WO2019214632A1 - 叶片及使用其的轴流叶轮 - Google Patents

叶片及使用其的轴流叶轮 Download PDF

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Publication number
WO2019214632A1
WO2019214632A1 PCT/CN2019/085923 CN2019085923W WO2019214632A1 WO 2019214632 A1 WO2019214632 A1 WO 2019214632A1 CN 2019085923 W CN2019085923 W CN 2019085923W WO 2019214632 A1 WO2019214632 A1 WO 2019214632A1
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WO
WIPO (PCT)
Prior art keywords
blade
projection
ranges
tip
circular arc
Prior art date
Application number
PCT/CN2019/085923
Other languages
English (en)
French (fr)
Inventor
袁斌
冯世峰
汪洪丹
吴成刚
Original Assignee
约克广州空调冷冻设备有限公司
江森自控科技公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201820688573.1U external-priority patent/CN208294835U/zh
Priority claimed from CN201810437361.0A external-priority patent/CN108506247A/zh
Application filed by 约克广州空调冷冻设备有限公司, 江森自控科技公司 filed Critical 约克广州空调冷冻设备有限公司
Priority to US17/054,146 priority Critical patent/US11519422B2/en
Priority to EP19800854.2A priority patent/EP3816454A4/en
Publication of WO2019214632A1 publication Critical patent/WO2019214632A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/388—Blades characterised by construction
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • F05D2240/301—Cross-sectional characteristics

Definitions

  • the present application relates to the field of rotating machinery such as fans, pumps and compressors, and more particularly to a blade and an axial flow impeller using the same.
  • Exemplary embodiments of the present application may address at least some of the above problems.
  • the present application provides a blade comprising: an upper surface and a lower surface, the upper surface being a pressure surface, the lower surface being a suction surface; a tip and a blade root; a leading edge and a trailing edge Wherein the pressure surface and the suction surface extend from the tip to the blade root, respectively, and extend from the leading edge to the trailing edge, respectively; and a bent portion, the bent portion
  • the pressure is convex toward the suction surface; wherein the bent portion has a lowest point in a radial section of the blade, and a line connecting the lowest point extends in a direction from the leading edge to the trailing edge .
  • the projection of the blade tip in the axial direction is a circular arc projection 1; the projection of the blade root in the axial direction is a circular arc projection 2; the connection point of the lowest point
  • the axial projection is a circular arc projection three; the circular arc projection one, the circular arc projection two and the circular arc projection three are concentric.
  • the curve of the bent portion along the radial section of the blade satisfies:
  • m is equal to n
  • w/h has a value ranging from 0.05 ⁇ w/h ⁇ 0.4.
  • the present application provides an axial flow impeller, characterized by comprising: a hub having a central axis, the hub being rotatable about the central axis, the axial section of the hub a circular shape; and at least two blades disposed on an outer circumferential surface of the hub, each of the at least two blades comprising: an upper surface and a lower surface, the upper surface being a pressure surface, the lower surface being a suction surface; a tip and a blade root; a leading edge and a trailing edge, wherein the pressure surface and the suction surface respectively extend from the blade tip to the blade root, and respectively a leading edge extending to the trailing edge; and a bent portion arched from the pressure surface toward the suction surface; wherein the bent portion has a lowest radial section of the blade Point, the line connecting the lowest point extends in a direction from the leading edge to the trailing edge.
  • the present application provides a blade comprising: an upper surface and a lower surface, the upper surface being a pressure surface, the lower surface being a suction surface; a tip and a blade root; a leading edge and a trailing edge Wherein the pressure surface and the suction surface extend from the blade tip to the blade root, respectively, and extend from the leading edge to the trailing edge, respectively; front and rear portions, the front portion being close to the a blade tip, the rear portion being adjacent to the blade root; and a front arching portion, the front arching portion being located at the front portion, the front arching portion facing the pressure surface from the suction force Arching; wherein the front bulge has a highest point in a radial section of the blade, and the line of the highest point extends along the leading edge to the trailing edge direction.
  • the projection of the blade tip in the axial direction is a circular arc projection 1; the projection of the blade root in the axial direction is a circular arc projection 2; the line connecting the highest point is axially
  • the projection is a circular arc projection four; the circular arc projection one, the circular arc projection two and the circular arc projection four are concentric.
  • the radial position of the front bulge at the highest point on the radial section of the blade gradually increases from the tip to the trailing edge direction from the tip end The leaf root offset.
  • the projection of the line of the highest point in the axial direction is an involute.
  • the ratio of the arch width w of the trailing edge to the length of the trailing edge ranges from 0.05 or more and 0.3 or less.
  • the curve of the front bulge along the radial section of the blade satisfies:
  • m is equal to n
  • w/h has a value ranging from 0.05 ⁇ w / h ⁇ 0.4.
  • the blade further comprising a bent portion, the bent portion arching from the pressure surface toward the suction surface; wherein the bent portion is on a radial section of the blade There is a lowest point, the line connecting the leading point extending in the direction from the leading edge to the trailing edge, and the line connecting the lowest point is in the rear portion.
