WO2010135932A1 - 应用于水动节能冷却塔的直联低速小型混流式水轮机 - Google Patents

应用于水动节能冷却塔的直联低速小型混流式水轮机 Download PDF

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Publication number
WO2010135932A1
WO2010135932A1 PCT/CN2010/071503 CN2010071503W WO2010135932A1 WO 2010135932 A1 WO2010135932 A1 WO 2010135932A1 CN 2010071503 W CN2010071503 W CN 2010071503W WO 2010135932 A1 WO2010135932 A1 WO 2010135932A1
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WIPO (PCT)
Prior art keywords
water
runner
diameter
inlet
outlet
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PCT/CN2010/071503
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English (en)
French (fr)
Inventor
顾星康
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南京星飞冷却设备有限公司
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Application filed by 南京星飞冷却设备有限公司 filed Critical 南京星飞冷却设备有限公司
Priority to SG2011087616A priority Critical patent/SG176258A1/en
Priority to EP10780014.6A priority patent/EP2436915A4/en
Priority to US13/322,554 priority patent/US9200612B2/en
Priority to RU2011152629/06A priority patent/RU2491444C1/ru
Priority to KR1020117031151A priority patent/KR101327340B1/ko
Priority to AU2010252496A priority patent/AU2010252496B2/en
Priority to JP2012512182A priority patent/JP2012528261A/ja
Priority to CA2763302A priority patent/CA2763302C/en
Priority to MX2011012560A priority patent/MX2011012560A/es
Publication of WO2010135932A1 publication Critical patent/WO2010135932A1/zh
Priority to ZA2011/09425A priority patent/ZA201109425B/en

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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
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/02—Machines or engines of reaction type; Parts or details peculiar thereto with radial flow at high-pressure side and axial flow at low-pressure side of rotors, e.g. Francis 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
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • 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
    • F03B17/00—Other machines or engines
    • F03B17/06—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head"
    • 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
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • This invention relates to a cooling tower, and more particularly to a water turbine for driving a cooling fan of a cooling tower, in particular, a gearbox without a reduction gear, which is designed by rationally designing the dimensions of various parts, in particular the inlet ring and the runner.
  • the output speed of the turbine is the fan speed rating, which eliminates the use of the gearbox used in the traditional counter-turbine turbine for the direct-coupled low-speed small Francis turbine used in the hydro-electric energy-saving cooling tower.
  • air-conditioning cooling towers especially industrial air-conditioning cooling towers, are designed to have enough rich energy to cool the circulating water.
  • the turbine is used to recover this part of the rich energy, which is converted into the rotary mechanical energy of the turbine.
  • Driving the cooling fan eliminates the need for a traditional high-power cooling motor, and the energy saving effect is remarkable.
  • the object of the present invention is to solve the problems of high noise, high failure rate and high manufacturing and maintenance cost of a cooling tower water turbine with a reduction gear box, and a design with high efficiency and small size can be widely applied.
  • the direct-coupled low-speed small-flow Francis turbine of the water-saving energy-saving cooling tower makes the cooling tower turbine completely bid farewell to the gear reducer.
  • a direct-connected low-speed small mixed flow turbine applied to a hydrodynamic cooling tower comprising: a volute 1 into the water;
  • a seat ring 2 having a single row of vanes arranged in a ring shape
  • a low-speed mixed-flow turbine runner 12 composed of a lower ring 3, a curved blade 4, and an upper crown 5; a straight-cone type outlet pipe 9 and a side outlet tank 10;
  • the seat ring 2 is mounted on the inner side of the volute 1 , and the water inlet between the guide vanes in the seat ring 2 communicates with the water outlet passage of the volute 1 , and the water inlet of the volute 1 communicates with the water outlet of the cooling tower circulating water pipe.
  • the water outlet between the guide vanes in the seat ring 2 communicates with the water inlet formed between the curved blades 4 in the middle of the runner, and the water outlet formed between the curved blades 4 communicates with the water inlet of the straight cone type outlet pipe 9
  • the water outlet of the cone outlet pipe 9 communicates with the water inlet of the side outlet tank 10, and the water outlet of the side outlet tank 10 communicates with the water inlet of the cooling tower circulation water pipe, wherein the runner 12 is provided with a bearing housing 6
  • the shaft 7 is installed in the bearing housing 6, and the cooling fan blade is directly mounted on the shaft 7; the value of the unit speed is
  • the upper crown surface and the lower ring surface of the runner 12 are curved surfaces, and the average curvature of the bus bar forming the upper crown surface is 1.6 rad/n! ⁇ 1.7 rad/m, the average curvature of the busbar forming the lower annulus is 4.8 rad/m ⁇ 4.9 rad/m ; the number of curved blades 4 in the runner 12 is 16-20, and the minimum thickness and maximum thickness of the curved blade wing The ratio is 0.28 ⁇ 0.34.
