CN101560936B - 水动节能型冷却塔直联低速小型混流式水轮机用转轮 - Google Patents

水动节能型冷却塔直联低速小型混流式水轮机用转轮 Download PDF

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CN101560936B
CN101560936B CN2009100273099A CN200910027309A CN101560936B CN 101560936 B CN101560936 B CN 101560936B CN 2009100273099 A CN2009100273099 A CN 2009100273099A CN 200910027309 A CN200910027309 A CN 200910027309A CN 101560936 B CN101560936 B CN 101560936B
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顾星康
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Nanjing Xingfei Cooling Equipment Co Ltd
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Priority to SG2011087624A priority patent/SG176259A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • 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
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    • 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
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    • 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"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F03B3/125—Rotors for radial flow at high-pressure side and axial flow at low-pressure side, e.g. for Francis-type turbines
    • 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
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    • F05B2250/70—Shape
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    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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Abstract

一种水动节能型冷却塔直联低速小型混流式水轮机用转轮，它包括上冠(1)、下环(3)及安装在所述上冠(1)和下环(3)之间的曲面叶片(2)，其特征是所述叶片(2)的进水边(4)的高度h与进水边(4)所对应处的直径D1的比值为0.18～0.22，叶片(2)的总高度H与直径D1的比值为0.35～0.42，出水边(5)与下环(3)交点A处所对应的直径D2与直径D1的比值为0.4～0.6，出水边(5)与上冠交点B处所对应的直径D3与直径D1的比值为0.3～0.45，上冠(1)上的泄水圆台处的直径D4与直径D1的比值为0.1～0.2，所述直径D1与冷却风叶的转速的关系为
Figure 200910027309.9_AB_0
。本发明具有结构简单，设计安装方便，能量转换效率高的优点。