  • the present application provides an axial flow impeller, comprising: a hub having an axis, the hub being rotatable about the axis, the hub having a circular cross section in the axial direction And at least two blades disposed on an outer circumferential surface of the hub, each of the at least two blades comprising: an upper surface and a lower surface, the upper surface being a pressure surface
  • the lower surface is a suction surface; a tip and a blade root; a leading edge and a trailing edge, wherein the pressure surface and the suction surface respectively extend from the blade tip to the blade root, and respectively from the front a rim extending to the trailing edge; a front portion and a rear portion, the front portion being adjacent to the blade tip, the rear portion being adjacent to the blade root; and a front arching portion, the front arching portion being located In the front portion, the front arch portion is arched from the suction force toward the pressure surface; wherein the front arch portion has a highest point on
  • the blade of the present application can suppress the flow separation of the blade surface and improve the detachment vortex of the surface, thereby improving the blade performance and reducing the running noise.
  • Figure 1 shows a perspective view of an impeller using a blade of one embodiment of the present application
  • Figure 2A shows a perspective view of the blade used in the impeller of Figure 1;
  • Figure 2B shows a radial cross-sectional view of the blade of Figure 2A
  • Figure 3 shows a perspective comparison of the blade of Figure 2A with a blade of the prior art
  • Figure 4 shows a comparison of the radial cross section of the blade of Figure 2A with a prior art blade
  • Figure 5 is a plan view showing the blade used in the impeller of Figure 1 in the axial direction;
  • Figure 6 shows a projection view of the blade in the axial direction in accordance with one example of the present application
  • Figure 7 is a view showing the relationship between the arch width w and the arch height h of the bent portion of the blade of Figure 6;
  • Figure 8 shows a perspective view of the blade of Figure 6
  • Figure 9 is a view showing the relationship between the arch width w and the arch height h of the front arch portion of the blade of Figure 8;
  • Figure 10 shows a perspective view of a blade in accordance with another example of the present application.
  • Figure 11 shows a projection view of the blade of Figure 10 in the axial direction.
  • FIG. 1 shows a perspective view of an impeller 100 using a blade of one embodiment of the present application.
  • the impeller 100 includes a hub 110 and three blades 112.
  • the hub 110 has a central axis, the hub 110 is rotatable about a central axis, the hub 110 is circular in cross section in the axial direction, and the three blades 112 are evenly disposed on the outer circumferential surface of the hub 110.
  • the hub 110 can be coupled to the blade 112 in one piece.
  • the hub 110 and the blades 112 are rotatable together about a central axis of the hub 110.
  • the impeller 100 of the present application rotates in a clockwise direction (ie, the direction of rotation indicated by the arrow in Figure 1).
  • FIG. 2A shows a perspective view of the blade 112 used by the impeller 100 of FIG. 1; and FIG. 2B shows a radial cross-sectional view of the blade of FIG. 2A.
  • 3 shows a perspective comparison of the blade 112 of FIG. 2A with the blade 310 of the prior art;
  • FIG. 4 shows a radial cross-sectional comparison of the blade of FIG. 2A with the blade 310 of the prior art.
  • the solid line in FIG. 2B indicates the blade 112 of the present application;
  • the broken line in FIG. 2B indicates the straight line connecting the blade tip 216 to the blade root 218 on a certain section;
  • the solid line in FIG. 4 indicates the blade 112 of the present application;
  • the dashed line in Figure 4 represents the blade 310 of the prior art.
  • the blade 112 includes an upper surface, a lower surface, a tip 216, a blade root 218, a leading edge 222, and a trailing edge 220.
  • the upper surface is a pressure surface 212 and the lower surface is a suction surface 214.
  • the tip 216 is the position at which the blade diameter is the largest on the blade 112, and the blade root 218 is the position at which the blade 112 is used to connect with the hub 110.
  • the pressure surface 212 and the suction surface 214 extend from the tip 216 to the blade root 218, respectively.
  • the leading edge 222 is the side of the blade 112 that faces the direction of rotation.
  • the leading edge 222 is the side of the blade 112 that faces the fluid.
  • the trailing edge 220 is the other side of the blade 112 opposite the leading edge 222.
  • the pressure surface 212 and the suction surface 214 extend from the leading edge 222 to the trailing edge 220, respectively.
  • the blade 112 includes a center line 255 that is shown as a midpoint M on a radial section of the blade 112.
  • the vertical projection point of the midpoint M on the straight line connecting the tip 216 of the radial section to the blade root 218 is the midpoint Q of the straight line.
  • the blade 112 also includes a front portion 242 and a rear portion 244.
  • the front portion 242 is the region of the blade 112 from the blade tip 216 to the center line 255 (i.e., the region near the blade tip 216), and the rear portion 244 is the region of the blade 112 from the center line 255 to the blade root 218 (ie, close to The area of the leaf root 218).
  • the blade 112 of the present application also includes a bend 262.
  • the bent portion 262 is arched from the pressure surface 212 to the suction surface 214.
  • the bent portion 262 of the blade 112 has the lowest point E.
  • a line 252 (e.g., as shown in FIG. 2A) joining the lowest points on the radial section of the bent portion 262 extends in a direction from the leading edge 222 to the trailing edge 220.
  • the bent portion 262 of the blade 112 of the present application forms a protrusion in the direction of the suction edge 214 along the leading edge 222 to the trailing edge 220, and breaks away from the radial direction. eddy.
  • the projections enable the large volume of high-strength stripping vortices located on the suction side 214 to split into small volume, low-intensity vortices, thereby reducing turbulent dissipation losses.
  • the bend 262 forms a groove in the pressure face 212 of the blade 112 such that a portion of the fluid leaking from the pressure face 212 to the suction face 214 is directed into the groove.