  • the guide vanes in the seat ring 2 are arranged in a single row, which serves as both a guiding action and a supporting action, and the ratio of the inner diameter D4 of the vane, the diameter D3 of the outer circle and the diameter D1 of the inlet of the runner 12 D ⁇ D ⁇ D 3 /D 1
  • the ratios are 1 to 1.1 and 1.15 to 1.25, the number of guide vanes is 15 to 19, and the guide vanes have a negative curvature wing shape.
  • the height H2 of the straight cone type outlet pipe 9 is 0.2 to 0.5 times the diameter D1 of the inlet 12 of the runner 12, and the diameter D5 of the outlet of the straight cone type outlet pipe is 0.45 to 0.75 times the diameter D1 of the inlet of the runner 12.
  • the height H3 of the side outlet tank 10 is 0.2 to 0.4 times the diameter D1 of the inlet 12 of the runner 12, and the outlet tank 10 is provided with 4 outlets, and the width B of each outlet is the inlet diameter D1 of the runner 12 0.4 to 0.6 times.
  • the maximum dimension L1 of the turbine in the left-right direction is 1.8 to 2.0 times the diameter D1 of the inlet 12 of the runner 12, and the maximum dimension L2 in the front-rear direction is 1.7 to 1.9 times the diameter D1 of the inlet of the runner 12.
  • the invention fundamentally solves the control problem of the output speed of the mixed flow turbine for the non-power generation type cooling tower by rational design and matching, and finally determines the size and shape of the negative-curvature guide vane in the seat ring by the rated rotational speed required for the cooling fan. And to determine the size and shape of the curved blades in the runner, and the computer can optimize the optimal size to meet the driving force requirements.
  • the invention can save the speed reducer, thereby greatly reducing the noise of the whole machine, reducing the manufacturing and maintenance costs, greatly increasing the trouble-free working time by more than 80%, and keeping the overall efficiency above 86%.
  • «u is the unit speed, "for the actual fan speed (r/min), D1 is the inlet inlet diameter (m), the inlet water pressure (in water column: m). Not only adapts to the characteristics of the cooling tower turbine, but also Helps reduce overall size and increase efficiency.
  • FIG. 1 is a front elevational view showing the overall structure of a volute of the present invention having a multi-metal trapezoidal cross section.
  • Figure 2 is a top plan view of Figure 1.
  • Fig. 3 is a front elevational view showing the overall structure of the volute of the present invention in the form of a multi-metal ellipse; and Figure 4 is a three-view view of the runner blade of the present invention.
  • Figure 5 is a schematic view of the three-view of the negative curvature guide vane of the present invention. detailed description
  • a direct-coupled low-speed small mixed flow turbine for a hydrodynamic cooling tower which comprises a metal volute 1 having an elliptical cross section (Fig. 3) or a trapezoidal shape (Fig. 1), one arranged in a single row of rings a seat ring 2 of the guide vane, a low-speed mixed-flow turbine runner 12 composed of a lower ring 3, a curved blade 4, and an upper crown 5, a straight-cone outlet pipe 9 and a side outlet tank 10, the seat ring 2 is mounted on On the inner side of the volute 1, the volute 1 is supported on the buttress 8, and the lower part of the runner 12 is mounted with a busbar 11, as shown in Fig.
  • the water inlet between the guide vanes in the seat ring 2 and the volute 1 The water outlet channel communicates with each other, and the water inlet of the volute 1 communicates with the water outlet of the cooling tower circulating water pipe, and the water outlet between the guide vanes in the seat ring 2 communicates with the water inlet formed between the curved blades 4 in the middle of the runner 12, and the curved surface
  • the water outlet formed between the blades 4 communicates with the water inlet of the straight cone type outlet pipe 9, the water outlet of the straight cone type outlet pipe 9 communicates with the water inlet of the side outlet tank 10, and the outlet of the side outlet tank 10 and the cooling tower circulate
  • the water inlet of the water pipe is connected, and the bearing wheel 6 is mounted on the rotating wheel, and the bearing seat 6 is A shaft 7 is mounted therein, and cooling fan blades (not shown) are directly mounted on the shaft 7.
  • the unit speed the value of the whole machine is between 28 and 42 (in the formula, "the rated speed of the cooling fan blade, D1 is the inlet diameter of the runner 12, and H is the inlet water pressure.
