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Article(id=1320037458159448486, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037383882519364, articleNumber=null, orderNo=null, doi=10.3969/j.issn.1005-0329.2025.12.012, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1750780800000, receivedDateStr=2025-06-25, revisedDate=1761667200000, revisedDateStr=2025-10-29, acceptedDate=null, acceptedDateStr=null, onlineDate=1792651055135, onlineDateStr=2026-10-22, pubDate=1767110400000, pubDateStr=2025-12-31, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1792651055135, onlineIssueDateStr=2026-10-22, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1792651055135, creator=13701087609, updateTime=1792651055135, updator=13701087609, issue=Issue{id=1320037383882519364, tenantId=1146029695717560320, journalId=1316781260334530699, year='2025', volume='53', issue='12', pageStart='1', pageEnd='118', issueExtLink='null', onlineDate='null', pubDate='1767110400000', pubDateStr='2025-12-31', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1792651037426, creator='13701087609', updateTime=1792656182714, updator='13701087609', preIssue=null, nextIssue=null, articleTotal=null, ext={EN=IssueExt(id=1320058964839093145, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037383882519364, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1320058964839093146, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1320037383882519364, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null, downloadFileDto=null}, startPage=102, endPage=108, ext={EN=ArticleExt(id=1320037458339803559, articleId=1320037458159448486, tenantId=1146029695717560320, journalId=1316781260334530699, language=EN, title=Dynamic balance analysis and optimization of high‑speed scroll compressor shaft system, columnId=null, journalTitle=Fluid Machinery, columnName=null, runingTitle=null, highlight=null, articleAbstract=

To address the noise and vibration issues of high‑speed，large‑displacement scroll compressors，a dynamic model of the shaft system was established based on multibody dynamics theory.The force characteristics of the main and auxiliary bearings under high‑speed operating conditions were analyzed，followed by the optimized design of the motor counterweights.Subsequently，whole‑machine vibration tests were carried out for verification.The results indicate that，over the entire speed range of the scroll compressor，the loads on both the main and auxiliary bearings increase with the rise in rotational speed before and after optimization.After optimization，the bearing loads are significantly lower across the entire speed range.Specifically，at 8 000 r/min，the load on the main bearing is reduced by 21.06 N，and that on the auxiliary bearing by 7.73 N.Furthermore，over the full speed range，the optimized prototype exhibits lower vibration acceleration than the original prototype at most rotational speeds.At 6 000 r/min，the total vibration acceleration decreases from 20.41 m/s² to 9.88 m/s².This study provides theoretical support for improving the dynamic balance performance of high‑speed scroll compressors.

, authors=Chenyu DONG, Dongyang XI, Siying LI, Jiangping CHEN, Junye SHI, authorsList=Chenyu DONG, Dongyang XI, Siying LI, Jiangping CHEN, Junye SHI, authorCompany=null, correspAuthors=null, authorNote=null, correspAuthorsNote=null, copyrightStatement=null, copyrightOwner=null, extLink=null, articleAbsUrl=null, sourceXml=null, magXml=null, pdfUrl=null, pdf=null, pdfFileSize=null, pdfExtLink=null, richHtmlUrl=null, mobilePdfUrl=null, reviewReport=null, pdfFirstPage=null, abstractGraph=null, abstractGraphContent=null, abstractVideo=null, citation=null, cebUrl=null, magXmlContent=null, mapNumber=null, fund=null), CN=ArticleExt(id=1320037461586194874, articleId=1320037458159448486, tenantId=1146029695717560320, journalId=1316781260334530699, language=CN, title=高速涡旋压缩机轴系动平衡分析与优化, columnId=1317484300472271469, journalTitle=流体机械, columnName=应用技术, runingTitle=null, highlight=null, articleAbstract=

针对高转速、大排量涡旋压缩机的噪声和振动问题，基于多体动力学理论构建了轴系的动力学模型，分析主、副轴承在高转速工况下的受力特性，进而优化设计电机平衡块，并开展整机振动试验验证。结果表明，在涡旋压缩机全转速范围内，优化前后主、副轴承受力均随转速提升而增加，优化后轴承受力在全转速范围内均显著小于优化前，8 000 r/min时，优化后主轴承受力减小21.06 N，副轴承受力减小7.73 N；在涡旋压缩机全转速范围内，优化后样机在多数转速下表现出较原型机更低的振动加速度，在6 000 r/min时，振动总和由20.41 m/s²降至9.88 m/s²。研究可为提高高速涡旋压缩机的动平衡性能提供理论支撑。

