WO2016151849A1 - タービン動翼及び可変容量タービン - Google Patents
タービン動翼及び可変容量タービン Download PDFInfo
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- WO2016151849A1 WO2016151849A1 PCT/JP2015/059419 JP2015059419W WO2016151849A1 WO 2016151849 A1 WO2016151849 A1 WO 2016151849A1 JP 2015059419 W JP2015059419 W JP 2015059419W WO 2016151849 A1 WO2016151849 A1 WO 2016151849A1
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- turbine
- wing
- short
- blade
- side end
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/141—Shape, i.e. outer, aerodynamic form
- F01D5/146—Shape, i.e. outer, aerodynamic form of blades with tandem configuration, split blades or slotted blades
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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
- F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
- F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
- F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
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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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
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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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/146—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by throttling the volute inlet of radial machines or engines
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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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
- F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
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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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/141—Shape, i.e. outer, aerodynamic form
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- 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
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/16—Control of working fluid flow
- F02C9/20—Control of working fluid flow by throttling; by adjusting vanes
- F02C9/22—Control of working fluid flow by throttling; by adjusting vanes by adjusting turbine vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D23/00—Other rotary non-positive-displacement pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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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
- F05D2210/00—Working fluids
- F05D2210/40—Flow geometry or direction
- F05D2210/43—Radial inlet and axial outlet
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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
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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
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/303—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the leading edge of a rotor blade
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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
- F05D2250/00—Geometry
- F05D2250/90—Variable geometry
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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 turbine blades and variable capacity turbines.
- Patent Document 1 in a mixed flow turbine having two scroll flow paths on the hub side and the shroud side, an intermediate-height intermediate blade is provided in a portion having impulse blade turbine characteristics on the hub side to improve impulse blade turbine characteristics
- a mixed flow turbine is disclosed that aims to reduce the moment of inertia of the entire turbine blade and to improve both the efficiency of the turbine and the transient response.
- the mixed flow turbine of Patent Document 1 there is a problem that the reduction of the moment of inertia is not sufficient, and it is difficult to improve the transient response.
- At least one embodiment of the present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to improve the turbine efficiency at a small flow rate and improve the transient response.
- a turbine blade comprises a hub portion connected to one end of a rotating shaft, a plurality of main wings provided at intervals on a circumferential surface of the hub portion, and a plurality of main wings And a short wing provided between two main wings adjacent to each other. Between two adjacent main wings, an inter-blade flow path is formed in which a fluid flows radially inward from the radially outer side of the turbine blade. And, the hub side end of the leading edge of the short wing is configured to be located radially inward of the hub side end of the leading edge of the main wing on the meridional plane.
- the fluid flowing into the turbine blade flows from the radially outer side of the turbine blade radially inward and obliquely to the leading edge of the main blade. For this reason, the fluid flowing into the turbine blade collides with the leading edge of the main blade and is separated, resulting in loss. Further, according to the findings of the inventor of the present invention, the fluid flowing into the turbine blade collides with the front edge of the main blade and exfoliates, thereby inducing a secondary flow having a swirl component in the inter-blade flow passage, Secondary flow also causes losses.
- the leading edge of the main wing by providing a short short wing whose leading edge position in the radial direction is the same as the leading edge position of the main wing between the two adjacent main wings, the leading edge of the main wing and It is possible to suppress the separation at the leading edge of the short wing.
- the reduction effect of the secondary flow flowing in the inter-blade flow path is limited. This is because the secondary flow flowing between the main wing and one surface of the short wing (for example, suction surface) and the secondary flow flowing between the adjacent main wing and the other surface of the short wing (for example, pressure surface) It is considered that the collision occurs at the downstream side of the short wing in the interflow passage and the loss is generated. Further, by providing the short blades radially outward in the turbine moving blade, the moment of inertia is increased, and the transient response is deteriorated.
- the turbine blade described in the above (1) includes a short blade provided between two adjacent main blades, and the hub side end of the leading edge of the short blade is a main blade on the meridional plane Is located radially inward of the hub end of the front edge of the.
- this configuration makes it possible to greatly reduce the loss due to the secondary flow flowing in the flow path between the next time. Further, by providing the short blade inward in the radial direction of the turbine moving blade, it is possible to suppress an increase in moment of inertia caused by providing the short blade.