  • the unit is the height of the water column m). It can be known from the formula that as long as the fan speed and the small head pressure H are determined (the two parameters are determined by the design parameters of the cooling tower), the only diameter of the inlet of the runner can be determined. To uniquely determine the dimensions of the various parts of the turbine, including runners, blades, seat rings, vanes, maximum length and maximum width:
  • the ratio of the outlet diameter of the runner 12 to the inlet diameter is
  • the upper crown surface and the lower ring surface of the runner 12 are both curved surfaces, wherein the average curvature of the bus bar forming the upper crown surface is 1.6 rad/m-1.7 rad/m, and the average curvature of the bus bar forming the lower crown surface is 4.8 rad/m -4.9 Rad/m ; the number of curved blades 4 in the runner 12 is 16 to 20, and the ratio of the minimum thickness to the maximum thickness of the curved blade is 0.28 to 0.34. As shown in Figure 4.
  • the guide vanes in the seat ring 2 are arranged in a single row, which serves as both a guiding action and a supporting action, and the ratio of the inner and outer circles of the vane to the nominal inlet diameter of the runner Dg/Di is 1 ⁇ : L.1 and 1.15 ⁇ 1.25, the number of guide vanes is 15 ⁇ 19, and the guide vanes adopt a negative curvature wing shape.
  • Figure 5 is a three-view projection of a negative curvature wing guide vane.
  • the height of the straight cone type outlet pipe 9 is 0.2 to 0.5 times the diameter D1 of the runner 12, and the diameter of the outlet of the straight cone type outlet is D5 which is 0.45 to 0.75 times the diameter D1 of the inlet 12 of the runner. As shown in Figure 1, 3.
  • the height H3 of the side outlet tank 10 is 0.2 to 0.4 times the diameter D1 of the inlet 12 of the runner 12, and the outlet tank 10 is provided with a total of four outlets, and the width B of each outlet is 0.4 to the diameter D1 of the inlet of the runner 12. 0.6 times. As shown in Figure 1, 3.
  • the maximum dimension L1 of the turbine in the left-right direction is 1.8 to 2.0 times the diameter D1 of the inlet of the runner, and the maximum dimension L2 in the front-rear direction is 1.7 to 1.9 times the diameter D1 of the inlet of the runner.
  • the efficiency of the turbine of the present invention can be kept at about 86% only when the value of the unit speed nil is between 28 and 42.
