CN216044015U

CN216044015U - Valve flap assembly for a charging device, turbine and charging device

Info

Publication number: CN216044015U
Application number: CN202120561719.8U
Authority: CN
Inventors: G·肖尔茨; A·林德; F·拉普
Original assignee: BorgWarner Inc
Current assignee: BorgWarner Inc
Priority date: 2021-03-04
Filing date: 2021-03-18
Publication date: 2022-03-15
Anticipated expiration: 2031-03-18
Also published as: DE202021101109U1

Abstract

The utility model relates to a flap assembly (10) for a charging device (1), a turbine and a charging device, the flap assembly comprising: a valve flap (100) having a valve disc (110) and a pin (120); an actuating arm (200), wherein the actuating arm is coupled with the valve flap (to transmit a closing force; a washer (400) arranged at an end (140) of the pin (120) remote from the valve disc (110), wherein a spring element is arranged around the pin (120) between the washer and the actuating arm, and wherein the spring element has in a radial direction (R) a first ring segment (510) and a second ring segment (520) extending from the first ring segment (510), characterized in that the first ring segment is designed to be planar and the second ring segment is designed to be conical and/or arcuate.

Description

Valve flap assembly for a charging device, turbine and charging device

Technical Field

The utility model relates to a flap assembly for a charging device, a turbine for a charging device having such a flap assembly, and a charging device having such a turbine.

Background

More and more newer generation vehicles are equipped with supercharging devices in order to achieve demand targets and legal requirements. In developing a supercharging device, individual components and the system as a whole are optimized with regard to their reliability and efficiency.

Known supercharging devices usually have at least one turbine which is driven by the exhaust gas of the combustion engine. The turbine is connected to a compressor via a common shaft, the compressor compressing fresh air taken in. Thereby, the amount of air or oxygen supplied to the engine for combustion to effect the reaction is increased. This in turn leads to a power boost of the combustion engine.

Modern charging devices are equipped with a power regulating device, by means of which the power generated by the charging device can be regulated or varied. Known power regulating devices are, for example, variable geometry turbines or wastegate flaps. A variable geometry turbine is an adjustable guide for varying the incoming airflow to the turbine wheel of the turbine. By varying the inlet air flow, in particular the flow rate of the exhaust gas flow fed to the turbine wheel can be varied, which produces a corresponding power variation of the supercharging device. In contrast to this, the wastegate flap essentially corresponds to an adjustable bypass, by means of which the exhaust gas can bypass the turbine. By varying the flow cross section of the bypass or wastegate duct, the pressure difference between the inlet and the outlet of the turbine wheel can be varied, which correspondingly influences the power of the turbine and thus of the charging device. A flap assembly may be used for opening and closing the wastegate passage. In addition to the flap assembly, an actuator and a spindle can be used, which is connected to the flap assembly, in particular to an actuating arm of the flap assembly. The main shaft is supported in a turbine housing, wherein the actuator applies a setting movement to the flap assembly. The flap arrangement can be pivoted between a position in which it closes the wastegate duct and a position in which it releases the wastegate duct.

In order to ensure the function of the wastegate system, a balance needs to be found between the three main requirements. These three requirements are combined by: as little exhaust gas leakage as possible occurs through a closed wastegate system, little wear of the components of the wastegate system (mainly in the contact areas of the individual components), and as little noise development as possible. In order to achieve as little exhaust gas leakage as possible through the closed wastegate system, a high closing force provided by the torque of the actuator is advantageous. Furthermore, leakage may be reduced when the angular change of the valve seat (e.g. due to thermal deformation) may be compensated for by the flap assembly. However, in order to be able to produce the angle compensation, the flap arrangement requires a plurality of parts which are arranged movably relative to one another, which in turn can lead to increased noise development and increased wear. To this end, spring elements may be provided which generate a pretensioning force for these components, which, however, may in turn lead to increased manufacturing, installation and costs.

SUMMERY OF THE UTILITY MODEL

The object of the utility model is to provide an improved flap arrangement for a supercharging device, by means of which the noise development and wear can be reduced in a cost-effective manner.

The utility model relates to a valve clack assembly. In addition, the utility model relates to a turbine having such a flap assembly and to a charging device having such a turbine.

The utility model relates to a valve flap assembly for a supercharging device, comprising: a valve flap having a valve disc and a pin; an actuation arm, wherein the actuation arm is coupled with the valve flap to transmit a closing force; a washer disposed at an end of the pin distal from the valve disc; wherein a spring element is arranged around the pin between the washer and the actuating arm, and wherein the spring element has a first ring segment and a second ring segment extending from the first ring segment in a radial direction; the first ring segment is designed to be planar and the second ring segment is designed to be conical and/or arcuate.

The present disclosure relates to a valve flap assembly for a supercharging device. The valve flap assembly includes: a valve flap having a valve disc and a pin; an actuation arm, wherein the actuation arm is coupled with the valve flap for transferring a closing force; and a washer disposed at an end of the pin distal from the valve disc. A spring element is disposed around the pin between the washer and the actuator arm. The spring element has a first ring segment and a second ring segment extending from the first ring segment in the radial direction R. The first ring segment is designed to be planar and the second ring segment is designed to be conical and/or curved. Pretensioning of these components can be produced by the spring element, so that noise, for example, rattling, knocking or rubbing against one another can be reduced. The wear behavior of the flap arrangement can thereby be significantly improved. The design of the spring element according to the utility model makes it possible to improve the stiffness characteristic and the stiffness characteristic of the spring element.

In one embodiment, the pin has a longitudinal axis Z, wherein the radial direction extends orthogonally to the longitudinal axis.

In one embodiment, the first ring segment may be in face contact with the washer or the actuator arm. In one embodiment, the second ring segment can be in line or surface contact with the washer or the actuating arm.

In one embodiment, the spring element can have a spring force of 20N to 100N, preferably 30N to 80N.

In one embodiment, the second ring segment can extend conically from the first ring segment at an angle β, wherein the angle β can be between 5 ° and 20 °, preferably between 7 ° and 17 °, particularly preferably between 9 ° and 15 °. In one embodiment, the second ring segment can extend conically from the first ring segment at an angle β. Alternatively, the second ring segment may be disposed at an angle β relative to and arcuately extend from the first ring segment.

In one embodiment, the spring element can have a first plane P1, which extends through the first ring segment and orthogonally to the longitudinal axis Z. The spring element can have a second plane P2 which faces the valve disk in the direction of the longitudinal axis Z and is arranged spaced apart from and parallel to the first plane, wherein the second ring segment can extend up to the second plane P2.

In one embodiment, the spring element may have an inner diameter D1 that is greater than the outer diameter D3 of the pin. The spring element may have an outer diameter d 3. The first ring segment may extend from the inner diameter d1 up to the intermediate diameter d 2. The second ring segment may extend from the intermediate diameter d2 up to the outer diameter d 3.

In one embodiment, the second ring segment can have a first partial ring segment which is designed to be conical and a second partial ring segment which is designed to be arcuate. In one embodiment, the spring element can have the first ring segment, then the first partial ring segment, then the second partial ring segment in the radial direction R. The second sub-ring segment may have a radius r1 of 0.3mm to 7.0mm, preferably 0.5mm to 5.0 mm. In one embodiment, the first partial ring segment can extend from the first ring segment at the angle β; and the second sub-ring segment may extend from the first sub-ring segment at the radius r 1.

In one embodiment, the second partial ring segment can be rounded off from the second plane P2 toward the first plane P1.

In one embodiment, the second ring segment may have a plurality of partial ring segments which extend from the first ring segment in the circumferential direction U relative to one another and are spaced apart from one another in the circumferential direction U. The plurality of partial ring segments can be designed in particular in the form of an arc.