  • the provision of the bent portion 262 can reduce turbulent dissipation losses and leakage losses to reduce noise while improving airflow and improving aerodynamic performance of the fan.
  • the blade 112 further includes a front arch 264.
  • the front arch 264 is located at the front portion 242 of the blade 112.
  • the front arching portion 264 is arched from the suction surface 214 toward the pressure surface 212.
  • FIG. 2B in the radial section of the blade 112, the front arch 264 of the blade 112 has the highest point F.
  • a line 254 (shown in FIG. 2A) connecting the highest point F on the radial section extends in a direction from the leading edge 222 to the trailing edge 220.
  • the front arch 264 of the blade 112 of the present application forms a groove in the direction of the leading edge 222 to the trailing edge 220 of the suction face 214 of the blade 112.
  • the groove is capable of damaging the leaking main fluid path such that the leakage flow of the front portion 242 is drawn into the groove, inhibiting the continued development of the leakage flow.
  • the groove actively transfers the load while reducing the blade load near the front portion 242, thereby achieving the effect of improving aerodynamic performance and improving fan efficiency.
  • the front arched portion 264 forms a projection in the direction of the leading edge 222 to the trailing edge 220 of the pressure surface 212 of the blade 112.
  • the protrusion can delay the position where the peeling vortex gradually peeling off from the leading edge 222 to the trailing edge 220, and split the large volume and high intensity vortex into a small volume and low intensity vortex, thereby reducing the turbulence intensity of the stripping vortex and reducing noise.
  • the blade 112 includes a bent portion 262 and a front raised portion 264.
  • the blade 112 of the present application may also include only one of the bent portion 262 and the front raised portion 264.
  • both the bent portion 262 and the front raised portion 264 extend from the leading edge 222 to the trailing edge 220, the bent portion 262 is in accordance with the present application.
  • the front bulge 264 may also extend only over a portion of the region from the leading edge 222 to the trailing edge 220 such that the blade 112 does not have a bend 262 and a front ridge 264 in some radial sections.
  • the bent portion 262 or the front raised portion 264 can extend from the leading edge 222 and end when the trailing edge 220 has not been reached.
  • the front arch 264 is located at the front 242 of the blade 112, while the bend 262 can be located anywhere on the blade 112. That is, the bend 262 can be located at the front portion 242 of the blade 112, the rear portion 244 of the blade 112, or the front portion 242 and the rear portion 244 of the blade 112.
  • the above arrangement of the blades 112 can reduce noise while improving fan efficiency.
  • Figure 5 shows a projection view of the blade used in the impeller of Figure 1 in the axial direction.
  • FIG. 6 shows a projection view of the blade 112 in the axial direction according to one example of the present application.
  • Figure 7 is a graph showing the relationship between the arch width w and the arch height h of the bent portion 262 of the blade 112 of Figure 6.
  • the broken line in Fig. 6 indicates the position of the line 252 at the lowest point in the radial direction of the bent portion 262.
  • the curve of the bent portion 262 along the radial section of the blade 112 satisfies:
  • ⁇ represents the circumferential angle.
  • a point P is taken on the tip 216, and the angle formed by the point P to the center O of the hub 110 and the line L of the tip 216 and the leading edge 222 to the center O of the hub 110 is Circumferential angle ⁇ (see Figure 5).
  • the arch width w represents the maximum width of the bent portion 262 in the radial section
  • the arch height h represents the height of the highest point of the bent portion 262 in the radial section from the lowest point.
  • m is equal to n
  • w/h has a value ranging from 0.05 ⁇ w/h ⁇ 0.4.
  • the radius of the lowest point of the radial direction of the bent portion 262 satisfies:
  • r1 is the outer radius of the blade 112
  • R2 is the radius of the hub 110
  • c ranges from 0.1 ⁇ c ⁇ 0.95.
  • the projection of the blade tip 216 of the blade 112 in the axial direction is a circular arc projection one (ie, the radius of the circular arc projection one is r1); the projection of the blade root 218 of the blade 112 in the axial direction is a circle.
  • the arcuate projection 2 i.e., the radius of the arcuate projection 2 is r2; the projection of the line 252 of the lowest point of the radial direction of the bent portion 262 in the axial direction is a circular arc projection three.
  • the circular arc projection 2 and the circular arc projection 3 are concentric, and the center of the circle is the projection point O of the axis of the hub 110 along the axial direction.
  • FIG. 8 shows a perspective view of the blade 112 of FIG. 6.
  • Fig. 9 is a view showing the relationship between the arch width w and the arch height h of the front bulging portion 264 of the blade 112 in Fig. 8.
  • the broken line in Fig. 8 indicates the position of the line 254 of the highest point in the radial direction of the front arch portion 264.
  • ⁇ represents the circumferential angle. Specifically, a point P is taken on the tip 216, and the angle formed by the point P to the line O of the hub 110 and the line connecting the tip 216 and the leading edge 222 to the center O of the hub 110 is the circumference.
  • the angle ⁇ (see Figure 5).
  • the value range of a is 0.2 ⁇ a ⁇ 2; the value range of b is 0.05 ⁇ b ⁇ 1; the value range of m is 1 ⁇ m ⁇ 3; the value of n ranges from 1 ⁇ n ⁇ 3; The value of ⁇ ranges from 0 ° ⁇ ⁇ ⁇ 180 °.
