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Article(id=1241686761915601004, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1241686759470329942, articleNumber=null, orderNo=null, doi=10.16579/j.issn.1001.9669.2025.09.019, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1748188800000, receivedDateStr=2025-05-26, revisedDate=null, revisedDateStr=null, acceptedDate=null, acceptedDateStr=null, onlineDate=1773970793465, onlineDateStr=2026-03-20, pubDate=1757865600000, pubDateStr=2025-09-15, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1773970793465, onlineIssueDateStr=2026-03-20, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1773970793465, creator=13701087609, updateTime=1773970793465, updator=13701087609, issue=Issue{id=1241686759470329942, tenantId=1146029695717560320, journalId=1227999626482147330, year='2025', volume='47', issue='9', pageStart='1', pageEnd='249', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1773970792882, creator=13701087609, updateTime=1773970911747, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1241687258093375901, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1241686759470329942, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1241687258093375902, tenantId=1146029695717560320, journalId=1227999626482147330, issueId=1241686759470329942, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=197, endPage=204, ext={EN=ArticleExt(id=1241686762133704819, articleId=1241686761915601004, tenantId=1146029695717560320, journalId=1227999626482147330, language=EN, title=Analysis and safety evaluation of steam turbine last stage blade vortex-induced response under deep peak shaving conditions, columnId=null, journalTitle=Journal of Mechanical Strength, columnName=null, runingTitle=null, highlight=null, articleAbstract=

To compensate for the intermittency of renewable energy generation, coal-fired power units are required to operate under low-load conditions over a long time, which causes the last stage blades of steam turbine low-pressure cylinders under small flow conditions persistently, leading to increased dynamic stresses and fatigue damage in the blades. To evaluate the safety of these last-stage blades, the fluid-structure interaction analysis of the last two-stage flow path and last stage rotating blades were conducted for a 660 MW air-cooled steam turbine under typical operating conditions. The results demonstrate that as the load decreases, both the maximum equivalent stress and deformation of the last stage rotating blades gradually diminish first, then slightly increasing. The maximum equivalent stress of the last stage rotating blades remains consistently below the material’s yield strength, indicating that the blades are in the stage of elastic deformation and no plastic deformation has occurred. Using the Goodman curve analysis method for the high-cycle fatigue life assessment of the last stage rotating blades, the dynamic stress levels of the last stage rotating blades fall within the safe zone of the Goodman curve,indicating that there is no risk of fatigue damage to the blades.

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ZHU Mingliang, E-mail：
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为弥补新能源发电的间歇性，火电机组需长期低负荷运行，使汽轮机低压缸末级叶片持续处于小流量工况，导致叶片出现动应力增加与疲劳损伤等问题。为评估末级叶片的安全性，对某660 MW空冷汽轮机典型运行工况下低压缸末两级流道与末级动叶片进行流固耦合分析。结果表明，随着负荷的下降，末级动叶片的最大等效应力与变形先逐渐减小，后有所上升。末级动叶的最大等效应力始终低于叶片的屈服强度；叶片处于弹性变形阶段，未发生塑性变形。采用Goodman曲线分析方法对末级动叶的高周疲劳寿命进行评估，在Goodman曲线中，末级动叶片的动应力水平处于安全范围，表明叶片无疲劳损伤风险。

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朱明亮，男，1984年生，安徽芜湖人，博士，教授，博士研究生导师；主要研究方向为机械结构疲劳与断裂；E-mail：。
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卞龙，男，2000年生，四川乐山人，硕士研究生；主要研究方向为高效灵活汽轮机设计技术；E-mail：。

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2.东方电气集团东方汽轮机有限公司，德阳　618000, bio={"content":"

卞龙，男，2000年生，四川乐山人，硕士研究生；主要研究方向为高效灵活汽轮机设计技术；E-mail：。

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卞龙，男，2000年生，四川乐山人，硕士研究生；主要研究方向为高效灵活汽轮机设计技术；E-mail：。

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tableContent=null), ArticleFig(id=1241810803230314899, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1241686761915601004, language=CN, label=图9, caption=典型工况下末级动叶动应力的Goodman曲线, figureFileSmall=dBkOnoVi9eA1NglyhzOYEA==, figureFileBig=Ss1Cw3zE5YPvt3b1LaBYXg==, tableContent=null), ArticleFig(id=1241810803356144031, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1241686761915601004, language=EN, label=Tab.1, caption=

