WO2015185408A1 - A spiral turbine casing of a turbocharger - Google Patents

A spiral turbine casing of a turbocharger Download PDF

Info

Publication number
WO2015185408A1
WO2015185408A1 PCT/EP2015/061682 EP2015061682W WO2015185408A1 WO 2015185408 A1 WO2015185408 A1 WO 2015185408A1 EP 2015061682 W EP2015061682 W EP 2015061682W WO 2015185408 A1 WO2015185408 A1 WO 2015185408A1
Authority
WO
WIPO (PCT)
Prior art keywords
spiral casing
base wall
turbocharger
wall
turbine
Prior art date
Application number
PCT/EP2015/061682
Other languages
French (fr)
Inventor
Mark Rankenberg
Koen KRAMER
Berend JONKERS
Rogier LAMMERS
Original Assignee
Mitsubishi Turbocharger And Engine Europe B.V.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Turbocharger And Engine Europe B.V. filed Critical Mitsubishi Turbocharger And Engine Europe B.V.
Priority to DE112015002597.9T priority Critical patent/DE112015002597T5/en
Publication of WO2015185408A1 publication Critical patent/WO2015185408A1/en

Links

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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • 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
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/54—Building or constructing in particular ways by sheet metal manufacturing

Definitions

  • the invention relates to a spiral turbine casing, a turbocharger turbine, a turbocharger, the use of such a turbocharger and a method of manufacturing a turbine spiral casing .
  • a spiral casing of a turbocharger turbine is for example known from DE-10.2004.039.477.
  • the known turbocharger turbine is partly shown in appended figure 1.
  • the spiral casing (10) comprises a base wall and a spiral casing wall.
  • the base wall of the spiral casing is a base plate (15).
  • the spiral casing is provided by welding the spiral casing wall (11) to the base plate (15) forming a connection between the spiral casing wall and the base plate.
  • the weld (16) has a closed or endless form around the central axis of the turbine housing (10) .
  • the base plate and the spiral casing wall are made of sheet metal, wherein the base plate in the known turbocharger turbine is a flat sheet metal plate with a constant thickness.
  • the known turbocharger turbine comprises further a turbine wheel and an exhaust gas control device for controlling the exhaust gas flow from the spiral casing to the turbine wheel.
  • the spiral casing has a special designed base wall, in that inside the spiral casing a portion of the base wall has a curvature.
  • This curvature inside the spiral casing optimizes in use the flow properties of exhaust gasses inside the spiral casing, e.g. optimizes the flow towards the central axis of the spiral casing.
  • This central axis coincides with the central axis of a turbine wheel of a turbocharger turbine such that in use the turbine wheel can be driven more efficiently by means of the turbine spiral casing according to claim 1. Further, undesired turbulences inside the spiral casing can be reduced by means of the curvature.
  • Such a spiral casing design improves the overall efficiency of the turbocharger turbine.
  • the base wall has a varying thickness to provide the base wall curvature inside the spiral casing.
  • the thickness of the base wall is measured in a (horizontal) direction extending parallel to the central axis.
  • the base wall according to this embodiment requires a varying thickness of the base wall to provide an inside surface of the base wall having a curvature. For example, it is possible to provide such a curvature by gradually increasing the thickness of the base wall from the end of the base wall facing the central axis towards the connection.
  • the side of the base wall opposite to the inside of the spiral casing can be fiat or substantially flat. This flat side of the base wall can advantageously be used to connect the spiral casing to other parts of the turbocharger turbine or a bearing housing of a turbocharger.
  • the base wall is a base plate having a constant thickness.
  • the base wall preferably extends in a longitudinal (vertical) direction and has vertically opposing ends, i.e. an end surface closer to the center axis of the spiral casing and an end surface further away of the center axis.
  • the thickness corresponds to the width of the base plate measured in a (horizontal) direction extending transversally to the longitudinal direction, i.e. the width is the distance between the side surfaces which extend between the end surfaces.
  • the base plate extends around the center axis of the spiral casing and has a disc or ring like shape with a through hole in the middle, wherein the center of the hole coincides with the center axis of the spiral casing.
  • the radius of the through hole is larger than the distance between the vertically spaced end surfaces of the base wall.
  • constant thickness has to be understood as having a thickness that only varies due to manuf cturing tolerances.
  • the curvature of the base plate is provided by bending the base plate such that the outer side of the base plate wall opposite to the inner side of the spiral casing is also curved.
  • the base plate is a sheet metal plate, which can be bent relatively easily.
  • the bent base plate provides additional advantages for assembling a turbine in a turbocharger , because the bent base plate can be used for clamping and/or to increase the contact pressure between parts of a turbocharger.
  • the bend in the base plate can also be used to provide an pre-tensioned contact between the spiral casing and other components of a turbocharger turbine or turbocharger, i.e. by means of the bend in the base plate such a contact is more flexible and more resistant to thermal stresses experienced for example during warming up.
  • the walls or inner surface parts of the base wall and the spiral casing wall are substantially V-shaped towards the connection. Such V-shaped walls further optimize the flow properties of exhaust gasses inside the spiral casing.
  • the inner surfaces of the spiral casing wall and the base wall towards the connection can be bent, wherein the curvature of the base wall may provide one bent wall part of the V-shape.
  • the base wall may also have more than one radius of curvature.
  • the invention also relates to a turbocharger turbine comprising a turbine spiral casing as discussed above.
  • the turbocharger turbine comprises an exhaust gas control device with a nozzle passage defined between a nozzle mount and a nozzle plate.
  • the exhaust gas control device comprises a nozzle passage defined between a nozzle mount and a nozzle plate, wherein the dimensions of the nozzle passage can be varied by means of vanes to control an exhaust gas flow between the spiral casing and a turbine wheel.
  • the base wall contacts the nozzle mount without being connected thereto. This contact provides a fluid tight connection between the nozzle mount and the base wall.
  • the invention relates to a turbocharger comprising the above described turbine.
  • a turbocharger has a compressor and between the turbine and the compressor a bearing housing.