  • the value of nil is less than 28, the measured rotational speed will be significantly lower.
  • the rated speed is more than 30%, and the efficiency must be increased by more than 90% on the basis of 1/3 of the speed.
  • the unit speed nil is preferably in the range of 28-42.
  • the water with a certain pressure and flow enters the seat ring through a certain amount of circulation of the volute, and the steering wheel and the speed increasing action impinge on the turbine runner to drive the runner to rotate, the runner drives the shaft 7 to rotate, and the shaft 7 drives the upper end.
  • the fan blades rotate to complete the conversion of water energy to mechanical energy.
  • the water coming out of the runner is finally discharged from the side outlet tank into the air conditioning system for circulation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Hydraulic Turbines (AREA)

Description

说明书
应用于水动节能冷却塔的直联低速小型混流式水轮机 技术领域
本发明涉及一种冷却塔， 尤其是一种驱动冷却塔冷却风扇的水轮机， 具 体地说是一种不带减速箱， 通过合理设计各部分尺寸尤其是进水座环和转轮 的关键参数使水轮机的输出转速为风机转速额定值从而省去传统反击式水轮 机使用的减速箱的应用于水动节能冷却塔的直联低速小型混流式水轮机。 背景技术
众所周知， 空调冷却塔尤其是工业空调冷却塔， 在设计时冷却循环水都 留有足够多的富裕能量， 为了实现节能的目的， 使用水轮机回收这部分富裕 能量， 将其转化为水轮机的旋转机械能用于驱动冷却风扇， 省去了传统的大 功率冷却电机， 节能效果十分显著。
现在我国的工业空调冷却塔循环水富裕水头一般在 4π！〜 15m之间， 布水 管处需要 0. 5π！〜 lm的压力水头，因此用于回收这部分循环水富裕水头的水轮 机工作在有背压的环境， 而冷却塔风机转速较低， 为了做到与冷却塔风扇直 联， 必须选用低速混流式水轮机， 而目前在我国水轮机型谱中， 能满足这种 工作环境的与冷却风机直联的低速混流式水轮机还没有， 需采用将一般混流 式水轮机通过一个减速器与冷却塔风机相联的驱动模式， 由于减速箱的工作 条件较差， 不仅噪音大、 寿命短， 而且也相应地提高了制造成本。 因此研制 出这种满足这种工作环境的低单位转速与冷却塔风机直联的混流式水轮机， 有着重大的现实意义。
申请人通过大量计算分析和实验认为， 只要合理地对水轮机各部分的尺 寸进行设计就可将水轮机的输出转速控制在希望的范围之内。 发明内容
本发明的目的是针对带有减速箱的冷却塔用水轮机存在的噪音大、 故障 率高， 制造和维护成本高的问题， 设计一种效率高、 尺寸小的可广泛应用于 水动节能冷却塔的直联低速小型混流式水轮机， 从而使冷却塔用水轮机彻底 与齿轮减速箱告别。
本发明的技术方案是：
一种应用于水动节能冷却塔的直联低速小型混流式水轮机， 它包括： 一个进水的蜗壳 1 ;
一个环形布置有单列导叶的座环 2;
一个由下环 3、 曲面叶片 4、 上冠 5组成的低转速混流式水轮机转轮 12; 一个直锥型出水管 9以及一个侧出水箱 10;
所述座环 2安装在蜗壳 1的内侧， 座环 2中的导叶之间的进水口与蜗壳 1的出水通道相通，蜗壳 1的进水口与冷却塔循环水管的出水口相通，座环 2 中的导叶之间的出水口与转轮中间的曲面叶片 4之间形成的进水口相通， 曲 面叶片 4之间形成的出水口与直锥型出水管 9的进水口相通， 直锥型出水管 9的出水口与侧出水箱 10的进水口相通， 侧出水箱 10的出水口与冷却塔循 环水管的进水口相通， 其特征是所述的转轮 12上安装有轴承座 6， 轴承座 6 中安装有轴 7， 轴 7 上直接安装有冷却风扇叶片； 单位转速 的值为
28-42， 式中《为冷却风扇叶片的额定转速， D1为转轮 12进水口直径， H为 进塔水压。
所述的转轮流道部分高度 HI 与转轮 12 的进水口直径之间的关系为： H1/D1=0.35~0.42， 转轮 12 的出水口直径 D2 与进水口直径 D1 的比值
Figure imgf000004_0001
转轮 12的上冠面与下环面均为曲面，其中形成上冠面的母线 平均曲率为 1.6rad/n！〜 1.7 rad/m， 形成下环面的母线平均曲率为 4.8 rad/m 〜 4.9 rad/m; 转轮 12中的曲面叶片 4的数量为 16〜20， 曲面叶片翼形最小厚 度与最大厚度之比为 0.28〜0.34。
所述的座环 2中的导叶成单列布置， 它既起导流作用又起支撑作用， 导 叶的内圆直径 D4、外圆直径 D3与转轮 12进水口直径 D1之比 D^D^ D3/D1 的比例分别为 1〜1.1与 1.15〜1.25， 导叶的数量为 15〜19， 导叶采用负曲率 翼形。