Basic parameters of the last two blades

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叶片类型
Type of the blade		静叶只数
Number of stationary blades		动叶只数
Number of rotor blades		动叶高度
Blade height of rotor blade /mm
次末级叶片
Penultimate stage blade		5882590
末级叶片
Last stage blade		60701 030
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末两级叶片基本参数

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叶片类型
Type of the blade		静叶只数
Number of stationary blades		动叶只数
Number of rotor blades		动叶高度
Blade height of rotor blade /mm
次末级叶片
Penultimate stage blade		5882590
末级叶片
Last stage blade		60701 030
), ArticleFig(id=1241810803528110513, tenantId=1146029695717560320, journalId=1227999626482147330, articleId=1241686761915601004, language=EN, label=Tab.2, caption=

Boundary conditions of each working condition

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工况
Working condition		入口流量
Inlet flow/（kg/s）		抽口流量
Extraction flow/（kg/s）		入口总压
Total pressure at inlet/MPa		出口静压
Static pressure at outlet /MPa		入口总焓
Total enthalpy at inlet/（kJ/kg）
100%THA150.5866.6440.091 50.012 671.16
50%THA82.1011.3280.048 90.012 690.68
20%THA38.61300.022 90.012 678.14
10%THA24.61600.014 30.012 678
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各工况边界条件

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工况
Working condition		入口流量
Inlet flow/（kg/s）		抽口流量
Extraction flow/（kg/s）		入口总压
Total pressure at inlet/MPa		出口静压
Static pressure at outlet /MPa		入口总焓
Total enthalpy at inlet/（kJ/kg）
100%THA150.5866.6440.091 50.012 671.16
50%THA82.1011.3280.048 90.012 690.68
20%THA38.61300.022 90.012 678.14
10%THA24.61600.014 30.012 678
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Material properties of the last stage blade

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弹性模量
Elastic modulus /MPa		泊松比
Poisson ratio		密度
Density/（kg/m3）
2.014 7×1050.37 700
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末级叶片材料属性

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弹性模量
Elastic modulus /MPa		泊松比
Poisson ratio		密度
Density/（kg/m3）
2.014 7×1050.37 700
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Maximum dynamic stress of danger points of the last stage rotor blade under typical working conditions

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工况
Operating condition		σa(归一化)Normalization
P1P2P3P4
100%THA0.048 00.017 30.044 90.047 0
50%THA0.025 60.005 40.024 00.024 6
20%THA0.008 70.007 60.012 70.012 0
10%THA0.024 90.015 60.036 60.031 8
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典型工况下末级动叶危险点的最大动应力

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工况
Operating condition		σa(归一化)Normalization
P1P2P3P4
100%THA0.048 00.017 30.044 90.047 0
50%THA0.025 60.005 40.024 00.024 6
20%THA0.008 70.007 60.012 70.012 0
10%THA0.024 90.015 60.036 60.031 8
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深度调峰下汽轮机末级叶片涡激响应分析与安全性评价
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卞龙 1, 2 , 范志飞 2 , 朱明亮 1 , 轩福贞 1
机械强度 | 2025,47(9): 197-204
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机械强度 | 2025, 47(9): 197-204
深度调峰下汽轮机末级叶片涡激响应分析与安全性评价
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卞龙1, 2 , 范志飞2, 朱明亮1 , 轩福贞1
作者信息
  • 1.华东理工大学 机械与动力工程学院，上海　200237
  • 2.东方电气集团东方汽轮机有限公司，德阳　618000

    • 卞龙，男，2000年生，四川乐山人，硕士研究生；主要研究方向为高效灵活汽轮机设计技术；E-mail：。

通讯作者:

朱明亮，男，1984年生，安徽芜湖人，博士，教授，博士研究生导师；主要研究方向为机械结构疲劳与断裂；E-mail：。
Analysis and safety evaluation of steam turbine last stage blade vortex-induced response under deep peak shaving conditions
Long BIAN1, 2 , Zhifei FAN2, Mingliang ZHU1 , Fuzhen XUAN1
Affiliations
  • 1.School of Mechanical and Power Engineering, East China University of Science and Technology, Shanghai 200237, China
  • 2.Dongfang Turbine Co., Ltd., Deyang 618000, China
出版时间: 2025-09-15 doi: 10.16579/j.issn.1001.9669.2025.09.019
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摘要
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为弥补新能源发电的间歇性，火电机组需长期低负荷运行，使汽轮机低压缸末级叶片持续处于小流量工况，导致叶片出现动应力增加与疲劳损伤等问题。为评估末级叶片的安全性，对某660 MW空冷汽轮机典型运行工况下低压缸末两级流道与末级动叶片进行流固耦合分析。结果表明，随着负荷的下降，末级动叶片的最大等效应力与变形先逐渐减小，后有所上升。末级动叶的最大等效应力始终低于叶片的屈服强度；叶片处于弹性变形阶段，未发生塑性变形。采用Goodman曲线分析方法对末级动叶的高周疲劳寿命进行评估，在Goodman曲线中，末级动叶片的动应力水平处于安全范围，表明叶片无疲劳损伤风险。

汽轮机  /  末级叶片  /  流固耦合  /  典型运行工况  /  安全评估

To compensate for the intermittency of renewable energy generation, coal-fired power units are required to operate under low-load conditions over a long time, which causes the last stage blades of steam turbine low-pressure cylinders under small flow conditions persistently, leading to increased dynamic stresses and fatigue damage in the blades. To evaluate the safety of these last-stage blades, the fluid-structure interaction analysis of the last two-stage flow path and last stage rotating blades were conducted for a 660 MW air-cooled steam turbine under typical operating conditions. The results demonstrate that as the load decreases, both the maximum equivalent stress and deformation of the last stage rotating blades gradually diminish first, then slightly increasing. The maximum equivalent stress of the last stage rotating blades remains consistently below the material’s yield strength, indicating that the blades are in the stage of elastic deformation and no plastic deformation has occurred. Using the Goodman curve analysis method for the high-cycle fatigue life assessment of the last stage rotating blades, the dynamic stress levels of the last stage rotating blades fall within the safe zone of the Goodman curve,indicating that there is no risk of fatigue damage to the blades.

