DE102020113799A1 - VALVE ARRANGEMENT - Google Patents

Abstract

The invention relates to a valve arrangement for controlling a bypass opening in a turbine housing. The valve arrangement comprises a lever arm and a valve body with a valve disk. The valve body and the lever arm are fixed to one another. The sealing shell furthermore comprises an annular sealing lip which is arranged in the radial direction outside the valve disk.

Description

Technical area

The present invention relates to a valve arrangement for controlling a bypass opening in a turbine housing. In particular, the present invention relates to a turbine and a supercharging device with a corresponding valve arrangement.

background

More and more vehicles of the newer generation are being equipped with charging devices in order to meet the requirements and legal requirements. When developing charging devices, it is important to optimize both the individual components and the system as a whole with regard to their reliability and efficiency.

Known exhaust gas turbochargers have a turbine with a turbine wheel, which is driven by the exhaust gas flow from the internal combustion engine. A compressor with a compressor wheel, which is arranged on a common shaft with the turbine wheel, compresses the fresh air drawn in for the engine. This increases the amount of air or oxygen that the engine has available for combustion. This in turn leads to an increase in the performance of the internal combustion engine. In certain operating states it may be desirable to increase or reduce the flow rate of the exhaust gases or the exhaust gas volume flow itself. In this regard, variable turbine geometries and / or valve arrangements with a bypass valve are known in the prior art (also known as “wastegate” or exhaust gas valve), which divert part of the exhaust gas past the turbine wheel in certain operating states.

Disadvantages of known bypass valves are pulse-related rattling and vibrations (NVH) between the bypass valve and the valve seat. This often leads to wear and tear and, together with the build-up of the lining and thermally induced deformations of the bypass valve and / or the valve seat, leads to leaks at the bypass opening between the bypass valve and the valve seat when closed.

The object of the present invention is to provide an optimized valve arrangement for controlling a bypass opening in a turbine housing, which overcomes or at least reduces the above-mentioned disadvantages of NVH and thermal deformations.

Summary of the invention

The present invention relates to a valve arrangement for controlling a bypass opening in a turbine housing according to claim 1. In particular, the present invention relates to a turbine and a supercharging device with a corresponding valve arrangement according to claims 14 and 15.

The present invention relates to a valve arrangement for controlling a bypass opening in a turbine housing. The valve arrangement comprises a lever arm and a valve body with a valve disk. The valve body and the lever arm are fixed to one another. The valve arrangement is characterized by a sealing shell with an annular sealing lip, the annular sealing lip being arranged in the radial direction outside the valve disk. This particularly advantageous embodiment of the valve arrangement enables gas pulses to be received by the valve disk. Due to the fixed arrangement on the lever arm, the gas pulses can be counteracted with a sufficient counterforce. In this way, vibrations, in particular pulse-related vibrations, and rattling (NVH: noise, vibration, and harshness) can be prevented or at least reduced. The sealing lip of the sealing shell, which is arranged radially outside the valve disk, takes on the sealing function of the valve arrangement. This means that the sealing function and the absorption of the gas impulse forces are performed by two different elements. A certain functional decoupling can thus be achieved, in particular in comparison to conventional valve arrangements from the prior art, in which the valve disk also takes on the sealing function.

In embodiments of the valve arrangement, the sealing shell can be arranged so as to be movable relative to the valve disk. This particularly advantageous embodiment enables flexible and operationally appropriate adaptation or alignment of the sealing shell or the sealing lip relative to the valve body or valve disk. As a result, the sealing function can also be improved in the event of thermally and / or wear-related deformations and / or deposit formation of the valve arrangement, since the sealing shell or the sealing lip can compensate for the deformations or the formation of deposits at least to a certain extent.

In configurations of the valve arrangement which can be combined with the preceding configuration, the sealing shell can have a sealing axis around which the annular sealing lip is arranged. The sealing shell can be movable relative to the valve disk in such a way that the sealing axis is relative to a valve axis of the Valve disk can be tilted by an angle α. In addition, the following can apply: 0 ° α 8 °, preferably 0 ° α 6 °, and particularly preferably 0 ° α 4 °. The tilting movement enables the bypass opening to be closed even if the valve disk is not (yet) aligned parallel to a plane of the bypass opening. This can be relevant for the case, for example, when a valve seat of the bypass opening is thermally deformed (unevenly) and / or when a deposit forms on the valve seat.

In configurations of the valve arrangement that can be combined with any of the preceding configurations, the sealing shell can be designed to be brought into contact with a valve seat of the bypass opening in a closing manner via the annular sealing lip. This means that preferably only the sealing shell can be brought into contact with the valve seat. The valve disk should be arranged above the valve seat and / or radially inside the valve seat.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, the sealing shell can be designed essentially in the shape of a dome. The sealing shell can have an outer surface, an inner surface. Furthermore, the sealing shell can have a central through hole. The through hole can be arranged between the outer surface and the inner surface. The outer surface can be spherical. The inner surface can be designed spherically.

In addition to the preceding configurations, the through-hole of the sealing shell can extend between a first peripheral edge on the inner surface and a second peripheral edge on the outer surface. In addition, a first bore diameter of the first circumferential edge can be larger, smaller or the same as a second bore diameter of the second circumferential edge. An inner wall of the through hole can be formed parallel to the seal axis. Alternatively, the inner wall of the through hole can be designed to taper conically inward in the axial direction. With in the axial direction inward is here meant a direction from the outer surface to the inner surface. Alternatively, the inner wall of the through hole can be designed to taper conically outwardly in the axial direction. With in the axial direction inward is meant here a direction from the inner surface to the outer surface.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, a first contact area can be formed between the lever arm and the sealing shell. Furthermore, a second contact area can be formed between the valve body and the sealing shell. In addition, the first contact area can be formed by the spherical outer surface and a first sliding surface which is formed on the lever arm. The second contact area can be formed by the spherical inner surface and a second sliding surface which is formed on the valve disk. More specifically, the first sliding surface is formed on a contact portion of the lever arm. The first sliding surface is arranged opposite the second sliding surface. In other words, this means that the sealing shell is arranged between the lever arm or the (ring-shaped) contact area and the valve disk. In particular, the sealing shell can be arranged axially between the lever arm and the valve disk. Alternatively formulated, the sealing shell is arranged between the first sliding surface and the second sliding surface. In addition, the first and / or the second contact area or their respective surfaces (outer surfaces and first sliding surface; inner surface and second sliding surface) can be designed in such a way that there is a flat contact or a linear contact. In particular in the case of linear contact, alternative structures for guiding the sealing shell, such as edges running around the circumference, can also be used instead of the first sliding surface and / or the second sliding surface. Both configurations have certain advantages. The design with linearly implemented contact has certain advantages in terms of manufacturing technology and, under certain circumstances, lower friction due to the reduced contact surface in the first and / or second contact area. The configuration with a flat contact has a reduced risk of entanglement / wedging and a better seal between the sealing shell and the lever arm or contact section and / or between the sealing shell and the valve body or valve disk. Furthermore, the sealing shell can be guided better through the flat contact.

In addition to the preceding configurations, the first sliding surface can be configured complementary to the spherical outer surface. In addition, the first sliding surface can at least partially surround the spherical outer surface towards the outside in a spherical direction. A spherical direction is to be understood here as a direction which starts from the center of the sphere of the outer surface. This particularly advantageous embodiment leads to a planar contact between the lever arm and the sealing shell. As a result, the sealing shell can on the one hand slide better through better guidance. On the other hand, a better sealing effect can be achieved between the lever arm and the sealing shell in the operating state as well. Farther a low NVH can be achieved, especially in the partially open position.

As an alternative or in addition to the preceding configurations, the second sliding surface can be configured to be complementary to the spherical inner surface. In addition, the spherical inner surface can at least partially surround the second sliding surface towards the outside in a spherical direction. Analogous to the above, the spherical direction is to be understood here again as a direction that starts from the center of the sphere of the inner surface. This particularly advantageous embodiment leads to flat contact between the valve disk and the sealing shell. As a result, the sealing shell can on the one hand slide better through better guidance. On the other hand, a better sealing effect in the operating state and a low NVH can be achieved, in particular in the partially open position.