In one embodiment, the spring element can have a third plane P3 which is oriented in the direction of the longitudinal axis Z toward the washer and is arranged at a distance from and parallel to the first plane P1.

In one embodiment, the partial ring segments of the plurality of partial ring segments can alternately extend from the first ring segment toward the second plane P2 or toward the third plane P3. In one embodiment, the plurality of partial ring segments can each be formed convexly with respect to a plane P1 extending through the first ring segment.

In one embodiment, the actuating arm can have a cylindrical recess on the side facing the washer, which recess extends into the actuating arm in the direction of the longitudinal axis. The cylindrical recess may have a diameter D5, which may be larger than the diameter D4 of the washer and/or may be larger than the outer diameter D3 of the spring element. In one embodiment, the washer can extend at least partially into the cylindrical recess.

In one embodiment, the recess has a recess bottom. The recess may in particular have a depth T1 measured parallel to the longitudinal axis Z between the recess bottom and the side face. The recess bottom may extend parallel to the side. In one embodiment, the recess can have a side wall which extends parallel to the longitudinal axis Z from the recess base towards the side face.

In a refinement, the actuating arm can have a through-passage at the first end, through which the pin can extend when the valve flap is coupled with the actuating arm.

In one embodiment, the circumferential first shoulder can extend from the bottom of the recess in the direction of the longitudinal axis Z toward the side. The first shoulder can be arranged in particular adjacent to the passage in the radial direction R and can have a first bearing surface which extends parallel to the recess base.

In one embodiment, a circumferential second shoulder can extend from the bottom of the recess in the direction of the longitudinal axis Z to the side, which second shoulder can be designed to be conical. The second shoulder can be arranged adjacent to the side wall in the radial direction R and extend conically towards the longitudinal axis Z. The second shoulder may have a second bearing surface that extends at an angle γ with respect to the bottom of the recess. In one embodiment, angle γ substantially corresponds to angle β.

In one embodiment, the second ring segment can rest at least partially on the second circumferential shoulder, in particular wherein the second ring segment can be in surface contact with the second circumferential shoulder.

The actuator arm may comprise a spindle for supporting the actuator arm, wherein the spindle may have an axis of rotation X.

In one embodiment, the spring element can be made of a metal sheet, which can have a sheet metal thickness of 0.15mm to 0.30mm, preferably 0.20mm to 0.25 mm.

The valve flap may include a first coupling section and the actuator arm may include a second coupling section. The first coupling section and the second coupling section are arranged and designed such that a contact area for transmitting a closing force can be formed between the first coupling section and the second coupling section.

In one embodiment, the first coupling section and/or the second coupling section can be designed in an annular manner. The first coupling section or the second coupling section can have a conical contact surface in the direction of the pin axis Z, which decreases radially outward from the pin. The respective other first or second coupling section may have a flat contact surface, wherein the contact area may be formed between the tapered contact surface and the flat contact surface.

In one embodiment, the conical surface can have an inclination angle α, wherein the inclination angle α can be between 1 ° and 6 °, preferably between 2 ° and 5 °, preferably about 3.5 °.

In one embodiment, the tapered surface may include a first tapered surface and a second tapered surface, wherein the second tapered surface may be externally contiguous with the first tapered surface. The first tapered surface may have a first inclination angle α 1 and the second tapered surface may have a second inclination angle α 2. In one embodiment, the first inclination angle α 1 can be between 1 ° and 5 °, preferably between 2 ° and 4 °, particularly preferably about 2.5 °. In one embodiment, the second angle of inclination α₂May be larger than the first inclination angle alpha₁. The second inclination angle can in particular be 0.5 ° to 1.5 °, preferably about 1 °, greater than the first inclination angle.

Advantageously, the pin has a longitudinal axis; and the radial direction extends orthogonal to the longitudinal axis; and the first ring segment is in face contact with the washer or the actuator arm.

Advantageously, the second ring segment is in line or surface contact with the washer or the actuating arm.

Advantageously, the second ring segment extends at an angle from the first ring segment, wherein the angle is between 5 ° and 20 °.

Advantageously, the second ring segment extends conically from the first ring segment at the angle; or the second ring segment is disposed at the angle relative to the first ring segment and extends arcuately from the first ring segment.

Advantageously, the spring element has a first plane extending through the first ring segment and extending orthogonally to the longitudinal axis; and the spring element has a second plane which is arranged in the direction of the longitudinal axis towards the valve disk and spaced apart from and parallel to the first plane, wherein the second ring segment extends up to the second plane.

Advantageously, the spring element has an inner diameter, the inner diameter of the spring element being greater than the outer diameter of the pin; and the spring element has an outer diameter, wherein the first ring segment extends from the inner diameter of the spring element up to an intermediate diameter of the spring element; and the second ring segment extends from the intermediate diameter of the spring element up to the outer diameter of the spring element.

Advantageously, the second ring segment has a first partial ring segment which is designed to be conical and has a second partial ring segment which is designed to be arcuate; and the spring element has the first ring segment, followed by the first sub-ring, followed by the second sub-ring segment in the radial direction.

Advantageously, the second sub-ring segment has a radius of 0.3mm to 7.0 mm; and the first sub-ring segment extends from the first ring segment at the angle; and the second sub-ring segment extends from the first sub-ring segment at the radius.

Advantageously, the second ring segment has a plurality of sub-ring segments which extend from the first ring segment in the circumferential direction relative to one another and are spaced apart from one another in the circumferential direction; and the spring element has a third plane which is arranged in the direction of the longitudinal axis towards the washer and spaced apart from and parallel to the first plane, wherein sub-ring segments of the plurality of sub-ring segments extend alternately from the first ring segment towards the second plane or towards the third plane.

Advantageously, the plurality of partial ring segments are each formed convexly with respect to a first plane extending through the first ring segment.

Advantageously, the actuating arm has a cylindrical recess on the side facing the washer, which recess extends into the actuating arm in the direction of the longitudinal axis.

Advantageously, the recess has a recess bottom, wherein the recess bottom extends parallel to the side face, and wherein the recess has a side wall extending parallel to the longitudinal axis from the recess bottom towards the side face.

Advantageously, the actuation arm has a through-going portion at a first end through which the pin extends when the flap is coupled with the actuation arm; and a circumferential first shoulder extends from the recess base in the direction of the longitudinal axis toward the side face, wherein the first shoulder is arranged adjacent to the passage in the radial direction and has a first bearing surface which extends parallel to the recess base.

Advantageously, a circumferential second shoulder extends from the recess base in the direction of the longitudinal axis toward the side face, the second shoulder being designed to be conical; and the second shoulder is arranged adjacent to the side wall in the radial direction and extends conically towards the longitudinal axis, wherein the second shoulder has a second bearing surface which extends at an angle to the recess bottom.

Advantageously, the second ring segment rests at least partially on the encircling second shoulder.

Advantageously, the second sub-ring segment has a radius of 0.5mm to 5.0 mm.

Advantageously, the plurality of partial ring segments are designed in the form of arcs.

Advantageously, the recess has a depth measured parallel to the longitudinal axis between the recess bottom and the side face.

Advantageously, the second ring segment is in surface contact with the encircling second shoulder.

The present disclosure also relates to a turbine for a supercharging device. The turbine comprises a turbine housing and a flap assembly according to any of the above-described embodiments, wherein the flap assembly is supported in the turbine housing by the main shaft. The turbine further comprises a valve seat in the turbine housing, wherein the valve flap assembly is pivotable between a first position in which the valve disc rests on the valve seat to close off the wastegate passage and at least one second position; in the second position, the valve disc is lifted away from the valve seat to release at least a portion of the wastegate passage.

The disclosure also relates to a charging device comprising a compressor and a turbine according to the above-described embodiment.

