Dual wastegate valve arrangement

Abstract

Double wastegate valve arrangement (10), comprising: - two wastegate valves (12) movable along a valve longitudinal axis (14), each of the two wastegate valves (12) having a rotationally symmetrical projecting upper section (28) formed around the valve longitudinal axis (14), - a valve arm (16) connected to an actuating shaft (18), and - an intermediate plate (20) which is loosely arranged between the valve arm (16) and the wastegate valves (12), wherein the intermediate plate (20) is pivotable about the valve arm (16) in a direction perpendicular to the valve longitudinal axis (14) and is supported on the rotationally symmetrically designed projecting lower surface sections (30) of the intermediate plate (20) on the rotationally symmetrically designed projecting upper surface sections (28) of the two wastegate valves (12).

Description

[0001] The invention relates to a double wastegate valve arrangement.

[0002] Turbochargers are used to increase the efficiency of internal combustion engines. An exhaust gas turbocharger is responsible for pumping compressed air into the engine. The turbocharger's compressor is driven by an exhaust gas-driven turbine. The rotation of a turbine wheel, caused by the engine's exhaust gases, is transferred via a shaft to a compressor wheel, thus compressing and pumping the air. The internal combustion engine, in conjunction with the exhaust gas turbocharger, can be used in vehicles such as cars or trucks. Turbochargers can be used with diesel or gasoline engines, as well as with engines powered by methane or compressed natural gas.

[0003] In some applications, particularly in light commercial vehicles, a twin-spiral turbine stage can be advantageous. In a twin-spiral turbine stage, the exhaust gas flow is routed through two separate spiral casings, each directing the exhaust gas pulsations directly into one half of the turbine wheel. Each spiral has its own wastegate opening.

[0004] Furthermore, double spirals are known in which the manifold and the turbine housing are divided into two flow paths, so that the firing order of the engine can change the flow and transfer the impulse energy directly to the turbine wheel.

[0005] What these applications have in common is the need to accommodate two wastegate ports. In principle, a two-port wastegate can be operated with a single valve plate. However, a large wastegate port and a large valve plate are required to achieve a high bypass ratio. Furthermore, the valve arm must be long to accommodate the large valve, resulting in high stress on the system.

[0006] US Patent 5,996,348 A discloses an improved wastegate valve for turbochargers with bifurcated exhaust inlets, comprising a first bypass orifice connected to a first portion of the exhaust inlet, a first valve disc engaging and sealing a seat surrounding the first orifice, a second bypass orifice connected to a second portion of the exhaust inlet, and a second valve disc engaging and sealing a seat surrounding the second orifice. The valves are actuated by a first, essentially tubular shaft rotatably mounted about an axis and having a central bore, and a second, essentially tubular shaft extending through the central bore of the first shaft and rotatably mounted therein about the axis.The two shafts are rotated simultaneously by a lever arm, which is connected to the first shaft at an end opposite the radial arm by a weld bead extending over the end face of the first shaft, the bore and a coplanar end of the second shaft.

[0007] US 8,336,309 B2 discloses a turbocharger wastegate valve assembly comprising a first bypass orifice communicating with a first portion of an exhaust inlet and a first valve element capable of engaging with and sealing a first valve seat surrounding the first bypass orifice. The valve assembly further comprises a second bypass orifice communicating with a second portion of an exhaust inlet and a second valve element capable of engaging with and sealing a second valve seat surrounding the second orifice. A shaft carries each valve element to rotate about a shaft axis to lift both the first and second valve elements out of sealing engagement with the first and second valve seats, respectively. The first valve seat is inclined relative to the second valve seat, and the shaft is free to move axially.

[0008] US 11,441,478 B2 discloses a turbine comprising a turbine casing defining a turbine inlet upstream of a turbine wheel and a turbine outlet downstream of the turbine wheel; and a wastegate valve assembly comprising at least one movable valve element mounted on a movable support element within a wastegate chamber communicating with the turbine inlet upstream of the turbine and having one or more chamber outlets communicating with a turbine outlet. The valve element may rotate slightly about the support element, the degree of rotation in the respective directions being limited by collisions between a respective endpoint on a boundary region on a rear surface of a sealing section of the valve element and a respective endpoint on a boundary region on a front surface of the support element.

