WO2016103572A1 - ロータ - Google Patents
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- Publication number
- WO2016103572A1 WO2016103572A1 PCT/JP2015/005837 JP2015005837W WO2016103572A1 WO 2016103572 A1 WO2016103572 A1 WO 2016103572A1 JP 2015005837 W JP2015005837 W JP 2015005837W WO 2016103572 A1 WO2016103572 A1 WO 2016103572A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- blade
- line
- radial direction
- leading edge
- Prior art date
Links
- 238000010248 power generation Methods 0.000 abstract description 22
- 239000012530 fluid Substances 0.000 abstract description 16
- 230000002093 peripheral effect Effects 0.000 description 14
- 230000000052 comparative effect Effects 0.000 description 5
- 230000007423 decrease Effects 0.000 description 3
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 230000001154 acute effect Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
- F03D1/06—Rotors
- F03D1/0608—Rotors characterised by their aerodynamic shape
- F03D1/0633—Rotors characterised by their aerodynamic shape of the blades
- F03D1/0641—Rotors characterised by their aerodynamic shape of the blades of the section profile of the blades, i.e. aerofoil profile
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/04—Machines or engines of reaction type; Parts or details peculiar thereto with substantially axial flow throughout rotors, e.g. propeller turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
- F03B3/121—Blades, their form or construction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
- F03D1/06—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
- F03D1/06—Rotors
- F03D1/0608—Rotors characterised by their aerodynamic shape
- F03D1/0633—Rotors characterised by their aerodynamic shape of the blades
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/16—Air or water being indistinctly used as working fluid, i.e. the machine can work equally with air or water without any modification
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/20—Rotors
- F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05B2240/301—Cross-section characteristics
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/20—Rotors
- F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05B2240/303—Details of the leading edge
-
- 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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
-
- 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
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the present invention relates to a rotor for a wind-hydraulic machine comprising a hub supported by a main shaft and a blade having a base end coupled to the hub.
- a blade leading edge connects a rotor radial inner end and a rotor radial outer end of the leading edge on a projection plane perpendicular to the rotation center axis of the rotor.
- a projection plane perpendicular to the rotation center axis of the rotor There is one that projects forward in the rotational direction of the rotor with respect to the first line segment (for example, Patent Document 1).
- the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a rotor for a wind and hydraulic power machine in which the stability of power generation efficiency with respect to fluctuations in fluid speed and direction is improved. .
- the gist configuration of the present invention for achieving the above object is as follows.
- the rotor of the present invention is A rotor for a wind and hydraulic power machine comprising a hub supported by a main shaft and a blade having a proximal end coupled to the hub, In the projection plane perpendicular to the rotation center axis of the rotor, the leading edge of the blade has a leading edge peak portion protruding in a mountain shape toward the front side in the rotor rotation direction only at two different rotor radial direction positions.
- the tangent line of the hub at the rotor circumferential center point of the base end of the blade is a first virtual line VL1
- imaginary line VL2 is assumed
- the leading edge of the blade has a protruding tip of one of the leading edge crests at a portion on the inner side in the rotor radial direction from the second imaginary line VL2, and is located on the outer side in the rotor radial direction from the second imaginary line VL2. It is preferable that the portion has a protruding tip of the other front edge crest. According to this configuration, it is possible to further improve the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid.
- the rotor of the present invention In the projection plane, Parallel to the first imaginary line VL1 and away from the first imaginary line VL1 to the opposite side of the hub by a length of 0.25, 0.75, and 1.00 times the blade length BL.
- the width BW4 of the blade along VL4 and the width BW5 of the blade along the fifth virtual line VL5 are inequalities BW1 ⁇ BW3 BW3>BW2>BW4> BW5 Is preferably satisfied. With this configuration, it is possible to further improve the stability of the power generation efficiency against fluctuations in the speed and direction of the fluid.
- the leading end of the leading edge crest on the inner side in the rotor radial direction is the front end of the blade on the inner side in the rotor radial direction and the front side on the outer side in the rotor radial direction. It is preferable to be on the front side in the rotor rotation direction with respect to the first line segment L1 connecting the protruding tip of the edge mountain portion. According to this configuration, the output coefficient when the peripheral speed ratio is relatively low can be greatly improved.
- the protruding tip of the leading edge crest on the outer side in the rotor radial direction is the protruding tip of the leading edge crest on the inner side in the rotor radial direction, and the leading edge of the blade It is preferable that it exists in the rotor rotation direction front side with respect to the 2nd line segment L2 which tied the rotor radial direction outer side. According to this configuration, the output coefficient when the peripheral speed ratio is relatively high can be greatly improved.