  • the arch width w represents the maximum width of the front arch 264 in the radial section of the blade 112
  • the arch height h represents the height of the front arch 264 at the lowest point of the highest point in the radial section of the blade 112.
  • m is equal to n and w/h has a value ranging from 0.05 ⁇ w/h ⁇ 0.4.
  • the axial projection of the line 254 at the highest point is gradually offset from the tip 216 to the blade root 218 along the leading edge 222 to the trailing edge 220.
  • an end point K (shown in FIG. 9) of the front arched portion 264 is any point on the tip 216.
  • the circumferential angle ⁇ is 0°
  • the arch width w is equal to the arch height h equal to 0, and at this time, the arch width and the arch height of the blade 112 are both 0, and the end point K coincides with the intersection L of the tip 216 and the leading edge 222.
  • the value of the circumferential angle ⁇ increases, so that the values of the arch width w and the arch height h also gradually become larger.
  • the radially highest point 254 of the front raised portion 264 is slowly away from the tip 216 in a direction from the leading edge 222 to the trailing edge 220, thereby forming a front portion 242 of the blade 112 substantially as indicated by the dashed line in FIG.
  • the projection of the line 254 at the highest point in the axial direction is an involute.
  • the ratio of the arch width w of the trailing edge 220 to the length of the trailing edge 220 ranges from greater than or equal to 0.05 and less than or equal to 0.3.
  • FIG. 10 shows a perspective view of a blade 112 in accordance with another example of the present application.
  • Figure 11 shows a projection view of the blade 112 of Figure 10 in the axial direction.
  • the dotted line in Fig. 10-11 indicates the position of the line 254 of the highest point in the radial direction of the front arched portion 264.
  • the projection of the line 254 of the highest point of the front arch portion 264 in the axial direction is a circular arc projection four.
  • the arcuate projection four is concentric with the arcuate projection of the tip 216 and the arcuate projection of the blade root 218, the center of which is the projection point O of the axis of the hub 110 in the axial direction.
  • the blade section may have a plurality of blade sections from the leading edge to the trailing edge, which may be an equal thickness section or any two-dimensional airfoil.