  • the turbine can be connected to the bearing housing by means of a clamping mechanism using a connecting element and a clamping element.
  • the exhaust gas control device in the turbocharger according to the present invention can be clamped between the bearing housing and the base wall by means of the clamping mechanism, i.e. the exhaust gas control device is clamped without being connected to other components of the turbocharger .
  • Such clamping contact is more flexible and more heat resistant than a welded connection, i.e. the exhaust gas control device is supported by clamping, wherein the flexible clamping contact is able to withstand relative large temperature differences for a relative long period of time.
  • Figure 1 shows a part of a turbocharger according to the prior art in axial section
  • Figure 2a shows schematically a part of a turbocharger according to a first embodiment in axial section
  • Figure 2b shows schematically an enlarged view of a part of the turbocharger shown in figure 2a;
  • Figure 3 shows schematically a part of a turbocharger according to a second embodiment in axial section
  • Figure 4 shows schematically a part of a turbocharger according to a third embodiment in axial section
  • Figure 5 shows schematically a part of a turbochanger comprising a turbine 302 with a double wall spiral casing
  • FIG. 1 partly shows a turbocharger turbine known from the prior art.
  • a turbocharger turbine known from the prior art.
  • FIG. 1 A part of a turbocharger 1 according to a first embodiment is shown in figures 2a and 2b showing a part of a turbocharger turbine 2 and a part of a bearing housing 3.
  • the figures 3 and 4 show parts of a turbocharger 101; 201 according to a second and third embodiment.
  • the turbine 2; 102; 202 comprises a single flow spiral casing 8, 108; 208.
  • the turbocharger turbine 2; 102; 202 comprises a turbine wheel (not shown) , an exhaust gas control device 10; 210 and a spiral casing 8; 108; 208.
  • the spiral casing 8; 108; 208 comprises a spiral casing wall 4; 104; 204 and a base plate 5; 205.
  • the base plate 5 (figures 2a, b and 3) has a first end part 6 and a second end part 7, wherein the second end part 7 of the base plate 5 extends transversely to the central axis (not shown in figures 2a, b) of the turbine 2.
  • the central axis of the turbine 2 corresponds to the dotted line 28 shown in figure 1.
  • the central axis of the turbine 2 coincides with the central axis (not shown) of the spiral casing 8; 108; 208.
  • the spiral casing 8; 108; 208 is provided by connecting a first bent end part 9; 109; 209 of the spiral casing wall 4; 104; 204 to the first end part 6; 206 of the base plate 5; 205 such that the spiral casing 8; 108; 208 has a connection 51; 251 between the spiral casing wall 4; 104; 204 and the base plate 5; 205.
  • the connection 51; 251 fully extends around the central axis of the turbine 2; 102; 202.
  • connection 51; 251 is provided by tungsten inert gas (TIG) welding and/or laser beam welding (LBW) .
  • TIG tungsten inert gas
  • LW laser beam welding
  • the fully around the central axis extending endless form of the connection 51; 251 can be substantially circular.
  • the inner surface 53 of the spiral casing wall 4; 104; 204 and the inner surface 55 of the base plate 5; 205 are V-shaped 57 towards the connection 51; 251.
  • Inside the spiral casing 8; 108; 208 between the connection 51; 251 and the second end part 7; 207 of the base plate 5; 205 at least a portion of the base plate 5 has a curvature 61; 261.
  • the curvature 61 of the inside surface 59 continues in a continuous or smooth way to the connection 51 such that the curvature 61 also provides one of the V-shaped wall parts towards the connection 51, i.e. the curvature 61 forms the inner surface 55 of the base plate 5.
  • the V-shaped inner surfaces 53, 55 of the spiral casing wall 4 and the base plate 5 are bent.
  • the base plate 5; 205 has a first outer surface 62; 262, an opposite second surface 64; 264 which is located closer to the central axis than the first surface 62; 262 and two side surfaces 66, 68; 266; 268 extending between the first surface 62; 262 and the second surface 64; 264, wherein one of the two side surfaces is an outer side surface 68; 268 and a portion of the other side surface 66; 266 of the base plate 5; 205 extending between the connection 51; 252 and the other side surface 66; 266 is part of the inside surface of the spiral casing.
  • the part of the inside surface of the spiral casing further comprises the second surface 64 of the base plate 5.
  • the second surface 264 of the base wall 205 is positioned against a turbine element.
  • the second end 207 of the base plate 205 has the curvature 261, i.e. the second end 207 does not extend transversely to the central axis.
  • the base plate 5; 205 has an edge 72; 272 between the second surface 64; 264 and the other side surface 66; 266 of the base wall, wherein a vertically extending first virtual plane ⁇ not shown) extends between the central axis and the edge 72; 272.
  • the first virtual plane lies further from the center 95 inside the spiral casing than a second virtual plane extending between the connection and the central axis.
  • the horizontal distance between the first virtual plane and the second virtual plane corresponds to two times the thickness of the base plate 5; 205.
  • this distance is larger, wherein the maximum distance is two times smaller than the horizontal distance between the second virtual plane and the inside center 95 of the spiral casing 102.
  • the distance D (figure 3) between the connection 51 and an inside surface 63 of the second end part 7 of the base wall 5 or the edge 72 corresponds to about five times the thickness of the second end part 7 of the base wall 5.
  • the exhaust gas control device 10; 210 of the turbocharger turbine 2; 102; 202 comprises a nozzle mount 79.
  • the nozzle mount 79 is in the turbocharger according to the present invention clamped between the base plate 5; 205 and a turbine-side flange 77 of the bearing housing 3.
  • a more flexible clamping can be achieved such that the thermal stresses due to the temperature differences in use can be compensated.
  • Such flexible clamping provides a reliable fluid-tight sealing between the base plate 5; 205 and the nozzle mount 79.
  • the nozzle mount 79 supports by means of supporting pins 80 a nozzle plate 82 (figure 2a) .
  • the nozzle mount 79 and nozzle plate 82 define a nozzle passage 84 for guiding gasses from the spiral casing 8 to a turbine wheel (not shown) .
  • the exhaust gas flow between the spiral casing and the turbine wheel can be controlled by means of vanes (not shown) varying the dimensions of the nozzle passage.
  • the bearing housing 3; 103; 203 of the turbocharger 1; 101; 201 houses a common shaft ⁇ not shown) connecting a compressor wheel (not shown) with the turbine wheel.
  • the exhaust-gas- driven turbine 2; 102; 202 supplies the drive energy for the compressor.