- the trailing edge of the blade intersects with the third line segment L3 connecting the rotor radial inner end and the rotor radial outer end of the blade trailing edge at one point,
- the portion on the inner side in the rotor radial direction from the intersection with the third line segment L3 is on the rear side in the rotor rotation direction with respect to the third line segment L3.
- a portion on the outer side in the rotor radial direction with respect to the intersection with the third line segment L3 is on the front side in the rotor rotation direction with respect to the third line segment L3. According to this configuration, it is possible to further improve the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid.
- FIG. 1 It is a front view which shows one Embodiment of the rotor of this invention. It is a perspective view of the rotor shown in FIG. It is the figure which expand
- FIG. 1 is a front view showing an embodiment of a rotor of the present invention.
- FIG. 2 is a perspective view showing the rotor 1 shown in FIG.
- the rotor 1 of the present embodiment is used for a wind hydraulic machine, and more specifically, is used for a wind power generator in this example.
- the “wind hydraulic machine” in the present invention means a machine that uses power obtained by wind power or hydraulic power, such as a wind power generator (wind turbine, etc.) or a hydro power generator (water turbine, etc.).
- the rotor 1 of this embodiment can be used not only for a wind power generator but also for a hydroelectric power generator or other wind hydraulic machines.
- the rotor 1 of the present embodiment preferably has a diameter ⁇ of 741 to 1111 mm, for example, and in the example shown in the figure, the diameter ⁇ of the rotor 1 is 926 mm.
- the rotor 1 of the present embodiment includes a hub 10 supported by a main shaft (not shown), and three blades 20 having a base end 21 coupled to the hub 10.
- the main shaft (not shown) extends rearward from the back surface of the hub 10 when viewed in FIG. 1 and is horizontally installed in this example.
- the central axis of the main shaft becomes the rotation central axis O of the rotor 1.
- the number of blades 20 is not limited to three and can be any number.
- the blades 20 of the rotor 1 have the same shape in this example, but some blades may have a shape different from other blades.
- the leading edge 31 of the blade 20 is only in two different rotor radial positions, and the rotor
- the front edge crests 36 and 37 protrude in a mountain shape toward the front side in the rotation direction RD.
- the shape of the leading edge ridges 36 and 37 on the projection plane is, for example, a Gaussian curve, A shape that is retreated at both sides of the protruding tip, such as a triangular shape, and is not a shape in which only one side of the protruding tip is retracted, such as an inclined line or a proportional curve. ing.
- the projecting tip portions of the leading edge crests 36 and 37 on the projection plane are formed in a rounded curved shape, which is from the viewpoint of reducing air resistance and thus improving power generation efficiency. preferable.
- the projecting tip portions of the front edge crests 36 and 37 on the projection surface may be formed in a sharply pointed shape.
- the front edge 31 of the blade 20 has the first front edge peak portion 36 which is more radially inward of the two front edge peak portions 36 and 37, so that wind power generation when the peripheral speed ratio is relatively low.
- the output coefficient of the machine can be obtained sufficiently satisfactorily.
- the front edge 31 of the blade 20 has the second front edge peak portion 37 which is more radially outside of the two front edge peak portions 36 and 37, the peripheral speed ratio is relatively high.
- the output coefficient of the wind power generator can be obtained sufficiently satisfactorily. Therefore, according to this embodiment, for example, compared with a case where the front edge 31 has only one front edge crest, a sufficiently good output coefficient of the wind power generator is obtained for a wider range of peripheral speed ratios.
- the “output coefficient” is a ratio of the net output of the wind power generator to the kinetic energy of the free air flow passing through the rotor wind receiving area per unit time.
- the tangent of the hub 10 at the rotor circumferential center point 21a of the base end 21 of the blade 20 on the projection plane perpendicular to the rotation center axis O of the rotor 1 is defined as a first virtual line VL1.
- the leading edge 31 of the blade 20 has a protruding tip of the first leading edge peak portion 36 (one leading edge peak portion) at a portion on the inner side in the rotor radial direction from the second virtual line VL2.
- the “protruding tip” of the front edge crest refers to the peak of the mountain shape of the front edge crest.
- the “length BL of the blade 20” refers to a length (( ⁇ / 2) ⁇ r) obtained by subtracting the radius r of the hub 10 from the radius ( ⁇ / 2) of the rotor 10.