Drawings

FIG. 1 shows an isometric view of a supercharging device having a turbine and a flap assembly;

FIGS. 2A, 2B show cross-sectional views of a turbine having a valve flap assembly of the present invention in two different positions;

FIG. 3 shows a cross-sectional view of the valve flap assembly in a coupled state;

FIGS. 4A, 4B show cross-sectional views of a valve flap having a tapered contact surface;

5A-5C show a cross-sectional view of a valve flap assembly and a view of a spring element according to a first design;

6A-6C show a cross-sectional view of a valve flap assembly and a view of a spring element according to a second design;

FIGS. 7A, 7B show a cross-sectional view of a valve flap assembly and a view of a spring element according to a third design;

figures 8A-8C show a cross-sectional view of a valve flap assembly and a view of a spring element according to a fourth design.

Detailed Description

In the context of the present application, the longitudinal axis Z refers to an axis extending in the longitudinal direction of the pin 120, as shown for example in fig. 3. The radial direction R and the circumferential direction U are each relative to the pin axis Z. The contact plane E1 refers to the plane in which the actuator arm 200 and the valve flap 100 make contact, wherein the closing force is transmitted through this contact plane. The contact plane E1 extends in a radial direction, i.e. orthogonally to the longitudinal axis Z. It is noted that in an embodiment, the contact plane E1 may also be angled with respect to the longitudinal axis Z. The rotation axis X of the spindle 240 refers to an axis extending in the longitudinal direction of the spindle 240, as shown in fig. 3, for example. The rotation axis X extends parallel to the contact plane E1 and may lie in the contact plane E1. However, depending on the design of the actuator arm 200, the axis of rotation X may also be located above or below the contact plane E1. The spring element 500 may have a first plane P1, a second plane P2, and/or a third plane P3. The first plane always extends through the first ring segment. The second ring segment may extend up to a second plane P2 and/or a third plane P3. The second plane P2 and the third plane P3 are each located on a different side of the plane P1. In the coupled state, the plane P1 extends parallel to the longitudinal axis Z and/or parallel to the contact plane E1. The planes P2 and/or P3 respectively extend parallel to the plane P1.

When the actuator arm 200 is not connected to the valve flap 100, there is a decoupled state, such as shown in fig. 4A and 4B. When the actuator arm 200 is coupled with the valve flap 100, there is a coupled state, such as shown in fig. 3. The first position of the flapper assembly 10 relates to a state in which the valve face 150 is seated on the valve seat 40 and closes off the wastegate passage 60. The at least one second position of the flap assembly 10 relates to a state in which the valve face 150 is at least partially lifted away from the valve seat 40, so that the wastegate passage 60 is at least partially opened (see fig. 2A and 2B).

Fig. 1 shows a charging device 1 according to the utility model, comprising a turbine 20 according to the utility model, a compressor 50, an actuator 70 and a flap assembly 10 according to the utility model. The turbine 20 includes a turbine housing 30 in which a turbine wheel 21 is disposed. The compressor 50 comprises a compressor housing 52 in which a compressor wheel 51 is arranged. The compressor wheel 51 is connected to the turbine wheel 21 via a shaft 80, wherein the shaft 80 has a longitudinal axis X2 and is arranged in a bearing housing 90 which is coupled on the compressor side to the compressor housing 52 and on the turbine side to the turbine housing 30. A flap assembly 10 is provided to enable closing and opening of a wastegate WG of the turbine 20 when required. The wastegate WG has a wastegate passage 60, which may have one or more volutes 60. The flap assembly 10 may be coupled to the actuator 70 via a lever and/or an adjustment lever.

Fig. 2A and 2B show cross-sectional views of an inventive turbine 20 having an inventive flap assembly 10 in two different positions. The flap assembly 10 is supported in the turbine housing 30 by a main shaft 240. The turbine 20 further comprises a valve seat 40 in the turbine housing 30, wherein the flap assembly 10 is pivotable between a first position, in which the valve disc 110 rests on the valve seat 40 (see fig. 2A) to close off the wastegate passage 60 (or one or more volutes 60 of the wastegate passage), and at least one second position; in this second position, the valve disc 110 is lifted away from the valve seat 40 (see FIG. 2B) to release at least a portion of the wastegate passage 60. In the first position, the valve face 150 of the valve disc 110 is pressed against the valve seat 40.

Fig. 3 shows the flap arrangement 10 according to the utility model for a charging device 1 in a coupled state in a sectional view. The valve flap assembly 10 includes: a valve flap 100 having a valve disc 110 and a pin 120; and an actuator arm 200. The actuation arm 200 is coupled with the valve flap 100 to transmit the closing force, in particular via the contact area 300. The contact area 300 is located between the actuator arm 200 and the valve flap 100. The contact region 300 is in particular the region between the actuator arm 200 and the valve flap 100 via which a closing force can be transmitted from the actuator arm 200 to the valve flap 100. A closing force is required to press the valve disc 100 against the valve seat 40 in the turbine particle 30 so that the wastegate passage 60 of the wastegate WG is closed when required. The closing force can be transmitted to the flap assembly 10 by the actuator 70, in particular, thereby completing a rotational movement of the flap assembly 10 about the rotational axis. Valve flap assembly 10 further includes a washer 400 disposed at end 140 of pin 120 distal from valve disc 110. The valve flap assembly 10 includes a spring element 500 disposed about the pin 120 between the washer 400 and the actuation arm 200. In the following, different designs of the spring element 500 and their arrangement between the actuator arm 200, the pin 120 and the washer 400 will be explained in detail. As shown, for example, in fig. 3, the actuator arm 200 includes a spindle 240 for supporting the actuator arm 200, wherein the spindle 240 has an axis of rotation X. The rotation axis X extends in the longitudinal direction of the spindle 240.

A cross-sectional view of the valve flap assembly 10 and the valve flap 100 is shown in fig. 3, 4A and 4B. The pin 120 has a longitudinal axis Z which extends in the longitudinal direction of the pin 120. The radial direction R extends here orthogonally to the longitudinal axis Z. The pin 120 extends perpendicularly from the valve disc 110, with the pin axis Z perpendicular to the plane spanned by the valve disc 110. Valve disc 110 has a valve face 150 that is designed to seat on valve seat 40. The pin axis Z stands in particular orthogonally on the valve face 150. Pin 120 is disposed in the middle, i.e., at the geometric midpoint of valve disc 110. Alternatively, pin 120 may be disposed at any location on valve disc 110 or at the center of gravity of valve disc 110. Pin 120 is integrally formed with valve disc 110. Alternatively, valve disk 110 and pin 120 may be separate components that are connected to one another in a force-fit, form-fit, or material-fit manner. For example, pin 120 can be screwed onto valve disk 110. Alternatively, pin 120 may be provided with an external thread and valve disc 110 with an internal thread, wherein pin 120 may be screwed onto valve disc 110. Alternatively, the pin 120 may be secured to the valve disc 110 by a snap-fit connection or a rotational connection. In an embodiment, the pins 120 may be bonded, welded, or brazed to the valve disc 110. When pin 120 and valve disc 110 are separate components, pin 120 and valve disc 110 may have different materials or different material properties. For example, the material of the pin 120 and/or the valve disc 110 may be wear resistant. As shown, for example, in fig. 4A, pin 120 has a diameter D3. Pin 120 may be formed slotted (or stepped), particularly with a diameter D6 at the end 140 of pin 120 distal from valve disc 110. The slotted section of the pin extends from the first end at least partially toward the valve disc 110 at a diameter D6. Between diameter D3 and diameter D6, a shoulder is formed that may act as a stop for washer 400. Alternatively, pin 120 may have a diameter D3 from valve disc 110 to end 140. In another embodiment, pin 120 may be tapered from valve disc 110 toward end 140, for example, where pin 120 narrows from diameter D3 to diameter D6. In still other embodiments, the pin 120 may be formed tapered and slotted (or stepped).