所述的直锥型出水管 9的高度 H2为转轮 12进水口直径 D1的 0.2〜0.5 倍，直锥型出水管 9出口直径 D5为转轮 12进水口直径 D1的 0.45〜0.75倍。
所述的侧出水箱 10的高度 H3为转轮 12进水口直径 D1的 0.2〜0.4倍， 侧出水箱 10共设置有 4个出水口， 每个出水口宽度 B为转轮 12进水口直径 D1的 0.4〜0.6倍。
所述的水轮机的左右方向最大尺寸 L1为转轮 12进水口直径 D1的 1.8〜 2.0倍， 其前后方向最大尺寸 L2为转轮 12进水口直径 D1的 1.7〜1.9倍。
所述的直接影响本发明效率的导叶的迎水面的曲线方程为 y =AlX 4 +BlX 3 + dx2 +Di x+ ， 其中 AF-7 X 10— 8〜- 9 X 10— 8、 BF3.5 X 10—5〜5.5 X 10— 5、 d=-6.5 X lO—5〜- 8.5 X 10—5、 DF2.2 X 10 -1〜 2.6 X 10 1、 X 10—2〜- 1.3 X 10 1， 背水面的曲线方程为 y =A2x4 +B2x3 +C2x2 +D2 x+E2, 其中 A2=1.9 X 10— 9〜 2.3 X 10—9、 B2=-1.7 X 10— 6〜- 2.1 X 10— 6、 C2=-9.5 X 10— 4〜- 1.0 X 10— 3、 D2=2.5 X 10―1〜 3.0 X 10— E2=3.1〜3.7， 方程中 x、 y的单位为毫米， 且所述导叶的头 部迎水面和背水面之间圆滑连接， 所述导叶的尾部迎水面和背水面之间折线 连接。
本发明的有益效果：
本发明通过合理设计和匹配从根本上解决了非发电型冷却塔用混流式 水轮机输出转速的控制问题， 它可通过冷却风扇所需的额定转速最终确定座 环中负曲率导叶的尺寸和形状以及确定转轮中曲面叶片的尺寸和形状， 并可 通过计算机优化获得最佳的尺寸， 以满足驱动力的要求。
本发明可省去减速箱， 因此可大大减少整机的噪音， 降低制造和维护成 本，大大增加无故障工作时间 80%以上，同时可使整体的效率保持在 86%以上。 本发明突破了传统水轮设计中单位转速的使用范围， 使单位转速的取值 从传统的 80以上减少到 28-42之间， 即 Wll = 的值介于 28-42之间， 其中
«u为单位转速 ， 《为实际风机转速 （r/min)， D1为转轮进水边直径 （m)， 为进塔水压 (以水柱为单位： m)。不仅适应了冷却塔水轮机的特点， 而且有 利于减小整体尺寸， 提高效率。 附图说明
图 1是本发明的蜗壳断面为多金属梯形时整体结构正视示意图。
图 2是图 1的俯视示意图。
图 3是本发明的蜗壳断面为多金属椭圆形时整体结构正视示意图 图 4是本发明的转轮叶片三视示意图。
图 5是本发明的负曲率导叶翼形三视示意图。 具体实施方式
下面结合附图和实施例对本发明作进一步的说明。
如图 1-5所示。
一种应用于水动节能冷却塔的直联低速小型混流式水轮机， 它包括一个 进水的横断面呈椭圆形（图 3 )或梯形（图 1 ) 的金属蜗壳 1， 一个布置有单 列环形导叶的座环 2， 一个由下环 3、 曲面叶片 4、 上冠 5组成的低转速混流 式水轮机转轮 12，一个直锥型出水管 9以及一个侧出水箱 10，座环 2安装在 蜗壳 1的内侧， 蜗壳 1支承在支墩 8上， 转轮 12的下部安装有汇流盘 11， 如图 1所示， 座环 2中的导叶之间的进水口与蜗壳 1的出水通道相通， 蜗壳 1的进水口与冷却塔循环水管的出水口相通， 座环 2中的导叶之间的出水口 与转轮 12中间的曲面叶片 4之间形成的进水口相通，曲面叶片 4之间形成的 出水口与直锥型出水管 9的进水口相通， 直锥型出水管 9的出水口与侧出水 箱 10的进水口相通，侧出水箱 10的出水口与冷却塔循环水管的进水口相通， 所述的转轮上安装有轴承座 6，轴承座 6中安装有轴 7，轴 7上直接安装有冷 却风扇叶片（图中未示出）。整机的单位转速 = 的取值在 28-42之间（式 中《为冷却风扇叶片的额定转速， D1为转轮 12进水口直径， H为进塔水压， 单位为水柱高度 m)， 由公式可知，只要风扇的转速《和小头压力 H确定（这 两个参数由冷却塔的设计参数确定）即可确定唯一的转轮进水口直径/？，从 而可唯一地确定整个水轮机各部分 （包括转轮、 叶片、 座环、 导叶、 最大长 度和最大宽度） 的尺寸：
如转轮 12流道部分高度 H1/D1=0.35~0.42，， 转轮 12出水口直径与进水 口直径比值
Figure imgf000007_0001
转轮 12的上冠面与下环面均为曲面， 其中形成 上冠面的母线平均曲率为 1.6rad/m-1.7 rad/m， 形成下环面的母线平均曲率为 4.8 rad/m -4.9 rad/m; 转轮 12中的曲面叶片 4的数量为 16〜20， 曲面叶片翼 形最小厚度与最大厚度之比为 0.28〜0.34。 如图 4所示。
座环 2中的导叶成单列布置，它既起导流作用又起支撑作用，导叶的内、 外圆与转轮标称进口直径之比
Figure imgf000007_0002
Dg/Di分别为 1〜： L.1与 1.15〜1.25， 导 叶数为 15〜19， 导叶采用负曲率翼形。 图 5是一个负曲率翼形导叶的三视投 影图。
直锥型出水管 9的高度 H2为转轮 12进水口直径 D1的 0.2〜0.5倍， 直 锥型出水管 9出口直径 D5为转轮 12进水口直径 D1的 0.45〜0.75倍。 如图 1、 3所示。
侧出水箱 10的高度 H3为转轮 12进水口直径 D1的 0.2〜0.4倍，侧出水 箱 10共设置有 4个出水口， 每个出水口宽度 B为转轮 12进水口直径 D1的 0.4〜0.6倍。 如图 1、 3所示。