As an alternative or in addition to the preceding embodiments, a distance in the axial direction between the second sliding surface and the first sliding surface can be designed such that there is axial play between the lever arm, the sealing shell and the valve disk. This means that the sealing shell is minimally movable in the axial direction. This enables the sealing shell to slide along the inner surface and / or along the outer surface over the first sliding surface and / or the second sliding surface. This means that the sealing shell can slide relative to the lever arm and the valve disk. The axial play is composed of a first play between the first sliding surface and the spherical outer surface and a second play between the spherical inner surface and the second sliding surface. The axial play or the first and / or second play can be adjusted, for example, by a corresponding configuration of the valve body and / or the lever arm and / or the sealing shell (for example a thickness of the sealing shell). This means that the first and second contact areas are theoretically possible contact areas, but because of the play, they are present at the same time in very few operating states, or there is physical contact at the same time. For example, in the closed position of the valve arrangement, there is generally only one physical contact in the first contact area.

As an alternative or in addition to the preceding embodiments, the sealing shell can slide over the inner surface on the valve disk. Alternatively or additionally, the sealing shell can slide over the outer surface on the lever arm. This allows the seal axis to be adjusted relative to the valve axis. In this way, a geometry of the valve seat of the bypass opening and / or of the sealing shell itself that changes due to thermal deformation, deformation caused by wear or the build-up of deposits can be compensated.

In embodiments of the valve arrangement which can be combined with any of the preceding embodiments, the outer surface and the inner surface can be defined by spherical geometries with the same center. The sealing shell can have a uniform thickness in the axial direction between the spherical outer surface and the spherical inner surface. The sealing shell does not necessarily have to have a uniform thickness everywhere, but preferably at least in an area between the spherical section of the inner surface and the spherical section of the outer surface. The thickness of the sealing shell corresponds to the difference in radius between the outer surface and the inner surface. The inner surface and the outer surface can have different radii or curvatures but the same center. This means that the outer surface and the inner surface map partial surfaces of concentrically arranged spherical sections. In other words, the outer surface and the inner surface each define a section of a spherical shell, that is to say surface sections of the differential set of concentric balls.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, the annular sealing lip can have a sealing surface. The sealing surface can extend between an outer diameter of the sealing lip and an inner diameter of the sealing lip. Consequently, the sealing surface can also be referred to as an annular sealing surface. The sealing surface is particularly oriented in the axial direction. Alternatively, if the valve seat is inclined (e.g. conical or oblique), the sealing surface can also be designed correspondingly complementary.

In configurations of the valve arrangement that can be combined with any of the preceding configurations, a disk diameter of the valve disk can be smaller than an inner diameter of the sealing lip, so that there is a first radial clearance between the sealing lip and the valve disk. The dimensions of the valve disk and / or the sealing lip are selected in such a way that there is sufficient play to allow freedom of movement of the sealing shell relative to the valve disk and thus sliding along the spherical surfaces.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, the valve body can furthermore comprise a valve stem. The valve stem can protrude centrally from the valve disk in the axial direction and be attached to an annular contact portion of the lever arm. The center is to be seen as centered in the radial direction, i.e. where the valve axis runs. The valve stem protrudes into an opening in the contact section and is fastened there, in particular welded, punched, or fastened by another suitable joining method.

In addition to the preceding embodiment, the valve stem can extend through the through-hole of the sealing shell. A minimum diameter of the through hole can be larger than an outer diameter of the valve stem, so that there is a second radial play between the through hole and the valve stem. The dimensions of the through hole and / or the valve stem are selected such that there is sufficient play to allow freedom of movement of the sealing shell relative to the valve disk or the valve stem and thus to slide along the spherical surfaces. The sealing shell is basically arranged radially outside the valve stem.

As an alternative or in addition to the preceding embodiment, an outer diameter of the annular contact section can be greater than a minimum diameter of the through hole. This advantageous configuration can prevent the sealing shell from slipping off. In other words, this serves to secure the sealing shell in the axial direction between the lever arm or the contact section and the valve body or the valve disk.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, the annular sealing surface of the sealing lip can overlap a disk surface of the valve disk in the axial direction in every operating state of the valve arrangement. In this case, only the annular sealing surface of the sealing lip is designed to be brought into contact with a valve seat of the bypass opening to close it.

In configurations of the valve arrangement which can be combined with any of the preceding configurations, the valve disk can have a second sliding surface. The second sliding surface can extend between a radially outer circumferential edge and a radially inner circumferential edge. In addition, the radially outer circumferential edge can define a plate diameter and the radially inner circumferential edge can define an outer diameter of a valve stem. Alternatively or additionally, a first distance in the axial direction of the sealing shell between the first peripheral edge and an inner edge of the sealing lip can be made larger than the sum of an axial play that exists between the lever arm, the sealing shell and the valve disk and a second distance in the axial direction between the radially inner circumferential edge and the radially outer circumferential edge.

In embodiments of the valve arrangement which can be combined with any one of the preceding embodiments, the valve arrangement can furthermore comprise a rotation lock which prevents the sealing shell from rotating about the sealing axis of the sealing shell.

In embodiments of the valve arrangement which can be combined with any of the preceding embodiments, the valve arrangement can furthermore comprise a damping element. The damping element can be arranged between the lever arm and the sealing shell or between the valve disk and the sealing shell.

The invention further comprises a turbine for a supercharger. The turbine includes a turbine housing with a bypass opening and a turbine wheel rotatably arranged in the turbine housing. The turbine is characterized by a valve arrangement according to any one of the preceding embodiments. In addition, the bypass opening can be surrounded by a valve seat. The sealing lip can be brought into contact with the valve seat in order to close the bypass opening. Alternatively or additionally, the turbine housing can include a first volute, a second volute and a volute partition. The volute partition separates the first volute and the second volute from one another. In other words, the turbine can be designed as a multi-flow turbine (multiscroll), in particular as a double-flow turbine (dual volute) or a twin-flow turbine (twin scroll). Alternatively, however, a single-flow design is also possible. In addition, the bypass opening can have a first opening area which opens into the first volute and a second opening area which opens into the second volute. Alternatively or additionally, the valve arrangement can be arranged in such a way that an axis of rotation of the lever arm is arranged orthogonally to a main flow direction of the gases through the volutes and orthogonally to the volute partition. This is particularly advantageous in order to counteract a change in the valve seat due to the formation of deposits. From a small degree of opening of the valve arrangement, gases can flow out of the bypass opening in a simplified manner in the main flow direction due to the corresponding inclination of the valve disk - this means that the valve body has to counteract lower impulse forces and ultimately the entire valve arrangement is less stressed. Furthermore, a thermally induced deformation of the valve seat can be better counteracted.

In configurations of the turbine, a disk diameter of the valve disk can be designed to be essentially the same as a diameter of the bypass opening. This means that the plate surface can essentially cover the bypass opening. In particular, deviations from a minimally smaller or a minimally larger plate surface are possible. A minimally larger plate area is particularly preferred because a large part of the pulses can be absorbed by the valve plate here. However, the plate surface should not be chosen to be significantly larger than the bypass opening in order to provide sufficient room for movement for the sealing shell and sufficient space for the sealing lip or the sealing surface on the valve seat.

The invention also relates to a charging device with a compressor. The charging device is characterized by a turbine according to any one of the preceding embodiments. The turbine is rotationally coupled to the compressor. In addition, the charging device can furthermore comprise an electric motor which is rotationally coupled to the compressor.

Figure list

• 1 Figure 3 shows a side sectional view of the valve assembly;
• 2A-2B show the side sectional view from the 1 in comparison to a side sectional view of a deformed or warped valve arrangement (deformation shown in dotted lines);
• 3 show a side sectional view of the anti-rotation valve assembly;
• 4th Figure 3 shows a side sectional view of the valve assembly with a damping element;
• 5A-5B show exploded isometric views of a valve assembly with rotation lock from above and from below;
• 6th shows a side sectional view of the valve arrangement with a double-flow turbine housing rotated by 90 ° with respect to the preceding figures;
• 7th shows a supercharger with a turbine and the valve assembly.

Detailed description

In the context of this application, the terms axial and axial direction respectively relate 22nd on a valve axis 122 of the valve disc 110 . Radial or a radial direction 24 are relative to the axial direction 22nd or to the valve axis 122 to see. The circumferential direction 26th is also relative to the axial direction 22nd or to the valve axis 122 to see. The axial direction is analogous to this 22 ' , the radial direction 24 ' and the circumferential direction 26 ' to see, however, on the sealing shell 300 Respectively. In certain operating states or operating conditions, the axial direction 22nd of the valve disc 110 with the axial direction 22 ' the sealing shell 300 (and thus also the radial directions 24 , 24 ' and the circumferential directions 26th , 26 ' ) match (neutral state: see explanations below in connection with the 2A and 2 B) .

