传动轴平衡：综合指南
Devices for Dynamic Balancing of Driveshafts and Measurement System for Balancing Machines Balanset-4A – €6,803
想象一下，您正在驾驶一辆卡车，突然感到剧烈的震动，或者在加速或换挡时听到巨大的撞击声。这不仅仅是一种干扰，它可能是传动轴不平衡的征兆。对于工程师和技术人员来说，这样的震动和噪音预示着效率的下降、部件的磨损加速，如果不加以处理，还可能造成代价高昂的停机。
在本指南中，我们将提供传动轴平衡问题的实用解决方案。您将了解什么是传动轴以及为什么需要进行平衡，识别导致振动或噪音的常见故障，并遵循清晰的分步流程进行动态传动轴平衡。通过应用这些最佳实践，您可以节省维修费用，减少故障排除时间，并确保您的机械或车辆以最小的振动可靠运行。
目录
1.传动轴的类型
万向节驱动装置（传动轴）是一种在万向节中心相交的轴之间传递扭矩的装置，这些轴可以相对移动一定角度。在传统或全轮驱动配置的车辆中，传动轴将扭矩从变速箱（或分动箱）传递到驱动桥。对于全轮驱动车辆，万向节通常将变速箱的从动轴连接到分动箱的驱动轴，并将分动箱的从动轴连接到从动车桥主驱动装置的驱动轴。
安装在车架上的单元（例如变速箱和分动箱）由于其支架和车架本身的变形而彼此相对移动。同时，驱动桥通过悬架连接到车架，由于悬架弹性元件的变形，驱动桥可以相对于车架及其上安装的单元移动。这种移动不仅会改变连接单元的驱动轴的角度，还会改变单元之间的距离。
The universal joint drive has a significant disadvantage: the non-uniform rotation of the shafts. If one shaft rotates uniformly, the other does not, and this non-uniformity increases with the angle between the shafts. This limitation prevents the use of a universal joint drive in many applications, such as in the transmission of front-wheel-drive vehicles, where the main issue is transmitting torque to the turning wheels. This disadvantage can be partially compensated by using two universal joints on one shaft, set to equal joint angles (γ1 = γ2) with the yokes at both ends of the intermediate shaft in the same plane (in phase). Yokes phased 90° apart do not cancel the fluctuation — they add to it. However, in applications requiring uniform rotation, constant velocity joints (CV joints) are typically used instead. CV joints are a more advanced but also more complex design serving the same purpose.
万向节传动装置可由一个或多个万向节组成，通过传动轴和中间支撑连接。
图 1.万向节传动装置示意图：1、4、6 - 传动轴；2、5 - 万向节；3 - 补偿连接；u1、u2 - 轴间夹角
万向节传动装置一般由万向节2和5、驱动轴1、4和6以及补偿连接3组成。有时，驱动轴安装在与车架横梁连接的中间支架上。万向节确保在轴线成一定角度的轴之间传递扭矩。万向节分为非等速万向节和等速万向节。非等速万向节进一步分为弹性万向节和刚性万向节。等速万向节可以是带分度槽的球头万向节、带分度杆的球头万向节和凸轮万向节。它们通常安装在前导控制轮的驱动装置中，其中轴之间的角度可达45°，并且万向节的中心必须与车轮的旋转轴和转向轴的交点重合。
Elastic universal joints transmit torque between shafts with intersecting axes at an angle of 2...3° due to the elastic deformation of the connecting elements. A rigid non-uniform velocity joint transmits torque from one shaft to another through the movable connection of rigid parts. It consists of two yokes – 3 and 5, into the cylindrical holes of which the ends A, B, C, and D of the connecting element – the cross 4, are installed on bearings. The yokes are rigidly connected to shafts 1 and 2. Yoke 5 can rotate around axis B–D of the cross and at the same time, along with the cross, rotate around axis A–C, thereby enabling the transmission of rotation from one shaft to another with a changing angle between them.
图 2.刚性非匀速万向节示意图
If shaft 1 rotates around its axis by an angle α, then shaft 2 will rotate by an angle β over the same period. The relationship between the rotation angles of shafts 1 and 2 is determined by the expression tanα = tanβ * cosγ, where γ is the angle at which the axes of the shafts are positioned. This expression indicates that the angle β is sometimes less than, equal to, or greater than angle α. Equality of these angles occurs every 90° of rotation of shaft 1. Therefore, with uniform rotation of shaft 1, the angular velocity of shaft 2 is non-uniform and varies according to a sinusoidal law. The non-uniformity of shaft 2's rotation becomes more significant as the angle γ between the shaft axes increases.