水轮机的左右方向最大尺寸 L1为转轮进水口直径 D1的 1.8〜2.0倍，其 前后方向最大尺寸 L2为转轮进水口直径 D1的 1.7〜1.9倍。
作为直接影响水轮机效率的导叶的迎水面的曲线方程为 y =AlX 4 +BlX 3 + dx2 +Di x+Ei , 其中 AF-7 X 10— 8〜- 9 X 10— 8、 BF3.5 X 10—5〜5.5 X 10— 5、 d=-6.5 X lO—5〜- 8.5 X 10—5、 DF2.2 X 10 -1〜 2.6 X 10 1、 X 10—2〜- 1.3 X 10 1， 背水面的曲线方程为 y =A2x4 +B2x3 +C2x2 +D2 x+E2, 其中 A2=1.9 X 10— 9〜 2.3 X 10—9、 B2=-1.7 X 10— 6〜- 2.1 X 10— 6、 C2=-9.5 X 10— 4〜- l.O X 10— 3、 D2=2.5 X 10―1〜 3.0 X 10— E2=3.1〜3.7， 方程中 x、 y的单位为毫米， 且所述导叶的头 部迎水面和背水面之间圆滑连接， 所述导叶的尾部迎水面和背水面之间折线 连接。
由上可知， 本领域的技术人员根据本发明的所提供的公式即可很方便地 设计出符合要求的水轮机。 实验数据表明， 只有当单位转速 nil的取值介于 28-42之间时才能保证本发明的水轮机的效率保持在 86%左右， 而当 nil 的 取值小于 28时， 实测转速将明显低于额定转速 30%以上， 而要提高 1/3的转 速则效率必须原有基础上提高 90%以上， 而上单位转速 nil取值大于 42时， 不仅整体尺寸增加， 而且实测输出转速也会出现相同的情况， 因此单位转速 nil的取值范围以 28-42为最佳值。
本发明的主要工作过程：
一定压力及流量的水通过蜗壳形成一定的环量进入座环， 通过导叶的导 流与增速作用冲击水轮机转轮， 带动转轮旋转， 转轮带动轴 7转动， 轴 7带 动上端的风扇叶片转动， 完成水能到机械能的转换， 从转轮出来的水最后从 侧出水箱排出进入空调系统循环。
本发明未涉及部分均与现有技术相同或可采用现有技术加以实现。

Claims

权利要求书
1、 一种应用于水动节能冷却塔的直联低速小型混流式水轮机， 它包括：
一个进水的蜗壳 （1 ) ;
一个环形布置有单列导叶的座环 （2) ;
一个由下环 （3 )、 曲面叶片 （4)、 上冠 （5 ) 组成的低转速混流式水轮机 转轮 ( 12)；
一个直锥型出水管 （9 ) 以及一个侧出水箱 （10) ;
所述座环 （2) 安装在蜗壳 （1 ) 的内侧， 座环 （2) 中的导叶之间的进水 口与蜗壳 （1 ) 的出水通道相通， 蜗壳 （1 ) 的进水口与冷却塔循环水管的出 水口相通， 座环 （2) 中的导叶之间的出水口与转轮中间的曲面叶片 （4) 之 间形成的进水口相通， 曲面叶片 （4)之间形成的出水口与直锥型出水管（9) 的进水口相通， 直锥型出水管（9 )的出水口与侧出水箱（10)的进水口相通， 侧出水箱 （10) 的出水口与冷却塔循环水管的进水口相通， 其特征是所述的 转轮 （12) 上安装有轴承座 （6)， 轴承座 （6 ) 中安装有轴 （7 )， 轴 （7 ) 上 直接安装有冷却风扇叶片； 单位转速 的值为 28-42， 式中《为冷却风
Figure imgf000009_0001
扇叶片的额定转速， D1为转轮 （12) 进水口直径， H为进塔水压。
2、 根据权利要求 1所述的水轮机， 其特征是所述的转轮流道部分高度 HI与 转轮 （12) 的进水口直径之间的关系为： H1/D1=0.35~0.42， 转轮 （12) 的出 水口直径 D2与进水口直径 D1的比值
Figure imgf000009_0002
转轮（12)的上冠面与 下环面均为曲面， 其中形成上冠面的母线平均曲率为 1.6rad/n！〜 1.7 rad/m， 形 成下环面的母线平均曲率为 4.8 rad/m 〜4.9 rad/m; 转轮（12) 中的曲面叶片
(4)的数量为 16〜20，曲面叶片翼形最小厚度与最大厚度之比为 0.28〜0.34。
3、 根据权利要求 1所述的水轮机， 其特征是所述的座环 （2) 中的导叶成单 列布置， 它既起导流作用又起支撑作用， 导叶的内圆直径 D4、 外圆直径 D3
- 1 - 与转轮（12)进水口直径 Dl之比 Dg/Di的比例分别为 1〜1.1与 1.15〜 1.25， 导叶的数量为 15〜19， 导叶采用负曲率翼形。
4、 根据权利要求 1所述的水轮机， 其特征是所述的直锥型出水管 （9) 的高 度 H2为转轮 （12) 进水口直径 D1的 0.2〜0.5倍， 直锥型出水管 （9) 出口 直径 D5为转轮 （12) 进水口直径 D1的 0.45〜0.75倍。
5、 根据权利要求 1 所述的水轮机， 其特征是所述的侧出水箱 （10) 的高度 H3为转轮 （12) 进水口直径 D1的 0.2〜0.4倍， 侧出水箱 （10) 共设置有 4 个出水口， 每个出水口宽度 B为转轮 （12) 进水口直径 D1的 0.4〜0.6倍。
6、 根据权利要求 1所述的水轮机， 其特征是它的左右方向最大尺寸 L1为转 轮（12)进水口直径 D1的 1.8〜2.0倍， 其前后方向最大尺寸 L2为转轮（12) 进水口直径 D1的 1.7〜1.9倍。
7、根据权利要求 1所述的水轮机， 其特征是所述的导叶的迎水面的曲线方程 为 y =AlX 4 +BlX 3 +dx2 +Di x+ ， 其中 AF-7X10— 8〜- 9X10— 8、 6^3.5 X 10—5〜5.5X10—5、 （^=-6.5X10—5〜- 8.5X105、 DF2.2X 10 -1〜 2.6X 101、 =-9 X10— 2〜- 1.3X10— 背水面的曲线方程为 y=A2x4+B2x3 +C2x2 +D2x+E2, 其 中 Α2=1.9Χ10—9〜2.3Χ10—9、 Β2=-1.7 X 10- 6〜- 2.1 X 10- 6、 C2=-9.5 X 10— 4〜- 1.0 X10—3、 D2=2.5X10―1〜 3.0X10— E2=3.1〜3.7， 方程中 x、 y的单位为毫米， 且所述导叶的头部迎水面和背水面之间圆滑连接， 所述导叶的尾部迎水面和 背水面之间折线连接。