1 shows the valve arrangement 10 to control a bypass opening 420 in a turbine housing 400 . The valve arrangement 10 includes a lever arm 200 and a valve body 100 with a valve disc 110 . The valve body 100 and the lever arm 200 are fixed to each other. The valve arrangement 10 is characterized by a sealing shell 300 with an annular sealing lip 310 , the annular sealing lip 310 in the radial direction 24 outside the valve disk 110 is arranged. This particularly advantageous embodiment of the valve arrangement 10 allows gas pulses to pass through the valve disc 110 can be included. Due to the fixed arrangement on the lever arm 200 a sufficient counterforce can be opposed to the gas impulse forces. In this way, vibrations, in particular pulse-related vibrations, and rattling can be prevented or at least reduced. The radially outside of the valve disk 110 arranged sealing lip 310 the sealing shell 300 takes over the sealing function of the valve arrangement 10 . This means that the sealing function and the absorption of the gas pulses are performed by two different elements. A certain functional decoupling can thus be achieved, in particular in comparison to conventional valve arrangements from the prior art, in which the valve disk also takes on the sealing function.

The sealing shell 300 has a seal axis 302 around which the annular sealing lip 310 is arranged. In the 1 fall the seal axis 302 and a valve axis 122 of the valve disc 110 together. The sealing shell 300 however, is relative to the valve disc 110 movably arranged. More precisely, the sealing shell can 300 thereby relative to the valve disc 110 move so that the seal axis 302 relative to the valve axis 122 of the valve disc 110 at an angle α is tiltable. In this regard, the 2A a valve assembly 10 in a neutral position where there are no deformations and the seal axis 302 with the valve axis 122 coincides. That is, the axial directions 22nd , 22 ' agree. In the 2 B however, is a valve arrangement 10 shown in which the sealing shell 300 relative to the valve disc 110 is tilted. In the example, this is 2 B on thermal expansion of a valve seat 421 the bypass opening 420 which is shown schematically by the dotted area. For the angle α The following applies in particular: 0 ° α 8 °, preferably 0 ° α 6 °, and particularly preferably 0 ° α 4 °. The tilting movement enables the bypass opening to be closed 420 even if the valve disc 110 not (yet) parallel to a plane of the bypass opening 420 is aligned. This can be relevant, for example, when the valve seat is 421 the bypass opening 420 (unevenly) thermally deformed and / or if there is a deposit on the valve seat 421 forms. This particularly advantageous embodiment enables flexible and operationally appropriate adaptation or alignment of the sealing shell 300 or the sealing lip 310 relative to the valve body 100 or valve disc 110 and thus to the bypass opening or to the valve seat 421 . As a result, the sealing function can also be performed in the event of thermally and / or wear-related deformations and / or formation of deposits on the valve arrangement 10 and / or one in the installed state with the valve arrangement 10 connectable valve seat 421 can be improved as the sealing shell 300 or the sealing lip 310 can compensate for the deformations or the formation of deposits at least to a certain extent.

Again 1 can be seen, is the sealing shell 300 designed over the annular sealing lip 310 in the installed state with a valve seat 421 the bypass opening 420 to be brought into the plant with sealing. A turbine housing 400 with the bypass opening 420 and the valve seat 421 is in the 1 also indicated schematically. This means that only the sealing shell is preferred 300 with the valve seat 421 can be brought into plant. The valve disc 110 is above the valve seat 421 arranged. That is, the valve disc 110 is above the bypass opening 420 and spaced from the valve seat 421 arranged. The valve disc 110 has a plate diameter 112a on. The plate diameter 112a is minimally smaller than a diameter 426 the bypass opening 420 . Furthermore is the valve disc 110 above the bypass opening 420 or above the valve seat 421 or arranged at a distance from this. So comes the valve disc 110 not in contact with the valve seat 421 . In alternative configurations, the plate diameter 112a of the valve disc 110 but also essentially the same size or slightly larger than the diameter 426 the bypass opening 420 be formed (not shown). Especially when the plate diameter 112a larger than the diameter 426 the bypass opening 420 is formed, the valve disc should 110 spaced above from the valve seat 421 be arranged.

That is, the ring-shaped sealing lip 310 overlaps the valve disc 110 in the axial direction 22nd . As a result, the annular sealing surface 312 the sealing lip 310 the valve disc 110 or a plate surface 116 of the valve disc 110 in every operating state of the valve arrangement 10 in the axial direction 22nd overlaps, it can be achieved that only the annular sealing surface 312 the sealing lip 310 with the valve seat 421 the bypass opening 420 is brought into plant sealing. This spacing from the valve seat 421 or the overlap through the sealing lip 310 is with a slightly smaller valve disc 110 in the radial direction 24 not absolutely necessary (i.e.: plate diameter 112a is minimally smaller than diameter 426 the bypass opening 420 ). It is only essential here that there is contact between the valve disk 110 and the valve seat 421 is avoided. That means the plate surface 116 should be the bypass opening 420 essentially overlap, but the contact to the valve seat 421 should be through the sealing cup 300 be implemented. In particular, there are deviations from a minimally smaller or a minimally larger plate surface 116 compared to the bypass opening 420 possible. A beneficial effect of covering the bypass opening 420 through the valve disc 110 is that essentially all forces come from gas pulses from the valve disc 110 or a plate surface 116 of the valve disc 110 can be included. However, the plate surface should 116 or the plate diameter 112 also not significantly larger than the bypass opening 420 or their diameter 426 be chosen to allow sufficient freedom of movement for the sealing shell 300 and enough space for the sealing lip 310 on the valve seat 421 to provide. For example, the valve disc should 110 no more than up to 50% of a width of the valve seat 421 cover.

As in 1 and especially in 5B can be clearly seen, has the annular sealing lip 310 a sealing surface 312 on. The sealing surface 312 extends between an outside diameter 316a the sealing lip 310 and an inside diameter 314a the sealing lip 310 . That is the sealing surface 310 is ring-shaped and can therefore also be used as an annular sealing surface 310 are designated. The sealing surface is in particular in the axial direction 22 ' the sealing shell 300 oriented. Alternatively, for example if the valve seat 421 is inclined (eg conical or oblique), the sealing surface can also 312 be designed accordingly complementary. In all figures (see in particular 5B) is the sealing lip 310 designed as an annular projection in the axial direction 22 ' from the rest of the sealing shell 300 emerges. In alternative configurations that are not shown here, the sealing lip 310 but only as a sealing surface 312 be formed, that is, without a projection in the axial direction 22 ' .

In both cases, the plate diameter is 112a of the valve disc 110 made smaller than the inner diameter 314a the sealing lip 310 (see in particular 1 ). This allows a first radial play 318 between the sealing lip 310 and the valve disc 110 to be provided. Here are the dimensions of the valve disk 110 and / or the sealing lip 310 chosen so that there is sufficient play to allow freedom of movement of the sealing shell 300 relative to the valve disc 110 and thus to enable sliding along the spherical surfaces (see below).

As in the 5A and 5B The sealing shell is clearly visible 310 substantially dome-shaped. The sealing shell 310 has an outer surface 322 , an inner surface 324 and a central through hole 330 between the outer surface 322 and the inner surface 324 on. The outside surface 322 and the inner surface 324 are spherical. Due to the spherical design, on the one hand, the (partial) encasing of the valve disk 110 are made possible. On the other hand, the spherical design allows a sliding movement of the sealing shell 300 along the spherical inner surface 324 and the spherical outer surface 323 are made possible. By sliding along the spherical surfaces 322 , 324 can be a predefined tilting of the seal axis 302 relative to the valve axis 122 are made possible. This ultimately leads to a valve arrangement 10 with improved sealing function, since the sealing shell 300 individually according to the valve seat 421 can align. The through hole 330 the sealing shell 310 extends between a first peripheral edge 332 on the inner surface 324 and a second peripheral edge 334 on the outer surface 322 . Like especially the 2A can be seen, is a first bore diameter 332a at the first peripheral edge 332 is the same size as a second bore diameter 334a on the second peripheral edge 344 . That is, an inner wall of the through hole 330 between the first peripheral edge 332 and the second peripheral edge 334 is parallel to the seal axis 302 educated. In alternative configurations, the first bore diameter 332a also larger or smaller than the second bore diameter 334a his. That is, the inner wall of the through hole 330 can also be conical in the axial direction 22 ' be tapered inward or conical in the axial direction 22 ' be designed to taper outwards. With in the axial direction inward is here from the outer surface 322 to the inner surface 324 meant there. With in the axial direction 22 ' inward is here from the inner surface 324 to the outside surface 322 meant there.