[0009] US 11,149,579 B2 discloses a turbine comprising a turbine casing defining a turbine inlet upstream of a turbine wheel and a turbine outlet downstream of the turbine wheel; and a wastegate valve assembly comprising at least one movable valve element mounted on a movable support element within a wastegate chamber communicating with the turbine inlet upstream of the turbine and having one or more chamber outlets communicating with a turbine outlet. The valve element may rotate slightly about the support element, the extent of the rotation being limited by collisions between corresponding boundary regions on a rear face of a sealing section of the valve element and a front face of the support element.Each valve element is connected to the support element via a pin section of the valve element that passes through a washer with a non-circular outer profile, and the rotation of the washer is limited by contact surfaces of the support element.

[0010] In view of the prior art cited above, it is an object of the invention to provide a double wastegate valve arrangement which has improved durability and a reduced overall load in the system.

[0011] This problem is solved by independent claim 1. Further advantageous embodiments of the invention are the subject of the dependent claims. These can be combined with one another in a technologically meaningful way. The description, particularly in conjunction with the drawing, further characterizes and specifies the invention.

[0012] According to the invention, a double wastegate valve arrangement is created. The double wastegate valve arrangement comprises two wastegate valves movable along a valve longitudinal axis, each of the two wastegate valves having a rotationally symmetrical projecting upper section extending around the valve longitudinal axis, a valve arm connected to an actuating shaft, and an intermediate plate loosely arranged between the valve arm and the wastegate valves, wherein the intermediate plate is pivotable about the valve arm in a direction perpendicular to the valve longitudinal axis and is supported on the rotationally symmetrical projecting upper sections of the two wastegate valves via rotationally symmetrical projecting lower sections of the intermediate plate.

[0013] The double wastegate valve arrangement according to the invention can be used for twin-spiral housings and twin-spiral turbine housings. It features two wastegate ports and two separate wastegate valves mounted on a single valve arm. This arrangement allows for compensation of the thermal expansion of the turbine housing and dimensional deviations within the system, ensuring a tight seal for the wastegate valve. Each wastegate valve can move independently. Separate ports reduce the influence of exhaust gas pulsations, resulting in improved durability. Compared to a single valve plate with the same wastegate port area, the overall system load is lower due to the shorter arm. A key feature of this invention is its ability to compensate for variations between the two valves (ports) and ensure a proper seal between them.This is achieved by providing an intermediate plate between the valve arm and the two wastegate valves. This intermediate plate is not rigidly connected to the valve arm but can rotate. Consequently, an additional force is exerted on the wastegate valve that has not yet contacted its valve seat on the turbine housing, as the intermediate plate rotates towards this valve, while the other wastegate valve is already in contact with its valve seat.

[0014] According to one embodiment of the invention, the rotationally symmetrical projecting underside sections of the intermediate plate and the rotationally symmetrical projecting upperside sections of the wastegate valves are conical or chamfered.

[0015] Wastegate valves typically have a valve stem that runs along the valve's longitudinal axis. The valve stem is surrounded by projecting upper side plates. To ensure rotational symmetry, these upper side plates can be, for example, conical or chamfered. The corresponding lower side plates of the intermediate plate can have the same shape.

[0016] According to a further embodiment of the invention, the rotationally symmetrical projecting underside sections of the intermediate plate and the rotationally symmetrical projecting upperside sections of the wastegate valves are spherically shaped. In this embodiment, the radius of the concave spherical underside section of the intermediate plate can be greater than or equal to the radius of the convex spherical upperside section of the two wastegate valves.

[0017] To facilitate the movement of the wastegate valve relative to the intermediate plate, a spherical shape for the lower and upper sections is preferred. Slightly different radii can compensate for manufacturing tolerances.

[0018] According to a further embodiment of the invention, the actuating shaft is connected to the valve arm in a symmetrical position in the middle between the two wastegate valves.

[0019] In symmetrical applications with respect to the wastegate connections on the two spiral channels, the two wastegate valves can be connected in a symmetrical position, so that the system load on the valve arm is the same for both wastegate valves.

[0020] According to a further embodiment of the invention, the actuating shaft is connected to the valve arm in a position that is closer to one of the two wastegate valves.

[0021] This approach is particularly advantageous when the load on the different wastegate valves varies.

[0022] According to a further embodiment of the invention, protruding elements are formed on the two wastegate valves which, in conjunction with the intermediate plate, act as an anti-rotation device.