- the “radius ( ⁇ / 2) of the rotor 10” refers to the distance from the rotation center axis O of the hub 10 (and hence the rotation center axis O of the rotor 1) to the outermost end in the rotor radial direction of the blade 20. .
- the “radius r of the hub 10” means the circumscribed circle of the hub 10 on the projection plane. It shall refer to the radius of.
- the length BL of the blade 20 is 349 mm
- the radius r of the hub 10 is 114 mm.
- the leading edge 31 of the blade 20 has a protruding tip 36 a of the first leading edge peak portion 36 between the first virtual line VL ⁇ b> 1 and the second virtual line VL ⁇ b> 2 on the projection plane. Yes.
- the blades are parallel to the first imaginary line VL1 and project from the first imaginary line VL1 to the opposite side of the hub 10 on the projection plane perpendicular to the rotation center axis O of the rotor 1.
- Virtual lines at positions separated by 0.25 times, 0.75 times, and 1.00 times the length BL of 20 are respectively represented as a third virtual line VL3, a fourth virtual line VL4, and a fifth virtual line.
- the width BW4 of the blade 20 along the line VL4 and the width BW5 of the blade 20 along the fifth virtual line VL5 satisfy the following inequalities (1) and (2): BW1 ⁇ BW3 (1) BW3>BW2>BW4> BW5 (2)
- the width of the blade 20 measured in parallel with the first virtual line VL1 gradually decreases from the first virtual line VL1 toward the fifth virtual line VL5.
- BW1>BW3>BW2>BW4> BW5 the stability of the power generation efficiency with respect to fluctuations in wind speed and direction can be further improved.
- the width BW1 of the blade 20 along the first imaginary line VL1 and the fifth imaginary line VL5 are projected on the projection plane perpendicular to the rotation center axis O of the rotor 1.
- the width BW5 of the blade 20 satisfies the following inequality (3): BW1> BW5 (3)
- the width BW1 of the blade 20 along the first imaginary line VL1 and the second imaginary line VL2 are projected on the projection plane perpendicular to the rotation center axis O of the rotor 1.
- the width BW2 of the blade 20 and the width BW4 of the blade 20 along the fourth virtual line VL4 satisfy the following inequality (4): BW4 ⁇ BW1 ⁇ BW2 (4)
- the protruding tip 36a of the first leading edge peak 36 connects the rotor radial inner end 33 of the leading edge 31 of the blade 20 and the protruding tip 37a of the second leading edge peak 37 on the outer side in the rotor radial direction. It is on the front side of the rotor rotation direction RD with respect to the first line segment L1.
- the output coefficient can be greatly improved.
- the projecting tip 37a of the front edge crest 37 connects the projecting tip 36a of the first front edge crest 36 on the inner side in the rotor radial direction and the rotor radial outer end 35 of the front edge 31 of the blade 20. It is on the front side of the rotor rotation direction RD with respect to the second line segment L2.
- the output coefficient can be greatly improved.
- the rear edge 41 of the blade 20 is located on the projection surface perpendicular to the rotation center axis O of the rotor 1, and the rotor radial inner end 43 at the rear edge 41 of the blade 20.
- the rotor radial direction outer end 45 and the third line segment L3 intersects at one point, and in the rotor radial direction from the intersection 42 with the third line segment L3 of the rear edge 41 of the blade 20.
- the inner portion 46 is on the rear side of the rotor rotation direction RD with respect to the third line segment L3, and the portion 47 of the rear edge 41 of the blade 20 on the outer side in the rotor radial direction with respect to the intersection 42 with the third line segment L3.
- the projecting tips 36 a and 37 a of both front edge crests 36 and 37 are in front of the blade 20 on the projection plane perpendicular to the rotation center axis O of the rotor 1.
- the fourth line segment L4 connecting the rotor radial direction inner end 33 and the rotor radial direction outer end 35 at the edge 31 it is on the front side in the rotor rotation direction.
- the front edge 31 of the blade 20 is entirely on the front side in the rotor rotational direction RD with respect to the fourth line segment L4. According to this configuration, the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid can be further improved as compared with, for example, the case where the front edge 31 of the blade 20 is linear throughout.
- both the rotor radial direction outer end 35 of the front edge 31 and the rotor radial direction outer end 45 of the rear edge 41 are the fifth in the projection plane perpendicular to the rotation center axis O of the rotor 1.
- the rotor radial outer end 35 of the front edge 31 or the rotor radial outer end 45 of the rear edge 41 may be closer to the hub 10 than the fifth virtual line VL5.
