WO2016071959A1 - タービンハウジングおよびタービンハウジングの製造方法 - Google Patents
タービンハウジングおよびタービンハウジングの製造方法 Download PDFInfo
- Publication number
- WO2016071959A1 WO2016071959A1 PCT/JP2014/079239 JP2014079239W WO2016071959A1 WO 2016071959 A1 WO2016071959 A1 WO 2016071959A1 JP 2014079239 W JP2014079239 W JP 2014079239W WO 2016071959 A1 WO2016071959 A1 WO 2016071959A1
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- WIPO (PCT)
- Prior art keywords
- turbine housing
- turbine
- scroll
- turbine wheel
- plate member
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
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- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
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- 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
- F05D2230/10—Manufacture by removing material
-
- 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
- F05D2230/20—Manufacture essentially without removing material
- F05D2230/21—Manufacture essentially without removing material by casting
-
- 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
- F05D2230/90—Coating; Surface treatment
-
- 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
- F05D2250/50—Inlet or outlet
- F05D2250/51—Inlet
-
- 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
-
- 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
- F05D2300/00—Materials; Properties thereof
- F05D2300/50—Intrinsic material properties or characteristics
- F05D2300/516—Surface roughness
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present disclosure relates to a turbine housing and a method of manufacturing the turbine housing.
- a turbocharger includes a rotating shaft, a turbine wheel provided at one end of the rotating shaft, and a compressor wheel provided at the other end of the rotating shaft.
- the exhaust energy of the exhaust gas acts on the turbine wheel to rotate the rotating shaft at high speed, whereby the compressor wheel provided on the other end side of the rotating shaft is configured to compress the intake air.
- An engine equipped with a turbocharger can obtain a large output with a small displacement. For this reason, in recent years, particularly in an automobile engine, improvement of fuel consumption has been carried out by mounting a turbocharger and downsizing the engine. Under such circumstances, the need for a turbocharger for a small displacement engine is also increasing, and further miniaturization of the turbocharger is in progress.
- Turbocharger turbine housings are generally manufactured by casting.
- the surface roughness inside the housing is relatively rough compared to a large turbine housing.
- the tongue portion is relatively thick due to the relation of the minimum thickness at the time of manufacture by casting, the ventilation resistance of the exhaust gas becomes large.
- the casting error is relatively large as compared with a large turbine housing, the variation in the performance and the flow rate characteristic between products becomes large.
- Patent Document 1 An invention (Patent Document 1) is being filed.
- the turbine housing according to the prior application invention accommodates a plate member made of a sheet metal inside a castable turbine housing and forms an internal flow path by the plate member made of a sheet metal, but the structure is somewhat complicated.
- At least one embodiment of the present invention is an invention made on the basis of such prior art situation, and the object thereof is to reduce the ventilation resistance of the exhaust gas and improve the efficiency of the turbocharger.
- An object of the present invention is to realize a turbine housing that can be used with a simple structure.
- a turbine housing for accommodating a turbine wheel rotated by exhaust gas, comprising:
- the turbine housing is A scroll portion forming an annular scroll flow passage through which the exhaust gas supplied to the turbine wheel flows around the turbine wheel;
- An exhaust pipe portion forming an exhaust flow path through which the exhaust gas having passed through the turbine wheel flows along an axial direction of the turbine wheel;
- It is a shroud part which protrudes in the hub side in the connection part of the above-mentioned scroll part and the above-mentioned exhaust pipe part, and the perimeter face of the above-mentioned shroud part faces the above-mentioned scroll channel, and the inner circumference of the above-mentioned shroud part
- the surface is a cast turbine housing comprising: a shroud portion formed with a predetermined gap between the turbine wheel and a moving blade of the turbine wheel; In a cross section along the axial direction of the turbine wheel, a radial distance R1 from the axis of the turbine wheel to the tip
- the turbine housing according to the above (1) has a radial distance R1 from the axis of the turbine wheel to the tip of the shroud portion in a cross section along the axial direction of the turbine wheel, and a hub sidewall surface of the scroll portion from the turbine wheel axis
- the radius R2 'of the opening 16' in the turbine housing 2 'of the conventional comparative example shown in FIG. 12 is in the relationship of R1' ⁇ R2 '.
- the larger opening can be used to machine the inside of the turbine housing after casting. Therefore, the flow resistance of the exhaust gas in the turbine housing is reduced by processing the flow path surface of the region A on the inner peripheral side of the scroll flow path, which has a large flow velocity and a large influence on the air flow resistance. Thus, the efficiency of the turbocharger can be improved.
- the existence range in the radial direction of the region A is 1.15 D to 1.4 D, where D is the outer diameter of the turbine wheel. Configured to include at least a portion of the range of Also, in some embodiments, the radial range of the region A is configured to include at least a portion of the range of 1.20D to 1.4D. Furthermore, in some embodiments, the radial range of region A is configured to include at least a portion of the range of 1.25D to 1.4D.
- the region A is configured to include at least the inner peripheral side of the scroll flow passage, in particular, the flow velocity is large and the air flow resistance is largely affected. Therefore, the ventilation resistance of the exhaust gas in the turbine housing can be reduced to improve the efficiency of the turbocharger.
- the outer circumferential surface of the shroud portion in a cross section along the axial direction of the turbine wheel, is relative to the axial direction of the turbine wheel And the region A is configured to include at least a part of the outer peripheral surface.
- the region A is configured to include at least the outer peripheral surface of the shroud portion positioned on the inner peripheral side of the scroll passage, in particular, the flow velocity is large and the air flow resistance is large. . Further, when the outer peripheral surface of the shroud portion is an inclined surface as described above, the influence on the air flow resistance is particularly large because the contact area with the fluid is wide. Therefore, according to such an embodiment, the ventilation resistance of the exhaust gas in the turbine housing can be reduced to improve the efficiency of the turbocharger.
- a flow path portion disposed in the opening and facing the scroll flow path, and a turbine wheel And an annular first plate member having a back surface portion having a space between the rear surface portion and the rear surface portion.
- a turbine housing first plate member which has a channel part which faces a scroll channel in an opening is arranged. Since this first plate member is a separate member from the cast turbine housing, it is easy to make the surface roughness of the first plate member smaller than the surface roughness of the turbine housing. Therefore, according to such an embodiment, the flow resistance of the exhaust gas flowing through the scroll flow passage can be reduced by reducing the roughness of the flow passage portion of the first plate member facing the scroll flow passage.
- the turbine housing forms an introduction channel that guides exhaust gas introduced from the outside of the turbine housing to the scroll channel. It further comprises a department. And the tongue part which divides an introductory flow path and a scroll flow path to radial direction is formed by the tongue part member separate from the turbine housing which extends toward the shroud part from the 1st plate member side.