[0023] To prevent the wastegate valves from rotating around their longitudinal axis, anti-rotation devices are provided that limit the movement of the wastegate valves relative to the intermediate plate.

[0024] According to a further embodiment of the invention, the intermediate plate pivots around the valve arm by forming corresponding curved areas on the intermediate plate and the valve arm. In this embodiment, a positively curved area can be formed on the intermediate plate and a negatively curved area on the valve arm. Furthermore, the curved areas can be cylindrical, and the radius of the cylindrical area on the intermediate plate can be less than or equal to the radius of the cylindrical area on the valve arm.

[0025] The contact surface between the valve arm and the intermediate plate is formed by corresponding curved areas, which are preferably cylindrical. Accordingly, a cylindrical recess is formed in the center of the valve arm. In the center of the intermediate plate is a cylindrical convex surface that contacts the concave cylindrical surface of the valve arm. The diameter of the concave cylinder of the valve arm is equal to or greater than that of the convex cylinder of the intermediate plate. Using different radii allows for the compensation of manufacturing tolerances and ensures smooth movement of the parts. Due to this contact arrangement, the intermediate plate can tilt relative to the valve arm. The sealing surfaces of the wastegate valves cover the deviations of each wastegate seat separately. This ensures that both wastegate valves are sealed when closed.

[0026] According to a further embodiment of the invention, the valve arm has a pin that engages in the intermediate plate and establishes a pivotable connection. In this embodiment, the pivotable connection can be limited by a stop element.

[0027] In contrast to the previous embodiment, the intermediate plate is connected to the valve arm via a pin / hole interface. The pin is part of the valve arm, and the hole is part of the intermediate plate. The diameter of the pin is equal to or smaller than that of the hole, resulting in a loose fit. The intermediate plate can rotate around the axis of the valve arm pin. This allows the wastegate assembly to accommodate and compensate for geometric deviations of the assembly and the wastegate seats, thereby ensuring the sealing of both wastegate valves.

[0028] Advantageously, the double wastegate valve arrangement described above can be used with a twin volute or a double spiral housing.

[0029] Furthermore, a turbocharger can incorporate the double wastegate valve arrangement described above. The turbocharger can be used in an internal combustion engine powered by diesel, hydrogen, methane, or compressed natural gas (CNG).

[0030] The concept according to the invention can be used in all applications with a high wastegate bypass ratio and high durability requirements. The invention leads to reduced exhaust gas leakage through the wastegate valve in turbine housings with two wastegate valves. The invention reduces the overall load on the wastegate system compared to a single-valve solution with the same wastegate connection area.

[0031] In the figures, identical or similarly functioning components are provided with the same reference designations.

[0032] In the characters: Fig. Figure 1 shows a first embodiment of a double wastegate valve arrangement in a perspective side view, Fig. Figure 2 shows the double wastegate valve arrangement of Fig. 1 in a cross-sectional view, Fig. Figure 3 shows a variant of the first embodiment of a double wastegate valve arrangement in a perspective side view, Fig. Figure 4A shows the double wastegate valve arrangement of Fig. 1 in another cross-sectional view during operation, Fig. Figure 4B shows the double wastegate valve arrangement of Fig. 1 in another cross-sectional view during operation, Fig. Figure 5 shows a second embodiment of a double wastegate valve arrangement in a perspective side view, Fig. Figure 6 shows the double wastegate valve arrangement of Fig. 5 in another cross-sectional view during operation, Fig. Figure 7 shows the double wastegate valve arrangement of Fig. 5 in another cross-sectional view during operation, Fig. Figure 8A shows a first variant of the second embodiment of a double wastegate valve arrangement in a perspective side view, Fig. Figure 8B shows a second variant of the second embodiment of the double wastegate valve arrangement in a perspective side view. Fig. Figure 8C shows a third variant of the second embodiment of a double wastegate valve arrangement in a perspective side view, and Fig. Figure 9 shows a turbocharger with the double wastegate valve arrangement according to the invention in a schematic representation.

[0033] Fig. Figure 1 shows a first embodiment of a double wastegate valve arrangement 10 in a perspective side view.