As in particular in 2A can be seen are the outer surface 322 and the inner surface 324 defined by spherical geometries with the same center. The sealing shell 300 in the axial direction 22 ' between the spherical outer surface 322 and the spherical inner surface 324 a uniform thickness 323 on. In alternative configurations, the sealing shell 300 not necessarily a uniform thickness everywhere 323 exhibit. The sealing shell preferably has 300 but at least in a region between the spherical section of the inner surface 324 and the spherical portion of the outer surface 322 a uniform thickness 323 on. The fat 323 the sealing shell 300 corresponds to the difference in radius between the spherical outer surface 322 and the spherical inner surface 324 . That is, the inner surface 324 and the outer surface 322 have different radii or curvatures but the same center. Where is the radius of the outer surface 322 larger than the radius of the inner surface 324 . This means that the outer surface 322 and the inner surface 324 Correspond to partial areas of concentrically arranged spherical sections. In other words, define the outer surface 322 and the inner surface 324 each a section of a spherical shell, i.e. surface sections of the difference in the set of concentric spheres.

Like in the 1 shown is a first contact area 12th between the lever arm 200 and the sealing cup 300 and a second contact area 14th between the valve body 100 and the sealing cup 300 educated. This is the first contact area 12th from the spherical outer surface 322 and a first sliding surface 212 that on the lever arm 200 is formed, formed. The second contact area 14th is from the spherical inner surface 324 and a second sliding surface 114 on the valve disc 110 is formed, formed. More precisely, the lever arm points 200 a contact section 210 on. Via the contact section 210 is the lever arm 200 with the valve body 100 or the valve disc 110 coupled. So is the lever arm 200 via the contact section 210 with the sealing shell 300 coupled. This is the first sliding surface 212 at the contact portion 210 of the lever arm 200 educated. The first sliding surface 212 is opposite to the second sliding surface 114 arranged. That means the sealing shell 300 between the lever arm 200 or the contact area 210 and the valve disc 110 is arranged. More precisely is the sealing shell 300 while axially between the lever arm 100 and the valve disc 110 arranged. The sealing shell is formulated as an alternative 300 between the first sliding surface 212 and the second sliding surface 114 arranged. The first contact area 12th and the second contact area 14th or their respective surfaces (outer surface 322 and first sliding surface 212 ; Inner surface 324 and second sliding surface 114 ) are designed in the present embodiments such that a Flat contact in the respective contact areas 12th , 14th may be present. This is for example in the closed state of the valve arrangement 10 (such as in 1 and 6th ) the case. Here it can be clearly seen that the outer surface 322 and the first sliding surface 212 in the first contact area 12th lie flat against each other. Theoretically, the inner surface could also be used here 324 and the second sliding surface 114 in the second contact area 14th lie flat against each other. However, this is in the closed state of the valve arrangement 10 due to axial play 326 , which is explained below, hardly or not possible. The flat contact in the first contact area 12th is achieved in that the first sliding surface 212 complementary to the spherical outer surface 322 is designed. The flat contact in the second contact area 14th is made possible by the fact that the second sliding surface 114 complementary to the spherical inner surface 324 is designed. These particularly advantageous configurations thus lead to a flat contact (depending on the operating state or degree of opening of the valve arrangement 10 or axial play 326 ) between the lever arm 200 and the sealing cup 300 or between the valve disc 110 and the sealing cup 300 . This allows the sealing shell 300 on the one hand, better gliding through better guidance. On the other hand, there can be a better sealing effect between the lever arm 200 and sealing cup 300 be achieved. Furthermore, a low NVH can be achieved, especially in the partially open position. As an alternative to the flat contact, between the lever arm 200 and the sealing cup 300 in the first contact area 12th and / or between the valve disc 110 and the sealing cup 300 in the second contact area 14th a linear contact can be formed. In the case of linear contact, instead of the first sliding surface 212 and / or the second sliding surface 114 also alternative structures for guiding the sealing shell 300 such as in the circumferential direction 26th circumferential edges are used. The first sliding surface would also be conceivable 212 conical or with a larger radius than the outer surface 322 to train. The second sliding surface could be analogous 114 with a smaller radius than the inner surface 324 be formed or the inner surface 324 could be conical. Both configurations have certain advantages. The design with linearly implemented contact has certain manufacturing advantages and, under certain circumstances, a lower risk of wear in the first contact area 12th and / or in the second contact area 14th . The configuration with a flat contact has a reduced risk of entanglement / wedging and a better seal between the sealing shell 300 and the lever arm 200 or contact section 210 and / or between the sealing shell 300 and the valve body 100 or valve disc 110 .

As already mentioned, a distance is in the axial direction 22nd between the second sliding surface 114 and the first sliding surface 212 designed such that an axial play 326 between the lever arm 200 , the sealing shell 300 and the valve disc 110 is present (see 2A) . This is the sealing shell 300 on the one hand minimally movable in the axial direction 22 ' . On the other hand, by choosing a correspondingly small game 326 good guidance is provided and vibration is reduced. Through the game 326 becomes a sliding of the sealing cup 300 along the inner surface 324 and / or along the outer surface 322 over the first sliding surface 212 or the second sliding surface 114 enables. That means sliding of the sealing cup 300 relative to the lever arm 200 and the valve disc 110 is possible. The axial play 326 is composed of a first play between the first sliding surface 212 and the spherical outer surface 322 and a second clearance between the spherical inner surface 324 and the second sliding surface 114 . The axial play 326 or the first and / or second play can be achieved, for example, by a corresponding design of the valve body 110 and / or the lever arm 200 and / or the sealing shell 300 (For example, a thickness through appropriate design 323 the sealing shell 300 and design of the distance in the axial direction 22nd between the second sliding surface 114 and the first sliding surface 212 ) can be set.

Due to the presence of axial play 326 is in the closed state of the embodiment of the valve assembly 10 only in the first contact area 12th a contact exists (see for example 6th ). The power flow runs from the lever arm 200 or the contact section 210 over the first sliding surface 212 and the outer surface 322 through the sealing shell 300 and then over the sealing surface 312 to the valve seat 421 and into the turbine housing 400 (see dashed line in 6th ). Due to the axial play 326 in this example there is no contact in the second contact area 14th , i.e. between the inner surface 324 and the second sliding surface 114 available. When lifting the valve disc 110 , so when opening the valve assembly 10 can the sealing shell 300 on the valve disc 110 and thus the inner surface can 324 and the second sliding surface 114 in the second contact area 14th to contact.

In other words, this means that the sealing shell 300 across the inner surface 324 on the valve disc 110 can slide off. Furthermore, the sealing shell 300 over the outer surface 322 on the lever arm 200 slide off. This allows a relative adjustment of the seal axis 302 to the valve axis 122 be implemented (see e.g. 2 B) . So one can get through thermal deformation, deformation caused by wear or the build-up of deposits that change the geometry of the valve seat 421 the bypass opening 420 be compensated. Thermal deformation or wear-related deformation or build-up of deposits on the sealing shell can also occur 300 be compensated.

All figures (see e.g. 5A) show that the valve body 100 furthermore a valve stem 120 includes. The valve stem 120 protrudes from the center of the valve head 100 in the axial direction 22nd emerged. Central is as central in the radial direction 24 to see, so there where the valve axis 122 runs. The contact section 210 of the lever arm 200 is ring-shaped and has an opening 216 on. The opening 216 is centered in the contact section 210 arranged. The valve stem 120 extends through the through hole 330 the sealing shell 300 , protrudes into the opening 216 of the lever arm 200 into it and is attached there. In particular is the valve stem 120 welded, punched, or by another suitable joining method on the lever arm 200 or contact section 210 attached. A minimum diameter of the through hole 330 is larger than an outer diameter 124 of the valve stem 120 so that between the through hole 330 and the valve stem 120 a second radial play 336 is present (see 1 ). Here are the dimensions of the through hole 330 and the valve stem 120 chosen so that there is sufficient play to allow freedom of movement of the sealing shell 300 relative to the valve disc 110 or to the valve stem 120 and thus to enable sliding along the spherical surfaces. The sealing shell 300 is basically radially outside the valve stem 120 arranged. With radial play 336 is a play in the radial direction 24 in the neutral state of the valve arrangement 10 (neutral state means: the seal axis 302 and the valve axis 122 coincide) to understand. That is called the radial play 336 is the distance that the sealing shell is 300 starting from the neutral state can be moved in all radial directions.