- a turbine moving blade not provided with the short blade or a turbine provided with the short blade at the radially outer position It is possible to reduce the number of wings as compared to blades. Therefore, although the loss due to the separation of the leading edge of each main wing increases, it is possible to suppress the loss due to the separation of the leading edge of the main wing as a whole of the turbine blade. In addition, reducing the number of wings can reduce the moment of inertia.
- the hub side end of the trailing edge of the short wing is in axial direction with the hub side end of the trailing edge of the main wing on the meridional plane Or the downstream end of the trailing edge of the main wing in the fluid flow direction.
- the secondary flow flowing between the main wing and one surface of the short wing and the secondary flow flowing between the adjacent main wing and the other surface of the short wing are the wings It is possible to prevent collisions in the flow path. Thereby, it is possible to reduce the loss due to the secondary flow flowing in the inter-blade flow path.
- the distance from the hub side end of the leading edge of the main wing to the hub side end of the trailing edge of the main wing on the meridional plane is Lh 1
- the hub side end of the leading edge of the short wing is 0.30 ⁇ It is configured to be located in a region satisfying Lh2 / Lh1 ⁇ 0.89.
- the separated flow generated by collision with the leading edge of the main wing is a short wing. Collide with the leading edge of the In addition, the moment of inertia also increases.
- the distance from the hub side end of the leading edge of the main wing to the hub side end of the leading edge of the short wing is too long, it is not possible to sufficiently suppress the loss due to the secondary flow in the flow path between the wings.
- the hub side end of the leading edge of the short wing is positioned in a region that satisfies 0.52 ⁇ Lh2 / Lh1 ⁇ 0.84. Configured to
- the hub side end of the leading edge of the short wing is positioned in a region satisfying 0.60 ⁇ Lh2 / Lh1 ⁇ 0.80.
- the hub side end of the trailing edge of the short wing is closer to the hub side end of the trailing edge of the main wing Is also configured to be located downstream in the fluid flow direction.
- the hub side end of the trailing edge of the short wing is configured to be located downstream of the hub side end of the trailing edge of the main wing in the fluid flow direction . That is, the hub side end of the trailing edge of the short wing is configured to be located on the meridional plane at the tip end side of the hub portion in the axial direction than the hub side end of the trailing edge of the main wing.
- the shroud side end of the trailing edge of the short blade is configured to be located on the trailing edge of the main wing on the meridional plane Be done.
- the short blade is compared with the case where the entire trailing edge of the short blade is positioned downstream of the trailing edge of the main wing while reducing the loss due to the secondary flow.
- the shape of can be reduced, and the moment of inertia can be reduced.
- the wing height of the short wing is configured to be lower than the wing height of the main wing.
- the effect of reducing the secondary flow flowing in the inter-blade flow path by providing the short wings contributes more to the hub-side portion of the short wings than the shroud-side portion. Therefore, according to the embodiment described in (8), by making the blade height of the short blade lower than that of the main blade, it is possible to reduce the moment of inertia while reducing the loss due to the secondary flow. It can.
- a variable capacity turbine comprises a turbine bucket according to any of the above (1) to (8), a turbine housing accommodating the turbine bucket, and a turbine bucket And a variable nozzle mechanism for controlling the flow direction of the fluid flowing toward the head.
- the flow direction of the fluid flowing into the turbine blades is smaller at higher flow rates than at high flow rates.
- the angle between it and the tangential direction is smaller. For this reason, the loss due to separation generated when the fluid flowing into the turbine moving blade collides with the leading edge of the main blade is greater in the small flow rate than in the large flow rate. Therefore, according to the embodiment described in the above (9), since the above-described turbine moving blade is provided, it is possible to improve the turbine efficiency at a small flow rate in the variable capacity turbine.
- FIG. 1 is a cross-sectional view of a variable capacity turbine according to an embodiment of the present invention. It is a figure showing a turbine bucket concerning one embodiment of the present invention.
- FIG. 5 is a diagram showing a meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- FIG. 5 is a diagram showing a meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- FIG. 5 is a diagram showing a meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- FIG. 5 is a diagram showing a meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- FIG. 5 is a diagram showing a meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- variable capacity turbine concerning one embodiment of the present invention, it is an explanatory view for explaining the flow of the fluid at the time of large flow volume and small flow volume. It is a figure showing a turbine bucket concerning a 1st comparative form. It is a figure showing a turbine bucket concerning a 2nd comparative form.
