combustion engine and a motor vehicle so that a needs-based supply of at least one bearing of an exhaust gas turbocharger of the internal combustion engine can be implemented in a particularly simple manner.

According to the invention, this object is achieved by an internal combustion engine with the features of claim 1 and by a motor vehicle with the features of claim 10. Advantageous refinements of the invention are the subject of the dependent claims.

A first aspect of the invention relates to an internal combustion engine for a motor vehicle, which is preferably designed as a reciprocating piston machine and is also referred to as a motor or internal combustion engine. This means that the motor vehicle in its completely manufactured state has the internal combustion engine and can be driven by means of the internal combustion engine, in particular by means of an internal combustion engine. The motor vehicle is designed, for example, as a motor vehicle, in particular as a passenger vehicle. However, the motor vehicle can also be designed as a motorcycle or as a motorcycle.

The internal combustion engine has at least one exhaust gas turbocharger, by means of which the internal combustion engine or at least one combustion chamber of the internal combustion engine can be supplied with compressed air. The exhaust-gas turbocharger comprises at least one housing, at least one rotor and at least one bearing, by means of which or via which the rotor is rotatably mounted on the housing. The housing is also referred to as a bearing housing or a turbocharger housing and is, for example, a bearing housing on which the running gear is rotatably supported by the bearing. For this purpose, the bearing comprises, for example, at least one roller bearing or at least one sliding bearing. The bearing is also referred to as a bearing point, is a bearing point and comprises a bearing point at which the rotor is rotatably mounted on the housing. The rotor includes, for example, a turbine wheel, a shaft and a compressor wheel, the turbine wheel and the compressor wheel also being referred to as impellers. The running wheels are, for example, non-rotatably connected to the shaft, wherein at least or precisely one of the running wheels can be formed in one piece with the shaft. The turbine wheel can be driven, for example, by exhaust gas from the internal combustion engine, in particular exhaust gas from the combustion chamber, and can thereby be rotated about an axis of rotation relative to the turbocharger housing. Since the turbine wheel is connected to the shaft in a rotationally fixed manner, the shaft is rotated about the axis of rotation relative to the housing because the turbine wheel is rotated about the axis of rotation relative to the turbocharger housing. In addition, because the compressor wheel is connected to the shaft in a rotationally fixed manner, it is rotated about the axis of rotation relative to the housing when the shaft and the turbine wheel are rotated about the axis of rotation relative to the housing. The compressor wheel can thus be driven by the turbine wheel via the shaft. By driving the compressor wheel, air, for example, which flows through an intake section of the internal combustion engine, also referred to as an intake duct, is compressed by means of the compressor wheel. As a result, the combustion chamber can be supplied with the air compressed by means of the compressor wheel. Overall, it can be seen that the shaft and the impellers are rotatable about the axis of rotation relative to the housing of the exhaust gas turbocharger.

The internal combustion engine also has at least one line through which a lubricant can flow and via which the bearing can be supplied with the lubricant for lubricating the bearing. The lubricant is preferably a liquid. In particular, the lubricant can be designed as an oil, which is, for example, an engine oil or is also referred to as engine oil. Since the camp by means of or via the line with the the Line flowing through lubricant is or is supplied, the line is a feed line or a feed channel, by means of which or which the lubricant is fed to the bearing or is to be fed. Thus, for example, the line is arranged upstream of the bearing in the direction of flow of the lubricant flowing towards the bearing. The bearing can be lubricated and / or cooled by means of the lubricant in order to be able to avoid excessively high friction and excessively high loads on the bearing or in the exhaust gas turbocharger.

The internal combustion engine also has at least one valve device arranged in the line, via which the bearing can be supplied with the lubricant flowing through the line. Thus, for example, the valve device is arranged upstream of the bearing in the direction of flow of the lubricant flowing through the line and thereby flowing towards the bearing. By means of the valve device, a flow cross-section through which the lubricant can flow and via which the bearing can be supplied with the lubricant can be set, that is to say varied. In other words, the flow cross section can be varied by means of the valve device, that is to say, for example, can be set to different values, in particular values greater than zero. Furthermore, it is conceivable that the flow cross-section and thus the line can be completely blocked or closed by means of the valve device, whereby a supply of the bearing with lubricant, in particular via the line, is at least temporarily prevented or can be prevented.

In order to be able to supply the bearing with the lubricant in a particularly simple and tailored manner, it is provided according to the invention that the valve device comprises at least one valve element which, along a direction of movement, in particular in different positions and / or in particular translationally, relative to a stop , in particular the valve device, is movable, whereby the flow cross-section is adjustable or variably adjustable or variable. In other words, the flow cross section can be set or, in particular completely, closed by moving the valve element, in particular translationally, along the direction of movement and relative to the stop, to the aforementioned values that differ from one another.

In particular, it is conceivable that the valve element can be moved along the direction of movement relative to the stop between at least three mutually different positions, in particular translationally. A first of the positions is, for example, a closed position of the valve element which, in the closed position, blocks or closes the flow cross-section and thus the line, in particular completely. As a result, in the closed position of the valve element, no more lubricant can flow through the lines, so that in the closed position of the valve element, the supply of lubricant to the bearing, in particular via the line, is at least temporarily prevented. A second of the positions is, for example, a first open position of the valve element, which in the first open position releases the flow cross-section and thus the line. As a result, lubricant can flow through the line in the first open position, so that the bearing is or can be supplied with lubricant via the line in the first open position. The third position is, for example, a second open position of the valve element, which releases the line and thus the flow cross section in the second open position. For example, in the second open position the valve element releases the flow cross-section or the line more or more than in the first open position and than in the closed position, so that the line or the flow cross-section is further released in the first open position compared to the closed position and further or more open than in the second open position is more blocked. Expressed again in other words, for example, the flow cross-section in the closed position is set to a first value which is zero. This means that the flow cross-section is set to zero in the closed position and is therefore completely blocked. In the first open position, for example, a second value of the flow cross section greater than zero is set by means of the valve element, and in the second open position a third value of the flow cross section greater than zero and compared to the first value is set by means of the valve element.