  • the bearing housing 3; 103; 203 comprises a compressor-side flange 71, a central section 73 which is integrally connected to the flange 71, and a turbine-side section 75 which has the turbine-side flange 77 which is integrally connected to the central section 73.
  • the central housing section 73, the compressor-side flange 71 and the turbine-side flange 77 are formed in one piece.
  • the turbine 2; 102; 202 is connected to the flange 77 by means of an annular clamping element 81.
  • the bearing housing 3; 103; 203 and the turbine 2; 102; 202 differ from the turbocharger of the prior art shown for example in figure 1, in that the connection between the bearing housing 3, 103; 203 and the turbine 2; 102; 202 is different, in particular the design of the base plate 5; 205 and the design of the connecting element 85; 185.
  • the connecting element 85; 185; 285 fully extends around the central axis of the turbine 2; 102; 202.
  • the connecting element 85; 185; 285 is preferably made of the same material as the base plate, i.e. sheet metal.
  • the connecting element 85; 185; 285 can also be identified as upper casing.
  • the base plate 5; 205, the spiral casing wall 4; 104; 204 and the connecting element 85, 185; 285 are made from sheet metal having a thickness ⁇ 3 mm, preferably a thickness ⁇ 2 mm such as 1,5 mm.
  • the thickness of the base plate 5 between the first end 6 and the second end 7 does not change neglecting manufacturing tolerances.
  • the connecting element 85; 185; 285 comprises:
  • the middle portion 89; 189; 289 of the connecting element 85; 185; 285 preferably extends parallel to the central axis of the turbine 2; 102; 202 / turbocharger 1; 101; 201.
  • the first end portion 87; 187; 287 preferably has an obtuse angle ⁇ (figure 3) with the middle portion 89; 189; 289, preferably about 135 degrees.
  • the second end portion 91; 191; 289 preferably extends transversely to the middle portion 89; 189; 289 of the connecting element 85; 185; 285.
  • the angle ⁇ (figure 3) between the second end portion 91; 191; 291 and the middle portion 89; 189; 289 of the connecting element 85; 185; 285 may range between 45-315 degrees, preferably between 80-100 degrees (figure 3 ⁇ or 260-280 degrees (figures 2a, b and figure 4) .
  • the connecting element 85 may also comprise an intermediate portion 93 between the middle portion 89 and the second end portion 91 as shown in figures 2a, 2b.
  • the intermediate portion 93 may have a first angle ⁇ (figure 2b) with respect to the middle portion (or horizontal) of for example 45 degrees and a second angle ⁇ (figure 2b) with respect to the second end portion 91 (or vertical) of for example 45 degrees.
  • the second end portion 91 of the connecting element 85 shown in figures 2a, 2b extends at least partially parallel to the first end part 6 of the base plate and may be connected thereto, for example by welding.
  • the second end portion 191 of the connecting element 185 shown in figure 3 extends at least partially parallel to the first end part 7 of the base plate 5 and may be clamped or connected thereto for example by welding.
  • the second end portion 291 of the connecting element 285 shown in figure 4 extends at least partially parallel to a middle section 298 of the base plate 205 and is connected thereto for example by welding.
  • the connecting element 85; 185; 285 By means of the connecting element 85; 185; 285 a reliable and relatively strong connection can be provided between the turbine 2; 102; 202 and the bearing housing 3; 103; 203.
  • the connecting element 85; 185; 285, the base plate 5; 205 and the clamping element 81 the nozzle mount 79 can be clamped between the second surface 264 of the base plate 205 (figure 4) or the outer side surface 64 of the base plate 5 and the turbine-side flange 77 of the bearing housing 3; 103; 203.
  • a relatively high contact force in a direction indicated by arrow PI (figure 2a) can be generated for clamping the nozzle mount 79.
  • the nozzle mount 79 is advantageously clamped to withstand material expansion and material contraction due to temperature differences in use of the turbine 2; 102; 202.
  • the maximum angle a between the ends of the legs of the V-shaped inner surfaces 57 is relatively large by means of the curvature 61 of the base plate 5.
  • the maximum angle ex (figure 3) is preferably smaller than 180 degrees.
  • the maximum angle a. is larger than 60 degrees, preferably larger than 90 degrees.
  • the angle cx will vary around the central axis of the turbine.
  • the connected end portions 6, 9; 109; 209 of the spiral casing wall 4; 104; 204 and the base wall 5; 205 extend parallel to each other and extend transversely to the central axis of the turbine.
  • This provides a reliable fluid tight seal and a strong connection between the base plate 5; 205 and the spiral casing wall 4; 104; 204.
  • the (vertical) length of the connected end portions 6; 9; 109; 209 is more than two times the thickness of the base plate 5; 205, preferably more than two and a half times the thickness of the base plate 5; 205.
  • spiral casing 8 with an inner surface 55 of the base plate wall 5 being less continuous or being less smooth with the curvature 61 compared to the embodiments shown in figures 2a, 2b and 3.
  • the base plate 205 shown in figure 4 is for example flat towards the connection 251.
  • the base plate 205 has a curved second end part 207, which provides the curvature 261 of the inside surface of the base plate 205.
  • the curvature of the inside surface of the base wall may have more than one radius of curvature .
  • the base wall is not a base plate, but a base wall having a varying thickness to provide the curvature of the inside surface.
  • a side of the base wall opposite to the spiral casing can be flat or substantially flat, whereas the side facing the inside of the spiral casing comprises a curvature.
  • the thickness of the base wall at least partly varies to provide a curvature on the inside surface of the base wall .
  • a flat or partly flat outer side of the base wall can be used to easily fix and/or connect the turbine to the bearing housing.
  • Turbocharger assembly comprising a bearing housing and a turbine, wherein the bearing housing and the turbine are connected by means of a connecting element 85; 185; 285, wherein the connecting element 85; 185; 285 is preferably made of sheet metal, wherein an end portion of the connecting element in contact with a base plate 5; 205 of a spiral casing has an angle ⁇ of 45-315 degrees with respect to a middle or center portion of the connecting element.
  • the base plate has no curvature.
  • the end portion is connected to the base plate for example by welding.
  • the side of the connecting element opposing the base plate can be in contact with a nozzle mount of an exhaust gas control device for controlling the exhaust gas flow to the turbine.
  • a clamping element as indicated above with reference sign 81 it is possible to clamp the nozzle mount between the bearing housing and the base plate during assembling of a turbocharger.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Abstract