For example, as shown in fig. 3, the actuator arm 200 has a through-penetration 230 at the first end 220 through which the pin 120 extends when the valve flap 100 is coupled with the actuator arm 200. A washer 400 is arranged at end 140 of pin 120 remote from valve disc 110. If the valve flap 100 is coupled to the actuator arm 200, the pin 120 extends through the through-opening 230 and extends in the direction of the longitudinal axis Z via a side 260 of the actuator arm 200 facing away from the valve disk 110. The distal end 140 may extend, in particular, via the side of the actuator arm 200 facing away from the valve disk 110. In the coupled state, the washer 400 is arranged at the remote end 140 of the pin 120, thereby preventing the decoupling of the actuating arm 200 from the valve disc 100, in particular thereby positively retaining the actuating arm 200 between the washer 400 and the valve flap 100. The washer 400 is connected to the pin 120, in particular at the remote end 140, in a form-fitting, material-fitting and/or force-fitting manner. For the arrangement of the washer 400, a tongue-and-groove or a step (see above) and/or a groove extending in the circumferential direction around the pin 120 about the longitudinal axis Z is provided at the remote end 140 of the pin 120. In one embodiment, the washer 400 may be a retaining ring that is insertable into a recess. In the coupled state, a gap is provided in the radial direction of the pin 120, starting from the longitudinal axis Z, between the actuating arm 200 and the pin 120. In other words, the pin 120 extending through the through-going portion 230 may be arranged to provide a spacing in the axial direction R relative to the pin axis Z between an outer circumferential mantle surface of the pin 120 and an inner circumferential surface of the through-going portion 230. In addition, an axial gap is provided between the washer 400 and the actuator arm 200 and/or between the actuator arm 200 and the valve flap 100 in the direction of the pin axis Z of the pin 120. When the valve flap 100 is not seated on the valve seat 40, i.e. the actuation arm 200 does not transmit a closing force to the valve flap 100, an axial gap may occur between the first coupling section 130 and the second coupling section 210. This axial and radial clearance is provided such that the valve flap 100 can be moved relative to the actuator arm 200, whereby a tilting of the valve flap 100 relative to the actuator arm 200 can be achieved. If required, an angular compensation between the flap 100 and the valve seat 40 on closing can thereby be achieved, which can lead to an improved leakage behavior. This may be necessary, for example, in the case of thermal deformation of the turbine housing. When the valve flap 100 is lifted from the valve seat 40, the valve flap 100 can easily be displaced in the direction of the Z-axis relative to the actuating arm 200 due to the axial clearance.

As shown in fig. 3, the valve flap 100 comprises a first coupling section 130 and the actuation arm 200 comprises a second coupling section 210. The first coupling section 130 and the second coupling section 210 are arranged and designed such that a contact area 300 for transmitting a closing force is formed between the first coupling section 130 and the second coupling section 210. The design of the contact region 300 is achieved by means of the design of the

coupling sections

130, 210. The

coupling sections

130, 210 are placed on top of each other and the contact area 300 is exactly the area where the

coupling sections

130, 210 touch (i.e. contact) each other to transfer the closing force. This may be a contact between the

coupling sections

130, 210 in the direction of the longitudinal axis Z of the pin 120. The first coupling section 130 and/or the second coupling section 210 are designed in an annular manner. Alternatively, the first coupling section 130 and/or the second coupling section 210 may be designed as a ring sector. In particular, the first coupling section 130 extends annularly around the pin 120. The first coupling section 130 can extend around the pin 120 and from the valve disk 110 in the direction of the longitudinal axis Z. The second coupling section 210 can surround the through-opening 230 and extend from the valve disk 110 in the direction of the pin axis Z toward the valve disk 110. In other words, the second coupling section 210 can reliably extend in the circumferential direction around the through-opening 230 and from the side of the actuating arm 200 facing the valve disk 110 in the direction of the longitudinal axis Z towards the valve disk 110.

As shown in fig. 3, the contact area 300 for transmitting the closing force is located in the contact plane E1. The contact plane E1 is orthogonal to the longitudinal axis Z, and in particular parallel to the valve disc face 150, which is located on the opposite side of the valve disc 110 from the pin 120. The definition of the contact plane E1 relates to a state of the valve flap assembly 10 in which the valve flap 100 is not tilted with respect to the actuator arm 200. The contact plane E1 is located between the first coupling section 130 and the second coupling section 210. The two

coupling sections

130, 210 may each be of planar design, i.e., extend orthogonally to the longitudinal axis Z (in the contact plane E1 and/or parallel to the valve disk surface 150) in the radial direction R. In one embodiment, a surface contact can be formed between the two

coupling sections

130, 210. The distance D between the longitudinal axis Z and the axis of rotation X, measured in the radial direction R_XZCan be smallAt 25 mm. In one embodiment, the spacing may be less than 23mm, preferably less than 21 mm. The contact plane E1 may be arranged just between the first coupling section 130 and the second coupling section 210 (i.e. in the region where the two

coupling sections

130, 210 are in contact). In an embodiment, instead of being orthogonal, the contact plane E1 may be at a different angle relative to the longitudinal axis Z and/or the valve face 150. This means that the first coupling section 130 and the second coupling section 210 are designed such that they are in "oblique" contact (i.e. not in contact only in the direction of the longitudinal axis Z), and the contact area 300 for transmitting the closing force is therefore also designed to be "oblique". This can have the advantage for certain designs of the flap assembly 10 that not only a closing force component in the direction of the longitudinal axis Z but also a force component in the radial direction R is provided on the valve seat 40 when closing takes place, which can contribute to an improved closing behavior.

The first coupling section 130 is integrally formed with the valve disc 110 and/or the pin 120. Alternatively, the first coupling section 130 and the valve disk 110 and/or the pin 120 may be separate components and may be connected to one another in a material-fitting manner (e.g. by welding, soldering, gluing), form-fitting manner or force-fitting manner. The first coupling portion 130 can also be screwed onto the valve disk 110, for example. The individual components may then have different material properties, wherein the material of the first coupling section 130 may be more wear-resistant than the material of the valve disc 110 and/or the pin 120, for example. Thereby reducing material costs. The first coupling section 130 may be seated on the valve disc 110 and/or the pin 120 by a MIM method (metal injection molding) or a precision casting method. The second coupling section 210 may be integrally formed with the actuator arm 200. Alternatively, the second coupling section 210 and the actuating arm 200 may be separate components and may be connected to one another in a material-fitting manner (e.g. by welding, soldering, gluing), form-fitting manner or force-fitting manner. The second coupling section 210 can, for example, also be screwed onto the actuating arm 200. The individual components may then have different material properties, wherein the material of the second coupling section 210 may be more wear resistant than the material of the actuator arm 200, for example. Thereby reducing material costs. The second coupling section 210 may be positioned on the actuator arm 200 by a MIM method (metal injection molding) or precision casting method.

In an embodiment, a twist stop may be provided between the first coupling section 130 and the second coupling section 210 and/or between the washer 400 and the actuation arm 200, which twist stop prevents twisting relative to the actuation arm 200 in the coupled state in the circumferential direction U of the valve flap 100. In one embodiment of the rotation stop, one of the first coupling section 130 or the second coupling section 210 can engage in a form-fitting manner in a recess of the respective other second coupling section 210 or first coupling section 130. Alternatively or additionally, the twist stop may be integrated into the washer 400. The washer 400 may have a protrusion extending from a side facing the actuator arm 200 in the direction of the longitudinal axis Z towards the actuator arm 200. The protrusion of the washer 400 may be designed for engagement into a recess in the actuator arm 200 on the side of the actuator arm 200 facing the washer 400. Here, the projection of the washer 400 can form, together with the two side walls of the recess in the actuating arm 200 which limit in the circumferential direction, a twist stop between the actuating arm 200 and the valve flap 100.