  • the arch width w and the arch height h is listed in the present application, the arc-shaped features of the front arched portion 264 and the bent portion 262 in the present application may also use arcs, parabolas, etc., and the present application can also be implemented. Improve the performance of the blade and reduce the noise.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种叶片（112）以及使用其的叶轮（100），叶片（112）包括：上表面和下表面，上表面为压力面（212），下表面为吸力面（214）；其中压力面（212）和吸力面（214）分别从叶尖（216）延伸至叶根（218），并且分别从前缘（222）延伸至尾缘（220）；前部和后部，前部靠近叶尖（216），后部靠近叶根（218）；以及弯折部（262），弯折部（262）从压力面（212）向吸力面（214）拱起；其中，弯折部（262）在叶片（112）的径向截面上具有最低点（E），最低点（E）的连线沿前缘（222）到尾缘（220）的方向延伸。该叶片能够抑制叶片表面的流动分离，改善表面的脱离涡，减少叶尖泄漏，从而提高叶片性能，降低运行噪声。

Description

叶片及使用其的轴流叶轮 技术领域
本申请涉及风机、泵和压缩机等旋转机械领域，更确切的说是一种叶片及使用其的轴流叶轮。
背景技术
传统的叶片通常为扭曲的光滑流线型叶片，由于叶片表面流动分离严重，形成涡流，叶尖泄漏很难避免，因此叶片性能较低，噪声较大。
发明内容
本申请的示例性实施例可以解决至少一些上述问题。
根据本申请的第一方面，本申请提供一种叶片，包括：上表面和下表面，所述上表面为压力面，所述下表面为吸力面；叶尖和叶根；前缘和尾缘，其中所述压力面和所述吸力面分别从所述叶尖延伸至所述叶根，并且分别从所述前缘延伸至所述尾缘；以及弯折部，所述弯折部从所述压力面向所述吸力面拱起；其中，所述弯折部在所述叶片的径向截面上具有最低点，所述最低点的连线沿所述前缘到所述尾缘的方向延伸。
根据上述第一方面的叶片，所述叶尖沿轴向的投影为圆弧形投影一；所述叶根沿轴向的投影为圆弧形投影二；所述最低点的所述连线沿轴向的投影为圆弧形投影三；所述圆弧形投影一、所述圆弧形投影二以及所述圆弧形投影三是同心的。
根据上述第一方面的叶片，所述弯折部沿所述叶片的径向截面的曲线满足：
拱宽w＝a×θ m，其中a的取值范围为0.2≤a≤2；m的取值范围为1≤m≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°；拱高h＝b×θ n，其中0b的取值范围为0.05≤b≤1；n的取值范围为1≤n≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°。
根据上述第一方面的叶片，m等于n，并且w/h的取值范围为0.05≤w/h≤0.4。
根据本申请的第二方面，本申请提供一种轴流叶轮，其特征在于包括：轮毂，所述轮毂具有中心轴线，所述轮毂能够绕所述中心轴线转动，所述轮毂沿轴向的截面为圆形；和至少两片叶片，所述至少两片叶片布置在所述轮毂的外圆周面上，所述至少两片叶片中的每一片包括：上表面和下表面，所述上表面为压力面，所述下表面为吸力面；叶尖和叶根；前缘和尾缘，其中所述压力面和所述吸力面分别从所述叶尖延伸至所述叶根，并且分别从所述前缘延伸至所述尾缘；以及弯折部，所述弯折部从所述压力面向所述吸力面拱起；其中，所述弯折部在所述叶片的径向截面上具有最低点，所述最低点的连线沿所述前缘到所述尾缘的方向延伸。
根据本申请的第三方面，本申请提供一种叶片，包括：上表面和下表面，所述上表面为压力面，所述下表面为吸力面；叶尖和叶根；前缘和尾缘，其中所述压力面和所述吸力面分别从所述叶尖延伸至所述叶根，并且分别从所述前缘延伸至所述尾缘；前部和后部，所述前部靠近所述叶尖，所述后部靠近所述叶根；以及前部拱起部，所述前部拱起部位于所述前部，所述前部拱起部从所述吸力面向所述压力面拱起；其中，所述前部拱起部在所述叶片的径向截面上具有最高点，所述最高点的连线沿所述前缘到所述尾缘方向延伸。
根据上述第三方面的叶片，所述叶尖沿轴向的投影为圆弧形投影一；所述叶根沿轴向的投影为圆弧形投影二；所述最高点的连线沿轴向的投影为圆弧形投影四；所述圆弧形投影一、所述圆弧形投影二以及所述圆弧形投影四是同心的。
根据上述第三方面的叶片，所述前部拱起部在所述叶片的径向截面上的最高点的径向位置沿所述前缘到所述尾缘方向逐渐从所述叶尖向所述叶根偏移。
根据上述第三方面的叶片，所述最高点的连线沿轴向的投影为渐开线。
根据上述第三方面的叶片，所述尾缘的拱宽w占所述尾缘长度的比例范围为大于等于0.05且小于等于0.3。
根据上述第三方面的叶片，所述前部拱起部沿所述叶片的径向截面的曲线满足：
拱宽w＝a×θ m，其中a的取值范围为0.2≤a≤2；m的取值范围为1≤m≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°；拱高h＝b×θ n，其中b的取值范围为0.05≤b≤1；n的取值的取值范围为1≤n≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°。
根据上述第三方面的叶片，m等于n，并且w/h的取值范围为0.05≤w/h≤0.4。
根据上述第三方面的叶片，所述叶片还包括弯折部，所述弯折部从所述压力面向所述吸力面拱起；其中，所述弯折部在所述叶片的径向截面上具有最低点，所述最低点的连线沿所述前缘到所述尾缘的方向延伸，并且所述最低点的所述连线在所述后部内。