The invention relates to a spiral turbine casing comprising a spiral casing wall and a base wall. The base wall and the spiral casing wall have a connection which fully extends around a central axis, wherein a portion of the base wall is part of an inside surface of the spiral casing, said portion of the base wall has a curvature. The invention relates further to a turbocharger turbine comprising the above turbine spiral casing, and a turbocharger comprising such a turbocharger turbine.

Description

Title: A spiral turbine casing of a turbocharger
The invention relates to a spiral turbine casing, a turbocharger turbine, a turbocharger, the use of such a turbocharger and a method of manufacturing a turbine spiral casing .
A spiral casing of a turbocharger turbine is for example known from DE-10.2004.039.477. The known turbocharger turbine is partly shown in appended figure 1. The spiral casing (10) comprises a base wall and a spiral casing wall. The base wall of the spiral casing is a base plate (15). The spiral casing is provided by welding the spiral casing wall (11) to the base plate (15) forming a connection between the spiral casing wall and the base plate. The weld (16) has a closed or endless form around the central axis of the turbine housing (10) . The base plate and the spiral casing wall are made of sheet metal, wherein the base plate in the known turbocharger turbine is a flat sheet metal plate with a constant thickness. The known turbocharger turbine comprises further a turbine wheel and an exhaust gas control device for controlling the exhaust gas flow from the spiral casing to the turbine wheel.
It is a drawback of the known turbocharger turbine that the spiral casing does not provide an optimal flow of the exhaust gasses inside the spiral casing.
Therefore, it is an object of the present invention to provide a relatively cost effective spiral casing having improved flow properties increasing the efficiency of the turbocharger turbine in use . This object is achieved by a spiral turbine casing according to claim 1.
The spiral casing has a special designed base wall, in that inside the spiral casing a portion of the base wall has a curvature. This curvature inside the spiral casing optimizes in use the flow properties of exhaust gasses inside the spiral casing, e.g. optimizes the flow towards the central axis of the spiral casing. This central axis coincides with the central axis of a turbine wheel of a turbocharger turbine such that in use the turbine wheel can be driven more efficiently by means of the turbine spiral casing according to claim 1. Further, undesired turbulences inside the spiral casing can be reduced by means of the curvature. Such a spiral casing design improves the overall efficiency of the turbocharger turbine.
In a first embodiment the base wall has a varying thickness to provide the base wall curvature inside the spiral casing. The thickness of the base wall is measured in a (horizontal) direction extending parallel to the central axis. The base wall according to this embodiment requires a varying thickness of the base wall to provide an inside surface of the base wall having a curvature. For example, it is possible to provide such a curvature by gradually increasing the thickness of the base wall from the end of the base wall facing the central axis towards the connection. The side of the base wall opposite to the inside of the spiral casing can be fiat or substantially flat. This flat side of the base wall can advantageously be used to connect the spiral casing to other parts of the turbocharger turbine or a bearing housing of a turbocharger. In a second embodiment, the base wall is a base plate having a constant thickness. The base wall preferably extends in a longitudinal (vertical) direction and has vertically opposing ends, i.e. an end surface closer to the center axis of the spiral casing and an end surface further away of the center axis. The thickness corresponds to the width of the base plate measured in a (horizontal) direction extending transversally to the longitudinal direction, i.e. the width is the distance between the side surfaces which extend between the end surfaces. The base plate extends around the center axis of the spiral casing and has a disc or ring like shape with a through hole in the middle, wherein the center of the hole coincides with the center axis of the spiral casing. The radius of the through hole is larger than the distance between the vertically spaced end surfaces of the base wall. In this context constant thickness has to be understood as having a thickness that only varies due to manuf cturing tolerances. The curvature of the base plate is provided by bending the base plate such that the outer side of the base plate wall opposite to the inner side of the spiral casing is also curved. Preferably, the base plate is a sheet metal plate, which can be bent relatively easily. The bent base plate provides additional advantages for assembling a turbine in a turbocharger , because the bent base plate can be used for clamping and/or to increase the contact pressure between parts of a turbocharger. In addition, the bend in the base plate can also be used to provide an pre-tensioned contact between the spiral casing and other components of a turbocharger turbine or turbocharger, i.e. by means of the bend in the base plate such a contact is more flexible and more resistant to thermal stresses experienced for example during warming up. The walls or inner surface parts of the base wall and the spiral casing wall are substantially V-shaped towards the connection. Such V-shaped walls further optimize the flow properties of exhaust gasses inside the spiral casing. The inner surfaces of the spiral casing wall and the base wall towards the connection can be bent, wherein the curvature of the base wall may provide one bent wall part of the V-shape. In addition, the base wall may also have more than one radius of curvature.
The invention also relates to a turbocharger turbine comprising a turbine spiral casing as discussed above. The turbocharger turbine comprises an exhaust gas control device with a nozzle passage defined between a nozzle mount and a nozzle plate. The exhaust gas control device comprises a nozzle passage defined between a nozzle mount and a nozzle plate, wherein the dimensions of the nozzle passage can be varied by means of vanes to control an exhaust gas flow between the spiral casing and a turbine wheel. The base wall contacts the nozzle mount without being connected thereto. This contact provides a fluid tight connection between the nozzle mount and the base wall.
Further, the invention relates to a turbocharger comprising the above described turbine. Such a turbocharger has a compressor and between the turbine and the compressor a bearing housing. The turbine can be connected to the bearing housing by means of a clamping mechanism using a connecting element and a clamping element. Further, the exhaust gas control device in the turbocharger according to the present invention can be clamped between the bearing housing and the base wall by means of the clamping mechanism, i.e. the exhaust gas control device is clamped without being connected to other components of the turbocharger . Such clamping contact is more flexible and more heat resistant than a welded connection, i.e. the exhaust gas control device is supported by clamping, wherein the flexible clamping contact is able to withstand relative large temperature differences for a relative long period of time.