According to the invention, the valve device furthermore comprises at least one spring element which is at least indirectly, in particular directly, supported or can be supported on the valve element along the direction of movement, on the one hand, in particular directly, and on the other hand, at least indirectly, in particular directly, on the valve element. in particular translational movement of the valve element is changeable or adjustable. This means that the valve device also includes the stop. In other words, the valve element is moved, for example, in a first direction coinciding with the direction of movement relative to the stop and is moved towards the stop, so that, for example, the first direction points to the stop, thus, for example, the spring element is tensioned, in particular compressed. As a result, the spring element provides, for example, a spring force by means of which, for example, the valve element can be moved relative to the stop in a second direction that coincides with the direction of movement and is opposite to the first direction and, for example, can be moved away from the stop. In other words, if the valve element is moved, for example, in the second direction relative to the stop, in particular in a translatory manner, the spring element, for example, is thereby at least partially relaxed and, for example, steered. In particular, it can be provided that the spring element is arranged between the valve element and the stop along the direction of movement.

In addition, the valve device according to the invention comprises at least one expansion material element, also referred to as an expansion material working element, which deforms as a function of its temperature, as a result of which the stop can be moved along the direction of movement, in particular translationally. In other words, the expansion element is deformable as a function of its temperature and thus as a function of temperature, in particular reversibly or non-destructively, with the expansion element, for example, expanding as the temperature of the expansion element increases. For example, if the temperature of the expansion element drops, the expansion element contracts, for example. Due to, in particular reversible, deformations of the expansion element resulting from temperature changes in the expansion element, which is deformable, for example, at least in the direction of movement, in particular reversibly, as a result of its temperature changes, the stop can be moved along the direction of movement, in particular translationally. In particular, the stop can be moved relative to the valve element along the direction of movement by temperature-related deformations of the expansion element. In particular, it is conceivable that the stop is moved along the direction of movement by means of the expansion element, that is, by deformation of the expansion element, in such a way that the stop is moved in the second direction relative to the valve element and is thus moved towards the valve element. In this way, for example, the spring element is tensioned or compressed. Alternatively or additionally, it is conceivable that the stop is moved by means of the expansion element, i.e. by means of a deformation of the expansion element, in such a way that the stop is moved in the first direction relative to the valve element and is thus moved away from the valve element, whereby for example the Spring element is at least partially relaxed or steered.

By using both the expansion element and the spring element, a temperature-dependent as well as pressure-dependent setting of the flow cross-section can be implemented in a particularly simple and thus cost-effective, space-saving and weight-saving manner. The pressure-dependent setting of the flow cross-section can be implemented, for example, by means of the spring element, since the valve element can be moved along the direction of movement against the spring element or against the spring force of the spring element depending on a pressure of the lubricant. The lubricant flowing through the line or received in the line can, for example, contact the valve element at least indirectly, in particular directly, or apply a pressure of the lubricant. The lubricant can for example move the valve element along the direction of movement against the spring force when the pressure is sufficiently high that a force resulting from the pressure of the lubricant and acting on the valve element and opposing the spring force is greater than the spring force.

The spring force provided by the spring element depends on the tension of the spring element, whereby - as described above - the tension of the spring element can be adjusted by moving the stop along the direction of movement and in particular relative to the valve element. Since the stop can be moved by means of the expansion element and thereby by deforming the expansion element along the direction of movement, in particular relative to the valve element, and since the expansion element deforms independently depending on its temperature, the tension of the spring element and thus that of the spring element depend provided spring force from the temperature of the expansion element. This allows the temperature-dependent setting or adjustability of the flow cross-section to be realized.

In particular, it can be provided that the temperature of the expansion material depends on a temperature of the lubricant. As a result, the flow cross-section can be adjusted both as a function of the pressure of the lubricant and as a function of the temperature of the lubricant by means of the valve device. As a result, the bearing can be supplied with the lubricant in a particularly simple manner as a function of the temperature and as a function of the pressure, an additional active control, regulation or control external to the valve device not being provided and not required. In other words, with respect to the valve device external, in addition to Actuators and controls provided for the valve device are avoided in order to adjust the flow cross-section as a function of temperature and pressure, since only such a temperature- and pressure-dependent setting of the flow cross-section can take place independently by the valve device. Overall, it can be seen that the valve device thus functions or can act as both a pressure-dependent and temperature-dependent throttle for the pressure and temperature-dependent setting of the flow cross section.

The invention is based on the following findings: The bearing of the exhaust gas turbocharger, the bearing of which is also referred to as a bearing or is part of a bearing, is acted upon and thus supplied with the lubricant, which is embodied as oil, for example, in order to avoid excessive friction in the exhaust gas turbocharger and to cool the storage sufficiently. The exhaust gas turbocharger has an air path and an exhaust gas path, or both an air path and an exhaust gas path run through the exhaust gas turbocharger. The exhaust gas for driving the turbine wheel flows through the exhaust gas path and thus through the exhaust gas turbocharger, in particular through a turbine housing or through a turbine of the exhaust gas turbocharger, and the air, which is compressed by means of the compressor wheel, flows through the air path and thus through the exhaust gas turbocharger or through a Compressor of the exhaust gas turbocharger. The turbine here comprises the turbine wheel and a turbine housing of the exhaust gas turbocharger, the turbine wheel of which is rotatably arranged in the turbine housing. The compressor comprises the compressor wheel and a compressor housing of the exhaust gas turbocharger, in whose compressor housing the compressor wheel is rotatably received. The turbine housing can be designed in one piece with the housing of the exhaust gas turbocharger, or the housing and the turbine housing are components that are designed separately from one another and connected to one another. Furthermore, it is conceivable that the compressor housing and the housing of the exhaust gas turbocharger are formed integrally with one another, or the compressor housing and the housing are formed as components that are formed separately from one another and connected to one another. To avoid, for example, that an excessive amount of the lubricant penetrates into the air path and into the exhaust gas path, in particular after the bearing has been lubricated by means of the lubricant, a respective seal, in particular a labyrinth seal, is provided, for example. By means of the respective seal, for example, the air or exhaust gas path is sealed against a lubricant path through which the lubricant can flow and for example running in or through the exhaust gas turbocharger.