As illustrated in fig. 4A and 4B, the first coupling section 130 and/or the second coupling section 210 have a conical contact surface 800 in the direction of the longitudinal axis Z, which decreases radially outward from the pin 120. In the case of a first coupling section 130 having a conical surface 800, this conical surface can therefore be lowered in the direction of the longitudinal axis Z toward the valve disk 110. For the case where the second coupling section 210 has a conical surface 800, this conical surface can therefore be lowered in the direction of the longitudinal axis Z towards the actuator arm 200. The respective other first coupling section 130 or second coupling section 210 may have a flat contact surface, wherein a contact area 300 is formed between the conical contact surface 800 and the flat contact surface. In one embodiment, the contact area 300 can also be formed between the first coupling section 130 and the second coupling section 210 if the two

coupling sections

130, 210 have a conical contact surface 800. In these embodiments, a line contact can be formed between the two

coupling sections

130, 210. A better introduction of force into the valve flap 100 is achieved by the conical contact surface 800 when it is pressed by the actuator arm 200 against the valve seat 40. The contact area 300 is formed by a line contact between the first coupling section 130 and the second coupling section 210. The lever arm of the actuator arm 200 can thereby be shortened, which in turn increases the closing force of the flap assembly 10 and thus improves the leakage behavior. This is achieved by: due to the conical shape, the region of the bearing point or second coupling section 210 which transmits the closing force onto the first coupling section 130 is moved further in the direction of the longitudinal axis X, the actuation arm 200 can be shortened and the entire valve flap 100 can thus be deflected along the contact plane E1 towards the main axis 240. The cone is designed here such that the valve disk 110 does not strike the actuator arm 200 even in the case of the greatest possible tilting of the valve flap 100 relative to the actuator arm 200. This also ensures and improves the introduction of concentrated forces. The conical surface 800 has an inclination angle α, wherein the inclination angle α may be between 1 ° and 6 °, preferably between 2 ° and 5 °, and particularly preferably between 3.2 ° and 3.7 °.

In one embodiment, the tilt angle α may be about 3.5 °. In another embodiment and as illustrated in fig. 4B, the tapered surfaces include a first tapered surface 810 and a second tapered surface 820. Second tapered surface 820 is externally contiguous with first tapered surface 810, wherein first tapered surface 810 extends between a pin diameter D3 and a diameter D1 (measured parallel to valve surface 150 about longitudinal axis Z). The second tapered surface 820 extends between this diameter D1 and a diameter D2 (measured parallel to the valve face 150 about the longitudinal axis Z). The first tapered surface 810 has a first inclination angle α 1, and the second tapered surface 820 has a second inclination angle α 2. The first inclination angle α 1 may be between 1 ° and 5 °, preferably between 2 ° and 4 °, and particularly preferably between 2.2 ° and 2.8 °. In one embodiment, the first inclination angle α 1 may be about 2.5 °. The second inclination angle α 2 can be greater than the first inclination angle α 1, in particular wherein the second inclination angle (α 2) can be greater than the first inclination angle α 1 by 0.5 ° to 1.5 °, preferably by about 1 °. Alternatively, the first coupling section 130 and the second coupling section 210 may be designed to be flat (or planar) such that a surface contact is formed in the contact region 300.

As illustrated in fig. 3 and 5A-8C, the valve flap assembly 10 according to the present invention includes a spring element 500 disposed about the pin 120 between the washer 400 and the actuating arm 200. The spring element 500 has a first ring segment 510 and a second ring segment 520 extending from the first ring segment 510 in the radial direction R. The first ring segment 510 is designed to be planar and the second ring segment 520 is designed to be tapered and/or arcuate. Pretensioning of the components (in particular of the flap 100 when it is coupled to the actuator arm 200) can be produced by the spring element 500, so that the formation of noise, for example, rattling or rubbing against one another can be reduced. The wear behavior of the flap arrangement 10 can thereby be significantly improved. By the inventive design of the spring element 500, the stiffness characteristic and the stiffness characteristic of the spring element 500 can be improved. In particular, the conical and/or curved design of the second ring segment and its contact with further components (in particular the actuating arm 200) can reduce the stress of the spring element 500 and thus the wear.

The spring element 500 can provide a higher spring force for a smaller installation space. In one embodiment, the spring element 500 may have a spring force of 20N to 100N, preferably 30N to 80N. In an embodiment, however, a higher spring force may also be provided. A plurality of spring elements 500 can also be arranged one above the other (in parallel or in series or in combination) in order to be able to adapt the force and travel characteristics of the spring elements 500, for example. The first ring segment 510 may be tapered (or in other words linear) or curved. In one embodiment, a subsection of the first ring segment 510 can be designed as conical and another subsection can be designed as curved (or rounded). Alternatively or additionally, the spring element 500 can also be arranged between the valve flap 100 and the actuating arm 200, in particular between the first coupling section 130 and the second coupling section 210. The spring element 500 may be a compression spring, in particular a disk spring. The spring element 500 can generate a pretension force in the direction of the longitudinal axis Z (in particular in the direction of the longitudinal axis Z) between the washer 400 and the actuation arm 200 or between the actuation arm 200 and the flap 100. A plurality of spring elements 500 may also be provided. These spring elements may be arranged between the washer 400 and the actuation arm 200 and between the actuation arm 200 and the valve flap 100 in order to create a pretension between the mentioned components. Due to the pretensioning force in the direction of the longitudinal axis Z, a pretensioning force can also be generated in the radial direction R starting from the longitudinal axis Z due to the friction forces between the spring element 500 and the respective component. By means of the axial and radial play, the valve flap 100 can be tilted relative to the actuating arm 200, so that an angular compensation between the valve disk 110 and the valve seat 40 can also be achieved during the closing process (for example due to thermal deformations or wear of the turbine housing). Thereby improving leakage behavior. If the flap assembly 10 is lifted from the valve seat 40, the flap 100 can return to a "normal state" in which the longitudinal axis Z of the pin 120 (and thus the flap 100) extends substantially orthogonally to the side of the actuation arm 200 facing the washer 400, due to the pretensioning force of the spring element 500. The spring element 500 may be made of sheet metal having a sheet metal thickness of 0.15mm to 0.30mm, preferably 0.20mm to 0.25 mm.

Fig. 5A-8C show cross-sectional views of some designs of the valve flap assembly 10, the spring element 500 and its arrangement between the actuation arm 200 and the washer 400. The longitudinal axis Z of the pin also illustrates the axis (in particular the axis of symmetry) of the spring element 500 in the coupled state.

As shown in fig. 5A, 6A, 7A, and 7B, the first ring segment 510 is in face contact with the washer 400 or the actuating arm 200. In one embodiment (see fig. 8A), the first ring segment 510 may however also be arranged spaced apart from the actuating arm 200 and the washer 400 in the direction of the pin axis Z. The second ring segment 520 makes line or face contact with the washer 400 and/or the actuator arm 200. In a preferred embodiment, the first ring segment 510 is in surface contact with the washer 400 (in particular in the region adjoining the inner diameter of the washer 400 in the radial direction R). In this design, the second ring segment 520 may be in face contact with the actuator arm 200 (see fig. 7A, 7B) or in line contact with the actuator arm 200 (see fig. 5A, 6A, 8A). Primary stresses (particularly pressure stresses) may be reduced during operation by the face contact of the spring element 500 with the actuator arm 200 and/or the washer 400.