To explain the invention in more detail, exemplary embodiments thereof will hereinafter be described with reference to the accompanying drawings, wherein:
Figure 1 shows a part of a turbocharger according to the prior art in axial section;
Figure 2a shows schematically a part of a turbocharger according to a first embodiment in axial section;
Figure 2b shows schematically an enlarged view of a part of the turbocharger shown in figure 2a;
Figure 3 shows schematically a part of a turbocharger according to a second embodiment in axial section;
Figure 4 shows schematically a part of a turbocharger according to a third embodiment in axial section;
Figure 5 shows schematically a part of a turbochanger comprising a turbine 302 with a double wall spiral casing
308.
In this description, identical or corresponding parts have identical or corresponding reference numerals.
Figure 1 partly shows a turbocharger turbine known from the prior art. For a description of the known turbocharger turbine in detail reference is made to DE-10.200 .039. 77. A part of a turbocharger 1 according to a first embodiment is shown in figures 2a and 2b showing a part of a turbocharger turbine 2 and a part of a bearing housing 3. The figures 3 and 4 show parts of a turbocharger 101; 201 according to a second and third embodiment. The turbine 2; 102; 202 comprises a single flow spiral casing 8, 108; 208.
The turbocharger turbine 2; 102; 202 comprises a turbine wheel (not shown) , an exhaust gas control device 10; 210 and a spiral casing 8; 108; 208. The spiral casing 8; 108; 208 comprises a spiral casing wall 4; 104; 204 and a base plate 5; 205. The base plate 5 (figures 2a, b and 3) has a first end part 6 and a second end part 7, wherein the second end part 7 of the base plate 5 extends transversely to the central axis (not shown in figures 2a, b) of the turbine 2. The central axis of the turbine 2 corresponds to the dotted line 28 shown in figure 1. The central axis of the turbine 2 coincides with the central axis (not shown) of the spiral casing 8; 108; 208. The spiral casing 8; 108; 208 is provided by connecting a first bent end part 9; 109; 209 of the spiral casing wall 4; 104; 204 to the first end part 6; 206 of the base plate 5; 205 such that the spiral casing 8; 108; 208 has a connection 51; 251 between the spiral casing wall 4; 104; 204 and the base plate 5; 205. The connection 51; 251 fully extends around the central axis of the turbine 2; 102; 202. The connection 51; 251 is provided by tungsten inert gas (TIG) welding and/or laser beam welding (LBW) . The fully around the central axis extending endless form of the connection 51; 251 can be substantially circular. The inner surface 53 of the spiral casing wall 4; 104; 204 and the inner surface 55 of the base plate 5; 205 are V-shaped 57 towards the connection 51; 251. Inside the spiral casing 8; 108; 208 between the connection 51; 251 and the second end part 7; 207 of the base plate 5; 205 at least a portion of the base plate 5 has a curvature 61; 261. In the embodiments shown in figures 2a, b and 3, the curvature 61 of the inside surface 59 continues in a continuous or smooth way to the connection 51 such that the curvature 61 also provides one of the V-shaped wall parts towards the connection 51, i.e. the curvature 61 forms the inner surface 55 of the base plate 5. The V-shaped inner surfaces 53, 55 of the spiral casing wall 4 and the base plate 5 are bent.
The base plate 5; 205 has a first outer surface 62; 262, an opposite second surface 64; 264 which is located closer to the central axis than the first surface 62; 262 and two side surfaces 66, 68; 266; 268 extending between the first surface 62; 262 and the second surface 64; 264, wherein one of the two side surfaces is an outer side surface 68; 268 and a portion of the other side surface 66; 266 of the base plate 5; 205 extending between the connection 51; 252 and the other side surface 66; 266 is part of the inside surface of the spiral casing. In the embodiments shown in figures 2a, b and 3, the part of the inside surface of the spiral casing further comprises the second surface 64 of the base plate 5. In the embodiment shown in figure 4 the second surface 264 of the base wall 205 is positioned against a turbine element. The second end 207 of the base plate 205 has the curvature 261, i.e. the second end 207 does not extend transversely to the central axis.
The base plate 5; 205 has an edge 72; 272 between the second surface 64; 264 and the other side surface 66; 266 of the base wall, wherein a vertically extending first virtual plane {not shown) extends between the central axis and the edge 72; 272. The first virtual plane lies further from the center 95 inside the spiral casing than a second virtual plane extending between the connection and the central axis. In the embodiments shown in figures 2a, b and 4 the horizontal distance between the first virtual plane and the second virtual plane corresponds to two times the thickness of the base plate 5; 205. In the embodiment of the spiral casing 102 shown in figure 3 this distance is larger, wherein the maximum distance is two times smaller than the horizontal distance between the second virtual plane and the inside center 95 of the spiral casing 102. The distance D (figure 3) between the connection 51 and an inside surface 63 of the second end part 7 of the base wall 5 or the edge 72 corresponds to about five times the thickness of the second end part 7 of the base wall 5.
The exhaust gas control device 10; 210 of the turbocharger turbine 2; 102; 202 comprises a nozzle mount 79. The nozzle mount 79 is in the turbocharger according to the present invention clamped between the base plate 5; 205 and a turbine-side flange 77 of the bearing housing 3. By means of the curvature 61; 261 of the base plate 5; 205 a more flexible clamping can be achieved such that the thermal stresses due to the temperature differences in use can be compensated. Such flexible clamping provides a reliable fluid-tight sealing between the base plate 5; 205 and the nozzle mount 79. The nozzle mount 79 supports by means of supporting pins 80 a nozzle plate 82 (figure 2a) . The nozzle mount 79 and nozzle plate 82 define a nozzle passage 84 for guiding gasses from the spiral casing 8 to a turbine wheel (not shown) . The exhaust gas flow between the spiral casing and the turbine wheel can be controlled by means of vanes (not shown) varying the dimensions of the nozzle passage. The bearing housing 3; 103; 203 of the turbocharger 1; 101; 201 houses a common shaft {not shown) connecting a compressor wheel (not shown) with the turbine wheel. The exhaust-gas- driven turbine 2; 102; 202 supplies the drive energy for the compressor. The bearing housing 3; 103; 203 comprises a compressor-side flange 71, a central section 73 which is integrally connected to the flange 71, and a turbine-side section 75 which has the turbine-side flange 77 which is integrally connected to the central section 73. The central housing section 73, the compressor-side flange 71 and the turbine-side flange 77 are formed in one piece. The turbine 2; 102; 202 is connected to the flange 77 by means of an annular clamping element 81. The bearing housing 3; 103; 203 and the turbine 2; 102; 202 differ from the turbocharger of the prior art shown for example in figure 1, in that the connection between the bearing housing 3, 103; 203 and the turbine 2; 102; 202 is different, in particular the design of the base plate 5; 205 and the design of the connecting element 85; 185. The connecting element 85; 185; 285 fully extends around the central axis of the turbine 2; 102; 202. The connecting element 85; 185; 285 is preferably made of the same material as the base plate, i.e. sheet metal. The connecting element 85; 185; 285 can also be identified as upper casing.