根据本申请的第四方面，本申请提供一种轴流叶轮，其特征在于包括：轮毂，所述轮毂具有轴线，所述轮毂能够绕所述轴线转动，所述轮毂沿轴向的截面为圆形；和至少两片叶片，所述至少两片叶片布置在所述轮毂的外圆周面上，所述至少两片叶片中的每一片包括：上表面和下表面，所述上表面为压力面，所述下表面为吸力面；叶尖和叶根；前缘和尾缘，其中所述压力面和所述吸力面分别从所述叶尖延伸至所述叶根，并且分别从所述前缘延伸至所述尾缘；前部和后部，所述前部靠近所述叶尖，所述后部靠近所述叶根；以及前部拱起部，所述前部拱起部位于所述前部，所述前部拱起部从所述吸力面向所述压力面拱起；其中，所述前部拱起部在所述叶片的径向截面上具有最高点，所述最高点的连线沿所述前缘到所述尾缘方向延伸。
本申请的叶片能够抑制叶片表面的流动分离，改善表面的脱离涡，从而提高叶片性能，降低运行噪声。
附图说明
本申请特征和优点可通过参照附图阅读以下详细说明得到更好地理解，在整个附图中，相同的附图标记表示相同的部件，其中：
图1示出了使用本申请的一个实施例的叶片的叶轮的立体图；
图2A示出了图1中的叶轮所使用的叶片的立体图；
图2B示出了图2A中的叶片的沿径向的截面图；
图3示出了图2A中的叶片与现有技术中叶片的立体对比图；
图4示出了图2A中的叶片与现有技术中叶片的沿径向的截面的对比图；
图5示出了图1中的叶轮所使用的叶片沿轴向的投影图；
图6示出了根据本申请的一个示例的叶片沿轴向的投影图；
图7示出了图6中的叶片的弯折部的拱宽w与拱高h的关系图；
图8示出了图6中的叶片的立体图；
图9示出了图8中的叶片的前部拱起部的拱宽w与拱高h的关系图；
图10示出了根据本申请的另一个示例的叶片的立体图；
图11示出了图10中的叶片沿轴向的投影图。
具体实施方式
下面将参考构成本说明书一部分的附图对本申请的各种具体实施方式进行描述。应该理解的是，虽然在本申请中使用表示方向的术语，诸如“前”表示靠近叶尖、“后”表示靠近叶根、“前缘”表示沿叶片转向的前端边缘、“尾缘”表示沿叶片转向的后端边缘、“上”表示上表面(即压力面)、“下”表示下表面(即吸力面)等方向或方位性的描述本申请的各种示例结构部分和元件，但是在此使用这些术语只是为了方便说明的目的，基于附图中显示的示例方位而确定的。由于本申请所公开的实施例可以按照不同的方向设置，所以这些表示方向的术语只是作为说明而不应视作为限制。在以下的附图中，同样的零部件使用同样的附图号，相似的零部件使用相似的附图号，以避免重复描述。
图1示出了使用本申请的一个实施例的叶片的叶轮100的立体图。如图1所示，叶轮100包括轮毂110和三个叶片112。轮毂110具有中心轴线，轮毂110能够绕中心轴线转动，轮毂110沿轴向的截面为圆形，三个叶片112均匀地布置在轮毂110的外圆周面上。轮毂110可以与叶片112连接成一体。轮毂110和叶片112能够一同绕轮毂110的中心轴线进行旋转。作为一个示例，本申请的叶轮100按顺时针方向(即图1中箭头所示旋转方向)进行旋转。
图2A示出了图1中的叶轮100所使用的叶片112的立体图；图2B示出了图2A中的叶片的沿径向的截面图。图3示出了图2A中的叶片112与现有技术中的叶片310的立体对比图；图4示出了图2A中的叶片与现有技术中的叶片310的沿径向的截面对比图，以更好地示出本申请的叶片112与现有技术中叶片310的区别。其中，图2B中的实线表示本申请的叶片112；图2B中的虚线表示某一截面上叶尖216到叶根218的直线连线；图4中的实线表示本申请的叶片112；图4中的虚线表示现有技术中叶片310。
如图2A‐4所示，叶片112包括上表面、下表面、叶尖216、叶根218、前缘222和尾缘220。其中，上表面为压力面212，下表面为吸力面214。叶尖216为叶片112上叶片直径最 大的位置，叶根218为叶片112用于与轮毂110连接的位置。压力面212与吸力面214分别从叶尖216延伸至叶根218。前缘222为叶片112的迎着旋转方向的一侧。换句话说，当叶片112绕轮毂110的中心轴线旋转时，前缘222为叶片112迎着流体的一侧。尾缘220为叶片112中与前缘222相反的另一侧。压力面212与吸力面214分别从前缘222延伸至尾缘220。叶片112包括中分线255，中分线255在叶片112的径向截面上显示为中分点M。所述中分点M在该径向截面上的叶尖216与叶根218的直线连线上的垂直投影点为所述直线连线的中点Q。叶片112还包括前部242和后部244。其中，前部242为叶片112的从叶尖216到中分线255的区域(即靠近叶尖216的区域)，后部244为叶片112的从中分线255到叶根218的区域(即靠近叶根218的区域)。
本申请的叶片112还包括弯折部262。弯折部262从压力面212向吸力面214拱起。如图2B所示，在叶片112的径向截面上，叶片112的弯折部262具有最低点E。将弯折部262的径向截面上的最低点连起来的连线252(例如，图2A所示)是沿前缘222到尾缘220的方向延伸的。参考图4，与现有技术中叶片310不同的是，本申请的叶片112的弯折部262在吸力面214沿前缘222到尾缘220的方向形成凸起，从径向方向上破坏剥离涡。该凸起能够使位于吸力面214的大体积高强度的剥离涡***成小体积低强度的涡，从而降低湍流耗散损失。此外，弯折部262在叶片112的压力面212形成凹槽，以使得一部分从压力面212泄漏到吸力面214的流体引导进入此凹槽中。由此，弯折部262的设置能够减少湍流耗散损失和泄漏损失，以在改善气流和提高风机气动性能的同时降低噪声。
继续参考图2A‐4，叶片112还包括前部拱起部264。前部拱起部264位于叶片112的前部242。前部拱起部264从吸力面214向压力面212拱起。如图2B所示，在叶片112的径向截面上，叶片112的前部拱起部264具有最高点F。将该径向截面上的最高点F连起来的连线254(如图2A所示)是沿前缘222到尾缘220的方向延伸的。与现有技术中叶片310不同的是，本申请的叶片112的前部拱起部264在叶片112的吸力面214沿前缘222到尾缘220的方向形成凹槽。该凹槽能够破坏泄漏的主流流体路径，使得前部242的泄漏流吸入此凹槽内，抑制泄漏流动的继续发展。此外，该凹槽在降低前部242附近的叶片载荷的同时主动转移载荷，从而达到提升气动性能、提高风机效率的效果。另外，前部拱起部264在叶片112的压力面212沿前缘222到尾缘220的方向形成凸起。该凸起能够延缓从前缘222到尾缘220逐渐剥离的剥离涡发生的位置，并将大体积高强度的涡***成小体积低强度的涡，从而降低该剥离涡的湍流强度，降低噪音。