[0034] The double wastegate valve assembly 10 comprises two wastegate valves 12, which are movable along a valve longitudinal axis 14. The valve arm 16 is connected to an actuating shaft 18, which rotates about its longitudinal axis, so that the valve arm 16 is moved up or down along the valve longitudinal axis 14. An intermediate plate 20 is loosely arranged between a valve arm 16 and the two wastegate valves 12. Each of the two wastegate valves 12 comprises a valve stem 22, which is guided with clearance through openings in the valve arm 16 and in the intermediate plate 20, so that it can move easily in a direction perpendicular to the valve longitudinal axis 14. One end of the valve stem 22 is secured by a washer 24 resting on the valve arm 16. The two wastegate valves 12 have protruding elements 26 which, in conjunction with the intermediate plate 20, act as a rotation inhibition or anti-rotation device.

[0035] The intermediate plate 20 is pivotable about the valve arm 16 in a direction perpendicular to the valve longitudinal axis 14. The intermediate plate 20 rests on the rotationally symmetrically designed projecting lower surface sections 30 on the rotationally symmetrically designed projecting upper surface sections 28 of the two wastegate valves 12.

[0036] In Fig. 2, which the double wastegate valve arrangement 10 from Fig. As shown in Figure 1 in a cross-sectional view, the valve stems 22 are surrounded by rotationally symmetrical, projecting upper sections 28. These rotationally symmetrical, projecting upper sections 28 can be shaped in various ways around the valve's longitudinal axis 14, e.g., conically, as a chamfer, or spherically. The rotationally symmetrical, projecting upper sections 28 of the wastegate valves 12 are in contact with corresponding rotationally symmetrical, projecting lower sections 30 formed on the intermediate plate 20. Accordingly, the intermediate plate 20 rests on the wastegate valves 12 via rotationally symmetrical, projecting lower sections 30 and the rotationally symmetrical, projecting upper sections 28.If the upper surface sections 28 and the lower surface sections 30 are spherical or spherical, it is advantageous that a radius of the concave spherical lower surface section 30 at the intermediate plate 20 is greater than or equal to a radius of the convex spherical upper surface section 28 at the two wastegate valves 12.

[0037] Furthermore, in the Fig. 1 and Fig. 2 can be seen that the actuating shaft 18 is connected to the valve arm 16 in a symmetrical position in the middle between the two wastegate valves 12.

[0038] As shown in the perspective side view of the double wastegate valve arrangement 10 in Fig. As shown in Figure 3, the actuating shaft 18 can also be connected to the valve arm 16 in a position that is closer to one of the two wastegate valves 12.

[0039] A key feature of the invention is the ability to compensate for deviations between the two wastegate valves 12 and to ensure a proper seal between the two valves 12. This is achieved by providing an intermediate plate 20 between the valve arm 16 and the two wastegate valves 12. This intermediate plate is not rigidly connected to the valve arm 16 but is pivotable. The intermediate plate 20 is pivotable about the valve arm 16 in a direction perpendicular to the longitudinal axis 14 of the valve. Several embodiments are possible to make the intermediate plate 20 pivotable. In the embodiment described in the Fig. In the embodiment shown in 1 to 3, corresponding curved areas 32, 34 are formed on the intermediate plate 20 and the valve arm 16.

[0040] A positively curved region 32 is formed on the intermediate plate 20 and a negatively curved region 34 on the valve arm. In a preferred embodiment, the curved regions 32, 24 are cylindrically shaped, and the radius of the cylindrical region 32 on the intermediate plate 20 is less than or equal to the radius of the cylindrical region 34 of the valve arm 16. Accordingly, an additional force is exerted on the wastegate valve 12, which has not yet contacted its valve seat on the turbine housing, because the intermediate plate 20 rotates towards this valve, while the other wastegate valve 12 is already in contact with its valve seat.

[0041] This allows horizontal offsets 36 of the two wastegate valves 12 to be compensated for, as in Fig. 4A can be seen, which shows the double wastegate valve arrangement 10 of Fig. 1 shows a cross-sectional view during operation.

[0042] Furthermore, deviations in the valve longitudinal axis 14 can also be compensated, as by the inclined valve longitudinal axis 14' in Fig. 4B indicated the double wastegate valve arrangement 10 of Fig. 1 shows a cross-sectional view during operation.

[0043] Furthermore, to minimize noise, disc springs can be incorporated into the double wastegate valve assembly 10, creating constant contact between the components that are arranged with clearance. For example, a disc spring could be installed below the washer 24, between the washer 24 and the valve arm 16.

[0044] In Fig. Figure 5 shows another embodiment of the double wastegate valve arrangement 10 in a perspective side view. The same embodiment is shown in Fig. 6 shown in a side cross-sectional view.