An outer diameter (see half the outer diameter, i.e. radius 214 ) of the annular contact portion 210 is made larger than a minimum diameter of the through hole 330 . This advantageous configuration can prevent the sealing shell from slipping 300 be prevented. In other words, this serves to secure the sealing shell 300 in the axial direction 22nd between the lever arm 200 or the contact section 210 and the valve body 100 or the valve disc 110 . This can be clearly seen when comparing the 2A and 2 B . which have a neutral state of the valve assembly 10 in the closed state and a fully tilted state of the valve arrangement 10 show in closed position. As already mentioned, the seal axis is correct 302 and the valve axis 122 in the neutral state of the valve assembly 10 match. In a slightly tilted (also fully tilted state as in 2 B) is the seal axis 302 around the angle α from the valve axis 122 inclined. In 2 B it becomes clear that half the outer diameter (radius 214 ) of the annular contact portion 210 should be at least greater than the sum of twice the second radial clearance 336 (approximately double radial play 336 , Deviations may result from tilting) and half the outer diameter 124 of the valve stem 120 to prevent the sealing shell from slipping 300 to prevent. Alternatively, if the contact section 210 For example, it is not designed to be annular, at least part of the outer contour of the contact section should be 210 have the dimension just mentioned to prevent the sealing shell from slipping 300 to prevent.

As already mentioned, the valve plate 110 a second sliding surface 114 on. The second sliding surface 114 extends between a radially outer peripheral edge 112 and a radially inner peripheral edge 113 (please refer 2A) . The radially outer peripheral edge defines 112 a plate diameter 112a . The radially inner circumferential edge 113 defines the outside diameter 124 a valve stem 120 . A first distance 342 in the axial direction 22 ' the sealing shell 300 between the first peripheral edge 332 and an inside edge 314 the sealing lip 310 should be made larger than the sum of the axial play 326 that is between the lever arm 200 , the sealing shell 300 and the valve disc 100 is present, and a second distance 344 in the axial direction 22nd between the radially inner circumferential edge 113 and the radially outer peripheral edge 112 . The inside edge 314 represents the radially inner boundary of the sealing surface 312 on the inside diameter 314a the sealing lip 310 represent.

Like that 3 , 5A and 5B can be seen, includes the valve assembly 10 still a rotation lock 360 . The rotation lock 360 rotation of the sealing cup 300 around the seal axis 302 the sealing shell 300 prevent. At the same time, the rotation lock 360 sliding in the radial direction 24 ' or along the spherical surfaces 322 , 324 to. The rotation lock is shown in the corresponding figures 360 as a head start 360 formed from the valve disc 110 in the axial direction 22nd to the sealing shell 300 rises up and into a corresponding recess 362 in the sealing shell 300 intervenes. Here is the dimension of the projection 360 in the radial direction 24 less than the dimension of the recess 362 in the radial direction 24 ' .

The 4th shows a further embodiment of the valve arrangement 10 , in which the valve assembly 10 furthermore a damping element 350 include. The damping element 350 is between the valve disc 110 and the sealing cup 300 arranged. In the present example, the damping element is 350 designed as a spring, in particular as an octopus spring with several spring arms. In alternative configurations, however, other suitable damping or spring elements can also be used. The damping element can also 350 alternatively or additionally between the lever arm 200 and the sealing cup 300 be arranged.

The invention further comprises a charging device 30th with a turbine 40 and a compressor 50 (please refer 7th ). The turbine 40 includes a turbine housing 400 with a bypass opening 420 (covered by valve arrangement 10 in 7th ) and one in the turbine housing 400 rotatably arranged turbine wheel (not shown). The turbine 40 comprises the valve assembly just described 10 . The turbine housing 400 includes a first volute 412 , a second volute 414 and a volute partition 413 . Out 6th it can be seen that the volute partition 413 the first volute 412 and the second volute 414 separated from each other. That is called the turbine 40 is designed as a multi-flow turbine (multiscroll), in particular as a double-flow turbine (dual volute) or twin-flow turbine (twin scroll). Alternatively, however, a single-flow design is also possible. As already mentioned above is the bypass opening 420 from a valve seat 421 surround. The sealing lip 310 can do this with the valve seat 421 be brought into contact with the bypass opening 420 to close. The valve arrangement 10 further comprises a rotatable spindle 204 with an axis of rotation 202 . The spindle 204 is with the lever arm 200 firmly connected. Thus is the lever arm 200 or also the sealing shell 300 and the valve body 100 over the spindle 204 rotatable around the axis of rotation. The spindle 204 is like in 7th shown in the turbine housing 400 rotatably mounted.

In the present exemplary embodiment a multi-flow turbine with a first volute 412 and a second volute 414 includes the bypass opening 420 a first opening area 422 that is in the first volute 412 opens and a second opening area 424 that is in the second volute 414 flows out. The valve arrangement 10 is arranged in such a way that the axis of rotation 202 orthogonal to a main flow direction of the gases through the volutes 412 , 414 and orthogonal to the volute partition 413 is arranged. The main flow direction is in 7th shown with the dashed arrow. In the 6th the main flow direction emerges from the plane of the drawing. In 6th is to illustrate the principle of the present invention, the course of the force flow of the gas pulses (from the first volute 412 ) represented by the dotted line. It becomes clear that forces caused by gas pulses are mainly caused by the valve disc 110 can be recorded and through the fixed connection with the lever arm 200 essentially vibration-free from the valve assembly 10 can be directed. This is also the case with the valve arrangement in a slightly open position 10 or a thermally deformed valve seat 421 , as in 2 B shown, given. As already mentioned above, clamping forces can be efficiently released from the spindle at the same time 204 or the lever arm 200 over the sealing shell 300 on the valve seat 421 or the turbine housing 400 be directed. The explanations just explained are furthermore advantageous in order to change the valve seat 421 to counteract by deposit formation. Even from a low degree of opening of the valve arrangement 10 can gases through the corresponding inclination of the valve disk 110 simplified in the main flow direction from the bypass opening 420 outflow - this causes the valve body 100 counteract lower impulse forces and ultimately the entire valve assembly 10 less burdened. Furthermore, thermally induced deformation of the valve seat can occur 421 better counteracted. The turbine 40 the charger 30th is with the compressor 30th rotationally coupled. In alternative embodiments, the charging device 30th further comprise an electric motor connected to the compressor 40 is rotationally coupled (not shown).

List of reference symbols

10

Valve arrangement

12

First contact area

14th

Second contact area

α

Angle between seal axis and valve axis

22, 22 '

Axial direction (valve disc / sealing cup)

24, 24 '

Radial direction (valve disc / sealing cup)

26, 26 '

Circumferential direction (valve disc / sealing shell)

30th

Charging device

40

turbine

50

compressor

100

Valve body

110

Valve disc

112

Outer circumferential edge

112a

Plate diameter

113

Inner circumferential edge

114

Second sliding surface

116

Plate surface

120

Valve stem

122

Valve axis

124

Outside diameter valve stem

200

Lever arm

202

Axis of rotation

204

spindle

210

Contact section

212

First sliding surface

214

Outside diameter of contact section

216

opening

300

Sealing shell

302

Seal axis

310

Sealing lip

312

Sealing surface

314

Inner edge of the sealing lip

314a

Inner diameter of the sealing lip

316

Outer edge of the sealing lip

316a

Outside diameter of the sealing lip

318

First radial play

322

Exterior surface

323

Thickness of the sealing shell

324

Inner surface

326

Axial play

330

Through hole

332

First peripheral edge

332a

First hole diameter

334

Second peripheral edge

334a

Second hole diameter

336

Second radial clearance

342

First distance

344

Second distance

350

Damping element

360

Rotation lock?