- the tongue is formed by the tongue member separate from the turbine housing. For this reason, when processing the inside of a turbine housing using an opening after casting, the tongue does not disturb the processing as in the case where the tongue is integrally formed with the cast turbine housing. Thus, the inside of the turbine housing can be easily processed. Further, the tongue can be thinner than in the case where the tongue is integrally formed with the cast turbine housing. As a result, it is possible to suppress the generation of flow distortion that occurs on the downstream side of the tongue, and to reduce the flow resistance of the exhaust gas flowing from the introduction flow path to the scroll flow path.
- the tongue member is a first plate member.
- the first plate member is made of sheet metal and has a bent portion which is bent along the axial direction of the turbine wheel, and the bent portion forms a tongue.
- the sheet metal tongue portion formed separately from the turbine housing by a simple structure with a small number of parts. Can be formed.
- the second plate is provided in the opening of the turbine housing so as to cover a part of the flow passage portion of the first plate member. It further comprises a member. And the said tongue part member is a 2nd plate member.
- the embodiment described in the above (7) further includes a second plate member disposed so as to cover a part of the flow passage portion of the first plate member. And a tongue part is formed of this 2nd plate member. According to such an embodiment, it is possible to form a tongue separate from the turbine housing with a simple structure without applying special processing to the first plate member.
- the second plate member is made of sheet metal and has a bent portion that is bent along the axial direction of the turbine wheel, The bent portion forms a tongue.
- the second plate member is an annular member extending along the entire circumferential direction of the turbine wheel. Then, in the cross section along the axial direction of the turbine wheel, the flow path portion facing the scroll flow path excluding the portion covered by the second plate member in the first plate member is the entire circumference of the turbine wheel in the circumferential direction Are configured to have the same radial width.
- the radial width of the flow passage surface exposed to the high temperature exhaust gas in the first plate member can be made uniform over the entire circumference of the turbine wheel in the circumferential direction. .
- the amount of heat input to the first plate member can be made uniform over the circumferential direction, and nonuniform deformation of the first plate member due to thermal expansion can be prevented.
- a rotary shaft coupled to a turbine wheel is rotatably supported on the back side of the turbine housing.
- the bearing housings for housing the bearing devices are connected.
- the turbine housing further includes an introduction pipe portion forming an introduction flow passage for introducing the exhaust gas introduced from the outside of the turbine housing into the scroll flow passage.
- a tongue that radially divides the introduction passage and the scroll passage is formed by a tongue member separate from the turbine housing and extending from the bearing housing toward the shroud.
- the tongue is formed by a tongue member separate from the turbine housing and extending from the bearing housing toward the shroud. For this reason, when processing the inside of a turbine housing using an opening after casting, the tongue does not disturb the processing as in the case where the tongue is integrally formed with the cast turbine housing. Thus, the inside of the turbine housing can be easily processed.
- the tongue member comprises a third plate member connected to the bearing housing.
- the tongue is formed by the third plate member connected to the bearing housing. Since the third plate member is a separate member from the cast turbine housing, it is easier to form the tongue thinner than when the tongue is integrally formed with the cast turbine housing. . As a result, it is possible to suppress the occurrence of flow distortion that occurs on the downstream side of the tongue, and to reduce the flow resistance of the exhaust gas flowing from the introduction flow path to the scroll flow path. Also, the tongue can be formed by a simple structure for connecting the third plate member to the bearing housing.
- the third plate member is made of sheet metal.
- the tongue portion can be thinly formed by a simple structure.
- the region A is a circumferential direction of the turbine wheel The same radial width is formed over the entire circumference.
- the tongue is formed by a separate member separate from the turbine housing.
- the tongue 50' is integrally formed with the turbine housing 2 ', so the tongue 50' becomes an obstacle and the turbine wheel Region A could not be formed with the same radial width over the entire circumference of 5 'in the circumferential direction. Therefore, according to the embodiment described in (13), by forming the region A in the same radial width over the entire circumferential direction of the turbine wheel, the entire circumferential direction of the turbine wheel The ventilation resistance of the exhaust gas can be reduced.
- the flow passage center of the introduction flow passage in a cross section viewed from the axial direction of the turbine wheel Is formed into an S-shaped curve which is curved radially inward and then curved radially outward from the inlet of the introduction channel toward the junction with the scroll channel.
- the tongue portion is formed by a plate-like member made of a sheet metal.
- the pressure difference between the outer peripheral side and the inner peripheral side of the tongue portion acts on the tongue portion because the tongue portion is thin.
- the ventilation resistance may increase.
- the pressure difference acting on the tongue may cause deformation of the tongue.
- the pressure on the inner peripheral side of the tongue is lower than that on the outer peripheral side of the tongue because the pressure is reduced by the high-speed exhaust gas flow.
- a method of manufacturing a turbine housing for accommodating a turbine wheel rotated by exhaust gas, comprising:
- the turbine housing is A scroll portion forming an annular scroll flow passage through which the exhaust gas supplied to the turbine wheel flows around the turbine wheel;
- An exhaust pipe portion forming an exhaust flow path through which the exhaust gas having passed through the turbine wheel flows along an axial direction of the turbine wheel;
- It is a shroud part which protrudes in the hub side in the connection part of the above-mentioned scroll part and the above-mentioned exhaust pipe part, and the perimeter face of the above-mentioned shroud part faces the above-mentioned scroll channel, and the inner circumference of the above-mentioned shroud part
- the surface includes a shroud portion formed with a predetermined gap between the turbine wheel and a moving blade of the turbine wheel; In a cross section along the axial direction of the turbine wheel, a radial distance R1 from the axis of the turbine wheel
- the roughness of the flow passage surface inside the turbine housing is reduced by processing the inside of the turbine housing after casting using a larger opening than before. Can do.
- the flow resistance of the exhaust gas in the turbine housing is reduced by processing the flow path surface of the region A corresponding to the inner peripheral side of the scroll flow path having a large flow velocity and large influence on air flow resistance and reducing its roughness. The efficiency of the turbocharger can be improved.
- the processing of the flow passage surface of the region A is machining.
- the inside of the turbine housing can be machined after casting using a larger opening than before. Therefore, the roughness of the flow passage surface inside the turbine housing can be reduced in a simple manner.
- the processing of the flow passage surface in the region A is performed by inserting a cutting tool from the opening into the inside of the cast turbine housing and casting It consists of lathe processing which cuts or grinds the flow-path surface of field A by rotating the turbine housing which was done.
- turbocharger in the turbocharger concerning one embodiment of the present invention, it is a sectional view showing the section which met in the direction of an axis of the axis of rotation.
- a turbine housing concerning one embodiment of the present invention, it is an important section sectional view showing an important section along with an axial direction of the turbine wheel.
- FIG. 5 is a cross-sectional view showing the shroud side in the Y1-Y1 cross section of FIG. 2
- FIG. 3 is a cross-sectional view showing a hub side in a Y1-Y1 cross section of FIG. 2;
- a turbine housing concerning one embodiment of the present invention, it is an important section sectional view showing an important section along with an axial direction of the turbine wheel. In a turbine housing concerning one embodiment of the present invention, it is an important section sectional view showing an important section along with an axial direction of the turbine wheel.