As shown in fig. 5A-8C, the second ring segment 520 extends from the first ring segment 510 at an angle β. In one embodiment, the angle β can be between 5 ° and 20 °, preferably between 7 ° and 17 °, particularly preferably between 9 ° and 15 °. The second ring segment 520 may extend conically from the first ring segment 510 at an angle β. In other words, the second ring segment 520 may extend linearly from the first ring segment 510 at an angle β. Alternatively, the second ring segment 520 may be disposed at an angle β relative to the first ring segment 510 and extend arcuately from the first ring segment 510.

As shown in fig. 5C, 6C and 8C, the spring element 500 has a first plane P1 extending through the first ring segment 510 and orthogonally to the longitudinal axis Z. The spring element 500 has a second plane P2 which is arranged in the direction of the longitudinal axis Z (in the assembled state toward the valve disk 110) and at a distance from and parallel to the first plane P1, wherein the second ring segment 520 extends as far as the second plane P2. The spring element 500 has an inner diameter D1 that is greater than the outer diameter D3 of the pin 120. Furthermore, the spring element 500 has an outer diameter d 3. The first ring segment 510 extends from an inner diameter d1 up to an intermediate diameter d 2. The second ring segment 520 extends from the intermediate diameter d2 up to an outer diameter d 3.

According to the embodiment of fig. 5A to 5C, the second ring segment 520 may have a first partial ring segment 521 that is designed to be conical and may have a second partial ring segment 522 that is designed to be arcuate. The spring element 500 may have, in the radial direction R, a first ring segment 510, followed by a first sub-ring segment 521, followed by a second sub-ring segment 522. In an embodiment, the second sub-ring segment 522 may have a radius r1 of 0.3mm to 7.0mm, preferably 0.5mm to 5.0 mm. The stiffness of the spring element can be increased by increasing the radius r 1. In particular, the main stresses in the spring element 500 can be reduced by setting and/or increasing the radius r1, which in turn can contribute to an improvement in the stiffness characteristic and the stiffness characteristic curve of the spring element 500. Line contact between the second ring segment 520 and the actuator arm 200 or washer 400 may also be created by the radius r 1. The sliding of the spring element 500 on the actuating arm 200 or on the washer 400 during tilting can be improved in the partial ring segment 522 by means of the radius r1, so that wear due to friction can be reduced. According to the embodiment in fig. 5A to 5C, the first partial ring segment 521 extends from the first ring segment 510 at an angle β, and the second partial ring segment 522 extends from the first partial ring segment 521 at a radius r 1. The second sub-ring segment 522 is rounded from the second plane P2 toward the first plane P1. In other words, the second sub-ring segment 522 has a convex course with respect to the first plane P1.

In the embodiment of fig. 8A to 8C, the second ring segment 520 has a plurality of partial ring segments 523, which extend from the first ring segment 510 in the circumferential direction U relative to one another and are spaced apart from one another in the circumferential direction U, in particular wherein the plurality of partial ring segments 523 are designed in an arc-shaped manner. Alternatively, the plurality of sub-ring segments 523 may be tapered (or linear). The plurality of partial ring segments 523 can each extend linearly or arcuately from the first partial ring segment at an angle β. In embodiments, the plurality of sub-ring segments 523 may extend from the first ring segment 510 alternately linearly or arcuately. The spring element 500 has a third plane P3 which is directed towards the washer 400 in the direction of the longitudinal axis Z and is arranged spaced apart and parallel to the first plane P1. The sub-ring segments of the plurality of sub-ring segments 523 extend alternately from the first ring segment 510 towards the second plane P2 or towards the third plane P3. The engagement diameter can be increased and the overall height of the spring element 500 can be reduced by this embodiment. The radial and axial play can thereby be kept as small as possible, which in turn can contribute to reduced wear and reduced noise (e.g., rattle or rattle). In one embodiment, 8 partial ring segments can be provided, which extend alternately in the direction of the second plane P2 or the third plane P3. However, other numbers of partial ring segments 523, for example four, six, ten, twelve or more partial ring segments 523, may also be provided. The plurality of sub ring segments 523 are each formed convexly about a plane P1 extending through the first ring segment 510.

As shown in fig. 5A, 6A, 7B and 8B, the actuator arm 200 has a cylindrical recess 250 (in particular a closure) on the side 260 facing the washer 400, which extends into the actuator arm 200 in the direction of the longitudinal axis Z. The recess 250 is designed to accommodate at least a portion of the spring element 500. The cylindrical recess 250 has a diameter D5 which is greater than the diameter D4 of the washer 400 and/or greater than the outer diameter D3 of the spring element 500. In one embodiment, the washer 400 may extend at least partially into the cylindrical recess 220.

Fig. 5A, 6A, 7B, and 8B illustrate: the notch 250 has a notch bottom 270 and a depth T1, particularly wherein the depth T1 is measured parallel to the longitudinal axis Z between the notch bottom 250 and the side 260. The recess bottom 270 extends parallel to the side 260. The recess 250 has a side wall 273 that extends parallel to the longitudinal axis Z from the recess bottom 270 towards the side 260. The encircling first shoulder 271 extends from the recess bottom 270 in the direction of the longitudinal axis Z towards the side 260. The first shoulder 271 is arranged adjacent to the passage 230 in the radial direction R and has a first bearing surface 274 which extends parallel to the recess base 270. By means of the shoulder 271 with the bearing surface 274, a stop can be provided in the longitudinal direction Z for the washer 400 and the first ring segment 510 of the spring element 500 in order to limit the maximum relative movement of the valve flap 100 and/or the spring element 500 with respect to the actuating arm 200. In particular, a defined stop can be provided for the spring element 500 and the washer. The second sub-ring segment 520 of the spring element 500 can be brought into abutment against the recess bottom 270 by line contact or surface contact.

As illustrated in the embodiment in fig. 7A and 7B, a circumferential second shoulder 272, which is designed to be tapered, extends from the recess base 270 in the direction of the longitudinal axis Z toward the side 260. The second shoulder 272 is arranged adjacent to the side wall 273 in the radial direction R and extends conically towards the longitudinal axis Z. The second shoulder 272 has a second bearing surface 275 that extends at an angle γ with respect to the recess bottom 270. The angle γ may substantially correspond to the angle β. The second ring segment 520 rests at least partially on the surrounding second shoulder 272, in particular wherein the second ring segment 520 is in surface contact with the surrounding second shoulder 272. The design of the spring element 500 according to the embodiment shown in fig. 6A to 6C substantially corresponds to the design of the spring element 500 shown in fig. 7A and 7B. In the embodiment of fig. 6A, however, no encircling second shoulder 272 is provided, so that the ring segment 520 of the spring element 500 is in line contact with the recess bottom 270.

Although the utility model has been described and defined hereinabove, it should be understood that the utility model can also be defined alternatively according to the following embodiments:

1. a valve flap assembly (10) for a supercharging device (1), the valve flap assembly comprising:

a valve flap (100) having a valve disc (110) and a pin (120);

an actuation arm (200), wherein the actuation arm (200) is coupled with the valve flap (100) for transferring a closing force,

a washer (400) arranged at an end (140) of the pin (120) remote from the valve disc (110),

wherein a spring element (500) is arranged around the pin (120) between the washer (400) and the actuating arm (200), and

wherein the spring element (500) has a first ring segment (510) and a second ring segment (520) extending from the first ring segment (510) in the radial direction (R),

characterized in that the first ring segment (510) is designed to be planar and the second ring segment (520) is designed to be conical and/or curved.

2. The flap assembly according to embodiment 1, characterized in that the pin (120) has a longitudinal axis (Z); and the radial direction (R) extends orthogonally to the longitudinal axis (Z).

3. The valve flap assembly (10) according to embodiment 1 or embodiment 2, characterized in that the first ring segment (510) is in surface contact with the washer (400) or the actuating arm (200).

4. The valve flap assembly (10) according to any of the preceding embodiments, characterized in that the second ring segment (520) forms a line contact or a surface contact with the washer (400) or the actuating arm (200).

