Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
  • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
  • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
  • F01D25/243—Flange connections; Bolting arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
  • F01D9/00—Stators
  • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
  • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
  • F01D9/048—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector for radial admission
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
  • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
  • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
  • F01D25/246—Fastening of diaphragms or stator-rings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2220/00—Application
  • F05D2220/40—Application in turbochargers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2240/00—Components
  • F05D2240/10—Stators
  • F05D2240/15—Heat shield
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2250/00—Geometry
  • F05D2250/70—Shape
  • F05D2250/71—Shape curved
  • F05D2250/711—Shape curved convex
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2260/00—Function
  • F05D2260/30—Retaining components in desired mutual position
  • F05D2260/31—Retaining bolts or nuts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2260/00—Function
  • F05D2260/30—Retaining components in desired mutual position
  • F05D2260/37—Retaining components in desired mutual position by a press fit connection

Definitions

• the present disclosure relates to a turbine housing clamp assembly for a turbine, and a turbine having a turbine housing clamp assembly.
• Turbines in particular radial turbines, are known from the prior art, which have a bearing housing, a turbine housing, a heat shield and a nozzle ring.
• the heat shield is clamped axially between the bearing housing and the nozzle ring, and radially through the turbine housing; or the nozzle ring is constrained axially by the bearing housing and radially by the turbine housing.
• EP 1 428 983 A1 describes an exhaust gas turbine housing.
• a clamped connection for a turbine according to claim 1 Furthermore, the object is achieved by a turbine with a turbine housing clamped connection according to claim 14 and by the use of a turbine housing clamped connection according to claim 15. Further embodiments, modifications and improvements will become apparent from the following description and the appended claims.
• a turbine housing clamp assembly for a turbine, in particular a radial exhaust gas turbine, is provided.
• the turbine housing clamp assembly has a bearing housing and a turbine housing, and a clamping component a clamping flange clamped between a bearing housing clamping portion of the bearing housing and a turbine housing clamping portion of the turbine housing.
• the clamping flange has a clamping surface on the bearing housing side with a convexly curved clamping surface area.
• the convexly curved clamping surface area defines a minimum radius of curvature.
• a ratio of the minimum radius of curvature and an inner radius of the clamping surface is at least 0.1 and/or at most 10, and preferably at least 0.5 and/or at most 2.0, and even more preferably at least 1.0 and/or at most 1.4.
• Figure 1 shows a turbine housing clamp assembly according to a
• Figure 2 shows a turbine housing clamp assembly according to a
• FIG. 3a shows a clamping component according to one embodiment.
• FIG. 3b shows a clamping component according to an embodiment
• FIGS. 1 and 2 each show a turbine housing clamp assembly according to one embodiment, with a clamping surface of a clamping flange on the bearing housing side being shown in greatly simplified form.
• the clamping assembly is shown in an installed state in a turbine.
• Exemplary configurations of the clamping surface on the bearing housing side are illustrated in FIGS. 3a and 3b.
• a turbine housing clamp assembly 100 for a turbine 200, 300, particularly a radial exhaust gas turbine is provided in accordance with a general aspect of the invention.
• the turbine housing clamp assembly 100 has a bearing housing 110 and a turbine housing 120 .
• the turbine housing clamping assembly 100 has (at least) one clamping component 130 , 140 with a clamping flange 137 , 147 clamped between a bearing housing clamping section of the bearing housing 110 and a turbine housing clamping section of the turbine housing 120 .
• the clamping flange 137, 147 can in each case be clamped or clamped directly (i.e. directly without other components arranged in between) by the bearing housing 110 and the turbine housing 120 or also indirectly (i.e. between clamping flange and bearing housing 110 or turbine housing 120 further components are arranged).
• the clamping component is a heat shield 130.
• FIG. 1 shows a clamp assembly 100 with a heat shield 130 as a clamp component.
• the heat shield 130 is typically a generally disk-shaped bulkhead for shielding the bearing housing 110 from hot gases or exhaust gases flowing through an inlet duct of the turbine.
• the turbine housing clamp assembly 100 preferably also has a nozzle ring 140—here as a further clamp component.
• the heat shield 130 can be clamped axially with its clamping flange 137 between the bearing housing clamping section of the bearing housing 110 and the nozzle ring 140 and clamped by the turbine housing clamping section of the turbine housing 120 .
• the heat shield 130 can also include one or more pads or edges 121 , 144 for resting on a pad or edge 141 of the bearing housing 110 and/or for laying on the turbine housing 120 , which with Screws 142 can be fixed on the turbine housing. By tightening the lugs 145, the heat shield 130 and the nozzle ring 140 are clamped between the turbine housing 120 and the bearing housing 110 and correspondingly fastened in the axial direction.