- the thickness of the blade 20 gradually decreases from the base end 21 of the blade 20 toward the outer end in the rotor radial direction.
- the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid can be further improved.
- the “thickness of the blade 20” refers to the blade 20 in an arbitrary virtual plane that includes the first virtual line VL1 and is parallel to a virtual plane that is parallel to the rotation center axis O of the rotor 1.
- the maximum thickness among the thicknesses of the blade 20 when measured perpendicular to an imaginary line passing through the leading edge 31 and the trailing edge 41 is assumed.
- the pitch angle (also referred to as “torsion angle”) of the blade 20 gradually decreases from the base end 21 of the blade 20 toward the rotor radial outer end. Yes. Thereby, the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid can be further improved.
- the “pitch angle” refers to the leading edge of the blade 20 in an arbitrary virtual plane that includes the first virtual line VL1 and is parallel to a virtual plane that is parallel to the rotation center axis O of the rotor 1.
- the pitch angle in a virtual plane including the first virtual line VL1 and parallel to the rotation center axis O of the rotor 1 is preferably 36.2 to 40.0 °, and in this example 38.1 °. is there.
- the pitch angle in the virtual plane including the fifth virtual line VL5 and parallel to the rotation center axis O of the rotor 1 is preferably 7.13 to 7.89 °, and in this example is 7.51 °. is there.
- FIG. 3 is a diagram in which the blade 20 shown in FIG. 1 is developed in a direction perpendicular to the rotation center axis O of the rotor 1, that is, the blade 20 has a pitch angle of 0 ° over the entire length of the blade 20. Is shown.
- the leading edge 31 of the blade 20 protrudes in a mountain shape toward the front side in the rotor rotational direction RD only at two different rotor radial direction positions. Have.
- the leading edge 31 of the blade 20 is located at a portion on the inner side in the rotor radial direction from the second virtual line VL2 (more specifically, the first virtual line VL1 and the second virtual line VL1).
- the imaginary line VL2 Between the imaginary line VL2 and a protruding tip 136a of the first leading edge crest 136, and a protruding tip 137a of the second leading edge crest 137 at a portion radially outside the second imaginary line VL2.
- a width BW13 of 20, a width BW14 of the blade 20 along the fourth virtual line VL4, and a width BW15 of the blade 20 along the fifth virtual line VL5 satisfy the following inequalities (4) and (5): BW11 ⁇ BW13 (5) BW13>BW12>BW14> BW15 (6)
- the width BW11 of the blade 20 along the first virtual line VL1 and the width BW15 of the blade 20 along the fifth virtual line VL5 are expressed by the following inequality (6 Meet): BW11> BW15 (7)
- the width BW11 of the blade 20 along the first virtual line VL1 and the width BW12 of the blade 20 along the second virtual line VL2 are expressed by the following inequality ( 8) is satisfied: BW12 ⁇ BW11 (8)
- the protruding tip 136 a of the first leading edge peak 136 on the inner side in the rotor radial direction of the two leading edge peaks 136, 137 is a blade.
- the protruding tip 137 a of the second front edge crest 137 of the two front edge crests 136, 137 on the outer side in the rotor radial direction is the rotor.
- the rear edge 41 of the blade 20 connects the rotor radial inner end 43 and the rotor radial outer end 45 of the rear edge 41 of the blade 20.
- the portion 146 that intersects with the third line segment L3 at one point, and the inner edge 146 of the trailing edge 41 of the blade 20 in the rotor radial direction from the intersection 142 with the third line segment L3 is located with respect to the third line segment L3.
- a portion 147 on the rear side of the rotor rotational direction RD and outside the intersection 142 with the third line segment L3 of the rear edge 41 of the blade 20 is rotator radial direction RD with respect to the third line segment L3.
- the projecting tips 136 a and 137 a of both the front edge crests 136 and 137 are the rotor radial inner end 33 and the rotor radial direction at the front edge 31 of the blade 20. It is on the front side in the rotor rotation direction with respect to the fourth line segment L4 connecting the outer end 35.
- the front edge 31 of the blade 20 is entirely on the front side in the rotor rotation direction RD with respect to the fourth line segment L4 in the developed view of FIG.
- the points equidistant from the front edge 31 and the rear edge 41 are the first center point P1, the second center point P2, the third center point P3, the fourth center point P4, and the fifth center point P5, respectively.
- the second center point P2 and the third center point P3 are on a line segment connecting the first center point P1 and the fourth center point P4.
- the angle ⁇ formed by the line segment connecting the first center point P1 and the fourth center point P4 and the line segment connecting the fourth center point P4 and the fifth center point P5 is as follows. 133 °.