Steam turbine  /  Last stage blade  /  Fluid-structure interaction  /  Typical operating condition  /  Safety assessment
卞龙, 范志飞, 朱明亮, 轩福贞. 深度调峰下汽轮机末级叶片涡激响应分析与安全性评价. 机械强度, 2025 , 47 (9) : 197 -204 . DOI: 10.16579/j.issn.1001.9669.2025.09.019
Long BIAN, Zhifei FAN, Mingliang ZHU, Fuzhen XUAN. Analysis and safety evaluation of steam turbine last stage blade vortex-induced response under deep peak shaving conditions[J]. Journal of Mechanical Strength, 2025 , 47 (9) : 197 -204 . DOI: 10.16579/j.issn.1001.9669.2025.09.019
正文
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0　引言
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我国新能源的快速发展使电网昼夜峰谷差增大，风电、光伏并网消纳难题加剧了调峰压力，弃风弃光问题突出，新能源发电的波动性催生了深度调峰需求。火电机组调峰时，汽轮机末级叶片持续处于小流量工况，可能引发流场恶化、脱流倒流、鼓风超温及振动加剧等问题，其结构完整性关乎电厂安全[1-4]。由于末级叶片承受更大的离心力，且长期工作于高温高压环境以及复杂流场中，开展有关低负荷末级叶片动力特性的研究，对确保机组长期深度调峰的安全性具有重要的实际意义。
长叶片受气动-强度双向耦合作用[5]，需基于流固耦合（Fluid-Structure Interaction, FSI）技术分析动态特性。BENRA等[6]指出，单向耦合适用于弱流固干扰场景，可用其伪瞬态计算方法[7]进行简化计算。小容积流量工况下，流场会出现鼓风[8]、紊乱等问题，汽轮机叶片可能因受瞬态载荷而发生疲劳损伤[9]，因此其疲劳强度和寿命对于电力系统的稳定性和电厂的经济效益至关重要。优化材料阻尼性能[10]、采用复合材料增加阻尼因子[11]与采用混合分析技术[12]等手段均可延长叶片寿命。
流场的瞬态特性会使叶片承受变化的动载荷，从而导致叶片产生疲劳损伤[13-15]。对于高速旋转的汽轮机末级叶片，其工作环境往往会严重偏离设计工况，使其安全运行受到威胁。目前，深度调峰下低压缸末级叶片的动态响应与疲劳寿命损伤研究[16-18]的理论还不成熟。本文针对深度调峰中的小流量工况，采用Ansys软件开展气动-结构流固耦合仿真，研究末级动叶片的动态响应与疲劳损伤机制，从而为叶片的状态监测及寿命预测提供支撑。
1　数值方法
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湍流模型包含湍流黏性系数方程和雷诺时均方程。CFX软件中采用的k-ω剪切应力传输模型因其广泛的适用性和较强的分离预测能力，在流体仿真计算中，尤其是在需要处理低雷诺数或复杂流动条件的情况下，表现出显著优势。其输运方程为
式中，ρ为流体密度；k为湍流动能；t为时间；xj为空间坐标的第j方向；uj为时均速度；μ为流体动力黏性系数；μt为湍动黏性系数；Gk为速度梯度引起的湍流动能k的生成项；Gb为浮力引起的湍流动能k的生成项；ε为耗散率；YM为流动脉动扩张的生成项；C1ε、C2ε和C3ε均为经验系数；σε为对应耗散率ε的普朗特数；σk为对应湍流动能k的普朗特数；Sk和Sε均为用户定义的源项。
2　计算模型
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2.1　流体域模型的说明与网格划分
本文以某660 MW空冷汽轮机低压缸末两级流道为研究对象，研究典型工况下末两级湿蒸汽流场的流动特性。末两级叶片的相关参数如表1所示。
根据通流方案与通流数据，使用专业仿真软件NUMECA建立末两级气道的三维流场物理模型。在入口位置延长进气流道，根据通流图在次末级流域出口与末级流域入口之间设置抽口，在末级出口位置添加导流环。利用NUMECA软件中的Autogrid5专家模式对末两级流体域网格进行划分，网格类型为不含中心节点的六面体网格，网格采用“HOH”型拓扑结构，并且设置边界层网格以提高计算精度。总网格单元数为2 514 236，网格节点数为2 627 976。网格示意图与边界条件分布如图1所示。
2.2　流体域边界条件与网格无关性验证
以汽轮机运行时汽轮机热力验收（Turbine Heat Acceptance, THA）工况对应的参数为基准，参考实际运行情况，确定进出口边界条件。介质选择steam3vl，设置次末级总压、总焓为进口边界条件，末级出口边界条件为平均静压，动叶转速为3 000 r/min。本研究设置的机组典型工况分别为100%THA、50%THA、20%THA与10%THA等4个工况，典型工况下的边界条件如表2所示。动静交界面选择混合平面，残差精度为10-6。