400

Turbine housing

412

First volute

413

Volute partition

414

Second volute

420

Bypass opening

421

Valve seat

422

First opening area

424

Second opening area

426

Bypass opening diameter

1. 1. Ventilanordnung (10) zum Steuern einer Bypassöffnung (420) in einem Turbinengehäuse (400) umfassend:
   • einen Ventilkörper (100) mit einem Ventilteller (110),
   • einen Hebelarm (200),
   • wobei der Ventilkörper (100) und der Hebelarm (200) aneinander fixiert sind,
   • gekennzeichnet durch
   • eine Dichtungsschale (300) mit einer ringförmigen Dichtlippe (310), wobei die ringförmige Dichtlippe (310) in radialer Richtung (24) außerhalb des Ventiltellers (110) angeordnet ist.
2. 2. Ventilanordnung (10) nach Ausführungsform 1, wobei die Dichtungsschale (300) relativ zum Ventilteller (110) beweglich angeordnet ist.
3. 3. Ventilanordnung (10) nach irgendeiner der Ausführungsformen 1 oder 2, wobei die Dichtungsschale (300) eine Dichtungsachse (302) aufweist, um welche die ringförmige Dichtlippe (310) angeordnet ist, und wobei die Dichtungsschale (300) relativ zum Ventilteller (110) derart beweglich ist, dass die Dichtungsachse (302) relativ zu einer Ventilachse (122) des Ventiltellers (110) um einen Winkel (α) verkippbar ist, und optional, wobei 0° ≤ (α) ≤ 8°, bevorzugt 0° ≤ (α) ≤ 6°, und besonders bevorzugt 0° ≤ (α) ≤ 4° gilt.
4. 4. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei die Dichtungsschale (300) ausgelegt ist, über die ringförmige Dichtlippe (310) mit einem Ventilsitz (421) der Bypassöffnung (420) verschließend in Anlage gebracht zu werden.
5. 5. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei die Dichtungsschale (300) im Wesentlichen kuppelförmig ausgebildet ist und eine Außenfläche (322), die sphärisch ausgebildet ist, eine Innenfläche (324), die sphärisch ausgebildet ist, und eine zentrale Durchgangsbohrung (330) zwischen der Außenfläche (322) und der Innenfläche (324) aufweist.
6. 6. Ventilanordnung (10) nach Ausführungsform 5, wobei sich die Durchgangsbohrung (330) zwischen einer ersten Umfangskante (332) an der Innenfläche (324) und einer zweiten Umfangskante (334) an der Außenfläche (322) erstreckt, und optional, wobei ein erster Bohrungsdurchmesser (332a) der ersten Umfangskante (332) größer, kleiner oder gleich groß ist wie ein zweiter Bohrungsdurchmesser (334a) der zweiten Umfangskante (334).
7. 7. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei ein erster Kontaktbereich (12) zwischen dem Hebelarm (200) und der Dichtungsschale (300) und ein zweiter Kontaktbereich (14) zwischen dem Ventilkörper (100) und der Dichtungsschale (300) ausgebildet ist.
8. 8. Ventilanordnung (10) nach Ausführungsform 7, wenn abhängig von irgendeiner der Ausführungsformen 5 oder 6, wobei der erste Kontaktbereich (12) von der sphärischen Außenfläche (322) und einer ersten Gleitfläche (212), die am Hebelarm (200) ausgebildet ist, gebildet wird und, wobei der zweite Kontaktbereich (14) von der sphärischen Innenfläche (324) und einer zweiten Gleitfläche (114), die am Ventilteller (110) ausgebildet ist, gebildet wird.
9. 9. Ventilanordnung (10) nach Ausführungsform 8, wobei die erste Gleitfläche (212) komplementär zur sphärischen Außenfläche (322) ausgestaltet ist und diese zumindest teilweise umgibt.
10. 10. Ventilanordnung (10) nach irgendeiner der Ausführungsformen 8 oder 9, wobei die zweite Gleitfläche (114) komplementär zur sphärischen Innenfläche (324) ausgestaltet ist und zumindest teilweise von dieser umgeben wird.
11. 11. Ventilanordnung (10) nach irgendeiner der Ausführungsformen 8 bis 10, wobei ein Abstand in axialer Richtung (22) zwischen der zweiten Gleitfläche (114) und der ersten Gleitfläche (212) derart ausgestaltet ist, dass ein axiales Spiel (326) zwischen dem Hebelarm (200), der Dichtungsschale (300) und dem Ventilteller (110) vorhanden ist.
12. 12. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wenn abhängig von Ausführungsform 5, wobei die Dichtungsschale (300) über die Innenfläche (324) auf dem Ventilteller (110) abgleiten kann und/oder, wobei die Dichtungsschale (300) über die Außenfläche (322) auf dem Hebelarm (200) abgleiten kann.
13. 13. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wenn abhängig von Ausführungsform 5, wobei die Außenfläche (322) und die Innenfläche (324) durch sphärische Geometrien mit gleichem Mittelpunkt definiert sind, und optional, so dass die Dichtungsschale (300) in axialer Richtung (22') zwischen der Außenfläche (322) und der Innenfläche (324) eine gleichmäßige Dicke (323) aufweist.
14. 14. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei die ringförmige Dichtlippe (310) eine Dichtungsfläche (312) aufweist, die sich zwischen einem Außendurchmesser (316a) der Dichtlippe (310) und einem Innendurchmesser (314a) der Dichtlippe (310) erstreckt.
15. 15. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei ein Tellerdurchmesser (112a) des Ventiltellers (110) kleiner ist als ein Innendurchmesser (314a) der Dichtlippe (310), so dass zwischen der Dichtlippe (310) und dem Ventilteller (110) ein erstes radiales Spiel (318) vorhanden ist.
16. 16. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei der Ventilkörper (100) weiterhin einen Ventilschaft (120) umfasst, der mittig aus dem Ventilteller (110) in axialer Richtung (22) hervorragt und an einem ringförmigen Kontaktabschnitt (210) des Hebelarms (200) befestigt ist.
17. 17. Ventilanordnung (10) nach Ausführungsform 16, wenn abhängig von Ausführungsform 5, wobei sich der Ventilschaft (120) durch die Durchgangsbohrung (330) erstreckt und wobei ein minimaler Durchmesser der Durchgangsbohrung (330) größer ist als ein Außendurchmesser (124) des Ventilschafts (120), so dass zwischen der Durchgangsbohrung (330) und dem Ventilschaft (120) ein zweites radiales Spiel (336) vorhanden ist.
18. 18. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei die Dichtungsschale (300) zwischen dem Hebelarm (200) und dem Ventilteller (110) angeordnet ist, und optional, wenn abhängig von Ausführungsform 16, wobei die Dichtungsschale (300) zwischen dem ringförmigen Kontaktabschnitt (210) und dem Ventilteller (110) angeordnet ist.
19. 19. Ventilanordnung (10) nach irgendeiner der Ausführungsformen 16 bis 18, wenn abhängig von Ausführungsform 5, wobei ein Außendurchmesser (214) des ringförmigen Kontaktabschnitts (210) größer ist als ein minimaler Durchmesser der Durchgangsbohrung (330).
20. 20. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wenn abhängig von Ausführungsform 14, wobei die ringförmige Dichtungsfläche (312) in jedem Betriebszustand der Ventilanordnung (10) eine Tellerfläche (116) des Ventiltellers (110) in axialer Richtung (22) überlappt, so dass nur die ringförmige Dichtungsfläche (312) der Dichtlippe (310) ausgelegt ist, mit einem Ventilsitz (421) der Bypassöffnung (420) verschließend in Anlage gebracht zu werden.
21. 21. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, wobei der Ventilteller (110) eine zweite Gleitfläche (114) aufweist, die sich zwischen einer radial äußeren Umlaufkante (112) und einer radial inneren Umlaufkante (113) erstreckt.
22. 22. Ventilanordnung (10) nach Ausführungsform 21, wobei die radial äußere Umlaufkante (112) einen Tellerdurchmesser (112a) definiert und wobei die radial innere Umlaufkante (113) einen Außendurchmesser (124) eines Ventilschafts (120) definiert.
23. 23. Ventilanordnung (10) nach irgendeiner der Ausführungsformen 21 oder 22, wenn abhängig von Ausführungsform 6, wobei ein erster Abstand (342) in axialer Richtung (22') zwischen der ersten Umfangskante (332) und einer Innenkante (314) der Dichtlippe (310) größer ausgebildet ist, als die Summe aus einem axialen Spiel (326), das zwischen dem Hebelarm (200), der Dichtungsschale (300) und dem Ventilteller (110) vorhanden ist, und einem zweiten Abstand (344) in axialer Richtung (22) zwischen der radial inneren Umlaufkante (113) und der radial äußeren Umlaufkante (112).
24. 24. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, weiterhin umfassend eine Rotationssicherung (360), die ein Rotieren der Dichtungsschale (300) um die Dichtungsachse (302) der Dichtungsschale (300) verhindert.
25. 25. Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen, weiterhin umfassend ein Dämpfungselement (350), das zwischen dem Hebelarm (200) und der Dichtungsschale (300) oder zwischen dem Ventilteller (110) und der Dichtungsschale (300) angeordnet ist.
26. 26. Turbine (40) für einen Aufladevorrichtung (30) umfassend:
    • ein Turbinengehäuse (400) mit einer Bypassöffnung (420),
    • einem in dem Turbinengehäuse (400) drehbar angeordneten Turbinenrad (42),
    • gekennzeichnet durch eine Ventilanordnung (10) nach irgendeiner der vorangehenden Ausführungsformen.
27. 27. Turbine (40) nach Ausführungsform 26, wobei die Bypassöffnung (420) von einem Ventilsitz (421) umgeben ist, mit dem die Dichtlippe (310) in Anlage bringbar ist, um die Bypassöffnung (420) zu verschließen.
28. 28. Turbine (40) nach irgendeiner der Ausführungsformen 26 oder 27, wobei das Turbinengehäuse (400) eine erste Volute (412), eine zweite Volute (414) und eine Volutentrennwand (413) umfasst, die die erste Volute (412) und die zweite Volute (414) voneinander separiert.
29. 29. Turbine (40) nach Ausführungsform 28, wobei die Bypassöffnung (420) einen ersten Öffnungsbereich (422), der in die erste Volute (412) mündet und einen zweiten Öffnungsbereich (424), der in die zweite Volute (414) mündet, aufweist.
30. 30. Turbine (40) nach irgendeiner der Ausführungsformen 28 oder 29, wobei die Ventilanordnung (10) derart angeordnet ist, dass eine Rotationsachse (202) des Hebelarms (200) orthogonal zu einer Haupströmungsrichtung der Gase durch die Voluten (412, 414) und orthogonal zur Volutentrennwand (413) angeordnet ist.
31. 31. Turbine (40) nach irgendeiner der vorangehenden Ausführungsformen, wobei ein Tellerdurchmesser (112a) des Ventiltellers (110) im Wesentlichen gleich groß wie ein Durchmesser (426) der Bypassöffnung (420) ausgebildet ist.
32. 32. Aufladevorrichtung (30) umfassend:
    • einen Verdichter (50),
    • gekennzeichnet durch eine Turbine (40) nach irgendeiner der vorangehenden Ausführungsformen, die mit dem Verdichter (50) rotatorisch gekoppelt ist und optional, wobei die Aufladevorrichtung weiterhin einen Elektromotor umfasst, der mit dem Verdichter (50) rotatorisch gekoppelt ist.