[0045] The double wastegate valve assembly 10 comprises two wastegate valves 12, which are movable along the valve longitudinal axis 14. The valve arm 16 is connected to the actuating shaft 18, which rotates about its longitudinal axis, so that the valve arm 16 is moved up or down along the valve longitudinal axis 14. The intermediate plate 20 is loosely arranged between the valve arm 16 and the two wastegate valves 12. Each of the two wastegate valves 12 comprises the valve stem 22, which is guided through openings in the intermediate plate 20 with clearance, allowing it to move easily in a direction perpendicular to the valve longitudinal axis 14. One end of the valve stem 22 is secured to the intermediate plate 20 by the washer 24. The two wastegate valves 12 have protruding elements 26 which, in conjunction with the intermediate plate 20, act as an anti-rotation device.

[0046] Similar to the previous embodiment of Fig. The double wastegate valve assembly 10 comprises valve stems 22, which are surrounded by rotationally symmetrical projecting upper sections 28. These rotationally symmetrical projecting upper sections 28 can be shaped in various ways around the valve longitudinal axis 14, e.g., conically, as a chamfer, or spherically. The rotationally symmetrical projecting upper sections 28 of the wastegate valves 12 are in contact with corresponding rotationally symmetrical projecting lower sections 30 formed on the intermediate plate 20. Accordingly, the intermediate plate 20 rests on the wastegate valves 12 via rotationally symmetrical projecting lower sections 30 and the rotationally symmetrical projecting upper sections 28.If the upper surface sections 28 and the lower surface sections 30 are spherical or spherical, it is advantageous that a radius of the concave spherical lower surface section 30 at the intermediate plate 20 is greater than or equal to a radius of the convex spherical upper surface section 28 at the two wastegate valves 12.

[0047] In this embodiment, the valve arm 16 includes a pin 40 that engages in a hole 42 in the intermediate plate 20, forming a rotary connection. Accordingly, the intermediate plate 20 is pivotable about the valve arm 16 in a direction perpendicular to the valve's longitudinal axis 14. As already described in the previous embodiment, an additional force is also exerted on the wastegate valve 12, which has not yet contacted its valve seat on the turbine housing, because the intermediate plate 20 rotates towards this valve, while the other wastegate valve 12 is already in contact with its valve seat.

[0048] This allows horizontal offsets 36 of the two wastegate valves 12 to be compensated for, as in Fig. 7 can be seen, which shows the double wastegate valve arrangement 10 of Fig. Figure 5 shows a cross-sectional view during operation. Furthermore, an inclination of the valve longitudinal axis 14 can also be compensated for.

[0049] The pivot connection formed by the pin 40 and the hole 42 is limited by a stop element 46. Various embodiments are possible for the stop element 46.

[0050] Exemplary solutions are found in the Fig. Figures 8A to 8C show the variants of the stop element 46 of the double wastegate valve arrangement 10 in a perspective side view.

[0051] In Fig. 8A is the stop element 46, which forms the anti-rotation device, defined by a pocket 48 in the valve arm 16 and a matching, projecting projection 44 on the intermediate plate 20 that fits into the pocket 48. The inclination between the valve arm 16 and the intermediate plate 20 is limited by a flat surface contact between the projection 44 and the pocket 48.

[0052] In Fig. In 8B, the stop element 46, which forms the anti-rotation device, is defined by a projecting projection 44 on the intermediate plate 20 and a corresponding flat surface on the top of the plate located on the valve arm 16. Similar to the previous version, the inclination is limited by contact with the flat surface.

[0053] In Fig. 8C the stop element 46, which forms the anti-rotation device, is formed by two projecting projections 44 on the valve arm 16 and matching flat surfaces on the sides of the intermediate plate 20.

[0054] As in Fig. As shown in Figure 9, the double wastegate valve arrangement 10 described above can be used with a turbocharger 50 having a double spiral or double spiral 52. The turbocharger 50 can be used in an internal combustion engine powered by diesel, hydrogen, methane, or compressed natural gas.

[0055] The concept according to the invention can be used in all applications with a high wastegate bypass ratio and high durability requirements. The invention leads to reduced exhaust gas leakage through the wastegate valve in turbine housings with two wastegate valves. The invention reduces the overall load on the wastegate system compared to a single-valve solution with the same wastegate connection area.