为保证计算结果的准确性，必须进行网格无关性验证。本文以THA工况下该汽轮机低压缸末级流场出口速度为评价指标，绘制了130万、250万与290万3套末两级流道网格，对网格无关性进行了验证。结果表明，当末两级流道网格数不低于250万时，末级流场出口速度不随网格数增加而变化。综合考虑计算时间与精度，末两级流道采用250万网格进行计算。
2.3　末级动叶网格划分与无关性验证
利用Ansys Workbench中的Mesh模块，通过控制全局网格对该末级叶片进行网格划分，网格类型为非结构化网格。分别绘制了末级叶片网格数为21 725、37 212、47 964、60 422、80 372的5套网格，通过监测末级动叶的轴向变形量对叶片的网格无关性进行验证。结果表明，当网格数量不低于47 964时，叶片的轴向变形量趋于稳定。因此，采用网格数为47 964的网格进行之后的结构域与流固耦合仿真，该套网格的节点数为79 408，网格示意图如图2所示。
2.4　末级动叶的边界条件
由于瞬态计算时无法在拉筋与围带的周期面设置循环对称约束，因此分别在围带与拉筋处通过旋转划分出2块印记面，在印记面上设置远端位移约束以模拟成圈叶片的运行情况。在叶根8个工作面上设置固定约束，在叶片整体加载3 000 r/min的转速以模拟离心效果。采用globally conservative插值法将流体域的数据传递到固体域，依靠耦合面上网格节点的映射，按比例将流体域的传递参数分配到各固体域节点上。叶片材料参数如表3所示。
3　结果分析与讨论
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典型工况下，将汽轮机末两级流体域在动叶入口的瞬态计算流量呈周期性波动判定为收敛。提取出收敛的流场中动叶壁面承受的瞬态汽动力数据，导入末级动叶叶身处流固耦合面并进行流固耦合计算，分析叶片的强度特性，并进行叶片的寿命与安全性分析。
3.1　流体域末级动叶表面的气流力分布
如图3所示，动叶所受的气流力在各个典型工况下的周期性波动都很明显，图中气流力的正负仅与方向有关。随着流量的减少，末级流道内流场稳定性降低，蒸汽在动叶表面出现径向流动并逐渐加剧，从而导致末级动叶所受径向力逐渐增加。末级动叶所受周向力与轴向力随着流量的减少在100%THA~50%THA工况下减小，在20%THA~10%THA工况下则逐渐增加。此时部分蒸汽吸收轴做功转化的能量，在叶片的推动下沿着流道前进，20%THA工况以下的鼓风现象明显。
3.2　叶片的应力与变形分布
图4所示为典型工况下末级动叶等效应力分布，每个分图中左边均为叶片背弧侧应力分布，右边均为内弧侧应力分布。背弧侧左边为进气边，内弧侧右边为进气边。无论在哪种工况下，叶片的最大等效应力均出现在叶身内弧侧根部靠近出气边的区域。在100%THA工况下，该应力为810.07 MPa；在50%THA工况下，该应力减小至789.89 MPa；在20%THA工况下，该应力继续下降到782.99 MPa，较100%THA工况减小了27.08 MPa；在10%THA工况下，该应力为801.91 MPa，较20%THA工况增加了18.92 MPa。叶型根部内弧侧的最大等效应力均小于叶片屈服强度，说明叶片相对安全。
图5所示为典型工况下末级动叶总变形分布。在100%THA工况下，叶片的总变形量从叶根向叶顶方向逐渐增大，总变形量最大的位置在叶顶围带处、80%出气边附近，最大总变形量为3.137 1 mm；在50%THA工况下，总变形量最大的位置在动叶顶部，最大总变形量为2.939 8 mm；在20%THA工况下，最大总变形量为2.867 mm，与100%THA工况相比下降了8.61%；在10%THA工况下，最大总变形量则上升到3.038 8 mm。总变形量随着流量的下降先减小后增加。
3.3　叶片寿命与安全性分析
根据第3.2节分析可知，末级动叶的最大等效应力810.07 MPa，低于其屈服强度，因此该叶片的失效主要由高周疲劳造成。本文采用Goodman曲线法对叶片的寿命进行评估。
基于汽轮机末级动叶在典型工况下的动态响应分析，绘制Goodman曲线时，取100%THA工况下叶片上应力较大的几个危险点进行监测，分别为P1（叶根背弧侧）、P2（叶根内弧侧）、P3（背弧拉筋底部）、P4（内弧拉筋底部），具体位置如图6所示。
在流场的影响下，末级动叶危险点的等效应力呈明显的非定常特性，表现为各危险点等效应力的周期性波动。其中，100%THA工况下危险点等效应力随时间的变化如图7所示。
典型工况下等效应力波峰对应的频率为3 000 Hz或6 000 Hz，与气流激振力频率对应。图8为100%THA工况下危险点等效应力频谱图，图中频率3 000 Hz对应的波峰幅值为各点在100%THA工况下的动应力。
根据典型工况下末级动叶危险点频谱图，统计得出典型工况下末级动叶危险点的最大动应力分布情况，如表4所示。整体上，从100%THA~20%THA，各危险点动应力逐渐减小，仅在叶根内弧P2点处，20%THA工况时动应力开始上升，说明随着流量的减少，复杂的流场最先影响到末级动叶叶根处。流量进一步减少到10%THA工况时，末级动叶的动应力水平整体上升。
Goodman曲线的数学表达式为