The base plate 5; 205, the spiral casing wall 4; 104; 204 and the connecting element 85, 185; 285 are made from sheet metal having a thickness ≤ 3 mm, preferably a thickness ≤ 2 mm such as 1,5 mm. The thickness of the base plate 5 between the first end 6 and the second end 7 does not change neglecting manufacturing tolerances. The connecting element 85; 185; 285 comprises:
- a first end portion 87; 187; 287 to be clamped between the flange 77 and the clamping element 81;
- a middle portion 89; 189; 289 and
- a second end portion 91; 191, 291.
The middle portion 89; 189; 289 of the connecting element 85; 185; 285 preferably extends parallel to the central axis of the turbine 2; 102; 202 / turbocharger 1; 101; 201. The first end portion 87; 187; 287 preferably has an obtuse angle ε (figure 3) with the middle portion 89; 189; 289, preferably about 135 degrees. The second end portion 91; 191; 289 preferably extends transversely to the middle portion 89; 189; 289 of the connecting element 85; 185; 285. The angle β (figure 3) between the second end portion 91; 191; 291 and the middle portion 89; 189; 289 of the connecting element 85; 185; 285 may range between 45-315 degrees, preferably between 80-100 degrees (figure 3} or 260-280 degrees (figures 2a, b and figure 4) . The connecting element 85 may also comprise an intermediate portion 93 between the middle portion 89 and the second end portion 91 as shown in figures 2a, 2b. The intermediate portion 93 may have a first angle η (figure 2b) with respect to the middle portion (or horizontal) of for example 45 degrees and a second angle φ (figure 2b) with respect to the second end portion 91 (or vertical) of for example 45 degrees. These angles may be varied to provide the angle β between the second end portion 91; 191 and the middle portion 89; 189 of the connecting element 85; 185 between 45- 315 degrees. The second end portion 91 of the connecting element 85 shown in figures 2a, 2b extends at least partially parallel to the first end part 6 of the base plate and may be connected thereto, for example by welding. The second end portion 191 of the connecting element 185 shown in figure 3 extends at least partially parallel to the first end part 7 of the base plate 5 and may be clamped or connected thereto for example by welding. The second end portion 291 of the connecting element 285 shown in figure 4 extends at least partially parallel to a middle section 298 of the base plate 205 and is connected thereto for example by welding. By means of the connecting element 85; 185; 285 a reliable and relatively strong connection can be provided between the turbine 2; 102; 202 and the bearing housing 3; 103; 203. In addition, by means of the connecting element 85; 185; 285, the base plate 5; 205 and the clamping element 81 the nozzle mount 79 can be clamped between the second surface 264 of the base plate 205 (figure 4) or the outer side surface 64 of the base plate 5 and the turbine-side flange 77 of the bearing housing 3; 103; 203. By means of the curvature 61 of the base plate 5; 205 a relatively high contact force in a direction indicated by arrow PI (figure 2a) can be generated for clamping the nozzle mount 79. The nozzle mount 79 is advantageously clamped to withstand material expansion and material contraction due to temperature differences in use of the turbine 2; 102; 202.
In the base plate 5 the maximum angle a between the ends of the legs of the V-shaped inner surfaces 57 is relatively large by means of the curvature 61 of the base plate 5. The maximum angle ex (figure 3) is preferably smaller than 180 degrees. The maximum angle a. is larger than 60 degrees, preferably larger than 90 degrees. Further, due to the shape of the spiral casing 8 the angle cx will vary around the central axis of the turbine.
As shown in figures 2a, 2b, 3 and 4 the connected end portions 6, 9; 109; 209 of the spiral casing wall 4; 104; 204 and the base wall 5; 205 extend parallel to each other and extend transversely to the central axis of the turbine. This provides a reliable fluid tight seal and a strong connection between the base plate 5; 205 and the spiral casing wall 4; 104; 204. Preferably, the (vertical) length of the connected end portions 6; 9; 109; 209 is more than two times the thickness of the base plate 5; 205, preferably more than two and a half times the thickness of the base plate 5; 205.
Depending on the desired flow properties inside the spiral casing 8, it is possible to design a spiral casing 8 with an inner surface 55 of the base plate wall 5 being less continuous or being less smooth with the curvature 61 compared to the embodiments shown in figures 2a, 2b and 3. The base plate 205 shown in figure 4 is for example flat towards the connection 251.
The base plate 205 has a curved second end part 207, which provides the curvature 261 of the inside surface of the base plate 205.
Further, it is also possible that the curvature of the inside surface of the base wall may have more than one radius of curvature .
In another embodiment {not shown} the base wall is not a base plate, but a base wall having a varying thickness to provide the curvature of the inside surface. For example, in such an embodiment a side of the base wall opposite to the spiral casing can be flat or substantially flat, whereas the side facing the inside of the spiral casing comprises a curvature. Between the second and the first end, the thickness of the base wall at least partly varies to provide a curvature on the inside surface of the base wall . A flat or partly flat outer side of the base wall can be used to easily fix and/or connect the turbine to the bearing housing.
Turbocharger assembly comprising a bearing housing and a turbine, wherein the bearing housing and the turbine are connected by means of a connecting element 85; 185; 285, wherein the connecting element 85; 185; 285 is preferably made of sheet metal, wherein an end portion of the connecting element in contact with a base plate 5; 205 of a spiral casing has an angle β of 45-315 degrees with respect to a middle or center portion of the connecting element. In such a turbocharger assembly it is possible that the base plate has no curvature. Further, it is possible that the end portion is connected to the base plate for example by welding. In addition, the side of the connecting element opposing the base plate can be in contact with a nozzle mount of an exhaust gas control device for controlling the exhaust gas flow to the turbine. By means of a clamping element as indicated above with reference sign 81 it is possible to clamp the nozzle mount between the bearing housing and the base plate during assembling of a turbocharger.