需要说明的是，尽管在图2A‐4所示的实施例中，叶片112包括弯折部262和前部拱起部264。但是根据本申请的原则，本申请的叶片112也可以只包括弯折部262和前部拱起部264中的一者。此外需要说明的是，尽管在图2A‐4所示的实施例中，弯折部262和前部拱起部264都从前缘222一直延伸到尾缘220，但是根据本申请，弯折部262和前部拱起部264也可以只在从前缘222到尾缘220的一部分区域上延伸，使得叶片112的一些径向截面上不具有弯折部262和前部拱起部264。例如，弯折部262或前部拱起部264可以从前缘222开始延伸，在还未到达尾缘220时就结束。此外，前部拱起部264位于叶片112的前部242，而弯折部262能够位于叶片112上的任何位置。也就是说，弯折部262能够位于叶片112的前部242、叶片112的后部244或叶片112的前部242和后部244。以上对叶片112的设置方式都能够在提高风机效率的同时降低噪声。
图5示出了图1中的叶轮所使用的叶片沿轴向的投影图。图6示出了根据本申请的一个示例的叶片112沿轴向的投影图。图7示出了图6中叶片112的弯折部262的拱宽w与拱高h的关系图。图6中的虚线表示弯折部262的径向的最低点的连线252的位置。
如图5‐7所示，弯折部262沿叶片112的径向截面的曲线满足：
拱宽w＝a×θ m；
拱高h＝b×θ n
其中，θ表示周向角度。具体而言，在叶尖216上任取一点P，点P到轮毂110中心O的连线与叶尖216与前缘222的交点L到轮毂110中心O的连线之间形成的夹角即为周向角度θ(参见图5)。
其中，0.2≤a≤2；0.05≤b≤1；1≤m≤3；1≤n≤3；并且0°≤θ≤180°。
拱宽w表示弯折部262在径向截面上的最大宽度，拱高h表示弯折部262在径向截面上的最高点距离最低点的高度。
作为一个示例，m等于n，并且w/h的取值范围为0.05≤w/h≤0.4。
作为另一个示例，当叶片112的外半径r1＝340mm时，a＝0.2，b＝1，并且m＝n＝1。
弯折部262的径向的最低点的半径满足：
rx＝c×(r1+r2)
其中，r1为叶片112的外半径；
r2为轮毂110的半径；
c的取值范围为0.1≤c≤0.95。
如图6所示，叶片112的叶尖216沿轴向的投影为圆弧形投影一(即，圆弧形投影一的半径为r1)；叶片112的叶根218沿轴向的投影为圆弧形投影二(即，圆弧形投影二的半径为r2)；弯折部262的径向的最低点的连线252沿轴向的投影为圆弧形投影三。圆弧形投影一、圆弧形投影二以及圆弧形投影三是同心的，其圆心都是轮毂110的轴线沿轴向的投影点O。
图8示出了图6中的叶片112的立体图。图9示出了图8中的叶片112的前部拱起部264的拱宽w与拱高h的关系图。图8中的虚线表示前部拱起部264的径向的最高点的连线254的位置。
如图8‐9所示，前部拱起部264在径向截面上的曲线满足：
拱宽w＝a×θ m；
拱高h＝b×θ n
其中，θ表示周向角度。具体而言，在叶尖216上任取一点P，点P到轮毂110中心O的连线与叶尖216与前缘222的交点到轮毂110中心O的连线之间形成的夹角即为周向角度θ(参见图5)。
其中，a的取值范围为0.2≤a≤2；b的取值范围为0.05≤b≤1；m的取值范围为1≤m≤3；n的取值的取值范围为1≤n≤3；θ的取值的取值范围为0°≤θ≤180°。
拱宽w表示前部拱起部264在叶片112的径向截面上的最大宽度，拱高h表示前部拱起部264在叶片112的径向截面上的最高点距离最低点的高度。
作为一个示例，m等于n并且w/h的取值范围为0.05≤w/h≤0.4。
作为另一个示例，当叶片112的外半径r1＝340mm时，a＝0.2，b＝1，并且m＝n＝1。
继续参考图8，最高点的连线254沿轴向的投影是沿前缘222到尾缘220方向逐渐从叶尖216向叶根218偏移的。具体来说，前部拱起部264的一端点K(如图9所示)为叶尖216上的任意一点。当周向角度θ为0°时，拱宽w等于拱高h等于0，此时叶片112的拱宽和 拱高都为0，端点K与叶尖216与前缘222的交点L重合。当端点K沿从前缘222到尾缘220方向移动时，周向角度θ的值增加，使得拱宽w和拱高h的值也慢慢变大。这样，前部拱起部264的径向的最高点254沿从前缘222到尾缘220方向慢慢远离叶尖216，从而形成大致如图8中虚线所示的位于叶片112的前部242的前部拱起部264的最高点的连线254。最高点的连线254沿轴向的投影为渐开线。
作为另一个示例，尾缘220的拱宽w占尾缘220长度的比例范围为大于等于0.05且小于等于0.3。
图10示出了根据本申请的另一个示例的叶片112的立体图。图11示出了图10中的叶片112沿轴向的投影图。图10‐11中的虚线表示前部拱起部264的径向的最高点的连线254的位置。如图10‐11所示，前部拱起部264的最高点的连线254沿轴向的投影为圆弧形投影四。圆弧形投影四与叶尖216的圆弧形投影一以及叶根218的圆弧形投影二是同心的，其圆心都是轮毂110的轴线沿轴向的投影点O。
需要说明的是，叶片112的从前缘到尾缘的叶型截面可以有多种，其可以为等厚度截面或者任何二维翼型。虽然本申请中列举了拱宽w与拱高h的关系式，但本申请中前部拱起部264和弯折部262的拱形特征也可以使用圆弧，抛物线等，同样能实现本申请中提高叶片性能和降低噪声的目的。
尽管本文中仅对本申请的一些特征进行了图示和描述，但是对本领域技术人员来说可以进行多种改进和变化。因此应该理解，所附的权利要求旨在覆盖所有落入本申请实质精神范围内的上述改进和变化。

Claims (14)

  1. 一种叶片(112)，包括：