• a, for example, circumferential, cylindrical inner surface of turbine housing 120 preferably rests on a, for example, circumferential, cylindrical outer surface of bearing housing 110 and is thus correspondingly opposite a turbine axis of the turbine and that arranged thereon Turbine wheel 143 centered.
• the clamping member 130, 140 is a
• Nozzle ring 140 In FIG. 1, the nozzle ring 140 is also provided as another such clamping component.
• the turbine housing clamp assembly 100 may further include a heat shield 160 .
• the heat shield 160 can be arranged radially further inwards than the nozzle ring 140 and can be braced axially by a second bearing housing clamping section. Furthermore, the heat shield 160 can be braced axially and radially by the nozzle ring 140, for example by means of a support of the nozzle ring 140.
• the heat shield 160 can typically be a substantially disk-shaped partition for shielding the bearing housing from hot gases or exhaust gases which flow through an inflow channel of the turbine stream. Heat shield 160 may further include one or more pads for abutting bearing housing 110 and/or abutting nozzle ring 140.
• the clamping flange 137, 147 of the clamping component - for example at least one of the
• the clamping components 130, 140 shown in FIGS. 1 and 2 have a clamping surface 131 on the bearing housing side with a convexly curved clamping surface region 132.
• FIGS. 3a and 3b embodiments of the clamping surface 131 on the bearing housing side are illustrated using the example of the clamping flange 137 of a heat shield 130.
• the clamping surface on the bearing housing side can be configured accordingly if the clamping component is not a heat shield and is, for example, a nozzle ring 140 , and the description of clamping flange 137 can also be used analogously for clamping flange 147 .
• the clamping component 130, 140 (as well as the bearing housing and the turbine housing) is configured to completely surround a turbine axis.
• the clamping component 130,140 can have a substantially disc-shaped cross section on.
• the clamping flange is preferably clamped over the entire circumference of the clamping component 130 , 140 between the bearing housing clamping section of the bearing housing 110 and the turbine housing clamping section of the turbine housing 120 .
• the clamping surface is preferably arranged radially on the outside of the clamping flange 137 .
• 3a and 3b each show examples of clamping surface 131 on the bearing housing side with a convexly curved clamping surface area 132 arranged radially on the outside.
• the axial direction is defined by the turbine axis, while the radial direction extends perpendicularly to the axial direction.
• the radial direction R from radially inside to radially outside
• the axial direction A are each symbolized by an arrow.
• the radially outer clamping surface portion 132 is convexly curved in a cross-sectional view including a turbine axis.
• the convexly curved clamping surface area 132 defines a minimum radius of curvature R K .
• the radius of curvature R K is symbolized by a double arrow in FIG. 3a.
• the convexly curved clamping surface area 132 also defines a segment of a circle of curvature U K .
• the segment of the circle of curvature is slightly or gently convexly curved or rounded.
• Clamping surface area 132 on the bearing housing side correspond to an axially outermost point of the convexly curved clamping surface area 132, as shown, for example, in FIG. 3b.
• the radially inner end 133 (seen in the resting state) has the smallest distance from the bearing housing clamping section and/or is clamped directly to the bearing housing clamping section.
• a point of the convexly curved clamping surface area 132 that is spaced apart from the radially inner end 133 can also correspond to an axially outermost point on the bearing housing side, as shown, for example, in FIG. 3a.
• an axially outermost point of the Circle of curvature segment U K also be arranged at any location along the circle of curvature segment U K.
• the bearing housing-side clamping surface 131 can be one or more
• the clamping surface on the bearing housing side defines at least one further clamping surface area.
• the further clamping surface area is preferably a radially inner clamping surface area and/or a radially outermost clamping surface area.
• FIG. 3b shows a clamping surface 131 on the bearing housing side with the convexly curved clamping surface region 132, a radially inner clamping surface region and a radially outermost clamping surface region.
• Clamping surface areas are preferably not convexly curved, but are essentially flat.
• the radially inner clamping surface area and/or the radially outermost clamping surface area can also have a convex-shaped section with a radius of curvature that is smaller than the minimum radius of curvature of the convexly curved clamping surface area 132.
• FIG. 3a illustrates a clamping surface 131 on the bearing housing side, in which the radially outer end 135 of the convexly curved clamping surface area 132 corresponds to the radial end 134 of the clamping surface on the bearing housing side.
• the convexly curved clamping surface area is preferably a radially outer one
• the clamping surface on the bearing housing side can also have the radially inner clamping surface area.
• the convexly curved (radially outer) clamping surface area 132 adjoins the radially inner clamping surface area continuously, preferably tangentially.