- 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 schematic cross-sectional view of a variable capacity turbine according to an embodiment of the present invention.
- a variable displacement turbine 10 according to an embodiment of the present invention includes a turbine bucket 1, a turbine housing 2 accommodating the turbine bucket 1, and a fluid (for example, flowing toward the turbine bucket 1) And a variable nozzle mechanism 3 for controlling the flow direction of the exhaust gas discharged from an engine (not shown).
- FIG. 2 is a view showing a turbine blade according to an embodiment of the present invention.
- (A) of FIG. 2 is a perspective view of the turbine bucket 1 and (b) of FIG. 2 is a diagram showing the flow of fluid flowing through the turbine bucket 1.
- the turbine rotor blade 1 includes a hub portion 11 connected to one end side of the rotation shaft 4, a plurality of main wings 12 provided at intervals on the circumferential surface of the hub portion 11, and a plurality of main wings It includes a short wing 13 provided between two adjacent main wings 12 of the twelve.
- an inter-blade flow path 14 in which the fluid flows radially inward from the radially outer side of the turbine bucket 1 is formed between the two adjacent main wings 12, 12. Be done.
- one short wing 13 is provided between two adjacent main wings 12, 12. And eight main wings 12 and eight short wings 13 are arranged alternately at equal intervals.
- the turbine moving blade 1 according to an embodiment of the present invention is not limited to this form, and two or more short blades 13 may be provided between two adjacent main blades 12, 12.
- the short wing 13 may not necessarily be provided between all the two adjacent main wings 12, 12, such as the short wings 13 may be provided alternately between the two adjacent main wings 12, 12. .
- the turbine housing 2 is formed along the extending direction of the scroll channel 21 formed on the outer peripheral side of the turbine bucket 1 and the rotation axis K of the rotating shaft 4.
- An outlet channel 22 is formed inside.
- the turbine housing 2 is connected to the bearing housing 5 on the side opposite to the open end of the outlet channel 22.
- a bearing 51 rotatably supporting the rotating shaft 4 is accommodated in the bearing housing 5.
- FIGS. 3 to 7 are diagrams showing the meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- the turbine rotor blade 1 according to one embodiment of the present invention has the hub side end 131 a of the front edge 131 of the short wing 13 on the meridional plane It is comprised so that it may be located inside radial direction rather than the hub side end 121a of 121.
- FIG. 1 is a diagram showing the meridional surface shape of a turbine bucket according to an embodiment of the present invention.
- the turbine rotor blade 1 has the hub side end 131 a of the front edge 131 of the short wing 13 on the meridional plane It is comprised so that it may be located inside radial direction rather than the hub side end 121a of 121.
- FIG. 10A is a view showing a turbine blade according to a first comparative embodiment.
- FIG. 10A (a) is a perspective view of a turbine rotor blade 1 '
- FIG. 10A (b) is a diagram showing the flow of fluid flowing through the turbine rotor blade 1'.
- FIG. 10B is the figure which showed the turbine moving blade concerning 2nd comparison form.
- FIG. 10B (a) is a perspective view of the turbine rotor blade 1 '
- FIG. 10B (b) is a diagram showing the flow of fluid flowing through the turbine rotor blade 1'.
- the fluid flowing into the turbine bucket 1 from the scroll passage 21 is, as indicated by an arrow f in FIG.
- the position of the front edge 131 ′ in the radial direction between two adjacent main wings 12 ′, 12 ′ is the front edge 121 of the main wing 12 ′.
- a short short wing 13 ' which is the same as the position of', separation at the front edge 121 'of the main wing 12' and the front edge 131 'of the short wing 13' can be suppressed.
- the reduction effect of the loss due to the secondary flow sf 'flowing in the inter-blade flow passage 14' is limited.
- the secondary flow sf2 'flowing between the lower surface 13 and the surface c collides on the downstream side of the short wing 13' in the inter-blade flow passage 14 'and a loss occurs.
- the short blades 13 'on the radially outer side of the turbine moving blade 1' the moment of inertia is increased, and the transient response is deteriorated.
- the turbine bucket 1 includes the short wing 13 provided between two adjacent main wings 12, and the hub side end of the front edge 131 of the short wing 13 131a is located radially inward of the hub end 121a of the front edge 121 of the main wing 12 on the meridional plane.