Description

水动节能型冷却塔直联低速小型混流式水轮机用转轮 
技术领域
本发明涉及一种冷却塔，尤其是一种冷却塔驱动用水轮机的转轮，具体地说是一种不带减速箱，通过合理设计水轮机转轮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水动节能冷却塔的直联低速小型混流式水轮机用转轮。 
背景技术
众所周知，为了实现节能的目的，现有的空调冷却塔已开始使用水轮机对冷却风扇进行驱动，它充分利用了冷却塔循环水流的能量将其转化为水轮机的驱动力，通过水轮机将水能转变成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4m～15m之间，布水管处需要0.5m～1m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。因此设计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。 
发明内容
本发明的目的是针对现有的冷却塔水轮机的输出轴需要通过减速箱才能驱动风叶的而造成噪音大、易发生故障及制造成本高的问题，设计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转轮，从而为最终省去齿轮减速传动机构奠定基础。 
本发明的技术方案是： 
一种应用于水动节能型冷却塔直联低速小型混流式水轮机转轮，它包括上冠1、下环3及安装在所述上冠1和下环3之间的曲面叶片2，所述曲面叶片2的一端为进水边4，该进水边4是转轮的高压侧，也是水流的径向流入侧，所述曲面叶片2的另一端为出水边5，该出水边是转轮的低压侧，也是水流的轴向流出侧；出水边5与下环3的连接点为A，叶片出水边5与上冠1的连接点为B，其特征是所述叶片2的进水边4的高度h与进水边4所对应处的直径D1的比值为0.18～0.22，叶片2的总高度H与直径D1的比值为0.35～0.42，出水边5与下环3交点A处所对应的直径D2与直径D1的比值为0.4～0.6，出水边5与上冠交点B处所对应的直径D3与直径D1的比值为0.3～0.45，上冠1上的泄水圆台处的直径D4与直径D1的比值为0.1～0.2，所述直径D1与冷却风叶的转速的关系为 其中n11为常数，称为单位转速，其取值范围为28-42，n为冷却风叶的额定转速，H为进塔水压(以水柱为单位：m)。 
所述的曲面叶片2数量为16～20片，叶片翼形最小厚度与最大厚度之比为0.28～0.34。 
本发明的有益效果： 
本发明为冷却塔用水轮机最终省去减速箱奠定了基础，利用本发明设计的转轮完全能满足使用要求，经试验证明，安装了本发明转轮的水轮机，其输出转速完全能满足使用要求，且转速的脉动范围较小。 
本发明结构简单，安装和使用均十分方便。 
本发明针对冷却塔用水轮机的特点，创造性地将单位转速n11从实际应用传统反击式水轮机的不小于80降至28-42之间，同时根据该单位转速确定了影响水轮机效率的关键元件的导叶的曲线方程，经过大量的计算与实验给出了转轮尺寸与叶片进水边尺寸D1之间的关系，同时给出了D1与冷却风扇转速之间的关系，为合理设计转轮提供了快捷方便的途径。 
经过实验证实，只有当单位转速介于28-42之间时确定的叶片进水边尺寸D1确定的转轮的尺寸才能使水轮机的整体效率维持在86％左右，大于42 或小于28时，其效率呈直线急剧下降。 
附图说明
图1为本发明的转轮的立体结构示意图。 
图2为本发明转轮各部分尺寸示意图。 
图3为本发明曲面叶片的立体结构示意图。 
图4为本发明曲面叶片的三视投影图。 
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2所示。 
一种应用于水动节能型冷却塔直联低速小型混流式水轮机转轮，它包括上冠1、下环3及安装在所述上冠1和下环3之间的数量为16～20片的曲面叶片2，如图1所示，曲面叶片2为翼形结构，如图3、4所示，叶片翼形最小厚度与最大厚度之比为0.28～0.34，所述曲面叶片2的一端为进水边4，该进水边4是转轮的高压侧，也是水流的径向流入侧，所述曲面叶片2的另一端为出水边5，该出水边是转轮的低压侧，也是水流的轴向流出侧；出水边5与下环3的连接点为A，叶片出水边5与上冠1的连接点为B，所述曲面叶片2的翼形最小厚度与最大厚度之比为0.28～0.34，曲面叶片2的尺寸及整个转轮的相关部分的尺寸关系为：进水边4的高度h与进水边4所对应处的直径D1的比值为0.18～0.22，叶片2的总高度H与直径D1的比值为0.35～0.42，出水边5与下环3交点A处所对应的直径D2与直径D1的比值为0.4～0.6，出水边5与上冠交点B处所对应的直径D3与直径D1的比值为0.3～0.45，上冠1上的泄水圆台处的直径D4与直径D1的比值为0.1～0.2，如图2所示。进水边直径D1与冷却风叶的转速的关系为 
Figure DEST_PATH_GSB00000051518300021
其中n11为常数，称为单位转速，其取值范围为28-42，n为冷却风叶的额定转速，H为进塔水压(以水柱为单位：m)。 
具体实施时一旦冷却塔风机叶片的转速确定后，再根据使用环境选定n11值，一般南方选值要高，北方选值要低一些，大多情况下选取35为宜，然后再由进塔水压H，即可确定D1的值，最后再根据D1的值确定曲面叶片、上冠及下环的各部分尺寸即可得到满足额定转速要求的转轮。 
以下是几个具体的计算例： 
例1 
设n11为35，进塔水压H为13m，风机叶片的额定转速n为136r/min，得D1为0.928m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为137r/min，符合设计要求。 
例2 
设n11为30，进塔水压H为15m，风机叶片的额定转速n为140r/min，得D1为0.830m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为138r/min，符合设计要求。 
例3 
设n11为40，进塔水压H为15m，风机叶片的额定转速n为130r/min，得D1为1.192m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为131r/min，符合设计要求。 
例4 
设n11为28，进塔水压H为13m，风机叶片的额定转速n为136r/min，得D1为0.742m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为130r/min，符合设计要求。 
例5 
设n11为42，进塔水压H为10m，风机叶片的额定转速n为140r/min，得D1为0.949m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为145r/min，符合设计要求。 
例6 
设n11为27，进塔水压H为13m，风机叶片的额定转速n为136r/min，得D1为0.712m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为110r/min，不符合设计要求。 
例7 
设n11为43，进塔水压H为10m，风机叶片的额定转速n为140r/min， 得D1为0.969m，设计一曲面叶片的形状如图3、4所示。安装实测风机叶片的转速为120r/min，不符合设计要求。 
对于本领域的技术人员而言，参照本发明所提供的叶片与转轮之间的各参数的关系，以及叶片进水边直径与单位转速及水头、风机叶片转速之间的关系即可很方便地得出木模，然后根据木模直接或稍加修整后即可设计得到理想的转换结构。 
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 (2)