The line comprises, for example, a first line part and a second line part, the first line part being, for example, a so-called oil gallery or main oil gallery. Via the oil gallery, for example, so-called main bearings, by means of which an output shaft of the internal combustion engine, for example designed as a crankshaft, is rotatably mounted on a housing part of the internal combustion engine designed, for example, as a crankcase, are supplied with lubricant. The bearing of the exhaust gas turbocharger is supplied with the lubricant flowing through the first line part, for example via the second line part, so that the second line part is arranged downstream of the first line part and upstream of the bearing in the flow direction of the lubricant flowing in particular from the first line part to the bearing. Thus, for example, the lubricant flows on its way to the bearing first through the first line part and thus through the oil gallery and then through the second line part. Both the main bearings and the bearings of the exhaust gas turbocharger are thus supplied with the lubricant via the oil gallery. Since the bearing of the exhaust gas turbocharger has a lower lubricant requirement than the main bearings, a rigid throttle is usually arranged downstream of the oil gallery and upstream of the bearing, for example in the second line part, through which a lubricant flowing to the bearing and, for example, the second line part can flow Forms or limits cross-section. Because the aforementioned throttle is a rigid throttle, this cross-section is fixed, that is to say not variable or unchangeable or rigid.

In contrast, it is now provided that the valve device arranged, for example, in the second line part and thus downstream of the first line part or downstream of the oil gallery and upstream of the bearing vary or set the flow cross-section and thereby for example both, in particular completely, and for example close to at least two of each other can set different values and values greater than zero. In this way, a particularly needs-based supply of the lubricant to the bearing, in particular from the oil gallery, can be implemented in a particularly simple manner.

In order to be sufficiently tight, that is to say to realize sufficient tightness, the rotating equipment should rotate at a speed which is greater than a defined minimum speed. Only in this way can the seal, embodied as a labyrinth seal, for example, achieve an adequate sealing effect and be sufficiently effective to avoid excessive large amount of the lubricant enters the air and exhaust pathways. If the speed of the rotor and consequently the sealing effect are not sufficient, which can be the case if the speed of the rotor is lower than the minimum speed, then, if no appropriate countermeasures have been taken, lubricant can enter the exhaust gas path or the turbine reach. This can lead to damage to the blades of the turbine wheel, in particular due to hot gas corrosion. In addition, an excessively large amount of the lubricant could get into the exhaust gas and poison exhaust gas aftertreatment devices, such as catalytic converters and / or particle filters, in particular Otto particle filters, arranged downstream of the turbine. As a result, an exhaust gas aftertreatment to be implemented by the exhaust gas aftertreatment devices can be adversely affected.

In addition, if the speed of the rotor is lower than the minimum speed and if no appropriate countermeasures have been taken, an excessively large amount of the lubricant can get into the air path or into the compressor. As a result, for example, an excessively large amount of the lubricant can get into the combustion chamber, which can also lead to damage. In addition, in both cases, lubricant is withdrawn from a lubricant circuit, also referred to as an oil circuit or designed as an oil circuit, which can lead to an undesirable and excessively large consumption of lubricant.

• - Vermeidung eines unerwünschten und übermäßig großen Schmiermittelverbrauchs infolge von nicht-funktionsfähigen Dichtungen des Abgasturboladers
• - Vermeidung einer übermäßigen Heißgaskorrosion an Schaufeln des Turbinenrads durch in den Abgaspfad übertretendes Schmiermittel, insbesondere aus dem Sch m ierm ittelkreislauf
• - Vermeidung von unerwünschten Schädigungen beziehungsweise Vergiftungen von Abgasnachbehandlungseinrichtungen
• - die Ventileinrichtung ist eine kostengünstige Alternative zu einem elektrischen beziehungsweise elektrisch betreibbaren oder schaltbaren Schaltventil im Schmiermittelkreislauf, mittels welchem aktiv eine Zufuhr des Schmiermittels zu dem Lager des Abgasturboladers einstellbar, insbesondere regelbar, ist oder eingestellt, insbesondere geregelt, wird.

The aforementioned disadvantages and problems can now be avoided in the internal combustion engine according to the invention, since the flow cross-section can be set, in particular regulated, both as a function of temperature and as a function of pressure. For this purpose, the valve device acts in the manner described as a temperature and pressure-dependent, in particular as a temperature and pressure-regulated, throttle. In particular, the invention can achieve the following advantages:

• - Avoidance of an undesirable and excessively large consumption of lubricant due to non-functional seals of the exhaust gas turbocharger
• Avoidance of excessive hot gas corrosion on the blades of the turbine wheel due to lubricant escaping into the exhaust gas path, in particular from the lubricant circuit
• - Avoidance of undesired damage or poisoning of exhaust gas aftertreatment devices
• The valve device is an inexpensive alternative to an electrical or electrically operated or switchable switching valve in the lubricant circuit, by means of which a supply of lubricant to the bearing of the exhaust gas turbocharger is actively adjustable, in particular regulatable, or adjusted, in particular regulated.