- this configuration makes it possible to largely reduce the loss due to the secondary flows sf1 and sf2 flowing in the flow path 14 between next time as compared with the turbine rotor blade 1 'of the second comparative embodiment.
- by providing the short blades 13 inside the turbine moving blade 1 in the radial direction it is possible to suppress an increase in the moment of inertia due to the short blades 13 as compared with the second comparative embodiment described above.
- the turbine rotor blade 1 of the first comparative embodiment in which the short blades are not provided by providing the short blades 13 inside the radial direction of the turbine rotor blade 1.
- the number of main blades can be reduced.
- eight main wings 12 and eight short wings 13 are provided, whereas in the first comparative embodiment, eleven main wings 12 'are provided.
- ten main wings 12 'and ten short wings 13' are provided.
- the short blade 13 When the short blade 13 is provided on the radially inner side of the turbine moving blade 1, the short blade 13 crosses the minimum width portion of the inter-blade flow passage 14. For this reason, in order to make the minimum width part (throat part) of the main wing 12 and the short wing 13 into an appropriate throat width, the number of main wings 12 will be reduced. Therefore, according to the turbine rotor blade 1 according to one embodiment of the present invention, although the loss due to the separation of the front edge 121 of each main wing 12 increases, the separation due to the separation at the front edge 121 of the main wing 12 as the entire turbine rotor blade 1 Loss can be suppressed. In addition, by reducing the number of main wings 12, the moment of inertia can be reduced.
- the hub end 132a of the trailing edge 132 of the short wing 13 of the turbine bucket 1 is the trailing edge 122 of the main wing 12 on the meridional plane. Or at the same position in the axial direction as the hub side end 122a of the hub 12 or at the downstream side in the fluid flow direction (the tip side of the hub portion 11 in the axial direction) than the hub side end 122a of the trailing edge 122 of the main wing 12 Configured to
- the hub end 132a of the trailing edge 132 of the short blade 13 of the turbine bucket 1 is the hub end of the trailing edge 122 of the main wing 12 on the meridional plane. It is located at the same position in the axial direction as 122a.
- the hub side end 132a of the trailing edge 132 of the short wing 13 of the turbine bucket 1 is on the hub side of the trailing edge 122 of the main wing 12 on the meridional plane. It is configured to be positioned on the tip side of the hub portion 11 in the axial direction with respect to the end 122a.
- the secondary flow sf1 flowing between the main wing 12 and the one surface 13a of the short wing 13 and the secondary flow sf2 flowing between the adjacent main wing 12 and the other surface 13b of the short wing 13 Can be prevented from colliding in the inter-blade flow passage 14. Thereby, it is possible to reduce the loss due to the secondary flows sf1 and sf2 flowing in the inter-blade flow path 14.
- FIG. 8A is a diagram showing the relationship between the leading edge position of the short blade and the turbine efficiency in the turbine bucket according to one embodiment of the present invention.
- FIG. 8B is a diagram showing the relationship between the position of the leading edge of the short blade and the moment of inertia in the turbine bucket according to one embodiment of the present invention.
- the horizontal axis represents the distance Lh1 from the hub side end 121a of the leading edge 121 of the main wing 12 to the hub side end 122a of the trailing edge 122 of the main wing 12 on the meridional plane.
- the ratio (Lh2 / Lh1) of Lh2 to Lh1 is shown.
- the vertical axis in FIG. 8A indicates the change in turbine efficiency relative to the reference turbine blade.
- the vertical axis in FIG. 8B indicates the change in moment of inertia with respect to the reference turbine blade.
- Lh2 / Lh1 is “0”, “0.2”, “0.4”, “0.6”, “0.8”, “1”.
- the changes in the turbine efficiency and the moment of inertia when changing were made were analyzed, and their approximate curves were obtained.
- a turbine blade having eight main wings and eight short wings is used.
- Lh2 / Lh1 in the horizontal axis in FIG. 8A and FIG. 8B is "0" for a turbine blade having only a main blade, and corresponds to a turbine blade having only 16 main blades.
- Lh 2 / Lh 1 is “1”, which means a turbine blade without a short blade, and corresponds to a turbine blade having only eight main blades.
- the above-mentioned reference turbine moving blade is a turbine moving blade 1 ′ having only 11 main blades shown in FIG. 10A.