Although the present invention has been described above and is defined in the appended claims, it should be understood that the invention may alternatively be defined in accordance with the following embodiments:

1. 1. Valve arrangement ( 10 ) to control a bypass opening ( 420 ) in a turbine housing ( 400 ) full:
   • a valve body ( 100 ) with a valve disc ( 110 ),
   • a lever arm ( 200 ),
   • where the valve body ( 100 ) and the lever arm ( 200 ) are fixed to each other,
   • marked by
   • a sealing shell ( 300 ) with an annular sealing lip ( 310 ), whereby the annular sealing lip ( 310 ) in radial direction ( 24 ) outside the valve disc ( 110 ) is arranged.
2. 2. Valve arrangement ( 10 ) according to embodiment 1, wherein the sealing shell ( 300 ) relative to the valve disc ( 110 ) is movably arranged.
3. 3. Valve arrangement ( 10 ) according to any one of embodiments 1 or 2, wherein the sealing shell ( 300 ) a seal axis ( 302 ) around which the annular sealing lip ( 310 ) is arranged, and wherein the sealing shell ( 300 ) relative to the valve disc ( 110 ) is movable in such a way that the seal axis ( 302 ) relative to a valve axis ( 122 ) of the valve disc ( 110 ) is tiltable by an angle (α), and optionally, where 0 ° (α) 8 °, preferably 0 ° (α) 6 °, and particularly preferably 0 ° (α) 4 °.
4. 4. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein the sealing shell ( 300 ) is designed over the annular sealing lip ( 310 ) with a valve seat ( 421 ) the bypass opening ( 420 ) to be brought into the plant with sealing.
5. 5. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein the sealing shell ( 300 ) is essentially dome-shaped and has an outer surface ( 322 ), which is spherical, an inner surface ( 324 ), which is spherical, and a central through hole ( 330 ) between the outer surface ( 322 ) and the inner surface ( 324 ) having.
6. 6. Valve arrangement ( 10 ) according to embodiment 5, wherein the through hole ( 330 ) between a first peripheral edge ( 332 ) on the inner surface ( 324 ) and a second peripheral edge ( 334 ) on the outer surface ( 322 ), and optionally, where a first bore diameter ( 332a ) of the first peripheral edge ( 332 ) is larger, smaller or the same size as a second hole diameter ( 334a ) of the second peripheral edge ( 334 ).
7. 7. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein a first contact area ( 12th ) between the lever arm ( 200 ) and the sealing shell ( 300 ) and a second contact area ( 14th ) between the valve body ( 100 ) and the sealing shell ( 300 ) is trained.
8. 8. Valve arrangement ( 10 ) according to embodiment 7, when dependent on any of embodiments 5 or 6, wherein the first contact area ( 12th ) from the spherical outer surface ( 322 ) and a first sliding surface ( 212 ) on the lever arm ( 200 ) is formed, is formed and, wherein the second contact area ( 14th ) from the spherical inner surface ( 324 ) and a second sliding surface ( 114 ) on the valve disc ( 110 ) is formed, is formed.
9. 9. Valve arrangement ( 10 ) according to embodiment 8, wherein the first sliding surface ( 212 ) complementary to the spherical outer surface ( 322 ) is designed and this at least partially surrounds.
10. 10. Valve arrangement ( 10 ) according to any of the embodiments 8 or 9, wherein the second sliding surface ( 114 ) complementary to the spherical inner surface ( 324 ) is designed and is at least partially surrounded by this.
11. 11. Valve arrangement ( 10 ) according to any of the embodiments 8 to 10, wherein a distance in the axial direction ( 22nd ) between the second sliding surface ( 114 ) and the first sliding surface ( 212 ) is designed in such a way that an axial play ( 326 ) between the lever arm ( 200 ), the sealing shell ( 300 ) and the valve disc ( 110 ) is available.
12. 12. Valve arrangement ( 10 ) according to any of the preceding embodiments, if dependent on embodiment 5, wherein the sealing shell ( 300 ) over the inner surface ( 324 ) on the valve disc ( 110 ) can slide off and / or, whereby the sealing shell ( 300 ) over the outer surface ( 322 ) on the lever arm ( 200 ) can slide.
13. 13. Valve arrangement ( 10 ) according to any of the preceding embodiments when dependent on embodiment 5, wherein the outer surface ( 322 ) and the inner surface ( 324 ) are defined by spherical geometries with the same center point, and optionally, so that the sealing shell ( 300 ) in the axial direction ( 22 ' ) between the outer surface ( 322 ) and the inner surface ( 324 ) a uniform thickness ( 323 ) having.
14. 14. Valve arrangement ( 10 ) according to any of the preceding embodiments, wherein the annular sealing lip ( 310 ) a sealing surface ( 312 ), which is between an outer diameter ( 316a ) the sealing lip ( 310 ) and an inner diameter ( 314a ) the sealing lip ( 310 ) extends.
15. 15. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein a plate diameter ( 112a ) of the valve disc ( 110 ) is smaller than an inner diameter ( 314a ) the sealing lip ( 310 ) so that between the sealing lip ( 310 ) and the valve disc ( 110 ) a first radial clearance ( 318 ) is available.
16. 16. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein the valve body ( 100 ) furthermore a valve stem ( 120 ), which comes from the center of the valve disc ( 110 ) in the axial direction ( 22nd ) protrudes and at an annular contact section ( 210 ) of the lever arm ( 200 ) is attached.
17. 17. Valve arrangement ( 10 ) according to embodiment 16, if dependent on embodiment 5, wherein the valve stem ( 120 ) through the through hole ( 330 ) extends and where a minimum diameter of the through hole ( 330 ) is larger than an outer diameter ( 124 ) of the valve stem ( 120 ) so that between the through hole ( 330 ) and the valve stem ( 120 ) a second radial clearance ( 336 ) is available.
18. 18. Valve arrangement ( 10 ) according to any one of the preceding embodiments, wherein the sealing shell ( 300 ) between the lever arm ( 200 ) and the valve disc ( 110 ) is arranged, and optionally, if dependent on embodiment 16, wherein the sealing shell ( 300 ) between the annular contact section ( 210 ) and the valve disc ( 110 ) is arranged.
19. 19. Valve arrangement ( 10 ) according to any of the embodiments 16 to 18, when dependent on embodiment 5, wherein an outer diameter ( 214 ) of the annular contact section ( 210 ) is larger than a minimum diameter of the through hole ( 330 ).
20. 20. Valve arrangement ( 10 ) according to any of the preceding embodiments, if dependent on the embodiment 14th , where the annular sealing surface ( 312 ) in every operating state of the valve arrangement ( 10 ) a plate surface ( 116 ) of the valve disc ( 110 ) in the axial direction ( 22nd ) overlaps so that only the annular sealing surface ( 312 ) the sealing lip ( 310 ) is designed with a valve seat ( 421 ) the bypass opening ( 420 ) to be brought into the plant with sealing.
21. 21. Valve arrangement ( 10 ) according to any of the preceding embodiments, wherein the valve disk ( 110 ) a second sliding surface ( 114 ), which extends between a radially outer peripheral edge ( 112 ) and a radially inner peripheral edge ( 113 ) extends.
22. 22. Valve arrangement ( 10 ) according to embodiment 21, wherein the radially outer peripheral edge ( 112 ) a plate diameter ( 112a ) and where the radially inner circumferential edge ( 113 ) an outside diameter ( 124 ) of a valve stem ( 120 ) Are defined.
23. 23. Valve arrangement ( 10 ) according to any of the embodiments 21 or 22, when dependent on embodiment 6, wherein a first distance ( 342 ) in the axial direction ( 22 ' ) between the first peripheral edge ( 332 ) and an inner edge ( 314 ) the sealing lip ( 310 ) is larger than the sum of an axial play ( 326 ) between the lever arm ( 200 ), the sealing shell ( 300 ) and the valve disc ( 110 ) is present, and a second distance ( 344 ) in the axial direction ( 22nd ) between the radially inner circumferential edge ( 113 ) and the radially outer peripheral edge ( 112 ).
24. 24. Valve arrangement ( 10 ) according to any one of the preceding embodiments, further comprising a rotation lock ( 360 ) that cause the sealing shell to rotate ( 300 ) around the seal axis ( 302 ) the sealing shell ( 300 ) prevented.
25. 25. Valve arrangement ( 10 ) according to any of the preceding embodiments, further comprising a damping element ( 350 ) between the lever arm ( 200 ) and the sealing shell ( 300 ) or between the valve disc ( 110 ) and the sealing shell ( 300 ) is arranged.
26. 26. Turbine ( 40 ) for a charger ( 30th ) full:
    • a turbine housing ( 400 ) with a bypass opening ( 420 ),
    • one in the turbine housing ( 400 ) rotatably arranged turbine wheel ( 42 ),
    • characterized by a valve arrangement ( 10 ) according to any of the preceding embodiments.
27. 27. Turbine ( 40 ) according to embodiment 26th , where the bypass opening ( 420 ) from a valve seat ( 421 ) is surrounded with which the sealing lip ( 310 ) can be brought into contact with the bypass opening ( 420 ) to close.
28. 28. Turbine ( 40 ) according to any of the embodiments 26th or 27 , where the turbine housing ( 400 ) a first volute ( 412 ), a second volute ( 414 ) and a volute partition ( 413 ) which includes the first volute ( 412 ) and the second volute ( 414 ) separated from each other.
29. 29. Turbine ( 40 ) according to embodiment 28, wherein the bypass opening ( 420 ) a first opening area ( 422 ), which is in the first volute ( 412 ) opens and a second opening area ( 424 ), which is in the second volute ( 414 ) opens.
30. 30. Turbine ( 40 ) according to any of the embodiments 28 or 29, wherein the valve arrangement ( 10 ) is arranged in such a way that an axis of rotation ( 202 ) of the lever arm ( 200 ) orthogonal to a main flow direction of the gases through the volutes ( 412 , 414 ) and orthogonal to the volute partition ( 413 ) is arranged.
31. 31. Turbine ( 40 ) according to any one of the preceding embodiments, wherein a plate diameter ( 112a ) of the valve disc ( 110 ) essentially the same size as a diameter ( 426 ) the bypass opening ( 420 ) is trained.
32. 32. Charger ( 30th ) full:
    • a compressor ( 50 ),
    • characterized by a turbine ( 40 ) according to any of the preceding embodiments which are associated with the compressor ( 50 ) is rotationally coupled and optionally, wherein the charging device further comprises an electric motor which is connected to the compressor ( 50 ) is rotationally coupled.