, authors=董辰宇, 郗冬阳, 李思莹, 陈江平, 施骏业, authorsList=董辰宇, 郗冬阳, 李思莹, 陈江平, 施骏业, authorCompany=null, correspAuthors=null, authorNote=

董辰宇（1999），男，硕士，主要从事电动涡旋压缩机研究与设计工作，通信地址：200240中国上海市东川路800号上海交通大学机械与动力工程学院，E-mail：。

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董辰宇（1999），男，硕士，主要从事电动涡旋压缩机研究与设计工作，通信地址：200240中国上海市东川路800号上海交通大学机械与动力工程学院，E-mail：。

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董辰宇（1999），男，硕士，主要从事电动涡旋压缩机研究与设计工作，通信地址：200240中国上海市东川路800号上海交通大学机械与动力工程学院，E-mail：。

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vibration sensor arrangement, figureFileSmall=s+Ejslh+lGqm63J9OVrRYQ==, figureFileBig=82e/p48DxI8zAt1Fd/TDCQ==, tableContent=null), ArticleFig(id=1320037466648719856, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037458159448486, language=CN, label=图9, caption=压缩机顶盖振动传感器布置, figureFileSmall=s+Ejslh+lGqm63J9OVrRYQ==, figureFileBig=82e/p48DxI8zAt1Fd/TDCQ==, tableContent=null), ArticleFig(id=1320037466711634417, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1320037458159448486, language=EN, label=Tab.1, caption=

Constraint relationships of each component

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序号部件运动副类型
1主、副轴承大地固定副
2上平衡块电机转子固定副
3下平衡块电机转子固定副
4电机转子主轴固定副
5扇形铁主轴固定副
6偏心套扇形铁固定副
7动涡旋盘偏心套圆柱副
8主、副轴承主轴圆柱副
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轴系各部件约束关系

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序号部件运动副类型
1主、副轴承大地固定副
2上平衡块电机转子固定副
3下平衡块电机转子固定副
4电机转子主轴固定副
5扇形铁主轴固定副
6偏心套扇形铁固定副
7动涡旋盘偏心套圆柱副
8主、副轴承主轴圆柱副
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Mass setting of each component in the shafting model

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部件动涡旋盘扇形铁上平衡块下平衡块
实测质量/g381.37315.5726.8738.15
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轴系模型各部件质量设置

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部件动涡旋盘扇形铁上平衡块下平衡块
实测质量/g381.37315.5726.8738.15
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Theoretical calculation of bearing loads before and after optimization

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项目主轴承受力/N副轴承受力/N
优化前78.8514.36
优化后51.4310.03
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优化前后理论计算轴承受力

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项目主轴承受力/N副轴承受力/N
优化前78.8514.36
优化后51.4310.03
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Vibration acceleration before optimization

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转速/（r·min-1）振动加速度/（m·s-²）
X方向Y方向Z方向总和
1 0000.560.500.630.97
2 0001.180.961.402.07
3 0002.151.572.453.62
4 0003.892.523.946.08
5 0005.473.456.228.97
6 0007.746.8617.6020.41
7 00012.208.4015.7021.58
8 00014.7010.6014.7023.34
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优化前振动加速度

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转速/（r·min-1）振动加速度/（m·s-²）
X方向Y方向Z方向总和
1 0000.560.500.630.97
2 0001.180.961.402.07
3 0002.151.572.453.62
4 0003.892.523.946.08
5 0005.473.456.228.97
6 0007.746.8617.6020.41
7 00012.208.4015.7021.58
8 00014.7010.6014.7023.34
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Vibration acceleration after optimization

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转速/（r·min-1）振动加速度/（m·s-²）
X方向Y方向Z方向总和
1 0000.530.440.860.80
2 0001.201.041.442.14
3 0001.461.402.583.28
4 0004.074.693.647.20
5 0005.033.993.857.49
6 0006.245.545.299.88
7 0007.875.156.5211.44
8 0009.647.368.0814.57
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优化后振动加速度