The valve element is, for example, movable relative to a valve housing of the valve device, in particular in a translatory manner. The valve housing can be formed by the line, in particular by the second line part, so that the valve housing is formed, for example, in one piece with the line, in particular in one piece with the second line part. Furthermore, it is conceivable that the valve housing is formed separately from the line or separately from the second line part. The valve element is, for example, at least partially, in particular at least predominantly or completely, received in the valve housing and can be moved relative to the valve housing along the direction of movement, in particular in a translatory manner. In this case, for example, the flow cross section is partially limited or formed by the valve housing and partially by the valve element. The valve element is preferably designed at least on the outer circumference as a ball and thus as a valve ball, as a result of which the flow cross section can be set particularly precisely and inexpensively.

It has been shown to be particularly advantageous if the expansion element and the spring element are connected in series, that is, in series with one another, along the direction of movement. As a result, the flow cross section can be set particularly advantageously both as a function of the pressure and as a function of the temperature.

In a particularly advantageous embodiment of the invention, the valve device has a valve seat which is formed, for example, by the aforementioned valve housing. The valve element is movable relative to the valve seat, in particular translationally, along the direction of movement. In the closed position described above, the valve element sits, for example, on the valve seat, whereby the valve element completely closes the flow cross-section and thus the line.

In the first open position the valve element has, for example, a first distance from the valve seat running along the direction of movement, and in the second open position the valve element has, for example, a second distance from the valve seat running along the direction of movement, the second distance being greater than the first distance is. Thus, for example, the flow cross-section is in the second The open position is greater than in the first open position, the flow cross section being greater than zero and thus released both in the first open position and in the second open position. In the closed position, the flow cross-section is zero and therefore completely closed.

Another embodiment is characterized in that the stop can be moved, in particular translationally, by deformations or by deforming the expansion element along the direction of movement relative to the valve seat or relative to the valve housing.

The lubricant that can be picked up or received in the line, in particular in the second line part and thereby directly touches the valve element or flows directly onto and / or around the valve element, moves the valve element in the first direction and thus against the spring force provided by the spring element, for example Stop when the lubricant has a pressure which corresponds to an opening pressure or is greater than the opening pressure. This is due, for example, to the fact that the opening pressure leads to a force acting on the valve element, pointing in the first direction and thus opposite to the spring force and also referred to as the opening force, which is greater than the spring force. Since the tension of the spring element and thus the spring force can be adjusted by moving the stop, the opening pressure can be adjusted, so to speak, by moving the stop. Since the stop can be moved by means of the expansion element and thus the movement of the stop and thus a position of the stop relative to the valve seat or relative to the valve along the direction of movement depends on the temperature of the expansion element, the opening pressure depends, so to speak, on the temperature of the expansion element . Since, for example, there can be an exchange of heat between the expansion element and the lubricant, the opening pressure is adjusted, so to speak, as a function of the temperature of the lubricant. An additional external activation or control can thus be avoided, so that the costs, the space requirement and the weight can be kept particularly low.

In a particularly advantageous embodiment of the invention, the valve element and the stop can be moved translationally relative to the valve seat along the direction of movement. As a result, the space requirement and thus the costs can be kept particularly low.

Another embodiment is characterized in that the valve seat tapers in a direction coinciding with the direction of movement, in particular in the second direction. In particular, the valve seat can be designed to be at least substantially conical or frustoconical. This allows the flow cross-section to be set particularly precisely.

In a particularly advantageous embodiment of the invention, the temperature of the expansion element can be changed as a result of a direct or indirect heat exchange between the expansion element and the lubricant. For example, the valve device is designed or arranged in such a way that the lubricant received in the line, in particular in the second line part, or the lubricant flowing through the line or the second line part can directly touch the expansion element and thereby, for example, flow directly onto and / or around it. This enables a direct heat exchange between the expansion element and the lubricant.

In order to avoid undesirable interactions between the expansion element and the lubricant, it is preferably provided that the expansion element and the lubricant can exchange heat via at most two, in particular via exactly one component provided in addition to the expansion element and in addition to the lubricant. In other words, it is preferably provided that a heat path extending from the lubricant received in the line, in particular in the second line part, to the expansion element or vice versa, via which heat can be exchanged between the expansion element and the lubricant, that is, can be exchanged, runs over at most two or over only or exactly one component provided in addition to the expansion element and in addition to the lubricant, so that, based on the heat path between the expansion element and the lubricant received in the line, in particular in the second line part, only or precisely one in addition to the expansion element and in addition to the lubricant provided component is arranged. As a result, a particularly effective and efficient heat exchange can take place between the expansion element and the lubricant, so that the temperature of the expansion element is at least essentially directly dependent on the temperature of the lubricant. In other words, the temperature of the expansion element can adapt or equalize to the temperature of the lubricant in a particularly short time, whereby the flow cross section can be set particularly well as a function of the temperature of the lubricant and as a function of the pressure of the lubricant.

In a further embodiment of the invention, the internal combustion engine has the aforementioned housing part, which is designed, for example, as a crankcase and which at least partially, in particular directly, delimits the combustion chamber of the internal combustion engine. In this case, the line comprises at least one channel running inside the housing part and through which the lubricant can flow, which channel is for example the aforementioned first line part or the oil gallery.

In order to be able to keep the installation space requirement particularly low, it is preferably provided that the valve element is received in at least one position of the valve element, in particular in the closed position, within the housing part and, for example, in the channel. In particular, it is preferably provided that the valve element is received within the housing part, in particular within the channel, at least in the closed position but preferably also in the first open position and in the second open position.

A second aspect of the invention relates to a motor vehicle, preferably designed as a motor vehicle, in particular a passenger vehicle, which has an internal combustion engine according to the invention according to the first aspect of the invention and can be driven by means of the internal combustion engine. Advantages and advantageous configurations of the first aspect of the invention are to be regarded as advantages and advantageous configurations of the second aspect of the invention and vice versa.