如果轴 2 的不均匀旋转传递到机组的轴上，则会在传动过程中产生额外的脉动载荷，并随角度 γ 的增大而增大。为了防止轴 2 的不均匀旋转传递到机组的轴上，在万向节传动中使用了两个万向节。安装时，γ1 和 γ2 的角度相等；固定在非均匀旋转轴 4 上的万向节叉应位于同一平面内。
万向节传动装置主要部件的设计如图3所示。非等速万向节由两个轭杆（1）组成，并通过十字轴（3）连接。其中一个轭杆有时带有法兰，而另一个轭杆则焊接在驱动轴管上，或带有用于连接到驱动轴的花键端（6）（或套筒）。十字轴的耳轴安装在两个轭杆的孔眼中，由滚针轴承（7）支撑。每个轴承都装在一个轴承箱（2）中，并通过一个轴承盖固定在轭杆孔眼中，轴承盖通过两个螺栓固定在轭杆上，螺栓通过垫圈上的卡舌锁定。在某些情况下，轴承通过卡簧固定在轭杆上。为了保持轴承的润滑并防止其受到水和灰尘的侵蚀，轴承配有橡胶自紧密封件。十字轴的内腔通过一个通向轴承的注油嘴注入润滑脂。十字接头通常配有安全阀，以防止因泵入十字接头的润滑脂压力而损坏密封件。花键连接件（6）使用黄油嘴（5）进行润滑。
图 3.刚性非匀速万向节的细节
The maximum angle between the axes of shafts connected by rigid non-uniform velocity universal joints usually does not exceed 20°, as efficiency significantly decreases at larger angles. If the angle between the shaft axes varies within 0...2°, the trunnions of the cross are deformed by the needle bearings, causing the universal joint to fail quickly.
在高速履带式车辆的传动中，经常使用齿式联轴器，这种万向节可以在轴线相交角度达 1.5...2° 的轴之间传递扭矩。
传动轴通常使用特殊钢无缝管或焊接管制成管状。万向节、花键套筒或尖端的轭焊接在管子上。为减少传动轴上的横向载荷，在装配万向节时进行动平衡。通过在传动轴上焊接平衡板或有时在万向节轴承盖下安装平衡板来纠正不平衡。在工厂对万向节传动装置进行装配和平衡后，花键连接部件的相对位置通常会用特殊标签进行标记。
万向节传动装置的补偿连接通常采用花键连接形式，允许万向节传动装置部件轴向移动。它包括一个花键头，与万向节传动装置的花键套配合。润滑油通过黄油接头进入花键连接，或在装配时涂抹，并在车辆长期使用后更换。通常会安装一个密封件和一个盖子，以防止润滑脂泄漏和污染。
对于长传动轴，中间支撑通常用于万向节传动。中间支撑通常包括一个用螺栓固定在车架横梁上的支架，支架上的球轴承安装在橡胶弹性圈中。轴承两侧用盖密封，并带有润滑装置。弹性橡胶圈有助于补偿由于车架变形可能造成的装配误差和轴承偏差。
带滚针轴承的万向节（图 4a）由轭、十字架、滚针轴承和密封件组成。带滚针轴承的杯装在十字架的耳轴上，并用密封件密封。滚针轴承杯用卡环或用螺丝固定的盖子固定在轭上。万向节通过十字架内部钻孔的黄油接头进行润滑。安全阀用于消除接头中过量的油压。在驱动轭匀速转动时，从动轭的旋转是不均匀的：每转一圈前进和落后驱动轭两次。为了消除非均匀旋转并减少惯性负载，使用了两个万向节。
在前驱动轮的传动装置中，安装了等速万向节。GAZ-66 和 ZIL-131 车辆的等速万向节传动装置由轭 2、5（图 4b）、四个球 7 和一个中心球 8 组成。驱动轭 2 与内轴是一体的，而从动轭则与外轴锻造在一起，外轴末端固定有轮毂。从动轭 2 到从动轭 5 的驱动力矩通过滚珠 7 传递，滚珠 7 沿着轭上的环形凹槽移动。中心球 8 的作用是使轭对中，并由螺柱 3 和 4 固定。由于机构相对于轭的对称性，轭 2 和轭 5 的旋转频率相同。轴长度的变化由轭与轴的自由花键连接来保证。
图 4.万向节：a - 万向节：1 - 盖；2 - 杯；3 - 滚针轴承；4 - 密封圈；5、9 - 轭；6 - 安全阀；7 - 十字架；8 - 黄油接头；10 - 螺钉；b - 等速万向节：1 - 内轴轴；2 - 驱动轭；3、4 - 螺柱；5 - 从动轭；6 - 外轴轴；7 - 滚珠；8 - 中心滚珠