- FIG. 10 is a cross-sectional view showing the hub side in the Y2-Y2 cross section of FIGS. 9A to 9C.
- a turbine housing concerning one embodiment of the present invention it is an important section sectional view showing an important section along with an axial direction of the turbine wheel.
- expressions that indicate that things such as “identical”, “equal” and “homogeneous” are equal states not only represent strictly equal states, but also have tolerances or differences with which the same function can be obtained. It also represents the existing state.
- expressions representing shapes such as quadrilateral shapes and cylindrical shapes not only represent shapes such as rectangular shapes and cylindrical shapes in a geometrically strict sense, but also uneven portions and chamfers within the range where the same effect can be obtained. The shape including a part etc. shall also be expressed.
- the expressions “comprising”, “having”, “having”, “including” or “having” one component are not exclusive expressions excluding the presence of other components.
- FIG. 1 is a cross-sectional view showing a cross section along an axial direction of a rotation axis of a turbocharger according to an embodiment of the present invention.
- the turbocharger 1 according to an embodiment of the present invention is, for example, a small-sized turbocharger mounted on an automobile engine or the like, although not particularly limited.
- a turbocharger 1 according to an embodiment of the present invention includes a turbine housing 2 for housing a turbine wheel 5, a compressor housing 3 for housing a compressor wheel 6, and a turbine wheel at one end. And 5, a bearing housing 4 for accommodating bearing devices 10A and 10B rotatably supporting a rotating shaft 7 to which the compressor wheel 6 is connected at the other end.
- the turbine wheel 5 is composed of a truncated conical hub portion 8 and a plurality of moving blades 9 provided at intervals on the outer peripheral surface of the hub portion 8.
- FIG. 2 is a sectional view of an essential part showing an essential part along the axial direction of the turbine wheel in the turbine housing 2 according to an embodiment of the present invention.
- FIG. 3 is a cross-sectional view showing the shroud side in the Y1-Y1 cross section of FIG.
- FIG. 4 is a cross-sectional view showing the hub side in the Y1-Y1 cross section of FIG.
- FIG. 5 is a view of a conventional turbine housing 2 ′ as a comparative example, and is a cross-sectional view corresponding to FIG.
- FIG. 6 is a view showing a modified example of the turbine housing 2 according to an embodiment of the present invention.
- FIG. 9D is a cross-sectional view showing the hub side in the Y2-Y2 cross section of FIGS. 9A to 9C.
- FIG. 12 is a cross-sectional view of relevant parts of a conventional turbine housing 2 'as a comparative example.
- turbine housing 2 'of the comparative example of FIG.5 and FIG.12 about the structure similar to the turbine housing 2 concerning one Embodiment of this invention, "'" is attached
- the turbine housing 2 includes the scroll portion 21, the exhaust pipe portion 22, and the connection portion between the scroll portion 21 and the exhaust pipe portion 22. It is a cast turbine housing 2 including a shroud portion 23 to be formed. That is, in the turbine housing 2, the scroll portion 21, the exhaust pipe portion 22 and the shroud portion 23 are integrally formed by casting. Further, as shown in FIG. 3, the turbine housing 2 is provided with an introduction pipe portion 25 integrally formed by casting on the inlet side of the scroll flow passage 12.
- the scroll portion 21 forms an annular scroll flow passage 12 around which the exhaust gas G supplied to the turbine wheel 5 flows, as shown in FIGS. 2 and 3.
- the scroll portion 21 has a shroud side wall surface 21 a and a hub side wall surface 21 c which extend in a direction orthogonal to the extending direction of the axis K of the turbine wheel 5 as wall surfaces facing the scroll passage 12. And an outer peripheral side wall surface 21b extending along the extending direction of the axis K and connecting the shroud side wall surface 21a and the hub side wall surface 21c.
- a connecting portion 26 connected to the bearing housing 4 via the coupling 27 is formed on the rear surface side of the scroll portion 21, a connecting portion 26 connected to the bearing housing 4 via the coupling 27 is formed.
- the scroll portion 21 of the other embodiment is a shroud side extending in a direction orthogonal to the extending direction of the axis line K of the turbine wheel 5 as a wall surface facing the scroll passage 12.
- a wall surface 21a and a hub side wall surface 21c, and an outer peripheral side wall surface 21b having an arc shape or a semicircular shape and connecting the shroud side wall surface 21a and the hub side wall surface 21c are provided.
- the shape of the scroll part 21 shown in FIG.2, FIG.3 and FIG.6 is an illustration, Comprising: The scope of the present invention is not limited.
- the shape of the scroll portion 21 may be any shape as long as the scroll flow passage 12 in which the exhaust gas G flows is formed inside, and various shapes can be adopted.
- the exhaust pipe portion 22 forms an exhaust flow passage 14 through which the exhaust gas G having passed through the turbine wheel 5 flows along the axial direction of the turbine wheel 5 as shown in FIGS. 1 and 2.
- a flange portion 24 flanged to an exhaust pipe (not shown) is formed on the front side of the exhaust pipe portion 22 .
- the shroud portion 23 is provided so as to protrude toward the hub side at the connection portion between the scroll portion 21 and the exhaust pipe portion 22.
- the outer peripheral surface 23 a of the shroud portion 23 faces the scroll flow passage 12, and the inner peripheral surface 23 c of the shroud portion 23 has a predetermined clearance c with the outer peripheral edge 9 c of the moving blade 9 of the turbine wheel 5.
- the outer peripheral surface 23a of the shroud portion 23 is an inclined surface which is inclined with respect to the extending direction of the axis K of the turbine wheel 5, and from the tip 23d of the shroud portion 23 to the shroud side wall surface 21a of the scroll portion 21. It extends obliquely toward the inner peripheral end 21 e. Further, between the outer peripheral surface 23 a and the inner peripheral surface 23 c of the shroud portion 23, a parallel surface 23 b extending in a direction orthogonal to the extending direction of the axis line K of the turbine wheel 5 is formed. At this time, the tip end 23d of the shroud portion 23 having the parallel surface 23b is a position on the outer peripheral side of the parallel surface 23b as shown in FIG. The distal end 23d of the shroud portion 23 having a curved distal end, which does not have the parallel surface 23b, is the portion located closest to the hub as shown in FIG.
- the turbine housing 2 according to at least one embodiment of the present invention, as shown in FIG. 2, FIG. 7, FIG. 8, FIG. 9A to FIG.
- the radial distance from the axis K of the turbine wheel 5 to the tip 23d of the shroud portion 23 is R1
- the radius from the axis K of the turbine wheel 5 to the inner circumferential end 21d of the hub sidewall 21c of the scroll portion 21 When the directional distance is R2, an opening 16 having a radius R2 such that R1 ⁇ R2 is formed on the hub side of the scroll portion 21.
- the predetermined range from the tip 23 d of the shroud portion 23 among the 21c and 23a is a region A
- the predetermined range adjacent to the region A is a region B
- the roughness of the flow passage surface in the region A is the flow passage surface in the region B It is configured to be smaller than the roughness of.