5. The valve flap assembly (10) according to one of the preceding embodiments, characterized in that the spring element (500) has a spring force of 20N to 100N, preferably 30N to 80N.

6. The flap assembly (10) according to one of the preceding embodiments, characterized in that the second ring segment (520) extends from the first ring segment (510) at an angle (β), wherein the angle (β) is between 5 ° and 20 °, preferably between 7 ° and 17 °, particularly preferably between 9 ° and 15 °.

7. The valve flap assembly (10) according to embodiment 6, characterized in that the second ring segment (520) extends conically from the first ring segment (510) at an angle (β).

8. The valve flap assembly (10) according to embodiment 6, characterized in that the second ring segment (520) is arranged at the angle (β) with respect to the first ring segment (510) and extends arcuately from the first ring segment (510).

9. The valve flap assembly (10) according to any one of the preceding embodiments, characterized in that the spring element (500) has a first plane (P1) which extends through the first ring segment (510) and extends orthogonally to the longitudinal axis (Z); and the spring element (500) has a second plane (P2) which is arranged in the direction of the longitudinal axis (Z) in a spaced-apart and parallel manner to the valve disk (110) and to the first plane (P1), wherein the second ring segment (520) extends as far as the second plane (P2).

10. The flap assembly according to any of the preceding embodiments, characterized in that the spring element (500) has an inner diameter (D1) which is larger than the outer diameter (D3) of the pin (120); and the spring element (500) has an outer diameter (d 3).

11. The flap assembly according to embodiment 10, characterized in that the first ring segment (510) extends from the inner diameter (d1) up to an intermediate diameter (d 2); and the second ring segment (520) extends from the intermediate diameter (d2) up to the outer diameter (d 3).

12. The valve flap assembly (10) according to one of the preceding embodiments, characterized in that the second ring segment (520) has a first sub-ring segment (521) which is designed conically and has a second sub-ring segment (522) which is designed arcuately.

13. The valve flap assembly (10) according to embodiment 12, characterized in that the spring element (500) has the first ring segment (510), followed by the first sub-ring segment (521), followed by the second sub-ring segment (522) in the radial direction (R).

14. The valve flap assembly (10) according to embodiment 12 or embodiment 13, characterized in that the second sub-ring segment (522) has a radius (r1) of 0.3mm to 7.0mm, preferably 0.5mm to 5.0 mm.

15. The valve flap assembly (10) of embodiment 14, wherein the first sub-ring segment (521) extends from the first ring segment (510) at the angle (β); and the second sub-ring segment (522) extends from the first sub-ring segment (521) at the radius (r 1).

16. The flap assembly (10) according to one of embodiments 12 to 15, characterized in that the second sub-ring segment is rounded from the second plane (P2) towards the first plane (P1).

17. The flap assembly (10) according to one of embodiments 1 to 6 and 8 to 11, characterized in that the second ring segment (520) has a plurality of partial ring segments (523) which extend from the first ring segment (510) relative to one another in the circumferential direction (U) and are spaced apart from one another in the circumferential direction (U), in particular wherein the plurality of partial ring segments (523) are designed in an arc shape.

18. The flap assembly (10) according to one of the embodiments 9 to 17, characterized in that the spring element has a third plane (P3) which is arranged in the direction of the longitudinal axis (Z) towards the washer (400) and spaced apart from and parallel to the first plane (P1).

19. The flap assembly (10) according to embodiment 18 as dependent on embodiment 17, characterized in that the sub-ring segments of the plurality of sub-ring segments (523) extend alternately from the first ring segment (510) towards the second plane (P2) or towards the third plane (P3).

20. The valve flap assembly (10) according to one of the embodiments 17 to 19, characterized in that the plurality of sub-ring segments (523) are each convexly formed relative to a plane (P1) extending through the first ring segment (510).

21. The valve flap assembly (10) according to one of the preceding embodiments, characterized in that the actuating arm (200) has a cylindrical recess (250) on the side (260) facing the washer (400), which recess extends into the actuating arm (200) in the direction of the longitudinal axis (Z).

22. The flap assembly (10) according to embodiment 21, characterized in that the cylindrical recess (250) has a diameter (D5) which is larger than the diameter (D4) of the washer (400) and/or larger than the outer diameter (D3) of the spring element (500).

23. The valve flap assembly (10) according to embodiment 21 or embodiment 22, characterized in that the gasket (400) extends at least partially into the cylindrical recess (220).

24. The valve flap assembly (10) according to any of embodiments 21 to 23, characterized in that the notch (250) has a notch bottom (270), in particular wherein the notch (250) has a depth (T1) measured parallel to the longitudinal axis (Z) between the notch bottom (270) and the side (260).

25. The valve flap assembly (10) of embodiment 24, wherein the recess bottom (270) extends parallel to the side (260).

26. The valve flap assembly (10) of embodiment 24 or embodiment 25, wherein the notch (250) has a sidewall (273) extending parallel to the longitudinal axis (Z) from the notch bottom (270) toward the side (260).

27. The valve flap assembly (10) according to any of the preceding embodiments, characterized in that the actuation arm (200) has a through-going portion (230) at the first end (220), through which the pin (120) extends when the valve flap (100) is coupled with the actuation arm (200).

28. The valve flap assembly (10) according to embodiment 27 as dependent on any of embodiments 24 to 26, characterized in that a surrounding first shoulder (271) extends from the recess bottom (270) in the direction of the longitudinal axis (Z) towards the side face (260), in particular wherein the first shoulder (271) is arranged adjacent to the through-opening (230) in the radial direction (R) and has a first bearing surface (274) which extends parallel to the recess bottom (270).

29. The valve flap assembly (10) according to one of the embodiments 21 to 28, characterized in that a circumferential second shoulder (272) extends from the recess base (270) in the direction of the longitudinal axis (Z) toward the side face (260), which second shoulder is designed to taper.

30. The valve flap assembly (10) according to embodiment 29, characterized in that the second shoulder (272) is arranged adjacent to the side wall (273) in the radial direction (R) and extends conically towards the longitudinal axis (Z), wherein the second shoulder has a second bearing surface (275) which extends at an angle (γ) relative to the recess bottom (270).

31. The valve flap assembly (10) of embodiment 30, wherein the angle (γ) substantially corresponds to the angle (β).

32. The valve flap assembly (10) according to one of the embodiments 29 to 31, characterized in that the second ring segment (520) rests at least partially on the encircling second shoulder (272), in particular wherein the second ring segment (520) is in surface contact with the encircling second shoulder (272).

33. The valve flap assembly (10) according to any of the preceding embodiments, characterized in that the actuation arm (200) comprises a spindle (240) for supporting the actuation arm (200), wherein the spindle (240) has an axis of rotation (X).

34. The valve flap assembly (10) according to any of the preceding embodiments, characterized in that the spring element (500) is made of a metal sheet having a sheet metal thickness of 0.15 to 0.30mm, preferably 0.20 to 0.25 mm.

35. The valve flap assembly (10) according to one of the preceding embodiments, characterized in that the valve flap (100) comprises a first coupling section (130) and the actuating arm (200) comprises a second coupling section (210), wherein the first coupling section (130) and the second coupling section (210) are arranged and designed such that a contact region (300) for transmitting a closing force is formed between the first coupling section (130) and the second coupling section (210).

36. The valve flap assembly (10) according to embodiment 35, characterized in that the first coupling section (130) and/or the second coupling section (210) are designed in an annular shape.

37. The valve flap assembly (10) according to embodiment 35 or embodiment 36, characterized in that the first coupling section (130) or the second coupling section (210) has a conical contact surface (800) in the direction of the pin axis (Z), which decreases radially outward from the pin (120), and wherein the respective other first coupling section (130) or second coupling section (210) has a flat contact surface, wherein the contact region (300) is formed between the conical contact surface (800) and the flat contact surface.