2.万向节驱动装置故障
万向节驱动故障通常表现为车辆行驶时，特别是在换挡和发动机曲轴转速突然升高时（例如，从发动机制动过渡到加速时），万向节出现剧烈敲击声。万向节故障的一个迹象是温度升高（超过 100°C）。出现这种情况的原因是万向节的衬套和耳轴、滚针轴承、十字架和花键连接严重磨损，导致万向节不对中，滚针轴承承受巨大的冲击轴向载荷。万向节十字架软木密封件的损坏会导致耳轴及其轴承的快速磨损。
在维护过程中，用手双向急转传动轴，检查万向节驱动装置。轴的自由旋转程度决定了万向节和花键连接的磨损程度。每行驶 8,000 至 10,000 公里，检查变速箱从动轴法兰和主传动齿轮传动轴与端部万向节法兰的螺栓连接情况以及传动轴中间支架的紧固情况。还要检查花键连接处的橡胶套和万向节十字的软木密封件的状况。所有紧固螺栓必须完全拧紧（拧紧扭矩为 8-10 kgf-m）。
万向节的滚针轴承使用变速箱用液体润滑油润滑；大多数车辆的花键连接使用润滑脂（US-1、US-2、1-13 等）润滑；严禁使用润滑脂润滑滚针轴承。在某些车辆中，花键连接采用变速箱油润滑。安装在橡胶套筒中的中间支撑轴承实际上不需要润滑，因为在工厂装配时已经进行了润滑。ZIL-130 车辆的支撑轴承在定期维护时（每行驶 1100-1700 公里）通过压力接头加注润滑脂。
图 5.万向节传动装置：1 - 用于固定传动轴的法兰；2 - 万向节十字架；3 - 万向节轭；4 - 滑动轭；5 - 传动轴管；6 - 封闭端滚针轴承
万向节传动装置由两个带滚针轴承的万向节（通过空心轴连接）和一个带渐开线花键的滑动轭组成。为确保可靠的防污保护并为花键连接提供良好的润滑，与变速箱副轴 (2) 连接的滑动轭 (6) 被放置在变速箱壳体的延伸部分 (1) 中。此外，花键连接的这一位置（在接头之间的区域之外）大大提高了万向节传动装置的刚度，并降低了滑动花键连接磨损时轴振动的可能性。
驱动轴由薄壁电焊管（8）制成，两个相同的轭（9）分别压入管内，然后通过电弧焊焊接在一起。十字轴（25）的滚针轴承座（18）压入轭（9）的孔眼中，并用弹簧挡圈（20）固定。每个万向节轴承包含22个滚针（21）。冲压盖（24）压入十字轴突出的耳轴上，并在耳轴上安装软木圈（23）。轴承润滑使用角形黄油嘴（17），该黄油嘴拧入十字轴中心的螺纹孔中，并与十字轴耳轴中的通孔相连。万向节十字轴的另一侧，中心位置有一个安全阀（16），用于在填充十字轴和轴承时释放多余的润滑脂，并防止十字轴内部在运行过程中压力过大（当压力达到约 3.5 千克/平方厘米时，安全阀启动）。之所以需要安装安全阀，是因为十字轴内部压力过大会导致软木密封圈损坏（挤压）。
图 6.传动轴组件：1 - 变速箱延长件；2 - 变速箱副轴；3 和 5 - 挡土板；4 - 橡胶密封件；6 - 滑动轭；7 - 平衡板；8 - 传动轴管；9 - 轭；10 - 法兰轭；11 - 螺栓；12 - 后桥驱动齿轮法兰；13 - 弹簧垫圈；14 - 螺母；15 - 后轴；16 - 安全阀；17 - 角形润滑脂接头；18 - 滚针轴承；19 - 轭眼；20 - 弹簧固定环；21 - 滚针；22 - 带环形端头的垫圈；23 - 软木环；24 - 冲压盖；25 - 十字架
驱动轴由两个万向节组装而成，两端均需通过焊接平衡板（7）到驱动轴管上进行仔细的动态平衡。因此，拆卸驱动轴时，必须仔细标记所有零件，以便将其重新安装到原位。不遵守此说明会破坏驱动轴的平衡，从而引起振动，进而损坏变速箱和车身。如果单个零件磨损，尤其是驱动轴管因冲击而弯曲，导致组装后无法进行动态平衡，则必须更换整根驱动轴。
可能的传动轴故障、原因和解决方案
| 故障原因 | 解决方案 |
|---|---|
| 传动轴振动 | |
| 1.轴因障碍物而弯曲 | 1.调直装配好的轴并进行动态平衡，或更换装配好的轴 |
| 2.轴承和交叉磨损 | 2.更换轴承和十字架，并对装配好的轴进行动态平衡 |
| 3.加长衬套和滑动轭磨损 | 3.更换加长杆和滑动轭，并对装配好的轴进行动态平衡 |
| 启动和滑行时的敲击声 | |
| 1.滑动轭花键或二级齿轮箱轴磨损 | 1.更换磨损部件。更换滑动轭时，对装配好的轴进行动态平衡。 |