- the roughness of the flow channel surface can be evaluated, for example, by the arithmetic mean roughness (Ra) defined in JIS B 0601-2001.
- the turbine housing 2 has a radial distance R1 from the axis K of the turbine wheel 5 to the tip 23d of the shroud portion 23 in a cross section along the extending direction of the axis K of the turbine wheel 5
- R1 the radial distance from the axis K of 5 to the inner circumferential end 21d of the hub side wall surface 21c of the scroll portion 21
- the opening 16 having a radius R2 such that R1 ⁇ R2 is on the hub side of the scroll portion 21 It is formed.
- the radius R2 'of the opening 16' in the turbine housing 2 'of the conventional comparative example shown in FIG. 12 is in the relationship of R1' ⁇ R2 '.
- the flow resistance of the exhaust gas G in the turbine housing 2 can be reduced and the efficiency of the turbocharger 1 can be improved by processing the flow passage surface of the above and reducing the roughness thereof.
- the method of processing the flow passage surface of the region A is not particularly limited. For example, machining is performed by inserting a cutting tool (tool) into the inside of the turbine housing 2 cast from the opening 16 and cutting or grinding the flow passage surface of the region A Done by In some embodiments, processing of the flow channel surface of the region A is performed by inserting a tool (tool) from the opening 16 into the inside of the cast turbine housing and rotating the cast turbine housing 2 in this state It consists of lathe processing which cuts or grinds the flow path surface of field A.
- machining is performed by inserting a cutting tool (tool) into the inside of the turbine housing 2 cast from the opening 16 and cutting or grinding the flow passage surface of the region A Done by
- processing of the flow channel surface of the region A is performed by inserting a tool (tool) from the opening 16 into the inside of the cast turbine housing and rotating the cast turbine housing 2 in this state It consists of lathe processing which cuts or grinds the flow path surface of field A.
- the presence range in is configured to include at least a part of the range of 1.15D to 1.4D.
- the inner diameter at the tip end 23 d of the shroud portion 23 is about 1.15 D
- the inner diameter at the inner circumferential end 21 e of the shroud side wall surface 21 a of the scroll portion 21 is about 1.4 D. That is, in the illustrated embodiment, the range of 1.15 to 1.4 D which is the existence range in the radial direction of the region A is an inclined surface corresponding to the outer peripheral surface 23 a of the shroud portion 23.
- the region A is configured to include at least the inner peripheral side of the scroll flow passage 12, in particular, the flow velocity is large and the influence on the air flow resistance is large. Further, when the outer peripheral surface 23a of the shroud portion 23 is an inclined surface as in the present embodiment, the contact area with the fluid is wide, so the influence on the air flow resistance is particularly large. Therefore, according to such an embodiment, by forming the region A in the above-described range, the ventilation resistance of the exhaust gas in the turbine housing 2 can be reduced, and the efficiency of the turbocharger 1 can be improved.
- the turbine housing 2 is disposed in the opening 16 described above and is a flow path facing the scroll flow path 12 It further includes an annular first plate member 40 having a portion 40 a and a back surface portion 40 b having a gap between the back surface of the turbine wheel 5.
- the first plate member 40 is held between the turbine housing 2 and the bearing housing 4 at an outer peripheral edge 40 c extending in a direction orthogonal to the extending direction of the axis K of the turbine wheel 5.
- it is fixed inside the turbine housing 2.
- channel part 40a which faces scroll channel 12 via step 40d extended along the extension direction of axis K of turbine wheel 5.
- the flow passage portion 40 a extends in a direction orthogonal to the extending direction of the axis line K of the turbine wheel 5.
- the back surface portion 40 b extends toward the axis K while being slightly inclined toward the back side so that a predetermined gap is formed between the back surface 40 b and the back surface of the turbine wheel 5.
- the flow passage portion 40 a and the back surface portion 40 b function to prevent the exhaust gas G flowing through the scroll flow passage 12 from leaking to the back surface side of the turbine wheel 5.
- the first plate member 40 is made of sheet metal.
- the first plate member 40 may be formed by precision casting, or may be formed by metal injection molding.
- the first plate member 40 having the flow passage portion 40 a facing the scroll flow passage 12 is disposed in the opening 16. Since the first plate member 40 is a separate member from the cast turbine housing 2, it is easy to make the surface roughness of the first plate member 40 smaller than the surface roughness of the turbine housing 2. is there. Therefore, according to such an embodiment, by reducing the roughness of the flow path portion 40a of the first plate member 40 facing the scroll flow path 12, the flow resistance of the exhaust gas flowing through the scroll flow path 12 is reduced. can do.
- the turbine housing 2 forms an inlet channel portion 18 that guides the exhaust gas G introduced from the outside of the turbine housing 2 to the scroll channel 12. Further comprising then, as shown in FIG. 7, FIG. 8, FIG. 9A, and FIG. 9B, the tongue portion 50 which divides the introduction flow passage 18 and the scroll flow passage 12 in the radial direction faces the shroud portion 23 from the first plate member 40 side. It is formed by a tongue member 50A that is separate from the turbine housing 2 and extends.
- a tongue 50B shorter than the conventional tongue 50 ' is formed at the connecting portion of the turbine housing 2 to the introduction pipe 25 scroll 21.
- the tongue member 50A is provided so as to be continuous with the short tongue 50B of the turbine housing 2 and extends to the end position of the conventional tongue 50 '.
- the tongue 50 is formed by the tongue member 50A separate from the turbine housing 2. Therefore, when processing the inside of the turbine housing 2 using the opening 16 after casting, the tongue 50 is processed as in the case where the tongue 50 'is integrally formed with the cast turbine housing 2'. It does not get in the way of Thus, the inside of the turbine housing 2 can be easily processed. Further, the tongue 50 can be thinner than in the case where the tongue 50 is integrally formed with the cast turbine housing 2. As a result, the occurrence of flow distortion that occurs on the downstream side of the tongue 50 can be suppressed, and the flow resistance of the exhaust gas G flowing from the introduction flow path 18 to the scroll flow path 12 can be reduced.
- the tongue member 50A comprises a fourth plate member 48 connected to the flow passage portion 40a of the first plate member 40.
- the fourth plate member 48 is connected to the flow passage portion 40 a of the first plate member 40 by, for example, a method such as welding.
- the fourth plate member 48 extends along the extending direction of the axis line K of the turbine wheel 5, and its tip end abuts on the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface.
- the fourth plate member 48 is made of sheet metal. Besides the sheet metal, the fourth plate member 48 may be formed by precision casting, or may be formed by metal injection molding.
- the tongue portion 50 by forming the tongue portion 50 by the fourth plate member 48 connected to the first plate member 40 by welding or the like, the tongue formed separately from the turbine housing 2 by a simple structure
- the portion 50 can be formed.
- the tip end of the fourth plate member 48 is in contact with the outer peripheral surface 23 a of the shroud portion 23 which is an inclined surface. For this reason, since the acting force in the radial direction from the outer peripheral side to the inner peripheral side acting on the fourth plate member 48 can be supported by the outer peripheral surface 23a by the pressure difference, the fourth member is formed thin. Vibration or deformation of the plate member 48 can be prevented.