- the wing height of the short wing is the same as the wing height of the main wing.
- analysis is performed using computational fluid dynamics (CFD), but the method of analysis is not particularly limited to computational fluid dynamics (CFD).
- the hub side end 131a of the front edge 131 of the short wing 13 is positioned in a region satisfying 0.30 ⁇ Lh2 / Lh1 ⁇ 0.89.
- the loss due to the secondary flows sf1 and sf2 flowing in the inter-blade flow path 14 is reduced, and 1% or more of the turbine blade 1 'serving as a reference having only 11 main It has become clear that turbine efficiency can be improved.
- the hub side end 131a of the front edge 131 of the short wing 13 is located in the area
- the hub side end 131a of the front edge 131 of the short wing 13 is positioned in a region satisfying 0.60 ⁇ Lh2 / Lh1 ⁇ 0.80. It became clear that the improvement of the turbine efficiency of 1.6% or more can be achieved with respect to turbine blade 1 'mentioned above by comprising.
- the hub side end 131 a of the trailing edge 131 of the short wing 13 flows more fluid than the hub side end 122 a of the trailing edge 122 of the main wing 12. It is configured to be located downstream (radially inward) in the direction.
- the secondary flow sf1 flowing between the main wing 12 and the one surface 13a of the short wing 13 and the secondary flow sf2 flowing between the adjacent main wing 12 and the other surface 13b of the short wing 13 Can be separated from the trailing edge 122 of the wing 12 downstream.
- the shroud end 132b of the trailing edge 132 of the short wing 13 is configured to be located on the trailing edge 122 of the main wing 12 on the meridional plane. Ru.
- the secondary flow sf1 flowing between the main wing 12 and the first face 13a of the short wing 13 and the secondary flow sf2 flowing between the adjacent main wing 12 and the second face 13b of the short wing 13 The effect of being able to move the collision position downstream of the trailing edge 122 of the main wing 12 contributes more to the hub side portion of the short wing 13 than to the shroud side portion. Therefore, according to such an embodiment, the secondary flow sf1 and sf2 cause the entire trailing edge 132 of the short wing 13 to be positioned downstream of the trailing edge 122 of the main wing 12 (FIG. 4).
- the shape of the short wing 13 can be reduced while reducing the loss, and the moment of inertia can be reduced.
- the wing height H2 of the short wing 13 is configured to be lower than the wing height H1 of the main wing 12.
- the effect of reducing the loss due to the secondary flow sf1 and sf2 flowing in the inter-blade flow passage 14 by providing the short wing 13 is that, as described above, the short wing 13 on the hub side is more than the shroud side portion Make a big contribution. Therefore, according to such an embodiment, by making the blade height H2 of the short blade 13 lower than the blade height H1 of the main blade 12, the loss due to the secondary flows sf1 and sf2 is reduced, and the moment of inertia is reduced. It can be planned.
- the wing height H2 of the short wing 13 is in the range of 1 / 3H1 ⁇ H2 ⁇ 2 / 3H1. According to such an embodiment, it is possible to appropriately reduce the moment of inertia while reducing the loss due to the secondary flows sf1 and sf2.
- variable capacity turbine 10 flows toward the turbine housing 2 housing the turbine bucket 1 and the turbine bucket 1 And a variable nozzle mechanism 3 for controlling the flow direction of the fluid.
- the variable nozzle mechanism 3 includes a nozzle mount 31, a nozzle plate 32, a nozzle support 33 and a nozzle vane 34.
- the nozzle mount 31 is a disk-shaped member having an opening at the central portion, and the outer peripheral portion thereof is held between the turbine housing 2 and the bearing housing 5 so that the space between the turbine housing 2 and the bearing housing 5 is obtained. It is fixed.
- the nozzle plate 32 is a disk-shaped member having an opening at a central portion, and is fixed to the shroud portion 23 of the turbine housing 2 at a position facing the nozzle mount 31.
- the nozzle mount 31 and the nozzle plate 32 are connected by a plurality of nozzle supports 33.
- a plurality of nozzle vanes 34 are arranged at intervals in the circumferential direction between the nozzle mount 31 and the nozzle plate 32.
- a nozzle flow passage 34 a is formed between the adjacent nozzle vanes 34, 34.