式中，σa为应力幅；σm为平均应力；σ-1为疲劳极限（完全交变应力下的疲劳强度）；σb为材料的抗拉强度。
根据末级动叶的最大动应力和平均应力绘制的典型工况下末级动叶动应力的Goodman曲线如图9所示。由图9可知，各工况下末级动叶的危险点应力状态均在Goodman曲线的下方；从100%THA~20%THA，各危险点逐渐偏离曲线，表明末级动叶运行安全性逐渐提高；在10%THA工况时，各危险点有靠近曲线的趋势，但均分布于曲线下方，说明负荷降低到10%THA工况时，末级动叶危险点动应力水平开始上升，但仍处于安全范围内。末级动叶在典型工况下未出现疲劳损伤风险。
4　结论
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通过建立某660 MW空冷汽轮机低压缸末两级流道与末级动叶模型，在流体域对深度调峰典型工况下末级动叶表面气流力分布与非定常特性进行了详细分析。在固体域采用流固耦合的方法对叶片的动态响应特性以及疲劳寿命进行研究，详细分析了典型工况下叶片特征参数的变化趋势。主要工作总结如下：
1）随着负荷降低，末级动叶片的最大等效应力先逐渐减小，至10%THA工况时有所上升。最大等效应力主要分布在叶根与拉筋底部。典型工况下末级动叶片的最大等效应力为810.07 MPa，低于叶片屈服强度，相对安全。
2）随着负荷的下降，末级动叶片的最大总变形量先减少后增加，在20%THA时相较于100%THA时下降了8.61%，在10%THA时上升至3.038 8 mm。
3）随着负荷的下降，末级动叶片的最大动应力在100%THA~20%THA时逐渐下降，在10%THA时有所上升。Goodman曲线显示，流量从100%THA减少到20%THA的过程中，各危险点逐渐偏离曲线；当减少至10%THA时，末级动叶危险点的动应力水平开始上升并靠近曲线，但仍处于安全范围。然而该研究尚未针对蒸汽损伤，尤其是水蚀对汽轮机末级叶片疲劳损伤的影响进行分析。因此，在不考虑环境因素影响的前提下，本研究通过流固耦合分析得到该空冷汽轮机末级动叶动应力水平未出现高周疲劳损伤风险的结论。
4）叶片的应力、变形及动应力在不同工况下的变化规律：从100%THA~20%THA工况均持续下降，至10%THA工况时较20%THA工况均出现回升趋势。因此，推荐该空冷汽轮机组调峰时的最低负荷控制在20%THA工况左右。在此工况下，汽轮机末级叶片处的流场虽开始出现鼓风现象但不明显，且末级动叶的应力、变形及动应力水平仍保持下降趋势，机组运行的安全性能够得到保证。该结论对电厂调峰与汽轮机安全运行具有一定的指导意义。
基金
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  • 国家自然科学基金项目(52321002)
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2025年第47卷第9期
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doi: 10.16579/j.issn.1001.9669.2025.09.019
  • 接收时间：2025-05-26
  • 首发时间：2026-03-20
  • 出版时间：2025-09-15
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  • 收稿日期：2025-05-26
基金
National Natural Science Foundation of China(52321002)
国家自然科学基金项目(52321002)
作者信息
    1.华东理工大学 机械与动力工程学院，上海　200237
    2.东方电气集团东方汽轮机有限公司，德阳　618000

通讯作者:

朱明亮，男，1984年生，安徽芜湖人，博士，教授，博士研究生导师；主要研究方向为机械结构疲劳与断裂；E-mail：。
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2种不同金属材料的力学参数
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Number of
species		 占总种数比例
Percentage of
total species (%)		 属
Genus		 种数
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鹅膏菌科Amanitaceae 2 11 5.26 鹅膏菌属 Amanita 10 4.78
小菇科 Mycenaceae 2 12 5.74 丝盖伞属 Inocybe 5 2.39
多孔菌科 Polyporaceae 8 14 6.70 蜡蘑属 Laccaria 5 2.39
红菇科 Russulaceae 3 23 11.00 小皮伞属 Marasmius 6 2.87
小菇属 Mycena 11 5.26
光柄菇属 Pluteus 5 2.39
红菇属 Russula 17 8.13
栓菌属 Trametes 5 2.39
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