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转速/（r·min-1）振动加速度/（m·s-²）
X方向Y方向Z方向总和
1 0000.530.440.860.80
2 0001.201.041.442.14
3 0001.461.402.583.28
4 0004.074.693.647.20
5 0005.033.993.857.49
6 0006.245.545.299.88
7 0007.875.156.5211.44
8 0009.647.368.0814.57
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高速涡旋压缩机轴系动平衡分析与优化
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董辰宇 , 郗冬阳 , 李思莹 , 陈江平 , 施骏业
流体机械 | 应用技术 2025,53(12): 102-108
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流体机械 |应用技术 2025 , 53 (12) : 102 -108
高速涡旋压缩机轴系动平衡分析与优化
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董辰宇 , 郗冬阳, 李思莹, 陈江平, 施骏业
作者信息
  • 上海交通大学 制冷及低温工程研究所，上海 200240
作者简介:

董辰宇（1999），男，硕士，主要从事电动涡旋压缩机研究与设计工作，通信地址：200240中国上海市东川路800号上海交通大学机械与动力工程学院，E-mail：。

Dynamic balance analysis and optimization of high‑speed scroll compressor shaft system
Chenyu DONG , Dongyang XI, Siying LI, Jiangping CHEN, Junye SHI
Affiliations
  • Institute of Refrigeration and Cryogenic Engineering，Shanghai Jiao Tong University，Shanghai 200240，China
出版时间: 2025-12-31 doi: 10.3969/j.issn.1005-0329.2025.12.012
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摘要
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针对高转速、大排量涡旋压缩机的噪声和振动问题，基于多体动力学理论构建了轴系的动力学模型，分析主、副轴承在高转速工况下的受力特性，进而优化设计电机平衡块，并开展整机振动试验验证。结果表明，在涡旋压缩机全转速范围内，优化前后主、副轴承受力均随转速提升而增加，优化后轴承受力在全转速范围内均显著小于优化前，8 000 r/min时，优化后主轴承受力减小21.06 N，副轴承受力减小7.73 N；在涡旋压缩机全转速范围内，优化后样机在多数转速下表现出较原型机更低的振动加速度，在6 000 r/min时，振动总和由20.41 m/s²降至9.88 m/s²。研究可为提高高速涡旋压缩机的动平衡性能提供理论支撑。

涡旋压缩机  /  动平衡  /  ADAMS软件  /  动力学

To address the noise and vibration issues of high‑speed，large‑displacement scroll compressors，a dynamic model of the shaft system was established based on multibody dynamics theory.The force characteristics of the main and auxiliary bearings under high‑speed operating conditions were analyzed，followed by the optimized design of the motor counterweights.Subsequently，whole‑machine vibration tests were carried out for verification.The results indicate that，over the entire speed range of the scroll compressor，the loads on both the main and auxiliary bearings increase with the rise in rotational speed before and after optimization.After optimization，the bearing loads are significantly lower across the entire speed range.Specifically，at 8 000 r/min，the load on the main bearing is reduced by 21.06 N，and that on the auxiliary bearing by 7.73 N.Furthermore，over the full speed range，the optimized prototype exhibits lower vibration acceleration than the original prototype at most rotational speeds.At 6 000 r/min，the total vibration acceleration decreases from 20.41 m/s² to 9.88 m/s².This study provides theoretical support for improving the dynamic balance performance of high‑speed scroll compressors.