- the nozzle vanes 34 are configured such that their blade angles change as the nozzle shaft 35 is rotated about its axis by the drive mechanism 36.
- FIG. 9 is an explanatory diagram for explaining the flow of fluid at high flow rates and low flow rates in the variable capacity turbine according to the embodiment of the present invention.
- each of the plurality of nozzle vanes 34 rotates in a direction in which the nozzle flow path 34 a formed between two adjacent nozzle vanes 34 expands.
- each of the plurality of nozzle vanes 34 rotates in the direction in which the nozzle flow path 34a formed between the two adjacent nozzle vanes 34 narrows.
- the flow directions fa and fb of the fluid flowing into the turbine moving blade 1 are smaller at the small flow rate (fa) than at the large flow rate (fb) with respect to the tangential direction of the turbine moving blade 1. For this reason, the loss caused by separation caused by the fluid flowing into the turbine moving blade 1 colliding with the front edge 121 of the main blade 12 has a greater effect at a small flow rate than at a large flow rate.
- variable displacement turbine 10 since the above-described turbine moving blade 1 is provided, it is possible to improve the turbine efficiency at a small flow rate.
- variable displacement turbine 10 shown in FIG. 1 described above is configured as a radial turbine in which a fluid flows from the radial direction to the turbine moving blade 1.
- variable capacity turbine 10 according to an embodiment of the present invention is not limited to this, and may be configured as a mixed flow turbine in which fluid flows in an oblique direction to the turbine moving blade 1.
- variable nozzle mechanism 4 rotating shaft 5 bearing housing 10 variable displacement turbine 11 hub portion 12 main wing 121 leading edge 121 a of main wing 121 side of wing leading edge of main wing hub side end 122 of leading edge of wing Hub end 13 Short wing 131 Short wing front edge 131a Short wing front edge Hub side end 132 Short wing trailing edge 132a Short wing trailing edge Hub side end 132b Short wing trailing edge 13a Short wing one surface 13b Short wing other surface 14 Wing flow channel 21 Scroll flow channel 22 Exit flow channel 23 Shroud portion 31 Nozzle mount 32 Nozzle plate 33 Nozzle support 34 Nozzle vane 34a Nozzle flow channel 35 Nozzle shaft 36 Drive mechanism 51 Bearing
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Abstract
Description
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。
また、以下の説明において、同じ構成には同じ符号を付してその詳細な説明を省略する場合がある。
また、以下の比較形態の説明において、実施形態に対応する構成には同じ符号に「´」を付してその詳細な説明を省略する場合がある。
図1に示すように、本発明の一実施形態にかかる可変容量タービン10は、タービン動翼1と、タービン動翼1を収容するタービンハウジング2と、タービン動翼1に向かって流れる流体(例えば、不図示のエンジンから排出される排気ガス)の流れ方向を制御するための可変ノズル機構3とを備える。