- the tongue member 50A is the first plate member 40 described above.
- the first plate member 40 is made of sheet metal and has a bending portion 40A which is bent along the extending direction of the axis line K of the turbine wheel 5, and the tongue portion 50 is formed by the bending portion 40A. Ru.
- the bending portion 40A is formed by, for example, a method such as pressing.
- the bent portion 40A extends along the extending direction of the axis K of the turbine wheel 5, and its tip end abuts on the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface.
- a sheet metal tongue portion formed separately from the turbine housing 2 by a simple structure with a small number of parts. 50 can be formed.
- the tip end of the bent portion 40A is in contact with the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface. For this reason, since it is possible to support the radial direction acting force from the outer peripheral side to the inner peripheral side acting on the bending portion 40A by the pressure difference by the outer peripheral surface 23a, the bending portion of the first plate member 40 made of sheet metal Vibration and deformation of 40A can be prevented.
- the turbine housing 2 is disposed at the opening 16 of the turbine housing 2 so as to cover a portion of the flow passage portion 40 a of the first plate member 40.
- the second plate member 44 is further provided.
- the tongue part member 50A mentioned above is the 2nd plate member 44.
- the second plate member 44 is made of sheet metal and has a bending portion 44A that is bent along the axial direction of the turbine wheel 5. Then, the tongue portion 50 described above is formed by the bent portion 44A.
- the second plate member 44 is held between the turbine housing 2 and the bearing housing 4 at an outer peripheral edge 44 c extending in a direction orthogonal to the extending direction of the axis K of the turbine wheel 5.
- it is fixed inside the turbine housing 2.
- channel part 44a which faces scroll channel 12 via step 44d extended along the extension direction of axis K of turbine wheel 5.
- the flow passage portion 44 a extends in a direction orthogonal to the extending direction of the axis line K of the turbine wheel 5.
- a portion 40a2 of the flow path portion 40a of the first plate member 40 is covered by the flow path portion 44a.
- the remaining portion 40a1 excluding the portion 40a2 covered by the flow passage portion 44a directly faces the scroll flow passage 12.
- a bent portion 44A extends from the flow passage 44a along the extending direction of the axis K of the turbine wheel 5 toward the shroud 23.
- the bending portion 44A is formed by being bent along the extending direction of the axis line K of the turbine wheel 5 from an intermediate position of the flow path portion 44a. And as shown to FIG. 9B, the flow-path part 44a is divided into 44a1 of outer peripheral side, and 44a2 of inner peripheral side bordering on this bending part 44A.
- the bending portion 44A is formed by a folded double plate, but is not limited thereto. In another embodiment, although not shown, the bent portion 44A is formed by a single plate without being folded back.
- the second plate member 44 is made of sheet metal, the second plate member 44 may be formed by precision casting other than sheet metal, and may be formed by metal injection molding. You may form.
- the tongue 50 is formed separately from the turbine housing 2 with a simple structure without applying special processing to the first plate member 40.
- the tip end of the bent portion 44A is in contact with the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface. For this reason, since the acting force in the radial direction from the outer peripheral side to the inner peripheral side acting on the bending portion 44A can be supported by the outer peripheral surface 23a by the pressure difference, the second plate member 44 formed thin. Vibration or deformation of the bending portion 44A can be prevented.
- the second plate member 44 is an annular member extending along the entire circumferential direction of the turbine wheel 5. Then, as shown in FIGS. 9A to 9C, the scroll excluding the portion 40a2 of the first plate member 40 covered by the second plate member 44 in the cross section along the extension direction of the axis line K of the turbine wheel 5
- the flow passage portion 40a1 facing the flow passage 12 is configured to have the same radial width rb over the entire circumferential direction of the turbine wheel 5, as shown in FIG. 9D.
- the separation distance rb between the inner peripheral end of the second plate member 44 and the front edge 9a of the moving blade 9 extends over the entire circumference of the turbine wheel 5 in the circumferential direction. It is formed equally.
- the radial width rb of the flow passage surface exposed to the high temperature exhaust gas in the first plate member 40 can be made uniform over the entire circumferential direction of the turbine wheel 5.
- the amount of heat input to the first plate member 40 can be made uniform over the circumferential direction, and nonuniform deformation of the first plate member 40 due to thermal expansion can be prevented.
- the back side of the turbine housing 2 is for receiving bearing devices 10A and 10B that rotatably support the rotating shaft 7 coupled with the turbine wheel 5.
- the bearing housing 4 is connected.
- the turbine housing 2 further includes an introduction pipe portion 25 forming an introduction flow passage 18 for guiding the exhaust gas G introduced from the outside of the turbine housing 2 to the scroll flow passage 12.
- the turbine housing 2 does not include the first plate member 40 and the second plate member 44 described above. Instead, the wall surface 4 a of the bearing housing 4 faces the scroll passage 12 and is disposed with a gap between it and the rear surface of the turbine wheel 5.
- the tongue 50 is formed by the tongue member 50 ⁇ / b> C separate from the turbine housing 2 and extending from the bearing housing 4 toward the shroud portion 23. Therefore, when processing the inside of the turbine housing 2 using the opening 16 after casting, the tongue 50 is processed as in the case where the tongue 50 'is integrally formed with the cast turbine housing 2'. It does not get in the way. Thus, the inside of the turbine housing 2 can be easily processed.
- the tongue member 50C described above comprises a third plate member 46 connected to the bearing housing 4.
- the third plate member 46 is connected to the wall surface 4 a of the bearing housing 4 by a method such as welding.
- the third plate member 46 extends along the extending direction of the axis line K of the turbine wheel 5, and its tip end abuts on the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface.
- the third plate member 46 is made of sheet metal.
- the third plate member 46 may be formed by precision casting, or may be formed by metal injection molding (Metal Injection Molding).
- the tongue portion 50 is formed by the third plate member 46 made of sheet metal connected to the wall surface 4 a of the bearing housing 4. Since the third plate member 46 is a separate member from the cast turbine housing 2, the tongue 50 is thinner than in the case where the tongue 50 is integrally formed with the cast turbine housing 2. It is easy. Thereby, generation
- the tip end of the third plate member 46 is in contact with the outer peripheral surface 23 a of the shroud portion 23 which is an inclined surface. For this reason, the force acting in the radial direction from the outer peripheral side to the inner peripheral side acting on the third plate member 46 can be supported by the outer peripheral surface 23 a by the pressure difference. Vibration and deformation can be prevented.
- the tongue member 50C comprises a projection 4A that is integrally manufactured with the cast bearing housing 4.
- the projecting portion 4A extends from the wall surface 4a of the bearing housing 4 along the extending direction of the axis K of the turbine wheel 5, and its tip end abuts on the outer peripheral surface 23a of the shroud portion 23 which is an inclined surface. There is.