scroll compressor  /  dynamic balance  /  ADAMS software  /  dynamics
董辰宇, 郗冬阳, 李思莹, 陈江平, 施骏业. 高速涡旋压缩机轴系动平衡分析与优化. 流体机械, 2025 , 53 (12) : 102 -108 . DOI: 10.3969/j.issn.1005-0329.2025.12.012
Chenyu DONG, Dongyang XI, Siying LI, Jiangping CHEN, Junye SHI. Dynamic balance analysis and optimization of high‑speed scroll compressor shaft system[J]. Fluid Machinery, 2025 , 53 (12) : 102 -108 . DOI: 10.3969/j.issn.1005-0329.2025.12.012
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0　引言
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随着新能源汽车的迅速发展和普及，提升续航里程和充电效率已成为市场的关键需求。这一趋势对电动汽车热管理系统制冷功率提出了更高的需求，从而促使涡旋压缩机向高转速、大排量方向不断发展。涡旋压缩机高转速与大排量不可避免地伴随着振动和噪声的增加，使得动平衡问题成为实现高速化的关键。动平衡性能的优化不仅对涡旋压缩机的工作稳定性和效率至关重要，也在降低噪声和振动方面发挥着重要作用，从而进一步推动其在电动汽车制冷系统中的应用［1-9］。
已有研究针对涡旋压缩机的动平衡问题提出了多种解决方案。邱海飞［10］基于APDL语言开发了主轴组件的参数化建模程序，优化了平衡块的质心位置，使主轴系统的1阶自振频率提升了9.49 Hz，改善了系统的动力学性能。缪仲威等［11］借助Excel软件的规划求解功能获得了动平衡的最优解，理论上可将不平衡量降至0。顾文等［12］通过优化偏心轮质量并利用ADAMS软件进行动力学仿真，研究了定转速条件下偏心轮质量与平衡铁质量对曲轴系统的影响规律。YUAN等［13］基于ADAMS建立了考虑气体力影响的涡旋轴系系统模型，优化了偏心轮质心位置，使驱动轴承的受力减少了18%，有效缓解了压缩机初期运行时的轴承冲击力。张亢等［14］通过动力学仿真优化了偏心轮结构，并进行振动测试，结果表明，在3 000 r/min工况下，x方向和y方向的振动分别降低了1.1 m/s²和0.8 m/s²。杨潍泽等［15］针对轴系结构动平衡方程进行优化，并对不同平衡块质量计算进行对比分析，得到最优的质量参数。李超等［16］采用平衡铁与曲柄销错开一定角度安装的方法，平衡了惯性力和气体力引起的转子系统动不平衡，从而提高涡旋压缩机的稳定性。邱海飞［17］通过柔性接触条件下的动力学仿真计算，深入分析主轴系统核心部件的运行状态及承载情况。李超等［18］运用多体动力学理论分析了不同间隙条件下曲柄销受力及驱动轴承角加速度等的变化规律。程军明等［19］对使用不对称代数螺线型线的涡旋压缩机进行了研究，分析了型线偏置对轴向气体力、背压力和轴承推力的影响。
综上所述，以往研究均未深入探讨高速运转工况下涡旋压缩机的动平衡问题，对其动平衡性能的影响缺乏系统分析。本文利用多体动力学理论对涡旋压缩机轴系进行参数化分析，通过仿真与振动试验验证优化效果，为提高高速涡旋压缩机的动平衡性能提供理论支持与实践依据。
1　轴系受力分析
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涡旋压缩机轴系结构如图1所示，涡旋压缩机轴系结构主要由主轴、电机转子、上平衡块、下平衡块、偏心销、扇形铁和动涡旋盘组成［20］。偏心机构主要包括动涡旋盘、扇形铁、电机转子平衡块这三部分，同时还包含偏心套、偏心销等次要结构。其中，动涡旋盘轴承孔内嵌有滑动轴承，进而与偏心套连接；偏心套与扇形铁间通过销子固定，嵌套入主轴中；转子平衡块通过铆钉固定在转子上，上、下平衡块为180°对置安装。通过电机驱动，主轴带动动涡旋盘在防旋环的限制下围绕静涡旋盘基圆中心进行公转平动，由上述偏心质量形成的离心力也随转动周期产生，成为电动涡旋压缩机轴系结构所受周期性激励的主要来源，因此，合理地设计各偏心部件质量及质心位置是改善涡旋压缩机轴系稳定性和提高压缩机运行效率、寿命的有效措施。
如图2所示，将轴系各部分偏心结构抽象为质点后进行简化受力分析，坐标原点建立在主轴承的质心处，惯性力可由各部件质量及质心坐标计算得到。