Claims

Claims
1. A spiral turbine casing comprising a spiral casing wall and a base wall, wherein the base wall and the spiral casing wall have a connection which fully extends around a central axis, wherein a portion of the base wall is part of an inside surface of the spiral casing, said portion of the base wall has a curvature.
2. The spiral casing according to claim 1, wherein the base wail is a plate having a constant thickness, for example a thickness of approximately 1,5 mm, wherein the curvature is provided by bending the plate.
3. The spiral casing according to claim 1, wherein the curvature is provided by varying the thickness of the base wall .
4. The spiral casing according to any of claims 1-3, wherein the base wall and/or the spiral casing wall are made from sheet metal.
5. The spiral casing according to any of claims 1-4, wherein inside the spiral casing an inner surface part of the base wall and an inner surface part of the spiral casing wall are V-shaped towards the connection, wherein preferably the curvature provides the shape of the inner surface part of the base wall.
6. The spiral casing according to any of claims 1-5, wherein the curvature has a variable radius of curvature around the central axis.
7. The spiral casing according to any of claims 1-6, wherein the base wall fully extends around a central axis, said base wall has a first surface, an opposite second surface which is located closer to the central axis than the first surface and two side surfaces extending between the first surface and the second surface, wherein one of the two side surfaces is an outer side surface and a portion of the other side surface of the base wall extending between the connection and the second surface is part of the inside surface of the spiral casing.
8. The spiral casing according to claim 7, wherein the part of the inside surface of the spiral casing further comprises the second surface of the base wall.
9. The spiral casing according to claim 7, wherein the second surface of the base wall is positioned against a turbine element.
10. The spiral casing according to any of claim 7-9, wherein the outer surface of the base wall is flat or substantially flat.
11. The spiral casing according to any of claims 7-10, wherein the base wall has an edge between the second surface and the portion of the other side surface of the base wall, wherein a first virtual plane extends between the central axis and the edge, the first virtual plane lies further from the center of the spiral casing inside the spiral casing than a second virtual plane between the connection and the central axis, wherein preferably the horizontal distance between the first virtual plane and the second virtual plane is two times smaller than the horizontal distance between the second virtual plane and the center of the spiral casing.
12. The spiral casing according to any of claims 1-11, wherein the connection comprises parallel extending connected portions of the spiral casing wall and the base wall.
13. The spiral casing according to claim 12, wherein the connected portions of the spiral casing wall and the base wall extend transversely to the central axis.
14. The spiral casing according to any of claims 1-13, wherein the spiral casing is a single flow spiral casing.
15. Turbocharger turbine assembly comprising a spiral casing according to any of claims 1-14.
16. Turbocharger turbine assembly according to claim 15, wherein the turbocharger turbine assembly comprises an exhaust gas control device to control an exhaust gas flow between the spiral casing and a turbine wheel.
17. Turbocharger turbine assembly according to claim 16, wherein the exhaust gas control device comprises a nozzle passage defined between a nozzle mount and a nozzle plate, wherein the dimensions of the nozzle passage can be varied by means of vanes to control an exhaust gas flow between the spiral casing and a turbine wheel.
18. Turbocharger turbine assembly according to claim 16 or 17, wherein the portion of the base wall contacts the nozzle mount without being connected thereto.
19. Turbocharger comprising a turbocharger turbine assembly according to any of claims 15-18.
20. Turbocharger according to claim 19, wherein the turbocharger has a bearing housing, wherein the bearing housing is connected to the turbocharger turbine by means of a clamping mechanism.
21. Turbocharger according to claim 20 and including a turbocharger turbine assembly according to claim 16, wherein by means of the clamping mechanism the exhaust gas control device is clamped between the base wall and the bearing hous ing .
22. Turbocharger according to claim 20 or 21, wherein the clamping mechanism comprises:
- a connecting element, preferably the connecting element fully extends around the central axis,
- a clamping element for clamping the connecting element to the bearing housing, preferably the clamping element fully extends around the central axis.
23. Turbocharger according to claim 22, wherein the connecting element comprises:
- a first end portion to be clamped by the clamping element to the bearing housing;
- a middle portion and
- a second end portion connected or clamped to the base wail.
24. The turbocharger according to claim 22 or 23, wherein the connecting element is made of sheet metal and/or the clamping element is made of sheet metal.
25. Use of a turbocharger according to any of claims 19-24.
26. Method of manufacturing the spiral turbine casing according to any one of claims 1-14, wherein the connection is provided by tungsten inert gas (TIG) welding and/or laser beam welding (LBW) .
PCT/EP2015/061682 2014-06-02 2015-05-27 A spiral turbine casing of a turbocharger WO2015185408A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015002597.9T DE112015002597T5 (en) 2014-06-02 2015-05-27 Spiral turbine housing for a turbocharger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL1040828A NL1040828B1 (en) 2014-06-02 2014-06-02 A spiral turbine casing of a turbocharger.
NL1040828 2014-06-02