- the stability of the power generation efficiency with respect to fluctuations in the speed and direction of the fluid can be further improved.
- the angle ⁇ formed above may take other values, and is preferably 120 to 146 °.
- the first center point P ⁇ b> 1 and the rotor circumferential center point 21 a of the base end 21 of the blade 20 overlap in the development view.
- the performance of the rotors of Comparative Examples 1 to 4 and the rotor of Example 1 of the present invention was evaluated by analysis.
- the rotors of Comparative Examples 1 to 4 and Example 1 are different from each other only in the shape of the blades.
- the rotor diameter ⁇ is 926 mm
- the blade length BL is 349 mm
- the hub radius r is 114 mm.
- the number of blades was three.
- the leading edge and the trailing edge of the blade were linear over the entire length of the blade.
- blade width center line means the first center point P1, the third center point P3, the second center point P2, the fourth center point P4, and the fifth center point P5 in this order in the blade. It points to a virtual line connected by line segments. “Bend at 0.25BL”, “Bend at 0.50BL”, and “Bend at 0.75BL” respectively mean that the blade width center line is bent at the third center point P3, bent at the second center point P2, 4 indicates bending at a center point P4.
- the rotor of the present invention can be used in a wind-hydraulic machine that uses power obtained by wind power, hydro wind power, or hydraulic power, such as a wind power generator using a horizontal axis rotor or the like, or a hydro power generator.
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Abstract
Description
しかしながら、従来のロータでは、流体の速度や向きの変動に対する発電効率の安定性について、十分に最適化されておらず、改善の余地があった。
主軸に支持されるハブと、該ハブに基端が結合されたブレードとを備える、風水力機械用のロータであって、
ロータの回転中心軸線に対して垂直な投影面において、前記ブレードの前縁が、互いに異なる2つのロータ径方向位置のみで、ロータ回転方向前側へ山状に突出した前縁山部を有することを特徴とする。
本発明のロータによれば、流体の速度や向きの変動に対する発電効率の安定性を向上できる。
前記投影面において、
前記ブレードの前記基端のロータ周方向中心点における前記ハブの接線を、第1仮想線VL1とし、
前記第1仮想線VL1に平行で、前記第1仮想線VL1から前記ハブとは反対側へ前記ブレードの長さBLの0.50倍の長さだけ離れた位置にある仮想線を、第2仮想線VL2としたとき、
前記ブレードの前縁は、前記第2仮想線VL2よりもロータ径方向内側の部分に、一方の前記前縁山部の突出先端を有し、前記第2仮想線VL2よりもロータ径方向外側の部分に、他方の前記前縁山部の突出先端を有していることが好ましい。
この構成によれば、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
前記投影面において、
前記第1仮想線VL1に平行で、前記第1仮想線VL1から前記ハブとは反対側へ前記ブレードの長さBLの0.25倍、0.75倍、1.00倍の長さだけ離れた位置にある仮想線を、それぞれ第3仮想線VL3、第4仮想線VL4、第5仮想線VL5としたとき、