图中，Fscm为动涡旋盘产生的惯性力；Fcpm为偏心销产生的惯性力；Fesm为扇形铁产生的惯性力；Fuwm为上转子平衡块产生的惯性力；Fuwmr为上转子平衡块惯性力的径向分量；Fuwmt为上转子平衡块惯性力的切向分量；Fdwm为下转子平衡块产生的惯性力；Fdwmr为下转子平衡块惯性力的径向分量；Fdwmt为下转子平衡块惯性力的切向分量；Fubr为主轴承载荷的径向分量；Fubt为主轴承载荷的切向分量；Fdbr为副轴承载荷的径向分量；Fdbt为副轴承载荷的切向分量；β为偏移角度；lscm为动盘惯性力力臂；lcpm为偏心销惯性力力臂；lesm为扇形铁惯性力力臂；luwm为上转子平衡块惯性力力臂；ldwm为下转子平衡块惯性力力臂；ldb为副轴承载荷力臂。
由于受力分解为径向、轴向两个方向，在涡旋压缩机运行过程中，上述各部分力的相对位置不会发生改变，可以得到如下方程。
径向力平衡方程：
        Fscm+Fcpm+Fdwmr+Fubr-Fesm-Fuwmr-Fdbr=0
切向力平衡方程：
Fdwmt+Fubt-Fuwmt-Fdbt=0
径向力矩平衡方程：
        Fscmlscm+Fcpmlcpm+Fuwmrluwm         +Fdbrldb-Fdwmrldwm-Fesmlesm=0
切向力矩平衡方程：
Fuwmtluwm+Fdbtldb-Fdwmtldwm=0
由上述公式可知，当主轴承载荷和副轴承载荷的径向、切向分量均为0时，轴系结构动平衡性能最优，因此，在保证动涡旋盘质量、质心位置不变的情况下，可以得到一组实现轴系动平衡的扇形铁、上平衡块、下平衡块质量分配方案。该计算方法具有一定的理论依据，但在计算过程中忽略了部分动态因素，也没有考虑到其他的非线性效应，这导致通过上述方法计算出的方案通常不是最优的。
2　轴系多体动力学建模
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基于上述分析的压缩机轴系动平衡理论，采用多体动力学软件ADAMS（automatic dynamic analysis of mechanical systems）进行运动仿真分析，并在此基础上开展参数化优化设计。ADAMS作为广泛应用的动力学仿真工具，能够快速高效地执行设计参数的优化，同时具备强大的后处理功能和良好的用户交互体验。
选用排量为50 mL/r的涡旋压缩机作为研究对象，其额定转速范围为1 000~8 000 r/min，由于研究方向为涡旋压缩机在高转速下的振动、噪声表现，故选用8 000 r/min的转速进行建模仿真。
2.1　模型建立与参数设置
在SolidWorks中建立轴系相关零部件的模型，并按照实际情况进行装配，如图3，4所示。
针对扇形铁和动盘的优化设计较为复杂，因此，以电机转子上、下平衡块的质量为主要优化变量。
模型导入后，根据涡旋压缩机实际运行中各部件运动关系施加相应约束，如表1所示。
模型中各部件质量设置为实测质量，相关数值如表2所示，其中，动涡旋盘组件包括动涡旋盘，以及与其固接的防旋环、耐磨圈、动盘轴承等部件。
2.2　仿真结果分析
为了合理监测传动系统的合力矩，在ADAMS中针对轴承建立了两个测量变量：Fx（测量旋转部件对主轴承x方向的合力）和Fy（测量旋转部件对主轴承y方向的合力）。设定的目标函数为最小化这两个测量变量，即最小化Fx和Fy，以使其值达到最低。
设置压缩机转子的转速为8 000 r/min，重力加速度为9.8 m/s，进行0.05 s的仿真分析，测量变量的变化仿真结果如图5所示。从图中可以看出，传动系统固定轴承处的合力在x和y轴上波动较大，且最高点与最低点之间的差值显著。这表明根据压缩机的平衡公式及理论，传动系统中仍存在较大的不平衡力。为进一步减小上下幅值波动范围，需对电动压缩机传动系统中的偏心旋转部件进行优化设计。
2.3　模型优化
鉴于动平衡参数众多，且压缩机传动系统其他部件的尺寸和质量难以改变，在分析中忽略气体力及其他因素，将电机转子上、下平衡块作为主要优化对象。保持设置条件一致，在ADAMS软件中选取上下平衡块质量作为优化变量，即DV1（上平衡块质量）和DV2（下平衡块质量）。初始值分别为54.6 g和48.8 g。
由于传动系统为刚性系统，因此，采用基于Newton-Raphson迭代算法的变系数BDF刚性积分法，以实现变阶、变步长的高效计算。ADAMS优化器设置最大迭代次数为50，最终在第19次迭代时合力达到最小，表明优化已达最佳，进一步迭代将导致误差上升。此时，设计变量DV1和DV2分别为65.0 g和55.0 g。将优化后的参数输入ADAMS进行0.05 s仿真，结果如图6所示。
通过使用优化后的参数对传动系统进行再次仿真，结果显示，合力的上下波动幅值差值分别比优化前减小了20.9 N和7.8 N。
将优化前的上、下平衡块质量带入式（1）（3）中，得到理论计算主、副轴承受力情况，如表3所示。
通过理论计算与仿真分析，优化后主、副轴承受力均有一定程度的减小，证明优化方案的可行性。然而，这一改进尚未达到更小的波动范围，可能需要进一步调整扇形铁并进行相应的参数化设计，以寻求最佳解决方案。因此，后续研究还需对传动系统的部分结构进行具体修改，并结合平衡块进行相应的调整。