    上表面和下表面，所述上表面为压力面(212)，所述下表面为吸力面(214)；
    叶尖(216)和叶根(218)；
    前缘(222)和尾缘(220)，其中所述压力面(212)和所述吸力面(214)分别从所述叶尖(216)延伸至所述叶根(218)，并且分别从所述前缘(222)延伸至所述尾缘(220)；
    其特征在于：所述叶片(112)还包括：
    弯折部(262)，所述弯折部(262)从所述压力面(212)向所述吸力面(214)拱起；
    其中，所述弯折部(262)在所述叶片(112)的径向截面上具有最低点，所述最低点的连线(252)沿所述前缘(222)到所述尾缘(220)的方向延伸。
  2. 如权利要求1所述的叶片(112)，其特征在于：
    所述叶尖(216)沿轴向的投影为圆弧形投影一；
    所述叶根(218)沿轴向的投影为圆弧形投影二；
    所述最低点的所述连线(252)沿轴向的投影为圆弧形投影三；
    其中，所述圆弧形投影一、所述圆弧形投影二以及所述圆弧形投影三是同心的。
  3. 如权利要求2所述的叶片(112)，其特征在于：
    所述弯折部(262)沿所述叶片(112)的径向截面的曲线满足：
    拱宽w＝a×θ m，其中，a的取值范围为0.2≤a≤2；m的取值范围为1≤m≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°；
    拱高h＝b×θ n，其中b的取值范围为0.05≤b≤1；n的取值范围为1≤n≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°。
  4. 如权利要求3所述的叶片(112)，其特征在于：
    m等于n，并且w/h的取值范围为0.05≤w/h≤0.4。
  5. 一种轴流叶轮(100)，其特征在于包括：
    轮毂(110)，所述轮毂(110)具有中心轴线，所述轮毂(110)能够绕所述中心轴线转动，所述轮毂(110)沿轴向的截面为圆形；和
    至少两片根据权利要求1‐4中任意一项所述的叶片(112)，所述至少两片叶片(112)布置在所述轮毂(110)的外圆周面上。
  6. 一种叶片(112)，包括：
    上表面和下表面，所述上表面为压力面(212)，所述下表面为吸力面(214)；
    叶尖(216)和叶根(218)；
    前缘(222)和尾缘(220)，其中所述压力面(212)和所述吸力面(214)分别从所述叶尖(216)延伸至所述叶根(218)，并且分别从所述前缘(222)延伸至所述尾缘(220)；
    前部(242)和后部(244)，所述前部(242)靠近所述叶尖(216)，所述后部(244)靠近所述叶根(218)；
    其特征在于：所述叶片(112)还包括：
    前部拱起部(264)，所述前部拱起部(264)位于所述前部(242)，所述前部拱起部(264)从所述吸力面(214)向所述压力面(212)拱起；
    其中，所述前部拱起部(264)在所述叶片(112)的径向截面上具有最高点，所述最高点的连线(254)沿所述前缘(222)到所述尾缘(220)方向延伸。
  7. 如权利要求6所述的叶片(112)，其特征在于：
    所述叶尖(216)沿轴向的投影为圆弧形投影一；
    所述叶根(218)沿轴向的投影为圆弧形投影二；
    所述最高点的连线(254)沿轴向的投影为圆弧形投影四；
    其中，所述圆弧形投影一、所述圆弧形投影二以及所述圆弧形投影四是同心的。
  8. 如权利要求6所述的叶片(112)，其特征在于：
    所述最高点的连线(254)沿轴向的投影是沿所述前缘(222)到所述尾缘(220)方向逐渐从所述叶尖(216)向所述叶根(218)偏移的。
  9. 如权利要求8所述的叶片(112)，其特征在于：
    所述最高点的连线(254)沿轴向的投影为渐开线。
  10. 如权利要求8所述的叶片(112)，其特征在于：
    所述前部拱起部(264)沿所述叶片(112)的径向截面的曲线满足：
    拱宽w＝a×θ m，其中0.2≤a≤2a的取值范围为；m的取值范围为1≤m≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°；
    拱高h＝b×θ n，其中b的取值范围为0.05≤b≤1；n的取值范围为1≤n≤3；θ为周向角度，并且θ的取值范围为0°≤θ≤180°。
  11. 如权利要求6‐10中任一项所述的叶片(112)，其特征在于：
    所述尾缘(220)处的拱宽w占所述尾缘(220)长度的比例范围为大于等于0.05且小于等于0.3。
  12. 如权利要求11所述的叶片(112)，其特征在于：
    m等于n，并且w/h的取值范围为0.05≤w/h≤0.4。
  13. 如权利要求6所述的叶片(112)，其特征在于还包括：
    弯折部(262)，所述弯折部(262)从所述压力面(212)向所述吸力面(214)拱起；
    其中，所述弯折部(262)在所述叶片(112)的径向截面上具有最低点，所述最低点的连线(252)沿所述前缘(222)到所述尾缘(220)的方向延伸，并且所述最低点的所述连线(252)位于所述后部(244)。
  14. 一种轴流叶轮(100)，其特征在于包括：
    轮毂(110)，所述轮毂(110)具有中心轴线，所述轮毂(110)能够绕所述中心轴线转动，所述轮毂(110)沿轴向的截面为圆形；和
    至少两片根据权利要求6‐13中任意一项所述的叶片(112)，所述至少两片叶片(112)均匀布置在所述轮毂(110)的外圆周面上。
PCT/CN2019/085923 2018-05-09 2019-05-08 叶片及使用其的轴流叶轮 WO2019214632A1 (zh)

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