前記第1仮想線VL1に沿う前記ブレードの幅BW1と、前記第2仮想線VL2に沿う前記ブレードの幅BW2と、前記第3仮想線VL3に沿う前記ブレードの幅BW3と、前記第4仮想線VL4に沿う前記ブレードの幅BW4と、前記第5仮想線VL5に沿う前記ブレードの幅BW5とが、不等式
BW1<BW3
BW3>BW2>BW4>BW5
を満たしていることが好ましい。
この構成により、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
前記投影面において、
前記2つの前縁山部のうちの、ロータ径方向内側のほうの前記前縁山部の突出先端が、前記ブレードの前縁のロータ径方向内側端と、ロータ径方向外側のほうの前記前縁山部の突出先端とを結んだ、第1線分L1に対して、ロータ回転方向前側にあることが好ましい。
この構成によれば、周速比が比較的低い時における出力係数をより大きく向上できる。
前記投影面において、
前記2つの前縁山部のうちの、ロータ径方向外側のほうの前記前縁山部の突出先端が、ロータ径方向内側のほうの前記前縁山部の突出先端と、前記ブレードの前縁のロータ径方向外側端とを結んだ、第2線分L2に対して、ロータ回転方向前側にあることが好ましい。
この構成によれば、周速比が比較的高い時における出力係数をより大きく向上できる。
前記投影面において、
前記ブレードの後縁は、前記ブレードの後縁におけるロータ径方向内側端とロータ径方向外側端とを結んだ、第3線分L3と、1点で交差しており、
前記ブレードの後縁のうち、前記第3線分L3との交点よりもロータ径方向内側の部分が、前記第3線分L3よりもロータ回転方向後側にあり、
前記ブレードの後縁のうち、前記第3線分L3との交点よりもロータ径方向外側の部分が、前記第3線分L3よりもロータ回転方向前側にあることが好ましい。
この構成によれば、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
なお、本発明でいう「風水力機械」とは、風力発電機(風車等)又は水力発電機(水車等)等の、風力又は水力により得られる動力を利用する機械を意味するものとする。
本実施形態のロータ1は、風力発電機だけでなく、水力発電機又は他の風水力機械にも用いることができる。
なお、ブレード20の数は、3つに限られず、任意の数とすることができる。
また、ロータ1の各ブレード20は、本例では互いに同一形状を有しているが、一部のブレードが他のブレードとは異なる形状を有していてもよい。
ここで、前縁山部36、37に関し、ロータ回転方向RDの前側へ「山状に突出した」とは、すなわち、上記投影面における前縁山部36、37の形状が、例えばガウス曲線や三角形状等のように、突出先端の両側部分で後退したような形状であって、例えば傾斜線や比例曲線等のように、突出先端の片側部分だけが後退したような形状ではないことを指している。
なお、本例では、上記投影面における前縁山部36、37の突出先端部分が、丸みを帯びた曲線状に形成されており、これは、空気抵抗の低減ひいては発電効率の向上の観点から好ましい。ただし、上記投影面における前縁山部36、37の突出先端部分は、鋭利に尖った形状に形成されてもよい。
ここで、「周速比」は、風速に対するブレード先端速度(ブレードの、ロータ径方向外側端部の回転方向の速度)の比であり、周速比をλ、風速をU (m/s)、ロータの回転速度をN (rpm)、ロータの直径をΦ (mm)とすると、λ=ΦN/(2U)で表すことができる。
また、「出力係数」は、ロータ受風面積を単位時間に通過する自由空気流の運動エネルギーに対する風力発電機の正味出力の比である。
この構成によれば、例えば第1前縁山部36の突出先端36aと第2前縁山部37の突出先端37aとの両方が第2仮想線VL2に対して同じ側にある場合に比べて、第1前縁山部36と第2前縁山部37とのロータ径方向位置が、ブレード20の前縁31内でより好適に分散されるので、より幅広い周速比の範囲に対して、十分良好な風力発電機の出力係数が得られるようになる。これにより、風の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
ここで、前縁山部の「突出先端」とは、前縁山部が有する山形状の頂点を指すものとする。「ブレード20の長さBL」とは、ロータ10の半径(Φ/2)からハブ10の半径rを差し引いた長さ((Φ/2)-r)を指す。また、「ロータ10の半径(Φ/2)」とは、ハブ10の回転中心軸線O(ひいてはロータ1の回転中心軸線O)から、ブレード20のロータ径方向最外端までの、距離を指す。なお、ロータ1の回転中心軸線Oに対して垂直な投影面において、ハブ10が円形状を有していない場合、「ハブ10の半径r」とは、当該投影面における、ハブ10の外接円の半径を指すものとする。
本例では、ブレード20の長さBLが349mmであり、ハブ10の半径rが114mmである。
BW1<BW3 ・・・(1)
BW3>BW2>BW4>BW5 ・・・(2)
上記不等式(1)と(2)を満たすことにより、例えば第1仮想線VL1と平行に測ったブレード20の幅が、第1仮想線VL1から第5仮想線VL5に向かって徐々に減少する場合(すなわち、BW1>BW3>BW2>BW4>BW5を満たす場合)に比べて、風の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
BW1>BW5 ・・・(3)
BW4<BW1<BW2 ・・・(4)