38. The valve flap assembly (10) according to embodiment 37, characterized in that the conical surface (800) has an inclination angle (α), wherein the inclination angle (α) is between 1 ° and 6 °, in particular between 2 ° and 5 °, preferably about 3.5 °.

39. The valve flap assembly (10) of embodiment 37, wherein the tapered surface comprises a first tapered surface (810) and a second tapered surface (820), wherein the second tapered surface (820) is externally contiguous with the first tapered surface (810), wherein the first tapered surface (810) has a first angle of inclination (α 1), and wherein the second tapered surface (820) has a second angle of inclination (α 2).

40. The valve flap assembly (10) according to embodiment 39, characterized in that the first angle of inclination (α 1) is between 1 ° and 5 °, in particular between 2 ° and 4 °, preferably about 2.5 °.

41. The valve flap assembly (10) of embodiment 39 or embodiment 40, wherein the second angle of inclination (α) is₂) Greater than the first inclination angle (alpha)₁) Especially wherein the second inclination angle (alpha)₂) Is greater than the first inclination angle (alpha)₁) 0.5 ° to 1.5 °, preferably about 1 °, greater.

42. A turbine (20) for a supercharging apparatus (1), the turbine comprising:

a turbine housing (30);

the valve flap assembly (10) according to any one of embodiments 1 to 41, wherein the valve flap assembly (10) is supported in the turbine housing (30) by the main shaft (240); and

a valve seat (40) in the turbine housing (30), wherein the valve flap assembly (10) is pivotable between a first position in which the valve disc (110) rests on the valve seat (40) to close off a wastegate passage (60); in the second position, the valve disc (110) is lifted away from the valve seat (40) to release at least a portion of the wastegate passage (60).

43. A supercharging apparatus (1) comprising:

a compressor; and

the turbine (20) of embodiment 42.

Claims

a valve flap (100) having a valve disc (110) and a pin (120);

an actuation arm (200), wherein the actuation arm (200) is coupled with the valve flap (100) to transmit a closing force,

2. The valve flap assembly of claim 1, wherein the pin (120) has a longitudinal axis (Z); and the radial direction (R) extends orthogonally to the longitudinal axis (Z); and the first ring segment (510) is in face contact with the washer (400) or the actuating arm (200).

3. The valve flap assembly (10) of claim 1 or claim 2, wherein the second ring segment (520) makes line or surface contact with the washer (400) or the actuator arm (200).

4. The valve flap assembly (10) of claim 1, wherein the second ring segment (520) extends from the first ring segment (510) at an angle (β), wherein the angle (β) is between 5 ° and 20 °.

5. The valve flap assembly (10) of claim 4, characterized in that the second ring segment (520) extends conically from the first ring segment (510) at the angle (β); or the second ring segment (520) is arranged at the angle (β) with respect to the first ring segment (510) and extends arcuately from the first ring segment (510).

6. The valve flap assembly (10) according to claim 2, characterized in that the spring element (500) has a first plane (P1) which extends through the first ring segment (510) and extends orthogonally to the longitudinal axis (Z); and the spring element (500) has a second plane (P2) which is arranged in the direction of the longitudinal axis (Z) in a spaced-apart and parallel manner to the valve disk (110) and to the first plane (P1), wherein the second ring segment (520) extends as far as the second plane (P2).

7. The flap assembly according to claim 1, characterized in that the spring element (500) has an inner diameter (D1) which is larger than an outer diameter (D3) of the pin (120); and the spring element (500) has an outer diameter (d3), wherein the first ring segment (510) extends from the inner diameter (d1) of the spring element up to the middle diameter (d2) of the spring element; and the second ring segment (520) extends from the intermediate diameter (d2) of the spring element up to the outer diameter (d3) of the spring element.

8. The flap assembly (10) of claim 4, characterized in that the second ring segment (520) has a first sub-ring segment (521) which is designed as a cone and has a second sub-ring segment (522) which is designed as an arc; and the spring element (500) has the first ring segment (510), followed by the first sub-ring segment (521), followed by the second sub-ring segment (522) in the radial direction (R).

9. The valve flap assembly (10) of claim 8, wherein the second sub-ring segment (522) has a radius (r1) of 0.3mm to 7.0 mm; and the first sub-ring segment (521) extends from the first ring segment (510) at the angle (β); and the second sub-ring segment (522) extends from the first sub-ring segment (521) at the radius (r 1).

10. The valve flap assembly (10) of claim 6, characterized in that the second ring segment (520) has a plurality of sub-ring segments which extend from the first ring segment (510) relative to each other in a circumferential direction (U) and which are spaced apart from each other in the circumferential direction (U); and the spring element has a third plane (P3) which is arranged in the direction of the longitudinal axis (Z) in a spaced and parallel manner to the washer (400) and to the first plane (P1), wherein the sub-ring segments of the plurality of sub-ring segments (523) extend alternately from the first ring segment (510) in the direction of the second plane (P2) or in the direction of the third plane (P3).

11. The valve flap assembly (10) of claim 10, wherein the plurality of sub-ring segments (523) are each convexly formed relative to a first plane (P1) extending through the first ring segment (510).

12. The valve flap assembly (10) according to claim 2, characterized in that the actuating arm (200) has a cylindrical recess (250) on the side (260) facing the washer (400), which recess extends into the actuating arm (200) in the direction of the longitudinal axis (Z).

13. The valve flap assembly (10) of claim 12, wherein the notch (250) has a notch bottom (270), wherein the notch bottom (270) extends parallel to the side (260), and wherein the notch (250) has a sidewall (273) extending parallel to the longitudinal axis (Z) from the notch bottom (270) toward the side (260).

14. The valve flap assembly (10) of claim 13, wherein the actuation arm (200) has a through-penetration (230) at a first end (220) through which the pin (120) extends when the valve flap (100) is coupled with the actuation arm (200); and a circumferential first shoulder (271) extends from the recess bottom (270) in the direction of the longitudinal axis (Z) toward the side face (260), wherein the first shoulder (271) is arranged adjacent to the passage (230) in the radial direction (R) and has a first bearing face (274) which extends parallel to the recess bottom (270).

15. The valve flap assembly (10) according to claim 14, characterized in that a circumferential second shoulder (272) extends from the recess base (270) in the direction of the longitudinal axis (Z) towards the side face (260), which second shoulder is designed to taper; and the second shoulder (272) is arranged adjacent to the side wall (273) in the radial direction (R) and extends conically towards the longitudinal axis (Z), wherein the second shoulder has a second bearing surface (275) which extends at an angle (γ) relative to the recess base (270).

16. The valve flap assembly (10) of claim 15, characterized in that the second ring segment (520) rests at least partially on the encircling second shoulder (272).

17. The valve flap assembly (10) of claim 9, wherein the second sub-ring segment (522) has a radius (r1) of 0.5mm to 5.0 mm.

18. The flap assembly (10) of claim 10, characterized in that the plurality of sub-ring segments are designed to be arcuate.

19. The valve flap assembly (10) of claim 13, wherein the notch (250) has a depth (T1) measured parallel to the longitudinal axis (Z) between the notch bottom (270) and the side (260).

20. The valve flap assembly (10) of claim 16, wherein the second ring segment (520) is in surface contact with the surrounding second shoulder (272).

21. A turbine (20) for a supercharging apparatus (1), characterized in that it comprises:

a turbine housing (30);

the valve flap assembly (10) according to any one of the preceding claims 1 to 20, wherein the valve flap assembly (10) is supported in the turbine housing (30) by a spindle (240); and

22. A supercharging arrangement (1), characterized in that it comprises:

a compressor; and

the turbine (20) of claim 21.