• FIG. 3b shows a continuous tangent transition from the radially inner end 133 to the flat radially inner clamping surface area.
• the radially inner clamping surface region preferably runs in a straight line in the radial direction. There can thus be a gentle, continuous transition between the convexly curved clamping surface area and the radially inner clamping surface area. This can also be a high local Surface pressure can be counteracted, both in the stationary and in the transient operating state.
• the radially inner clamping surface area can be designed to be essentially flat (seen in the radial direction).
• the clamping surface on the bearing housing side can have the radially outermost clamping surface area.
• the radially outermost clamping surface area can be continuous, preferably tangentially continuous, to the convexly curved (radially outer) clamping surface area.
• the radially outermost clamping surface area can be essentially flat (seen in the axial direction) and deviate slightly or gently from a flat course in the area of a transition to the convexly curved clamping surface area.
• An inner radius D R of the clamping surface is the radius measured starting from the center of gravity of the turbine axis or the center of gravity of a cross-sectional view of the clamping component.
• the inner radius D R is the radius measured in the idle state of the turbine housing clamped assembly or the turbine. For example, under high load conditions, a slight expansion and thus a change in the inner radius D R can occur due to heating. All characteristics or parameters disclosed herein are values measured at rest, unless expressly stated otherwise.
• the inner radius D R is the radius of the convexly curved clamping surface area, preferably the radius at the axially outermost point of the curved clamping surface area as seen on the bearing housing side. In some embodiments, the inner radius D R is the radius of the radially inner end 133. In other words, the inner radius D R is preferably the radial distance between the center of gravity of the turbine axis and the axially outermost point of the curved clamping surface area, viewed on the bearing housing side .
• the bearing housing can be made of the GGG40 alloy and the clamping component can be made of a higher-alloy, mostly heat-resistant material.
• the clamping component is typically located in a fluid channel and is therefore hotter than the contact point between the bearing housing and the clamping component.
• the clamping component heats up more quickly during operation and typically has a greater coefficient of thermal expansion than the bearing housing. Due to this asymmetrical heat input, there is a relative movement of the clamping component with respect to the bearing housing during the heating process and under changing load conditions.
• the turbine housing clamp assembly has a clamping component 130 with the convexly curved clamping surface area 132, through which wear of the components, and in particular the bearing housing, is significantly reduced.
• a clamping surface area with a slightly or gently convexly curved shape, both in terms of a "hot" condition (i.e. at high load conditions or at high temperatures of a fluid in the radial turbine), as well as the conditions during an entire warm-up process, as well as in a Resting state, a broad contact of the clamping surface is ensured and thus a high local surface pressure can be prevented.
• the clamping component can tilt slightly during the heating process without excessive local contact pressure occurring in a contact area between the bearing housing clamping section and the bearing housing-side clamping surface compared to a cold state.
• the inventors have also recognized that a high local surface pressure and associated fatigue wear can be counteracted most effectively if the ratio of the minimum radius of curvature and an inner radius of the clamping surface is at least 0.1 and/or at most 10, preferably at least 0.5 and/or or at most 2.0, and more preferably at least 1.0 and/or at most 1.4.
• the curved portion is at least 0.1 and/or at most 10, preferably at least 0.5 and/or or at most 2.0, and more preferably at least 1.0 and/or at most 1.4.
• Tilting here means that a radially inner part of the clamping flange is moved axially away from the bearing housing relative to a radially outer part of the clamping flange and/or is moved towards the turbine housing (tilts).
• the tilting can include a rolling movement and/or a sliding movement of the clamping surface.
• tilting can also take place without a fixed tilting point of the clamping surface being necessary.
• a flat contact is not necessarily to be understood as a full-surface contact between the bearing housing clamping section and the convexly curved clamping surface area.
• the curved clamping surface area is set up to ensure a flat contact with the bearing housing clamping section, however, the formation of a high local surface pressure is prevented.
• the convexly curved clamping surface area is thus set up to counteract wear on the bearing housing.
• an axial offset t between an axially outermost point of the curved clamping surface area 132 on the bearing housing side and the radially outer end 135 of the curved clamping surface area 132 is at least 0.01 mm and/or at most 0.5 mm, preferably 0.02 mm and/or at most 0.2 mm , and more preferably at least 0.03 mm and/or at most 0.1 mm.
• the axial offset t is illustrated by a double arrow.
• the axial offset can refer to the maximum achievable radius of curvature R K during operation, and in particular to the idle state. At higher load conditions, the clamping flange can tilt, which means that the axial offset t can decrease.