この構成によれば、例えば第1前縁山部36の突出先端36aが第1線分L1に対してロータ回転方向RDの後側にある場合に比べて、周速比が比較的低い時(例えば周速比が0.926の時)における出力係数をより大きく向上できる。
この構成によれば、例えば第2前縁山部37の突出先端37aが第2線分L2に対してロータ回転方向RDの後側にある場合に比べて、周速比が比較的高い時(例えば周速比が5.56の時)における出力係数をより大きく向上できる。
この構成によれば、例えば前記投影面においてブレード20の後縁41がその全体にわたって直線状である場合に比べて、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
この構成によれば、例えば前記投影面においてブレード20の前縁31がその全体にわたって直線状である場合に比べて、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
この構成によれば、例えばブレード20の前縁31がその全体にわたって直線状である場合に比べて、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
本明細書において、「ブレード20の厚さ」は、第1仮想線VL1を含むとともにロータ1の回転中心軸線Oに平行な仮想面に対して平行な、任意の仮想面内において、ブレード20の前縁31と後縁41とを通る仮想線に対して垂直に測ったときのブレード20の厚さのうち、最大のものを指すものとする。
本明細書において、「ピッチ角」とは、第1仮想線VL1を含むとともにロータ1の回転中心軸線Oに平行な仮想面に対して平行な、任意の仮想面内における、ブレード20の前縁31と後縁41とを通る仮想線と、該任意の仮想面とロータ1の回転中心軸線Oに対して垂直な仮想面との交線との、鋭角側のなす角度である。
なお、第1仮想線VL1を含むとともにロータ1の回転中心軸線Oに平行な仮想面内におけるピッチ角は、36.2~40.0°であることが好ましく、本例では38.1°である。また、第5仮想線VL5を含むとともにロータ1の回転中心軸線Oに平行な仮想面内におけるピッチ角は、7.13~7.89°であることが好ましく、本例では7.51°である。
本例では、図3の展開図において、ブレード20の前縁31が、互いに異なる2つのロータ径方向位置のみで、ロータ回転方向RDの前側へ山状に突出した前縁山部136、137を有している。
BW11<BW13 ・・・(5)
BW13>BW12>BW14>BW15 ・・・(6)
BW11>BW15 ・・・(7)
BW12<BW11 ・・・(8)
これにより、流体の速度や向きの変動に対する発電効率の安定性をさらに向上できる。
ただし、上記のなす角度θは、その他の値をとってもよく、120~146°であるのが好ましい。
図3の例では、その展開図において、第1中心点P1と、ブレード20の基端21のロータ周方向中心点21aとが、重なっている。
比較例1のロータは、ブレードの前縁及び後縁が、ブレードの全長にわたって直線状であるものとした。
比較例2~4のロータは、ブレードの前縁及び後縁が、それぞれ、第3仮想線VL3、第2仮想線VL2、第4仮想線VL4の位置で、ロータ回転方向前側に凸に湾曲するものとした。
実施例1のロータは、上述した図1~図3の例におけるブレード形状を有するものとした。
各ロータの他の諸元を、表1に示す。
表1において、「ブレード幅中心線」とは、ブレードにおける、第1中心点P1、第3中心点P3、第2中心点P2、第4中心点P4、及び第5中心点P5を、この順番で線分により繋げてなる仮想線を指している。「0.25BLで屈曲」、「0.50BLで屈曲」、「0.75BLで屈曲」とは、それぞれ、上記のブレード幅中心線が、第3中心点P3で屈曲、第2中心点P2で屈曲、第4中心点P4で屈曲していることを指している。
なお、実施例1のロータでは、周速比λ=3.7のときに出力係数が最大(0.398)となった。
10 ハブ
20 ブレード
21 ブレードの基端
21a ブレードの基端のロータ周方向中心点
31 前縁
33 前縁のロータ径方向内側端
35 前縁のロータ径方向外側端
36、136 第1前縁山部(ロータ径方向内側のほうの前縁山部)
36a、136a 第1前縁山部の突出先端
37、137 第2前縁山部(ロータ径方向外側のほうの前縁山部)
37a、137a 第2前縁山部の突出先端
41 後縁
42、142 後縁の、第3線分との交点
43 後縁のロータ径方向内側端
45 後縁のロータ径方向外側端
46、146 後縁のうち、第3線分との交点よりもロータ径方向内側の部分
47、147 後縁のうち、第3線分との交点よりもロータ径方向外側の部分
O ロータの回転中心軸線
RD 回転方向
r ハブの半径
Φ ロータの直径
θ 角度
Claims (6)
- 主軸に支持されるハブと、該ハブに基端が結合されたブレードとを備える、風水力機械用のロータであって、
ロータの回転中心軸線に対して垂直な投影面において、前記ブレードの前縁が、互いに異なる2つのロータ径方向位置のみで、ロータ回転方向前側へ山状に突出した前縁山部を有することを特徴とする、ロータ。 - 前記投影面において、
前記ブレードの前記基端のロータ周方向中心点における前記ハブの接線を、第1仮想線VL1とし、
前記第1仮想線VL1に平行で、前記第1仮想線VL1から前記ハブとは反対側へ前記ブレードの長さBLの0.50倍の長さだけ離れた位置にある仮想線を、第2仮想線VL2としたとき、