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102213177A (zh) * 2011-05-30 2011-10-12 辽宁海思达科技发展有限公司 冷却塔专用带配水器超低比转速高效率混流式水轮机
CN103225584A (zh) * 2013-03-19 2013-07-31 河海大学 高层供暖系统用微型混流式水轮机
US9200612B2 (en) 2009-05-27 2015-12-01 Nanjing Xingfei Cooling Equipment Co., Ltd. Direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy-saving cooling tower

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102011672B (zh) * 2010-12-08 2012-07-25 清华大学 一种采用新型导叶和转轮叶片型线的混流式水轮机
CN103953489B (zh) * 2013-08-02 2016-02-24 河海大学 一种用于直驱冷却塔风机的径流式水轮机转轮
WO2015031987A1 (en) * 2013-09-05 2015-03-12 Andritz Hydro Ltd. Spiral casing for a hydraulic turbine and method for arranging a spiral casing
CN103982362A (zh) * 2013-10-18 2014-08-13 河海大学 一种水动冷却塔直驱径流式水轮机
KR101451644B1 (ko) * 2014-02-17 2014-10-22 조수홍 친환경 냉각탑 수력 터빈 및 이를 포함하는 친환경 냉각탑
CN104100433B (zh) * 2014-07-11 2016-08-31 河海大学 混流式水泵水轮机转轮
EP3276157A1 (en) * 2016-07-25 2018-01-31 GE Renewable Technologies Hydraulic turbine
CN108425778B (zh) * 2018-03-28 2020-09-22 四川浩源机电有限责任公司 一种防止堵塞的混流式转轮
CN110469443B (zh) * 2019-07-05 2021-02-12 高邮市大江泵业有限公司 一种采用水冷却传动结构的冷却塔用水轮机
CN111535971A (zh) * 2020-05-11 2020-08-14 河海大学 一种带双进口式蜗壳的低比转速混流式水轮机
CN111535973A (zh) * 2020-05-11 2020-08-14 河海大学 一种适用于冷却塔的低比转速双进口蜗壳混流式水轮机
CN111594369A (zh) * 2020-05-11 2020-08-28 河海大学 一种适用于冷却塔的带双进口式蜗壳的混流式水轮机
CN111535974A (zh) * 2020-05-11 2020-08-14 河海大学 一种带双进口式蜗壳的低水头大流量混流式水轮机
CN111779613A (zh) * 2020-07-14 2020-10-16 黄鸿源 一种水轮发电机组

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004108186A (ja) * 2002-09-17 2004-04-08 Mitsubishi Electric Corp 発電プラントの冷却塔システム
CN201071779Y (zh) * 2007-06-22 2008-06-11 金先培 冷却塔用反击式水轮机
CN201228645Y (zh) * 2008-07-25 2009-04-29 南京星飞冷却设备有限公司 高效节能型冷却塔用水动冷却风机
CN101560940A (zh) * 2009-05-27 2009-10-21 南京星飞冷却设备有限公司 应用于水动节能冷却塔的直联低速小型混流式水轮机

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1251707A (zh) * 1969-05-14 1971-10-27
GB2049906A (en) * 1979-03-20 1980-12-31 Cooling Dev Ltd Apparatus for moving gas and distributing water in a cooling tower
US4976319A (en) * 1989-03-06 1990-12-11 Hale Fire Pump Company Water driven fan for firefighting
NZ258063A (en) * 1992-12-15 1997-03-24 Peter John Ward Exhaust fan system; power is provided by a water-driven turbine which has an enclosed rotor where water enters centrally and is directed radially outwards through spiral passages