図2に示すように、タービン動翼1は、回転軸4の一端側に連結されるハブ部11と、ハブ部11の周面に間隔を置いて設けられる複数の主翼12と、複数の主翼12のうちの互いに隣接する2つの主翼12,12の間に設けられる短翼13とを含んでいる。そして、隣接する2つの主翼12,12の間には、図2の矢印Rに示すように、タービン動翼1の半径方向外側から半径方向内側に向かって流体が流れる翼間流路14が形成される。
本発明の一実施形態にかかるタービン動翼1は、図2及び図3~図7に示すように、短翼13の前縁131のハブ側端131aが、子午面上において主翼12の前縁121のハブ側端121aよりも半径方向内側に位置するように構成される。
スクロール流路21からタービン動翼1に流入する流体は、図2の(b)の矢印fで示したように、タービン動翼1の半径方向外側から半径方向内側に向かって、主翼12の前縁121に対して斜め方向に流れる。このため、図10Aに示すように、タービン動翼1´に流入する流体が主翼12´の前縁121´に衝突して剥離し、損失が発生する。また、本発明者の知見によれば、タービン動翼1´に流入する流体が主翼12´の前縁121´に衝突して剥離することで、翼間流路14´内に旋回成分を有する二次流れsf´を誘発し、この二次流れsf´によっても損失が発生する。
したがって、本発明の一実施形態にかかるタービン動翼1によれば、各主翼12の前縁121の剥離による損失は大きくなるものの、タービン動翼1全体としての主翼12の前縁121における剥離による損失を抑制することが出来る。また、主翼12の枚数を減らすことで、慣性モーメントを低減することが出来る。
例えば、上述した図1に示す可変容量タービン10は、タービン動翼1に対して半径方向から流体が流入するラジアルタービンとして構成されている。しかしながら、本発明の一実施形態にかかる可変容量タービン10はこれに限定されず、タービン動翼1対して斜め方向に流体が流入する斜流タービンとして構成されてもよいものである。
2 タービンハウジング
3 可変ノズル機構
4 回転軸
5 軸受ハウジング
10 可変容量タービン
11 ハブ部
12 主翼
121 主翼の前縁
121a 主翼の前縁のハブ側端
122 主翼の後縁
122a 主翼の後縁のハブ側端
13 短翼
131 短翼の前縁
131a 短翼の前縁のハブ側端
132 短翼の後縁
132a 短翼の後縁のハブ側端
132b 短翼の後縁のシュラウド側端
13a 短翼の一面
13b 短翼の他面
14 翼間流路
21 スクロール流路
22 出口流路
23 シュラウド部
31 ノズルマウント
32 ノズルプレート
33 ノズルサポート
34 ノズルベーン
34a ノズル流路
35 ノズル軸
36 駆動機構
51 軸受
Claims (9)
- 回転軸の一端側に連結されるハブ部と、
前記ハブ部の周面に間隔を置いて設けられる複数の主翼と、
前記複数の主翼のうちの互いに隣接する2つの主翼の間に設けられる短翼と、を備えるタービン動翼であって、
前記隣接する2つの主翼の間には、前記タービン動翼の半径方向外側から半径方向内側に向かって流体が流れる翼間流路が形成され、
前記短翼の前縁のハブ側端は、子午面上において前記主翼の前縁のハブ側端よりも半径方向内側に位置する
タービン動翼。 - 前記短翼の後縁のハブ側端は、子午面上において、前記主翼の後縁のハブ側端と軸方向において同じ位置に位置するか、又は前記主翼の後縁のハブ側端よりも前記流体の流れ方向の下流側に位置する
請求項1に記載のタービン動翼。 - 前記子午面上における、前記主翼の前縁のハブ側端から前記主翼の後縁のハブ側端までの距離をLh1、
前記子午面上における、前記主翼の前縁のハブ側端から前記短翼の前縁のハブ側端までの距離をLh2、としたときに、
前記短翼の前縁のハブ側端は、0.30<Lh2/Lh1<0.89を満たす領域に位置する
請求項2に記載のタービン動翼。 - 前記短翼の前縁のハブ側端は、0.52<Lh2/Lh1<0.84を満たす領域に位置する
請求項3に記載のタービン動翼。 - 前記短翼の前縁のハブ側端は、0.60<Lh2/Lh1<0.80を満たす領域に位置する
請求項4に記載のタービン動翼。 - 前記短翼の後縁のハブ側端は、前記主翼の後縁のハブ側端よりも前記流体の流れ方向の下流側に位置する
請求項2から5の何れか一項に記載のタービン動翼。 - 前記短翼の後縁のシュラウド側端は、前記子午面上において、前記主翼の後縁上に位置する
請求項6に記載のタービン動翼。 - 前記短翼の翼高は、前記主翼の翼高よりも低い
請求項1から7の何れか一項に記載のタービン動翼。 - 請求項1から8の何れか一項に記載のタービン動翼と、
前記タービン動翼を収容するタービンハウジングと、
前記タービン動翼に向かって流れる流体の流れ方向を制御するための可変ノズル機構と、を備える可変容量タービン。
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PCT/JP2015/059419 WO2016151849A1 (ja) | 2015-03-26 | 2015-03-26 | タービン動翼及び可変容量タービン |
CN201580071129.4A CN107109943B (zh) | 2015-03-26 | 2015-03-26 | 涡轮动叶片及可变容量涡轮 |
US15/538,051 US10563515B2 (en) | 2015-03-26 | 2015-03-26 | Turbine impeller and variable geometry turbine |
EP15886402.5A EP3236007B1 (en) | 2015-03-26 | 2015-03-26 | Turbine rotor blade and variable capacity turbine |
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JP2017193985A (ja) * | 2016-04-19 | 2017-10-26 | 本田技研工業株式会社 | タービンインペラ |
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