• 1 ausschnittsweise eine schematische Perspektivansicht einer erfindungsgemäßen Verbrennungskraftmaschine für ein Kraftfahrzeug;
• 2 ausschnittsweise eine weitere schematische Perspektivansicht der Verbrennungskraftmaschine;
• 3 eine schematische Schnittansicht einer Ventileinrichtung der Verbrennungskraftmaschine; und
• 4 eine weitere schematische Schnittansicht der Ventileinrichtung.

Further details of the invention emerge from the following description of a preferred exemplary embodiment with the associated drawings. It shows:

• 1 a fragmentary schematic perspective view of an internal combustion engine according to the invention for a motor vehicle;
• 2 a detail of a further schematic perspective view of the internal combustion engine;
• 3 a schematic sectional view of a valve device of the internal combustion engine; and
• 4th a further schematic sectional view of the valve device.

Identical or functionally identical elements are provided with the same reference symbols in the figures.

1 shows a section of an internal combustion engine in a schematic perspective view 1 for a motor vehicle. This means that the motor vehicle in its fully manufactured state is the internal combustion engine 1 includes and by means of the internal combustion engine 1 is drivable. This includes the internal combustion engine 1 one as a crankcase 2 formed housing part through which several cylinders 3 are formed or limited. In the fully manufactured state of the internal combustion engine designed as a reciprocating piston engine 1 limit the cylinders 3 partly respective combustion chambers. In the respective cylinder 3 a piston, which cannot be seen in the figures, is received in a translationally movable manner, the piston likewise partially delimiting the respective combustion chamber. In addition, the respective combustion chamber is limited by a combustion chamber roof, which is formed by a cylinder head. The cylinder head is separate from the crankcase 2 formed and with the crankcase 2 connected. The respective piston is connected in an articulated manner via a respective connecting rod to an output shaft designed as a crankshaft, so that the translational movements of the respective piston in the respective cylinder 3 can be converted into a rotational movement of the crankshaft. The crankshaft is rotatable on the crankcase by means of respective main bearings, which cannot be seen in the figures 2 stored. The internal combustion engine can use the crankshaft 1 Provide torques for driving the motor vehicle.

The internal combustion engine 1 has at least one exhaust gas turbocharger 4th on. The exhaust gas turbocharger 4th comprises at least one housing, also referred to as a bearing housing, turbocharger housing or bearing housing 5 . Also includes the exhaust gas turbocharger 4th a turbine and a compressor. The turbine includes a turbine wheel which is about an axis of rotation relative to the housing 5 is rotatable. The compressor comprises a compressor wheel which is about the axis of rotation relative to the housing 5 is rotatable. The turbine wheel and the compressor wheel are also referred to as impellers and are components of a rotor that rotates around the axis of rotation relative to the housing 5 is rotatable. The running gear also includes a shaft which is connected to the running wheels in a rotationally fixed manner. The turbine wheel is made of exhaust gas from the cylinders 3 drivable and thereby about the axis of rotation relative to the housing 5 rotatable. The turbine wheel is driven thereby around the axis of rotation relative to the housing 5 rotated, the compressor wheel is thereby driven via the shaft of the turbine wheel.

The internal combustion engine 1 has one of the exhaust gas from the cylinders 3 through-flow exhaust tract, in which downstream the cylinder 3 Exhaust aftertreatment devices such as catalytic converters and / or particle filters can be arranged. It also includes the internal combustion engine 1 one of air through which the air can flow to and especially into the cylinder 3 to be led. The turbine is arranged in the exhaust tract and can be driven by the exhaust gas flowing through the exhaust tract. In addition, the compressor is arranged in the intake tract, so that the air flowing through the intake tract is or can be compressed by means of the compressor wheel. This allows the respective cylinder 3 be supplied with the air compressed by means of the compressor. Thus, the internal combustion engine 1 designed as a charged internal combustion engine or as a turbo engine.

The exhaust gas turbocharger 4th also has at least one bearing, by means of which the rotor can be rotated on the housing 5 is stored. It also includes the internal combustion engine 1 a line also referred to as a supply line or supply line 6th , through which a lubricant, preferably designed as an oil, can flow. The oil is also known as engine oil and can by means of the pipe 6th to be led to the camp. This means that the camp is by means of or via the line 6th can be supplied with the lubricant. By means of the lubricant, the bearing can be lubricated and cooled, so that excessive temperatures and excessive friction in the exhaust gas turbocharger 4th can be avoided. The administration 6th is also referred to as a channel or oil channel and comprises, for example, a first line part which is inside the crankcase 2 runs and is also referred to as the oil gallery or main oil gallery. In particular, the first line part runs directly through the crankcase in its circumferential direction 2 , in particular through a wall of the crankcase 2 , limited, so that's through the line 6th and thus lubricant flowing through the first conduit part the crankcase 2 or can touch the wall directly.

The administration 6th furthermore comprises a second line part fluidically connected to the first line part 7th through which the lubricant can flow. The second part of the line 7th is for example a separate from the crankcase 2 formed line element, which mechanically with the exhaust gas turbocharger 4th , especially with the case 5 , and with the crankcase 2 connected is. The lubricant (oil) can thus first flow through the first line part and then flow to the second line part, that is, flow out of the first line part and flow into the second line part, whereupon the oil flows through the second line part 7th can flow through. This is the second line part 7th in the direction of flow of the line 6th The lubricant flowing through and thereby flowing towards the bearing is arranged downstream of the first line part and upstream of the bearing. For example, the oil is conveyed from a reservoir by means of a pump, not shown in the figures, and through the line 6th promoted through, that is promoted through the line parts. The second part of the line 7th runs, for example, outside of the first line part and outside of the crankcase 2 .