JP3357962B2 (ja) * 1993-08-26 2002-12-16 株式会社日立製作所 可変速水車発電装置及び可変速水車の運転方法
JP3898311B2 (ja) * 1997-11-26 2007-03-28 株式会社東芝 水車またはポンプ水車
JP2003269313A (ja) * 2002-03-15 2003-09-25 Mitsubishi Heavy Ind Ltd 水車又はポンプ水車のキャビテーション壊食回避運転方法及びキャビテーション壊食量推定方法並びにそのプログラム
RU2321766C2 (ru) * 2006-05-19 2008-04-10 Открытое акционерное общество "Силовые машины-ЗТЛ, ЛМЗ, Электросила, Энергомашэкспорт" (ОАО "Силовые машины") Лопаточный аппарат рабочего колеса радиально-осевой гидротурбины
CN2926563Y (zh) * 2006-05-29 2007-07-25 陈谦 冷却塔水轮机
JP4703578B2 (ja) * 2007-01-19 2011-06-15 東京電力株式会社 フランシス型水車
CN201103510Y (zh) * 2007-12-06 2008-08-20 苏宏亮 轴伸贯流式冷却塔水动力风机
CN201173199Y (zh) * 2008-03-27 2008-12-31 苏宏亮 一种冷却塔水动力风机

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004108186A (ja) * 2002-09-17 2004-04-08 Mitsubishi Electric Corp 発電プラントの冷却塔システム
CN201071779Y (zh) * 2007-06-22 2008-06-11 金先培 冷却塔用反击式水轮机
CN201228645Y (zh) * 2008-07-25 2009-04-29 南京星飞冷却设备有限公司 高效节能型冷却塔用水动冷却风机
CN101560940A (zh) * 2009-05-27 2009-10-21 南京星飞冷却设备有限公司 应用于水动节能冷却塔的直联低速小型混流式水轮机

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
CHEN, YINGXIN.: "Energy saving renovation for the electric fans of the big mechanical ventilating cooling tower.", GENERAL MACHINERY, no. 10, October 2009 (2009-10-01), pages 72 - 75, XP008165526 *
ZHANG, HAILI ET AL.: "Optimization Research on Cooling Tower Francis Turbine Guide Vane in Place of Fan Motor.", ENERGY RESEARCH & UTILIZATION., no. 6, December 2008 (2008-12-01), pages 19 - 22, XP008165370 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9200612B2 (en) 2009-05-27 2015-12-01 Nanjing Xingfei Cooling Equipment Co., Ltd. Direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy-saving cooling tower
CN102213177A (zh) * 2011-05-30 2011-10-12 辽宁海思达科技发展有限公司 冷却塔专用带配水器超低比转速高效率混流式水轮机
CN103225584A (zh) * 2013-03-19 2013-07-31 河海大学 高层供暖系统用微型混流式水轮机

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US20120114471A1 (en) 2012-05-10
SG176258A1 (en) 2012-01-30
CA2763302A1 (en) 2010-12-02
RU2011152629A (ru) 2013-07-10
RU2491444C1 (ru) 2013-08-27
ZA201109425B (en) 2012-11-28
CA2763302C (en) 2014-02-18
EP2436915A1 (en) 2012-04-04
JP2012528261A (ja) 2012-11-12
MY155494A (en) 2015-10-30
EP2436915A4 (en) 2013-05-01
CN101560940A (zh) 2009-10-21
US9200612B2 (en) 2015-12-01
MX2011012560A (es) 2012-04-30
CN101560940B (zh) 2010-04-21
AU2010252496B2 (en) 2013-10-31
KR101327340B1 (ko) 2013-11-11

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