1.一种水动节能型冷却塔直联低速小型混流式水轮机用转轮，它包括上冠(1)、下环(3)及安装在所述上冠(1)和下环(3)之间的曲面叶片(2)，所述曲面叶片(2)的一端为进水边(4)，该进水边(4)是转轮的高压侧，也是水流的径向流入侧，所述曲面叶片(2)的另一端为出水边(5)，该出水边是转轮的低压侧，也是水流的轴向流出侧；出水边(5)与下环(3)的连接点为A，叶片出水边(5)与上冠(1)的连接点为B，其特征是所述叶片(2)的进水边(4)的高度h与进水边(4)所对应处的直径D1的比值为0.18～0.22，叶片(2)的总高度H与直径D1的比值为0.35～0.42，出水边(5)与下环(3)交点A处所对应的直径D2与直径D1的比值为0.4～0.6，出水边(5)与上冠交点B处所对应的直径D3与直径D1的比值为0.3～0.45，上冠(1)上的泄水圆台处的直径D4与直径D1的比值为0.1～0.2，所述直径D1与冷却风叶的转速的关系为 
Figure DEST_PATH_FSB00000140012700011
，其中D1为进水边(4)所对应处的直径，直径D1的单位为m，n11为常数，称为单位转速，其取值范围为28～42，n为冷却风叶的额定转速，额定转速n的单位为r/min，H为进塔水压，水压的单位为m水柱。
2.按权利要求1所述的转轮，其特征是所述的曲面叶片(2)数量为16～20片，叶片翼形最小厚度与最大厚度之比为0.28～0.34。 
CN2009100273099A 2009-05-27 2009-05-27 水动节能型冷却塔直联低速小型混流式水轮机用转轮 Expired - Fee Related CN101560936B (zh)

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CN2009100273099A CN101560936B (zh) 2009-05-27 2009-05-27 水动节能型冷却塔直联低速小型混流式水轮机用转轮
CA2763303A CA2763303C (en) 2009-05-27 2010-05-25 Runner for direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy-saving cooling tower
BRPI1009075A BRPI1009075A2 (pt) 2009-05-27 2010-05-25 rotor de turbina de água tipo vazão mista de pequeno porte e baixa velocidade e conexão direta, aplicada em uma torre de resfriamento para economia de energia hidrodinâmica.
SG2011087624A SG176259A1 (en) 2009-05-27 2010-05-25 Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower
US13/322,553 US9260969B2 (en) 2009-05-27 2010-05-25 Runner for direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy-saving cooling tower
MYPI2011005750A MY156030A (en) 2009-05-27 2010-05-25 Runner for direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy-saving cooling tower
RU2011152630/06A RU2492351C1 (ru) 2009-05-27 2010-05-25 Рабочее колесо для непосредственно соединенной тихоходной малой гидротурбины диагонального типа, применяемой в гидродинамической энергосберегающей охлаждающей башне
EP10780070.8A EP2436916A4 (en) 2009-05-27 2010-05-25 DREHRAD FOR USE OF LOW-SPEED, DIRECTLY-CONNECTED MIXED FLOW WATER TURBINES OF AN ENERGY-SAVING HYDRODYNAMIC COOLING TOWER
MX2011012561A MX2011012561A (es) 2009-05-27 2010-05-25 Rueda giratoria usada para la hidroturbina de flujo mezclado, de escala pequeña, de baja velocidad, de conexion directa de una torre de enfriamiento ahorradora de energia hidrodinamica.
PCT/CN2010/073241 WO2010135989A1 (zh) 2009-05-27 2010-05-25 水动节能型冷却塔直联低速小型混流式水轮机用转轮
KR1020117031152A KR101327341B1 (ko) 2009-05-27 2010-05-25 수력학적 에너지 절약형 냉각탑의 직결 저속 소형 혼류식 수력 터빈용 회전 휠
JP2012512190A JP2012528262A (ja) 2009-05-27 2010-05-25 ハイドロダイナミック式省エネ型冷却タワー直連結低速小型混流式水車用ランナ
AU2010252464A AU2010252464B2 (en) 2009-05-27 2010-05-25 Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower
ZA2011/09424A ZA201109424B (en) 2009-05-27 2011-12-21 Runner for direct-connected low-speed small mixed flow type water turbine applied in hydrodynamic energy -saving cooling tower.

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EP2436916A1 (en) 2012-04-04
US20130121838A1 (en) 2013-05-16
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CN101560936A (zh) 2009-10-21
MY156030A (en) 2015-12-31
JP2012528262A (ja) 2012-11-12
KR101327341B1 (ko) 2013-11-11
WO2010135989A1 (zh) 2010-12-02
ZA201109424B (en) 2012-12-27
KR20120033315A (ko) 2012-04-06
EP2436916A4 (en) 2013-05-01
BRPI1009075A2 (pt) 2016-07-05
RU2011152630A (ru) 2013-07-10
CA2763303A1 (en) 2010-12-02
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SG176259A1 (en) 2012-01-30

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