- the tongue portion 50 by forming the tongue portion 50 by the projecting portion 4A manufactured integrally with the cast bearing housing 4, the tongue portion which is separate from the turbine housing 2 by a simple structure. 50 can be formed.
- the flow path center 18 c of the introduction flow path 18 is the introduction flow path From the 18 inlets 18 a to the junction 18 b with the scroll flow path 12, it is formed into an S-curve curved inward in the radial direction after being curved inward in the radial direction.
- dotted lines show the shape of the introduction flow path 18 in the turbine housing 2 'of the conventional comparative example shown in FIG.
- the tongue portion 50 is formed by a plate member made of a sheet metal.
- the tongue portion 50 is thin, so that the pressure difference between the outer peripheral side and the inner peripheral side of the tongue portion 50 acts on the tongue portion. Vibration may occur, and the ventilation resistance may increase.
- the pressure on the inner circumferential side of the tongue 50 is lower than that on the outer circumferential side of the tongue 50 because the pressure is reduced by the high-speed exhaust gas flow.
- the flow path center 18c of the introduction flow path 18 is formed into an S-shaped curve, whereby the flow of exhaust gas flowing on the outer peripheral side of the tongue portion 50 is swirled outward.
- the pressure on the outer peripheral side of the tongue 50 can be reduced, and the pressure difference acting on the tongue 50 can be reduced.
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Abstract
Description
排気ガスによって回転するタービンホイールを収容するためのタービンハウジングであって、
前記タービンハウジングは、
前記タービンホイールの周囲において前記タービンホイールに供給される前記排気ガスが流れる環状のスクロール流路を形成するスクロール部と、
前記タービンホイールを通過した前記排気ガスが前記タービンホイールの軸線方向に沿って流れる排気流路を形成する排気管部と、
前記スクロール部と前記排気管部との接続部においてハブ側に迫り出して設けられるシュラウド部であって、前記シュラウド部の外周面は、前記スクロール流路に面するとともに、前記シュラウド部の内周面は、前記タービンホイールの動翼との間に所定の隙間を存して形成されるシュラウド部と、を含む鋳造製のタービンハウジングであって、
前記タービンホイールの軸線方向に沿った断面において、前記タービンホイールの軸線から前記シュラウド部の先端までの半径方向距離をR1、前記タービンホイールの軸線から前記スクロール部のハブ側壁面の内周端までの半径方向距離をR2としたときに、R1<R2となる半径R2を有する開口部が前記スクロール部のハブ側に形成され、
前記タービンホイールの軸線方向に沿った断面において、前記シュラウド部の先端よりも半径方向外側における前記スクロール流路に面する前記シュラウド部および前記スクロール部の流路面の内、前記シュラウド部の先端からの所定範囲を領域A、前記領域Aと隣接する所定範囲を領域Bとしたときに、前記領域Aにおける流路面の粗度が、前記領域Bにおける流路面の粗度よりも小さくなるように構成される。
また、幾つかの実施形態では、領域Aの半径方向における存在範囲は、1.20Dから1.4Dの範囲の少なくとも一部を含むように構成される。
さらに、幾つかの実施形態では、領域Aの半径方向における存在範囲は、1.25Dから1.4Dの範囲の少なくとも一部を含むように構成される。
また、鋳造製のタービンハウジングと一体的に舌部を形成する場合と比べて、舌部を薄く形成することが出来る。これにより、舌部の後流側で発生する流動ひずみの発生を抑制でき、導入流路からスクロール流路に流れる排気ガスの通気抵抗を小さくすることができる。
したがって、上記(13)に記載の実施形態によれば、タービンホイールの円周方向の全周に亘って領域Aを同一の半径方向幅に形成することで、タービンホイールの円周方向の全周に亘って排気ガスの通気抵抗を低減することが出来る。
したがって、上記(14)に記載の実施形態によれば、導入流路の流路中心をS字カーブに形成することで、舌部の外周側を流れる排気ガスの流れを外向きに旋回させることで、舌部外周側での圧力を低下させ、舌部に作用する圧力差を小さくすることが出来る。
排気ガスによって回転するタービンホイールを収容するためのタービンハウジングの製造方法であって、
前記タービンハウジングは、
前記タービンホイールの周囲において前記タービンホイールに供給される前記排気ガスが流れる環状のスクロール流路を形成するスクロール部と、
前記タービンホイールを通過した前記排気ガスが前記タービンホイールの軸線方向に沿って流れる排気流路を形成する排気管部と、
前記スクロール部と前記排気管部との接続部においてハブ側に迫り出して設けられるシュラウド部であって、前記シュラウド部の外周面は、前記スクロール流路に面するとともに、前記シュラウド部の内周面は、前記タービンホイールの動翼との間に所定の隙間を存して形成されるシュラウド部と、を含み、
前記タービンホイールの軸線方向に沿った断面において、前記タービンホイールの軸線から前記シュラウド部の先端までの半径方向距離をR1、前記タービンホイールの軸線から前記スクロール部のハブ側壁面の内周端までの半径方向距離をR2としたときに、R1<R2となる半径R2を有する開口部が前記スクロール部のハブ側に形成され、
前記タービンホイールの軸線方向に沿った断面において、前記シュラウド部の先端よりも半径方向外側における前記スクロール流路に面する前記シュラウド部および前記スクロール部の流路面の内、前記シュラウド部の先端からの所定範囲を領域A、前記領域Aと隣接する所定範囲を領域Bとしたときに、鋳造後に前記領域Aの流路面を加工し、前記領域Aにおける流路面の粗度が、前記領域Bにおける流路面の粗度よりも小さくなるようにする。
例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
一方、一の構成要素を「備える」、「具える」、「具備する」、「含む」、又は、「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。