Claims (15)

Valve arrangement (10) for controlling a bypass opening (420) in a turbine housing (400) comprising: a valve body (100) with a valve plate (110), a lever arm (200), the valve body (100) and the lever arm (200) on one another are fixed, characterized by a sealing shell (300) with an annular sealing lip (310), wherein the annular sealing lip (310) is arranged in the radial direction (24) outside the valve disk (110). Valve arrangement (10) according to Claim 1 , wherein the sealing shell (300) is arranged to be movable relative to the valve disk (110). Valve assembly (10) according to any one of the Claims 1 or 2 , wherein the sealing cup (300) has a sealing axis (302) around which the annular sealing lip (310) is arranged, and wherein the sealing shell (300) is movable relative to the valve disk (110) in such a way that the sealing axis (302) is movable relative to a valve axis (122) of the valve disk (110) is tiltable by an angle (a), and optionally, where 0 ° (a) 8 °, preferably 0 ° (α) 6 °, and particularly preferably 0 ° (α) 4 ° . The valve arrangement (10) according to any one of the preceding claims, wherein the sealing shell (300) is designed to be brought into contact with a valve seat (421) of the bypass opening (420) in a closing manner via the annular sealing lip (310). The valve assembly (10) according to any one of the preceding claims, wherein the sealing shell (300) is substantially dome-shaped and has an outer surface (322) which is spherical, an inner surface (324) which is spherical, and a central through hole (330 ) between the outer surface (322) and the inner surface (324). The valve assembly (10) according to any one of the preceding claims, wherein a first contact area (12) is formed between the lever arm (200) and the sealing shell (300) and a second contact area (14) is formed between the valve body (100) and the sealing shell (300) , and optional if dependent on Claim 5 wherein the first contact area (12) is formed by the spherical outer surface (322) and a first sliding surface (212) which is formed on the lever arm (200), and wherein the second contact area (14) is formed by the spherical inner surface (324) and a second sliding surface (114) formed on the valve disk (110) is formed. Valve arrangement (10) according to Claim 6 , wherein the first sliding surface (212) is designed complementary to the spherical outer surface (322) and at least partially surrounds it, and optionally, the second sliding surface (114) is designed complementary to the spherical inner surface (324) and is at least partially surrounded by it. Valve assembly (10) according to any one of the Claims 6 or 7th , wherein a distance in the axial direction (22) between the second sliding surface (114) and the first sliding surface (212) is designed such that an axial play (326) between the lever arm (200), the sealing shell (300) and the valve disk (110) is present. A valve assembly (10) according to any one of the preceding claims when dependent on Claim 5 , wherein the outer surface (322) and the inner surface (324) are defined by spherical geometries with the same center, and optionally so that the sealing shell (300) in the axial direction (22 ') between the outer surface (322) and the inner surface (324 ) has a uniform thickness (323). Valve arrangement (10) according to any one of the preceding claims, wherein a plate diameter (112a) of the valve plate (110) is smaller than an inner diameter (314a) of the sealing lip (310), so that between the sealing lip (310) and the valve plate (110) first radial play (318) is present. Valve arrangement (10) according to any one of the preceding claims, wherein the valve body (100) further comprises a valve stem (120) which protrudes centrally from the valve disk (110) in the axial direction (22) and at an annular contact portion (210) of the lever arm ( 200) is attached. The valve assembly (10) according to any one of the preceding claims, wherein the sealing cup (300) is arranged between the lever arm (200) and the valve disc (110), and optionally, if dependent on Claim 11 , wherein the sealing shell (300) is arranged between the annular contact portion (210) and the valve disk (110). The valve assembly (10) according to any one of the preceding claims, wherein the valve disc (110) has a second sliding surface (114) which extends between a radially outer circumferential edge (112) and a radially inner circumferential edge (113), and optionally, the radially outer circumferential edge (112) defines a plate diameter (112a) and wherein the radially inner circumferential edge (113) defines an outer diameter (124) of a valve stem (120). Turbine (40) for a supercharging device (30) comprising: a turbine housing (400) with a bypass opening (420), a turbine wheel (42) rotatably arranged in the turbine housing (400), characterized by a valve arrangement (10) according to any one of the preceding claims , and optionally, wherein the turbine housing (400) comprises a first volute (412), a second volute (414) and a volute partition (413) which separates the first volute (412) and the second volute (414) from one another. A supercharger (30) comprising: a compressor (50) characterized by a turbine (40) according to any one of the preceding claims rotatably coupled to the compressor (50) and optionally, the supercharger further comprising one Comprises an electric motor which is rotationally coupled to the compressor (50).

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