Especially good when viewed together with 2 to 4th it can be seen that the internal combustion engine 1 also one on the line 6th arranged valve device 8th having. By means of the valve device 8th is or becomes a flow cross section through which the lubricant can flow, in particular via the line 6th , adjustable or set, wherein the bearing can be or is supplied with the lubricant via the flow cross-section. In other words, the lubricant flows through the flow cross section on its way from the reservoir to the bearing.

In order to be able to supply the bearing with the lubricant particularly as required and in a particularly simple manner, the valve device comprises 8th a valve element embodied in the present case as a ball or valve ball 9 , which is shown along one in the figures by a double arrow 10 illustrated direction of movement in different positions relative to a stop 11 is translationally movable, whereby the example in 3 The flow cross-section for the lubricant, denoted by S, is adjustable, that is, variable. The valve device also includes 8th a valve housing 12 , which is separate from the valve element 9 is trained. Here is the valve element 9 in the valve housing 12 recorded. The valve body 12 comprises two housing components formed separately from one another and connected to one another 13 and 14th , the valve element 9 in the housing component 14th is recorded. The housing component 13 is thus for example a cover by means of which the housing component 14th is locked.

The valve device 8th also comprises at least one along the direction of movement on the one hand at least indirectly, in particular directly, on the stop 11 and on the other hand, at least indirectly, in particular directly, on the valve element 9 supported or supportable spring element 15th , which is also known as a valve spring. In the embodiment shown in the figures, the valve spring is designed as a helical spring. As the spring element 15th along the direction of movement and thereby in a direction coinciding with the direction of movement, by an arrow 16 illustrated and from the valve element 9 first direction pointing away at least indirectly, in particular directly, on the stop 11 is supported, is the attack 11 also known as a spring seat. In other words, the stop forms 11 a spring seat on which the spring element 15th sits. In a direction that coincides with the direction of movement and is opposite to the first direction, indicated by an arrow 17th illustrated and from the plot 11 The second direction pointing away is - as will be explained in more detail below - the valve element 9 on a corresponding valve seat 18th supportable. The valve seat 18th is, in particular directly, through the valve housing 12 , especially through the housing component 14th , educated. Will the valve element 9 moved in the first direction and thus on the stop 11 to moved, so the spring element 15th compressed and thereby stretched. Then, for example, the valve element 9 moved in the second direction and thus away from the stop 11 moved away, the spring element is thereby 15th at least partially relaxed or steered. Overall it can be seen that the valve element 9 along the direction of movement relative to the valve housing 12 and relative to the stop 11 is translationally movable. Thus is the valve element 9 along the direction of movement also relative to the valve seat 18th translationally movable.

The valve device 8th also includes an expansion element 19th , which in the embodiment shown in the figures is made of wax and is thus designed as a wax element. The expansion element 19th is in the valve body 12 , especially in the cover (housing component 13 ), recorded or arranged. Here is the stop 11 about a piston 20th with the expansion element 19th coupled or connected or operatively connected. Here is the piston 20th partly in the housing component 13 and partly in the housing component 14th arranged.

The expansion element 19th deforms independently depending on its temperature. In other words, the expansion element can be deformed independently or automatically as a function of its temperature. Expressed again in other words, in particular reversible or non-destructive deformations of the expansion element occur 19th when the temperature of the expansion element 19th changes. In particular, the expansion element is deformed 19th at least along the direction of movement when temperature changes of the expansion element 19th occur. As a result, at least part of the expansion element moves 19th at least along the direction of movement. These deformations or movements of the expansion element, which run at least along the direction of movement 19th be over the piston 20th on the stop 11 transferred so that the stop 11 due to the temperature-related or temperature-dependent deformations of the expansion element 19th along the direction of movement relative to the valve housing 12 and / or relative to the valve element 9 is translationally movable.

Furthermore, the expansion element 19th and the valve element 9 connected in series with one another along the direction of movement. From a synopsis of 3 and 4th it can be seen that the stop 11 by deforming the expansion element 19th along the direction of movement relative to the valve seat 18th or relative to the valve housing 12 between at least two different positions S1 and S2 is translationally movable. The position S1 is also referred to as the first stop position, the position S2 is also referred to as the second stop position.

For example, the expansion element 19th if warmed up or warmer, the expansion element expands, for example 19th out. As a result, for example, at least part of the expansion element moves 19th in the second direction or the expansion element 19th thereby moves the stop 11 in the second direction relative to the valve seat 18th and thus on the valve seat 18th to, in particular relative to the valve element 9 . For example, the expansion element 19th cooled or cooler, for example, the expansion element pulls itself 19th together. As a result, for example, at least part of the expansion element moves 19th in the first direction or the expansion element 19th thereby moves the stop 11 in the first direction relative to the valve seat 18th and thus from the valve seat 18th away, especially relative to the valve element 9 .

The valve element 9 is for example along the direction of movement relative to the stop 11 can be moved translationally between at least two positions that differ from one another and are also referred to as valve element positions. In this regard, it should be emphasized that the valve element positions of the valve element 9 on the stop 11 relate and depending on the positions S1 and S2 of the attack 11 to different positions of the valve element 9 regarding the valve seat 18th or with respect to the valve housing 12 being able to lead. In 3 and 4th a first of focusing on the stop 11 related valve element positions shown. Under the feature that the valve element positions on the stop 11 refer, it is to be understood that the valve element positions are positions of the valve element 9 regarding the attack 11 or relative to the stop 11 denote or are. The first valve element position is in 3 and 4th With V1 designated. In contrast, the positions relate S1 and S2 of the attack 11 on the valve seat 8th or on the valve housing 12 so that the stop positions are respective positions of the stop 11 relative to the valve seat 18th define or describe or are.