• an axial offset t between the radially inner end 133 of the curved clamping surface area 132 and the radially outer end 135 of the curved clamping surface area 132 can be at least 0.01 mm and/or at most 0.5 mm, preferably 0.02 mm and/or at most 0.2 mm , and more preferably at least 0.03 mm and/or at most 0.1 mm.
• the radially outer end 135 is offset axially toward the turbine housing due to the convex curvature.
• the radially inner end 133 is axially offset towards the bearing housing in some embodiments due to the convex curvature (as shown for example in Figure 3b), and in other embodiments also axially offset towards the turbine housing due to the convex curvature (as shown for example in Figure 3a).
• the radially outer end 135 can be the radially outermost point that can be reached during operation, with which a clamping with the bearing housing clamping section of the bearing housing 110 takes place.
• the minimum radius of curvature R K of the convexly curved clamping surface area 132 is at least 20 mm and/or at most 1000 mm, and preferably at least 50 mm and/or at most 500 mm, more preferably 100 mm and/or at most 200 mm. and most preferably at least 140mm and/or at most 160mm. In an exemplary embodiment, the minimum radius of curvature R K is 150 mm. A radius of curvature R K in the aforementioned range ensures a curvature which deviates sufficiently from a flat clamping surface area and at the same time does not have an excessive curvature. Additionally or alternatively, the inner radius D R of the clamping surface or of the convexly curved clamping surface area 132 can be at least 20 mm and/or at most 300 mm, preferably at least 100 and/or at most 140 mm.
• the curved clamping surface area 132 can have a radial extent of at least 0.5 mm and/or at most 10 mm.
• the curved clamping surface area 132 preferably has a radial extent of at least 3 mm and/or at most 6 mm.
• a radial distance between the radially inner end 133 of the curved clamping surface area 132 and the radial end 134 of the clamping surface on the bearing housing side can be at least 2 mm and/or at most 20 mm, preferably at least 6 mm and/or or at most 10 mm.
• Clamping surface area 132 and the inner radius D R of the clamping surface or of the convexly curved clamping surface area 132 can be at least 0.005 and/or at most 0.1, preferably at least 0.02 and/or at most 0.05.
• Offset t and the radial extent of the curved clamping surface area 132 is at least 5*10 3 and/or at most 0.02, and preferably at least 8*10 3 and/or at most 0.015.
• a ratio in the aforesaid range ensures a curvature which deviates sufficiently from a flat clamping surface area and at the same time does not lead to an excessive curvature.
• the curved clamping surface area 132 and in particular the radially inner one
• a central angle alpha a of the segment of a circle of curvature U K can be at least 0.5° and/or at most 4°, preferably at least 1.2° and/or at most 2.0°.
• the central angle alpha a is illustrated in FIG. 3a.
• a ratio of the axial offset t and the radius of curvature R « can be at least 2 * 10 4 and/or at most 2*10 3 , and preferably at least 3*10 4 and/or at most 8*10 4 .
• a tangent angle of the curved clamping surface area 132 relative to the radial direction can be at least 0.5° and/or at most 4°, preferably at least 1.2° and/or at most 2.0°. Furthermore, in a cross-sectional view containing the turbine axis, at least one tangent angle of curved clamping surface area 132 relative to the radial direction can be at least 0.5°, preferably at least 1.2°, and/or all tangent angles of curved clamping surface area 132 can be at most 4°, preferably at most, relative to the radial direction 2.0°.
• the further sides of the clamping flange are not particularly limited according to the present disclosure and can be designed according to the clamping flanges known in the prior art.
• a turbine preferably a centrifugal turbine 200, 300.
• the turbine has the turbine housing clamp assembly according to one of the embodiments described herein.
• the turbine is a power turbine and/or an exhaust gas turbine.
• the exhaust gas turbine can be an exhaust gas turbocharger turbine.
• a turbocharger comprising the turbine according to any of the embodiments described herein.
• the turbine may further include a turbine wheel 143 .
• One aspect relates to the use of a turbine housing clamp assembly for a radial turbine to counteract wear on a bearing housing of the radial turbine.
• the turbine housing clamp assembly and/or the radial turbine can be configured according to any of the embodiments disclosed herein.
• the turbine housing clamp assembly has a convexly curved clamping surface area, in particular according to one of the embodiments disclosed above.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Supercharger (AREA)

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Publications (1)

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ID=76829341

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• 2022
  • 2022-07-06 CN CN202280046383.9A patent/CN117916453A/zh active Pending
  • 2022-07-06 WO PCT/EP2022/068775 patent/WO2023280935A1/de active Application Filing
  • 2022-07-06 KR KR1020247003656A patent/KR20240026236A/ko active Search and Examination
  • 2022-07-06 EP EP22735489.1A patent/EP4367370A1/de active Pending

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