前記ブレードの前縁は、前記第2仮想線VL2よりもロータ径方向内側の部分に、一方の前記前縁山部の突出先端を有し、前記第2仮想線VL2よりもロータ径方向外側の部分に、他方の前記前縁山部の突出先端を有している、請求項1に記載のロータ。 - 前記投影面において、
前記第1仮想線VL1に平行で、前記第1仮想線VL1から前記ハブとは反対側へ前記ブレードの長さBLの0.25倍、0.75倍、1.00倍の長さだけ離れた位置にある仮想線を、それぞれ第3仮想線VL3、第4仮想線VL4、第5仮想線VL5としたとき、
前記第1仮想線VL1に沿う前記ブレードの幅BW1と、前記第2仮想線VL2に沿う前記ブレードの幅BW2と、前記第3仮想線VL3に沿う前記ブレードの幅BW3と、前記第4仮想線VL4に沿う前記ブレードの幅BW4と、前記第5仮想線VL5に沿う前記ブレードの幅BW5とが、不等式
BW1<BW3
BW3>BW2>BW4>BW5
を満たしている、請求項2に記載のロータ。 - 前記投影面において、
前記2つの前縁山部のうちの、ロータ径方向内側のほうの前記前縁山部の突出先端が、前記ブレードの前縁のロータ径方向内側端と、ロータ径方向外側のほうの前記前縁山部の突出先端とを結んだ、第1線分L1に対して、ロータ回転方向前側にある、請求項1~3のいずれか一項に記載のロータ。 - 前記投影面において、
前記2つの前縁山部のうちの、ロータ径方向外側のほうの前記前縁山部の突出先端が、ロータ径方向内側のほうの前記前縁山部の突出先端と、前記ブレードの前縁のロータ径方向外側端とを結んだ、第2線分L2に対して、ロータ回転方向前側にある、請求項1~3のいずれか一項に記載のロータ。 - 前記投影面において、
前記ブレードの後縁は、前記ブレードの後縁におけるロータ径方向内側端とロータ径方向外側端とを結んだ、第3線分L3と、1点で交差しており、
前記ブレードの後縁のうち、前記第3線分L3との交点よりもロータ径方向内側の部分が、前記第3線分L3よりもロータ回転方向後側にあり、
前記ブレードの後縁のうち、前記第3線分L3との交点よりもロータ径方向外側の部分が、前記第3線分L3よりもロータ回転方向前側にある、請求項1~3のいずれか一項に記載のロータ。
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- 2015-11-24 CN CN201580025528.7A patent/CN106460799B/zh not_active Expired - Fee Related
- 2015-11-24 CA CA2951217A patent/CA2951217C/en not_active Expired - Fee Related
- 2015-11-24 US US15/310,533 patent/US10288036B2/en not_active Expired - Fee Related
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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CN109424581A (zh) * | 2017-09-05 | 2019-03-05 | 博泽沃尔兹堡汽车零部件有限公司 | 风扇叶轮和带有这种风扇叶轮的散热器风扇模块 |
EP3450716A1 (de) * | 2017-09-05 | 2019-03-06 | Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg | Lüfterrad und kühlerlüftermodul mit einem solchen lüfterrad |
KR20190026623A (ko) * | 2017-09-05 | 2019-03-13 | 브로제 파르초이크타일레 게엠베하 운트 코. 콤만디트게젤샤프트 뷔르츠부르크 | 팬 휠 |
KR102151458B1 (ko) | 2017-09-05 | 2020-09-03 | 브로제 파르초이크타일레 에스에 운트 코. 콤만디트게젤샤프트, 뷔르츠부르크 | 팬 휠 |
US11022139B2 (en) | 2017-09-05 | 2021-06-01 | Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg | Fan wheel and radiator fan module with the fan wheel |
Also Published As
Publication number | Publication date |
---|---|
CN106460799A (zh) | 2017-02-22 |
EP3135905A4 (en) | 2018-01-03 |
US10288036B2 (en) | 2019-05-14 |
CA2951217A1 (en) | 2016-06-30 |
JP2016121616A (ja) | 2016-07-07 |
EP3135905B1 (en) | 2019-05-15 |
CA2951217C (en) | 2019-11-12 |
CN106460799B (zh) | 2019-03-15 |
US20170089322A1 (en) | 2017-03-30 |
JP6490421B2 (ja) | 2019-03-27 |
EP3135905A1 (en) | 2017-03-01 |
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