[0056] The features mentioned above and in the claims, and illustrated in the figures, can advantageously be implemented individually or in various combinations. The invention is not limited to the exemplary embodiments described, but can be modified in various ways within the scope of the skills of a person skilled in the art. List of reference numbers: 10 Double Wastegate Valve Arrangement 12 Wastegate valve 14 Valve longitudinal axis 14' Valve longitudinal axis 16 valve arm 18 Actuating shaft 20 intermediate plate 22 Valve shaft 24 Washer 26 preceding elements 28 Top part of the page 30 Lower part of the page 32 positively curved area 34 negatively curved area 36 offset 40 pens 42 holes 44 Boss 46 Stop element 48 bags 50 turbochargers 52 volutes QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] US 5 996 348 A

[0006] US 8 336 309 B2

[0007] US 11 441 478 B2

[0008] US 11 149 579 B2

[0009]

Claims

[1] Double wastegate valve arrangement (10), comprising: - two wastegate valves (12) which are movable along a longitudinal valve axis (14), each of the two wastegate valves (12) having a rotationally symmetrical projecting upper side section (28) formed around the longitudinal valve axis (14), - a valve arm (16) connected to an actuating shaft (18), and - an intermediate plate (20) which is loosely arranged between the valve arm (16) and the wastegate valves (12), wherein the intermediate plate (20) is pivotable about the valve arm (16) in a direction perpendicular to the longitudinal valve axis (14) and is supported on the rotationally symmetrical projecting upper side sections (28) of the two wastegate valves (12) via rotationally symmetrical projecting lower side sections (30) of the intermediate plate (20). [2] Double wastegate valve arrangement (10) according to claim 1, wherein the rotationally symmetrical projecting underside sections (30) of the intermediate plate (20) and the rotationally symmetrical projecting upper side sections (28) of the wastegate valves (12) are conical or chamfered. [3] Double wastegate valve arrangement (10) according to claim 1, wherein the rotationally symmetrical projecting underside sections (30) of the intermediate plate (20) and the rotationally symmetrical projecting upper side sections (28) of the wastegate valves (12) are spherical. [4] Dual wastegate valve assembly (10) according to claim 3, wherein a radius of the concave bottom portion (30) on the intermediate plate (20) is greater than or equal to a radius of the convex top portion (28) on the two wastegate valves (12). [5] Double wastegate valve arrangement (10) according to one of claims 1 to 4, wherein the actuating shaft (18) is connected to the valve arm (16) in a symmetrical position midway between the two wastegate valves (12). [6] Dual wastegate valve assembly (10) according to any one of claims 1 to 4, wherein the actuating shaft (18) is connected to the valve arm (16) at a position closer to one of the two wastegate valves (12). [7] Double wastegate valve arrangement (10) according to one of claims 1 to 6, wherein projecting elements (26) are formed on the two wastegate valves (12), which, in conjunction with the intermediate plate (20), act as an anti-twist device for the wastegate valves (12). [8] Double wastegate valve assembly (10) according to one of claims 1 to 7, wherein the intermediate plate (20) pivots about the valve arm (16) by corresponding curved portions (32, 34) formed on the intermediate plate (20) and the valve arm (16). [9] Double wastegate valve arrangement (10) according to claim 6, wherein a positively curved region (32) is formed on the intermediate plate (20) and a negatively curved region (34) is formed on the valve arm (16). [10] Double wastegate valve arrangement (10) according to claim 8 or 9, wherein the curved portions (32, 34) are cylindrical and a radius of the cylindrical portion (32) on the intermediate plate (20) is less than or equal to a radius of the cylindrical portion (34) of the valve arm (16). [11] Dual wastegate valve assembly (10) according to any one of claims 1 to 7, wherein the valve arm (16) has a pin (40) which engages in a hole (42) on the intermediate plate (20) and establishes a pivotal connection. [12] Dual wastegate valve assembly (10) according to claim 11, wherein the pivot connection is limited by a stop element (46). [13] Use of a double wastegate valve arrangement (10) according to one of claims 1 to 12 with a twin volute (52) or a double spiral housing. [14] Turbocharger (50) with a double wastegate valve arrangement (10) according to one of claims 1 to 12. [15] Turbocharger (50) according to claim 14 in an internal combustion engine powered by diesel, hydrogen, methane or compressed natural gas.

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