本発明の一実施形態にかかるターボチャージャ1は、特に限定されないが、例えば自動車用エンジン等に搭載される小型ターボチャージャである。
図1に示したように、本発明の一実施形態にかかるターボチャージャ1は、タービンホイール5を収容するためのタービンハウジング2、コンプレッサホイール6を収容するためのコンプレッサハウジング3、及び一端にタービンホイール5、他端にコンプレッサホイール6が連結される回転軸7を回転可能に支持する軸受装置10A,10Bを収容するためのベアリングハウジング4を備えている。また、タービンホイール5は、裁頭円錐状のハブ部8と、ハブ部8の外周面に間隔を置いて設けられる複数の動翼9とからなる。
また、図3に示すように、タービンハウジング2は、そのスクロール流路12の入口側に、鋳造によって一体的に形成される導入管部25を備えている。
これに対して、図12に示す従来の比較例のタービンハウジング2´における開口部16´では、その半径R2´は、R1´≧R2´の関係にある。この比較例のタービンハウジング2´においては、シュラウド部23´の平行面23b´及び内周面23c´(領域C)については加工されているが、開口部16´の半径R2´が、R1´≧R2´の関係にあるため、シュラウド部23´の外周面23a´までは加工することが困難であった。
幾つかの実施形態では、領域Aの流路面の加工は、鋳造されたタービンハウジングの内部に開口部16からバイト(工具)を挿入し、この状態で鋳造されたタービンハウジング2を回転させることで領域Aの流路面を切削または研削する旋盤加工からなる。
また、鋳造製のタービンハウジング2と一体的に舌部50を形成する場合と比べて、舌部50を薄く形成することが出来る。これにより、舌部50の後流側で発生する流動ひずみの発生を抑制でき、導入流路18からスクロール流路12に流れる排気ガスGの通気抵抗を小さくすることができる。
また、第4プレート部材48の先端部が傾斜面であるシュラウド部23の外周面23aに当接している。このため、圧力差によって第4プレート部材48に対して作用する外周側から内周側に向けての半径方向の作用力を外周面23aによって支持することが出来るため、薄肉に形成される第4プレート部材48の振動や変形を防止することが出来る。
また、屈曲部40Aの先端部が傾斜面であるシュラウド部23の外周面23aに当接している。このため、圧力差によって屈曲部40Aに対して作用する外周側から内周側に向かう半径方向の作用力を外周面23aによって支持することが出来るため、板金製の第1プレート部材40の屈曲部40Aの振動や変形を防止することが出来る。
また、幾つかの実施形態では、図9A,Bに示したように、第2プレート部材44は、板金製からなり、タービンホイール5の軸線方向に沿って折り曲げられてなる屈曲部44Aを有する。そして、この屈曲部44Aにより上述した舌部50が形成される。
なお、図9A,Bに示した実施形態では、屈曲部44Aは折り返された2重のプレートによって形成されているが、これに限定されない。他の実施形態では、図示しないが、屈曲部44Aは、折り返されずに1重のプレートによって形成される。
また、屈曲部44Aの先端部が傾斜面であるシュラウド部23の外周面23aに当接している。このため、圧力差によって屈曲部44Aに対して作用する外周側から内周側に向かう半径方向の作用力を外周面23aによって支持することが出来るため、薄肉に形成される第2プレート部材44の屈曲部44Aの振動や変形を防止することが出来る。
さらに、第3プレート部材46の先端部が傾斜面であるシュラウド部23の外周面23aに当接している。このため、圧力差によって第3プレート部材46に対して作用する外周側から内周側に向かう半径方向の作用力を外周面23aによって支持することが出来るため、板金製の第3プレート部材46の振動や変形を防止することが出来る。
したがって、このような実施形態によれば、導入流路18の流路中心18cをS字カーブに形成することで、舌部50の外周側を流れる排気ガスの流れを外向きに旋回させることで、舌部50の外周側での圧力を低下させ、舌部50に作用する圧力差を小さくすることが出来る。
2 タービンハウジング
3 コンプレッサハウジング
4 ベアリングハウジング
4A 突出部
4a 壁面
5 タービンホイール
6 コンプレッサホイール
7 回転軸
8 ハブ部
9 動翼
9a 前縁
9b 後縁
9c 外周縁
10A,B 軸受装置
12 スクロール流路
14 排気流路
16 開口部
18 導入流路
18a 入口部
18b 合流部
18c 流路中心
21 スクロール部
21a シュラウド側壁面(流路面)
21b 外周側壁面(流路面)
21c ハブ側壁面(流路面)
21d ハブ側壁面の内周端
21e シュラウド側壁面の内周端
22 排気管部
23 シュラウド部
23a 外周面(流路面)
23b 平行面
23c 内周面
23d シュラウド部の先端
24 フランジ部
25 導入管部
26 連結部
27 カップリング
40 第1プレート部材
40A 屈曲部
40a 流路部
40a1 第2プレート部材によって覆われていない部分
40a2 第2プレート部材によって覆われている部分
40b 背面部
40c 外周縁部
40d 段部
44 第2プレート部材
44A 屈曲部
44a 流路部
44a1 外周側の流路部
44a2 内周側の流路部
44c 外周縁部
44d 段部
46 第3プレート部材
48 第4プレート部材
50 舌部
50A 舌部部材
50B 舌部部材
50C 舌部部材
Claims (17)
- 排気ガスによって回転するタービンホイール(5)を収容するためのタービンハウジング(2)であって、
前記タービンハウジング(2)は、
前記タービンホイール(5)の周囲において前記タービンホイール(5)に供給される前記排気ガス(G)が流れる環状のスクロール流路(12)を形成するスクロール部(21)と、
前記タービンホイール(5)を通過した前記排気ガス(G)が前記タービンホイール(5)の軸線方向に沿って流れる排気流路(14)を形成する排気管部(22)と、
前記スクロール部(21)と前記排気管部(22)との接続部においてハブ側に迫り出して設けられるシュラウド部(23)であって、前記シュラウド部(23)の外周面は、前記スクロール流路(12)に面するとともに、前記シュラウド部(23)の内周面は、前記タービンホイール(5)の動翼(9)との間に所定の隙間(c)を存して形成されるシュラウド部(23)と、を含む鋳造製のタービンハウジング(2)であって、
前記タービンホイール(5)の軸線方向に沿った断面において、前記タービンホイールの軸線(K)から前記シュラウド部(23)の先端(23d)までの半径方向距離をR1、前記タービンホイールの軸線(K)から前記スクロール部(21)のハブ側壁面(21c)の内周端(21d)までの半径方向距離をR2としたときに、R1<R2となる半径R2を有する開口部(16)が前記スクロール部(21)のハブ側に形成され、
前記タービンホイール(3)の軸線方向に沿った断面において、前記シュラウド部(23)の先端(23d)よりも半径方向外側における前記スクロール流路(12)に面する前記シュラウド部(23)および前記スクロール部(21)の流路面(21a,21b,21c,23a)の内、前記シュラウド部(23)の先端(23d)からの所定範囲を領域A、前記領域Aと隣接する所定範囲を領域Bとしたときに、前記領域Aにおける流路面の粗度が、前記領域Bにおける流路面の粗度よりも小さくなるように構成されるタービンハウジング。 - 前記タービンホイール(5)の外径をDとしたときに、前記領域Aの半径方向における存在範囲は、1.15Dから1.4Dの範囲の少なくとも一部を含むように構成される請求項1に記載のタービンハウジング。
- 前記タービンホイール(5)の軸線方向に沿った断面において、前記シュラウド部(23)の外周面(23a)は、前記タービンホイールの軸線方向に対して傾斜する傾斜面からなり、前記領域Aは前記外周面(23a)の少なくとも一部を含むように構成される請求項1または2に記載のタービンハウジング。
- 前記開口部(16)に配設され、前記スクロール流路(12)に面する流路部(40a)と、前記タービンホイール(5)の背面との間に隙間を存する背面部(40b)と、を有する環状の第1プレート部材(40)をさらに備える請求項1~3の何れか一項に記載のタービンハウジング。