The valve element is located 9 in the first valve element position V1 while the attack 11 in his position S1 is located - what is in 3 is shown - then the following is the first valve element position V1 based on the valve seat 18th a closed position ST1 of the valve element 9 . The closed position ST1 is based on the valve seat 18th relative position of the valve element 9 or a position of the valve element relative to the valve seat 18th . The valve element sits in the closed position ST1 9 on the valve seat 18th , whereby the flow cross-section S. and thus the line 6th are completely closed or locked.

However, there is the valve element 9 in the first valve element position V1 while the attack 11 in the second position S2 is what is in 4th is shown, it is the first valve element position V1 based on the valve seat 18th a first open position O1 . In the first open position O1 is the valve element 9 , in particular completely, from the valve seat 18th spaced so that the valve element 9 the flow cross section S. and thus the line 6th releases. In the first open position O1 is a first value of the flow area S. set or in the first open position O1 is the flow cross-section S. set to the first value. The first open position O1 is a focus on the valve seat 18th relative position of the valve element 9 or a position of the valve element relative to the valve seat 18th . The first value is greater than 0.

Now, for example, the valve element 9 by means of the valve element 9 directly contacting lubricant, in particular by a pressure of the valve element 9 directly contacting lubricant, from the first valve element position V1 in the first direction relative to the valve housing 12 and in particular relative to the stop 11 moved translationally, so comes the valve element 9 For example, in the second valve element position, not shown in the figures. The valve element is in the second valve element position 9 closer to the stop along the direction of movement 11 arranged than in the first valve element position V1 . For example, there is the valve element 9 in the second valve element position, while the stop 11 in the position S2 is located, the second valve element position is related to the valve seat 18th a second open position not shown in the figures. In the second open position, the valve element is 9 the flow cross section S. more freely than in the first open position O1 so that the flow cross-section S. in the second open position is set to a second value greater than the first value or has the second value greater than the first value. The second value is greater than 0.

The valve element is located 9 for example in the second valve element position, while the stop 11 in the first position S1 is located, then the second valve element position is, for example, the open position O1 regarding the valve seat 18th or one of the first open position O1 and a third open position which is different from the second open position and in which the flow cross section S. for example, is set to a third value or has the third value. The third value is greater than 0. The third value can correspond to the first value. Or the third value is greater than the first value and in particular smaller than the second value. Or the third value is smaller than the first value and in particular smaller than the second value. The first value, the second value and the third value are preferably greater than zero.

Especially good 3 and 4th it can also be seen that the line part 7th or the line element separately from the valve housing 12 formed and mechanically and fluidically with the valve housing 12 connected, so that's the line 6th lubricant flowing through the valve housing 12 flow through and over the valve housing 12 in the line part 7th can flow. Also is the valve housing 12 separate from the crankcase 2 formed and mechanically and fluidically connected to the crankcase 2 connected. Thus, for example, the lubricant can flow from the first line part (oil gallery) into the valve housing 12 stream. The valve body 12 is partially within the crankcase 2 and partly outside the crankcase 2 arranged.

To the valve body 12 on the crankcase 2 to hold, comes a holder 22nd for use. The holder 22nd is for example separate from the crankcase 2 and separate from the valve housing 12 formed and each mechanically with the crankcase 2 and with the valve body 12 connected. Also is the valve element 9 both in the closed position S1 as well as in the respective open position in the crankcase 2 recorded. In the valve body 12 is for example a membrane 21st arranged, which is preferably formed from a rubber and thus designed as a rubber membrane. In this way it can be avoided that, for example, that of the valve housing 12 in the line part 7th flowing lubricant between the piston 20th and the Valve body 12 flows through and for example directly to the expansion element 19th got.

It is preferably provided that, based on one of the in the valve housing 12 and thus on the line 6th recorded or the valve housing 12 and the line 6th lubricant flowing through to the expansion element 19th or inversely running heat path, via which heat between that in the valve housing 12 absorbed lubricant and the expansion element 19th is exchangeable, at most two, in particular at most one, in addition to the lubricant and in addition to the expansion element 19th provided components are arranged in the heat path. Thus, the expansion element 19th and the lubricant exchange heat via a maximum of two components, in particular via a maximum of one component, so that the temperature of the expansion element 19th can adapt or equalize particularly quickly to the temperature of the lubricant. In the embodiment shown in the figures, there are at most two components arranged in the heat path, for example the piston 20th and the membrane 21st . This allows an indirect, but at the same time efficient and effective heat exchange between the expansion element 19th and the lubricant, which increases the temperature of the expansion element 19th can be changed effectively and efficiently.

In comparison to a mechanical, rigid throttle via which the bearing can be supplied with the lubricant, the valve device 8th a temperature and pressure-dependent supply of the bearing with the lubricant can be implemented in a simple manner. In particular, the valve device 8th act as temperature and pressure-dependent, especially temperature and pressure-regulated, throttle. A mechanical, rigid throttle is usually designed for hot oil, which is accompanied by a limitation of the oil throughput in order to avoid excessive oil loss via the bearing. In this way, oil consumption and excessive wetting of the running gear with oil can be avoided. Excessive application of oil to the exhaust gas aftertreatment device can also be avoided. Such a design of a mechanical, rigid throttle is naturally a compromise between cold operating states, in which the oil is viscous, and warm operating states, in which the oil is thinner or less liquid than the cold operating states. In the case of a mechanical, rigid throttle, the oil pressure would therefore have to be increased significantly at low temperatures of the oil, which is viscous at low temperatures, in order to be able to supply the bearing with sufficient oil in the case of the rigid throttle. Since, however, both the bearing and the main bearings of the crankshaft over the main bearings and the bearing of the exhaust gas turbocharger 4th common oil gallery are supplied with the oil, an increase in the oil pressure would lead to the entire internal combustion engine 1 would be operated on the high oil pressure, which would mean disadvantages in consumption and acoustics. These previously mentioned problems and disadvantages can now be solved with the aid of the valve device 8th be avoided.