同时对该涡旋压缩机全转速范围内优化前后的主、副轴承受力情况进行仿真分析，结果如图7所示。可以看出，优化前后的轴承受力均随着转速的提升而提升；优化后的轴承受力在全转速范围内均小于优化前，且在高转速时优化的效果更加明显。
3　振动噪声试验
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3.1　试验设置
传动系统的不平衡量与振动有着直接的关系，根据ZHU等［21］阐述压缩机的不平衡量与振动呈正相关的关系，理论上，减小不平衡力波动将会有效地降低振动，因此，对优化电机平衡块的压缩机做振动试验测试。
振动测试主要设备有汽车空调系统负载台（进行压缩机工况的调试）、LMS测试采集软件、振动加速度传感器。测试方法为：采用弹力绳将压缩机按实车位置悬挂于支架中心，在压缩机顶盖表面布置振动传感器，如图8，9所示；连接压缩机驱动线束，待压缩机运行稳定后进行测试，并记录有效振动量。
根据优化的电机平衡块信息，在基础样件上进行改进，分别减少平衡块的质量，加工最新的平衡块样件进行装配，并安装在台架上进行对比测试。测试工况吸气压力为0.3 MPa，排气压力为1.5 MPa，吸气过热度为10 K，转速范围为1 000~8 000 r/min。
3.2　试验结果
表4、表5列出不同转速下原型机与优化样机在X，Y，Z三个方向振动加速度及总和振动加速度。试验结果表明，随着转速增加，原型机在高转速时振动较大。优化后的系统在多数转速下表现出较原型机更低的振动加速度，在较低转速下，振动加速度的改善幅度有限，而在中高转速段（6 000 r/min及以上），优化效果则较为明显。在6 000 r/min时，振动总和由20.41 m/s²降至9.88 m/s²，减幅高达10.53 m/s²。这表明优化方案在高转速工况下能够有效减小振动，提高系统稳定性。通过最优理论解对电机平衡块得到求解方法，降低了压缩机的振动值，验证了最优解理论的可行性。
4　结论
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本文基于轴系动平衡理论，运用ADAMS动力学仿真对涡旋压缩机动平衡设计进行研究与分析，对涡旋压缩机全转速范围内优化前后主、副轴承受力情况进行仿真分析，得到如下结论。
（1）优化方案成功减小了主、副轴承处的载荷，不仅提升了涡旋压缩机的工作稳定性，还为降低结构应力及延长设备使用寿命提供了理论依据。
（2）优化前后的轴承受力均随着转速的提升而提升，优化后的轴承受力在全转速范围内均小于优化前，高转速时优化的效果更加明显，8 000 r/min时，优化后主轴承受力减小21.06 N，副轴承受力减小7.73 N。
（3）同一台样机的噪声与振动加速度在转速提升时均呈现上升趋势。同时，经过优化后的样机在这两项性能指标上均显著优于未优化样机。特别是在高转速条件下，优化效果更加明显，在6 000 r/min时，振动总和由20.41 m/s²降至9.88 m/s²，优化方案在实际应用中能够有效降低噪声和振动，提高涡旋压缩机的整体性能。

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2025年第53卷第12期
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doi: 10.3969/j.issn.1005-0329.2025.12.012
  • 接收时间：2025-06-25
  • 首发时间：2026-10-22
  • 出版时间：2025-12-31
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  • 收稿日期：2025-06-25
  • 修回日期：2025-10-29
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    上海交通大学 制冷及低温工程研究所，上海 200240
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2种不同金属材料的力学参数
科
Family		 属数
Number of
genus		 种数
Number of
species		 占总种数比例
Percentage of
total species (%)		 属
Genus		 种数
Number of
species		 占总种数比例
Percentage of total
species (%)
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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