Publications (1)

Publication Number Publication Date
WO2015185408A1 true WO2015185408A1 (en) 2015-12-10

Family

ID=51136695

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/061682 WO2015185408A1 (en) 2014-06-02 2015-05-27 A spiral turbine casing of a turbocharger

Country Status (3)

Country Link
DE (1) DE112015002597T5 (en)
NL (1) NL1040828B1 (en)
WO (1) WO2015185408A1 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10436069B2 (en) 2017-01-30 2019-10-08 Garrett Transportation I Inc. Sheet metal turbine housing with biaxial volute configuration
US10472988B2 (en) 2017-01-30 2019-11-12 Garrett Transportation I Inc. Sheet metal turbine housing and related turbocharger systems
US10494955B2 (en) 2017-01-30 2019-12-03 Garrett Transportation I Inc. Sheet metal turbine housing with containment dampers
US10544703B2 (en) 2017-01-30 2020-01-28 Garrett Transportation I Inc. Sheet metal turbine housing with cast core
US10690144B2 (en) 2017-06-27 2020-06-23 Garrett Transportation I Inc. Compressor housings and fabrication methods
US11732729B2 (en) 2021-01-26 2023-08-22 Garrett Transportation I Inc Sheet metal turbine housing

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29909018U1 (en) * 1999-05-26 2000-09-28 Gillet Heinrich Gmbh Turbine housing for exhaust gas turbochargers
DE10028160A1 (en) * 2000-06-07 2001-12-20 Borgwarner Inc Casing assembly for exhaust turbocharger turbine made of thin metal sheet and surrounded by insulation
EP2508731A1 (en) * 2011-02-02 2012-10-10 Mitsubishi Heavy Industries, Ltd. Sheet metal turbine housing
EP2525050A2 (en) * 2011-05-19 2012-11-21 Benteler Automobiltechnik GmbH Exhaust gas turbocharger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29909018U1 (en) * 1999-05-26 2000-09-28 Gillet Heinrich Gmbh Turbine housing for exhaust gas turbochargers
DE10028160A1 (en) * 2000-06-07 2001-12-20 Borgwarner Inc Casing assembly for exhaust turbocharger turbine made of thin metal sheet and surrounded by insulation
EP2508731A1 (en) * 2011-02-02 2012-10-10 Mitsubishi Heavy Industries, Ltd. Sheet metal turbine housing
EP2525050A2 (en) * 2011-05-19 2012-11-21 Benteler Automobiltechnik GmbH Exhaust gas turbocharger

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10436069B2 (en) 2017-01-30 2019-10-08 Garrett Transportation I Inc. Sheet metal turbine housing with biaxial volute configuration
US10472988B2 (en) 2017-01-30 2019-11-12 Garrett Transportation I Inc. Sheet metal turbine housing and related turbocharger systems
US10494955B2 (en) 2017-01-30 2019-12-03 Garrett Transportation I Inc. Sheet metal turbine housing with containment dampers
US10544703B2 (en) 2017-01-30 2020-01-28 Garrett Transportation I Inc. Sheet metal turbine housing with cast core
US11035254B2 (en) 2017-01-30 2021-06-15 Garrett Transportation I Inc Sheet metal turbine housing with cast core
US10690144B2 (en) 2017-06-27 2020-06-23 Garrett Transportation I Inc. Compressor housings and fabrication methods
US11732729B2 (en) 2021-01-26 2023-08-22 Garrett Transportation I Inc Sheet metal turbine housing

Also Published As

Publication number Publication date
NL1040828B1 (en) 2016-05-12
DE112015002597T5 (en) 2017-04-06

Similar Documents

Publication Publication Date Title
WO2015185408A1 (en) A spiral turbine casing of a turbocharger
JP5052649B2 (en) Turbine housing
JP5577264B2 (en) Exhaust manifold for internal combustion engine
US8888456B2 (en) Rotor and method for manufacturing a rotor for a turbo machine
JP4269184B2 (en) Exhaust gas turbine for exhaust gas turbocharger
KR101182121B1 (en) Turbo charger
JP5628190B2 (en) Ring segment positioning member
CN101652534A (en) Stator blade ring and axial flow compressor using the same
CN111902607B (en) Cooling apparatus for a turbine of a turbine engine
JP6240307B2 (en) Sheet metal turbine housing
JPWO2013065154A1 (en) Turbine housing and exhaust turbine supercharger
JP6506315B2 (en) Silencer
US20110120124A1 (en) Exhaust gas turbocharger
JP2012017847A (en) Fluid machine
EP2283218B1 (en) Thermal insulation structure
JPWO2019044776A1 (en) Turbocharger
US20060275151A1 (en) Pump and heat exchanger
JP5587415B2 (en) Insulation device suitable for insulating the gas discharge pipe of a refrigeration compressor, and the process of assembling the heat insulation device in the gas discharge pipe
US10077679B2 (en) Turbine housing
WO2015146895A1 (en) Steam turbine
KR101548449B1 (en) A transition piece assembly of a gas turbine
KR20090033003A (en) Blade structure of torque converter and method for manufacturing blade structure of torque converter
WO2002097353A1 (en) Pipe connection arrangement for a heat exchanger
WO2002095316A1 (en) Arrangement for connecting a pipe to a heat exchanger
WO2003023192A1 (en) A conduit for a gas turbine unit and a method of manufacturing a conduit

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15727338

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 112015002597

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15727338

Country of ref document: EP

Kind code of ref document: A1