• - Die Verbrennungskraftmaschine 1 soll im Schubbetrieb ohne Ladungswechselverluste drehen, zum Beispiel durch geschlossene Ventile, sodass der Kolben auf eine Gasfeder fährt, wodurch Verbrauchsvorteile realisiert werden können.
• - kein Luftüberschuss im Schubbetrieb im Abgastrakt, da ansonsten eine Funktionalität eines Ottopartikelfilters nicht mehr vorgegeben werden könnte, wodurch Emissionen gering gehalten werden können
• - Umsetzung für beide Fälle durch geschlossene Ventile (Ein- und/oder Auslassventil); Folge: Kein Luft- beziehungsweise Abgasmassenstrom zum Abgasturbolader 4, welcher nicht mehr mit der notwendigen Mindestdrehzahl drehen kann, die benötigt wird, um die Dichtwirkung der Ölversorgung zu gewährleisten.

In addition, the following additional requirements can be placed on the exhaust gas turbocharger 4th , especially in its operation, can be realized:

• - The internal combustion engine 1 should rotate in overrun mode without loss of gas exchange, for example through closed valves, so that the piston moves on a gas spring, which can be used to achieve consumption advantages.
• - No excess air in overrun mode in the exhaust tract, since otherwise the functionality of a gasoline particle filter could no longer be specified, which means that emissions can be kept low
• - Implementation in both cases by closed valves (inlet and / or outlet valve); Result: No air or exhaust gas mass flow to the exhaust gas turbocharger 4th which can no longer rotate at the minimum speed required to ensure the sealing effect of the oil supply.

The temperature-dependent setting of the flow cross-section S. takes place in the following way: the throttling effect is reduced in the case of viscous, cold oil, but throttled in the case of thin, warm oil. Thus, when the oil is cold, sufficient oil is brought to the bearing of the rotor, even if the exhaust gas turbocharger 4th or the rotor rotates quickly, which is the case, for example, at full load, and when the oil is warm, only as much lubricant as required is transported to the storage.

The pressure-dependent setting of the flow cross-section S. can take place as follows: change in the throttling effect via the spring-loaded valve element, which in the present case is designed as a ball valve 9 . The flow cross-section, also referred to as the valve opening cross-section S. is larger than with rigid chokes. The opening pressure is adjusted so that the regulating oil pressure of the fired engine is already used to open the valve element 9 leads. In the overrun mode, the target oil pressure in the engine should then be lowered below the opening pressure, the valve element 9 closes, the oil supply to the bearing is switched off.

List of reference symbols

1

Internal combustion engine

2

Crankcase

3

cylinder

4th

Exhaust gas turbocharger

5

casing

6

management

7th

Line part

8th

Valve device

9

Valve element

10

Double arrow

11

attack

12th

Valve body

13

Housing component

14th

Housing component

15th

Spring element

16

arrow

17th

arrow

18th

Valve seat

19th

Expansion element

20th

piston

21st

membrane

22nd

holder

O1

Open position

S.

Flow cross-section

S1

Closed position

V1

Valve element position

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102013203042 A1 [0002]
• DE 102011103657 A1 [0003]

Claims (10)

Internal combustion engine (1) for a motor vehicle, with at least one exhaust gas turbocharger (4), which has at least one housing (5), at least one rotor and at least one bearing by means of which the rotor is rotatably mounted on the housing (5), with at least one line (6) through which a lubricant can flow, via which the bearing can be supplied with the lubricant for lubricating the bearing, and with at least one valve device (8) arranged in the line (6), by means of which a flow cross-section (S) through which the lubricant can flow , via which the bearing can be supplied with the lubricant, is adjustable, characterized in that the valve device comprises: - at least one valve element (9) which is movable along a direction of movement (10) relative to a stop (11), whereby the flow cross-section (S) is adjustable; - At least one spring element (15) supported or capable of being supported along the direction of movement (10) at least indirectly on the stop (11) and at least indirectly on the valve element (9); and - at least one expansion element (19) which automatically deforms as a function of its temperature, whereby the stop (11) can be moved along the direction of movement (10). Internal combustion engine (1) after Claim 1 , characterized in that the expansion element (19) and the spring element (15) are connected in series with one another along the direction of movement (10). Internal combustion engine (1) after Claim 1 or 2 , characterized in that the valve device (8) has a valve seat (18), the valve element (9) along the direction of movement (10) relative to the valve seat (18) between a closed position (S1) in which the valve element (9) sits on the valve seat (18) and thereby completely closes the flow cross section (S), and at least two mutually different open positions (O1) can be moved for setting different values of the flow cross section (S). Internal combustion engine (1) after Claim 3 , characterized in that the stop (11) can be moved relative to the valve seat (18) along the direction of movement (10) by deformations of the expansion element (19). Internal combustion engine (1) after Claim 3 or 4th , characterized in that the valve element (9) and the stop (11) can be moved translationally relative to the valve seat (18) along the direction of movement (10). Internal combustion engine (1) according to one of the Claims 3 to 5 , characterized in that the valve seat (18) tapers in a direction (17) coinciding with the direction of movement (10). Internal combustion engine (1) according to one of the preceding claims, characterized in that the temperature of the expansion element (19) can be changed as a result of a direct or indirect heat exchange between the expansion element (19) and the lubricant. Internal combustion engine (1) according to one of the preceding claims, characterized in that the internal combustion engine (1) has at least one combustion chamber (3) of the internal combustion engine (1) at least partially limiting housing part (2), the line (6) at least one inside the Housing elements (2) running channel and through which the lubricant can flow. Internal combustion engine (1) after Claim 8 , characterized in that the valve element (9) is received in at least one position of the valve element (9) within the housing part (2). Motor vehicle with an internal combustion engine (1) according to one of the preceding claims.

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