- 前記タービンハウジング(2)は、前記タービンハウジング(2)の外部から導入される前記排気ガス(G)を前記スクロール流路(12)へと導く導入流路(18)を形成する導入管部(25)をさらに備え、
前記導入流路(18)と前記スクロール流路(12)とを半径方向に仕切る舌部(50)が、前記第1プレート部材(40)側から前記シュラウド部(23)に向かって延在する、前記タービンハウジング(2)とは別体の舌部部材(50A)により形成される請求項4に記載のタービンハウジング。 - 前記舌部部材(50A)は、前記第1プレート部材(40)であって、前記第1プレート部材(40)は、板金製からなり、前記タービンホイール(5)の軸線方向に沿って折り曲げられてなる屈曲部(40A)を有し、前記屈曲部(40A)により前記舌部(50)が形成される請求項5に記載のタービンハウジング。
- 前記タービンハウジング(2)の前記開口部(16)において、前記第1プレート部材(40)の流路部(40a)の一部を覆うように配設される第2プレート部材(50)をさらに備え、
前記舌部部材(50A)は、前記第2プレート部材(44)からなる請求項5に記載のタービンハウジング。 - 前記第2プレート部材(44)は、板金製からなり、前記タービンホイール(5)の軸線方向に沿って折り曲げられてなる屈曲部(44A)を有し、前記屈曲部(44A)により前記舌部(50)が形成される請求項7に記載のタービンハウジング。
- 前記第2プレート部材(44)は、前記タービンホイール(5)の周方向の全周に亘って延在する環状部材からなり、
前記タービンホイール(5)の軸線方向に沿った断面において、前記第1プレート部材(40)における前記第2プレート部材(44)で覆われている部分(40a2)を除いた前記スクロール流路(12)に面する流路部(40a1)が、前記タービンホイール(5)の周方向の全周に亘って同一の半径方向幅(rb)となるように構成されている請求項7又は8に記載のタービンハウジング。 - 前記タービンハウジング(2)の背面側には、前記タービンホイール(5)と連結される回転軸(7)を回転可能に支持する軸受装置(10A,10B)を収容するためのベアリングハウジング(4)が連結され、
前記タービンハウジング(2)は、前記タービンハウジング(2)の外部から導入される前記排気ガス(G)を前記スクロール流路(12)へと導く導入流路(18)を形成する導入管部(25)をさらに備え、
前記導入流路(18)と前記スクロール流路(12)とを半径方向に仕切る舌部(50)が、前記ベアリングハウジング(4)から前記シュラウド部(23)に向かって延在する、前記タービンハウジング(2)とは別体の舌部部材(50C)により形成される請求項1~3の何れか一項に記載のタービンハウジング。 - 前記舌部部材(50C)は、前記ベアリングハウジング(4)に接続される第3プレート部材(46)からなる請求項10に記載のタービンハウジング。
- 前記第3プレート部材(46)は、板金製からなる請求項11に記載のタービンハウジング。
- 前記タービンホイール(5)の軸線方向から視認した断面において、前記領域Aは、前記タービンホイール(5)の円周方向の全周に亘って同一の半径方向幅(ra)に形成される請求項5~12の何れか一項に記載のタービンハウジング。
- 前記タービンホイール(5)の軸線方向から視認した断面において、前記導入流路(18)の流路中心(18c)は、前記導入流路(18)の入口部(18a)から前記スクロール流路(12)との合流部(18b)に向かって、半径方向内側に湾曲した後に半径方向外側に湾曲するS字カーブに形成される請求項6、8及び12の何れか一項に記載のタービンハウジング。
- 排気ガスによって回転するタービンホイール(5)を収容するためのタービンハウジング(2)の製造方法であって、
前記タービンハウジング(2)は、
前記タービンホイール(2)の周囲において前記タービンホイール(5)に供給される前記排気ガス(G)が流れる環状のスクロール流路(12)を形成するスクロール部(21)と、
前記タービンホイール(5)を通過した前記排気ガス(G)が前記タービンホイール(5)の軸線方向に沿って流れる排気流路(14)を形成する排気管部(22)と、
前記スクロール部(21)と前記排気管部(22)との接続部においてハブ側に迫り出して設けられるシュラウド部(23)であって、前記シュラウド部(23)の外周面は、前記スクロール流路(12)に面するとともに、前記シュラウド部(23)の内周面は、前記タービンホイール(5)の動翼(9)との間に所定の隙間(c)を存して形成されるシュラウド部(23)と、を含み、
前記タービンホイール(5)の軸線方向に沿った断面において、前記タービンホイールの軸線(K)から前記シュラウド部(23)の先端(23d)までの半径方向距離をR1、前記タービンホイールの軸線(K)から前記スクロール部(21)のハブ側壁面(21c)の内周端(21d)までの半径方向距離をR2としたときに、R1<R2となる半径R2を有する開口部(16)が前記スクロール部(21)のハブ側に形成され、
前記タービンホイール(3)の軸線方向に沿った断面において、前記シュラウド部(23)の先端(23d)よりも半径方向外側における前記スクロール流路(12)に面する前記シュラウド部(23)および前記スクロール部(21)の流路面(21a,21b,21c,23a)の内、前記シュラウド部(23)の先端(23d)からの所定範囲を領域A、前記領域Aと隣接する所定範囲を領域Bとしたときに、鋳造後に前記領域Aの流路面を加工し、前記領域Aにおける流路面の粗度が、前記領域Bにおける流路面の粗度よりも小さくなるようにするタービンハウジングの製造方法。 - 前記領域Aの流路面の加工は、機械加工からなる請求項15に記載のタービンハウジングの製造方法。
- 前記領域Aの流路面の加工は、鋳造されたタービンハウジングの内部に前記開口部(16)からバイトを挿入し、鋳造されたタービンハウジングを回転させることで前記領域Aの流路面を切削または研削する旋盤加工からなる請求項16に記載のタービンハウジングの製造方法。
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WO2019171431A1 (ja) * | 2018-03-05 | 2019-09-12 | 三菱重工エンジン&ターボチャージャ株式会社 | ターボ過給機及び内燃機関 |
JP7037634B2 (ja) | 2018-03-05 | 2022-03-16 | 三菱重工エンジン&ターボチャージャ株式会社 | ターボ過給機及び内燃機関 |
CN111630258B (zh) * | 2018-03-05 | 2022-05-31 | 三菱重工发动机和增压器株式会社 | 涡轮增压器及内燃机 |
US11384683B2 (en) | 2018-03-05 | 2022-07-12 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Turbocharger and internal combustion engine |
WO2020050051A1 (ja) * | 2018-09-04 | 2020-03-12 | 株式会社Ihi | タービンおよび過給機 |
Also Published As
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EP3187710B1 (en) | 2018-09-05 |
CN107076015B (zh) | 2019-08-20 |
EP3187710A1 (en) | 2017-07-05 |
JPWO2016071959A1 (ja) | 2017-05-25 |
US20170204743A1 (en) | 2017-07-20 |
EP3187710A4 (en) | 2017-10-18 |
JP6351049B2 (ja) | 2018-07-04 |
US10519850B2 (en) | 2019-12-31 |
CN107076015A (zh) | 2017-08-18 |
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