| 2.将法兰轭固定到后车桥驱动齿轮法兰上的螺栓松动 | 2.拧紧螺栓 |
| 万向节密封件甩油 | |
| 万向节密封件软木环的磨损 | 更换软木环，在重新组装过程中保持所有传动轴部件的相对位置。如果十字架和轴承有磨损，则更换轴承和十字架，并对组装好的轴进行动态平衡。 |
3.传动轴平衡
在修理和组装传动轴后，要在机器上对其进行动态平衡。图 7 显示了平衡机的一种设计。该机器由一个底板 (18)、一个安装在四根垂直弹性杆 (3) 上的摆架 (8) 组成，确保其在水平面内摆动。固定在支架 (4) 上的支架和前座 (9) 安装在摆架 (8) 的纵向管上。后头架 (6) 安装在活动横梁 (5) 上，可对不同长度的传动轴进行动态平衡。头架主轴安装在精密滚珠轴承上。前头架 (9) 的主轴由安装在机器底座上的电动机通过三角皮带驱动和中间轴驱动，中间轴上安装有一个刻度盘 (10)（刻度盘）。此外，在机器底板 (18) 上还安装了两个带有可伸缩锁定销 (17) 的支架 (15)，以确保根据传动轴前端或后端的平衡情况固定摆架的前后端。
图 7.传动轴动平衡机
1-夹具；2-阻尼器；3-弹性杆；4-支架；5-可移动横梁；6-后头架；7-横杆；8-摆架；9-前驱动头架；10-刻度盘；11-毫伏计；12-换向器整流器轴刻度盘；13-磁电传感器；14-固定架；15-固定器架；16-支架；17-固定器；18-支撑板
固定支架 (14) 安装在机器板的后部，上面安装有磁电传感器 (13)，连杆与摆杆框架的两端相连。为防止框架共振，在支架 (4) 下方安装了注满油的阻尼器 (2)。
During dynamic balancing, the driveshaft assembly with the sliding yoke is installed and secured on the machine. One end of the driveshaft is connected by a flange-yoke to the flange of the front driving headstock, and the other end by the support neck of the sliding yoke to the splined sleeve of the rear headstock. Then the ease of rotation of the driveshaft is checked, and one end of the machine's pendulum frame is fixed using the fixator. After starting the machine, the limb of the rectifier is rotated counterclockwise, bringing the millivoltmeter needle to its maximum reading. The millivoltmeter reading corresponds to the magnitude of the imbalance. The millivoltmeter scale is graduated in gram-centimeters or grams of counterweight. Continuing to rotate the rectifier limb counterclockwise, the millivoltmeter reading is brought to zero, and the machine is stopped. Based on the rectifier limb reading, the angular displacement (angle of imbalance displacement) is determined, and by manually rotating the driveshaft, this value is set on the intermediate shaft limb. The welding place of the balancing plate will be on the top of the driveshaft, and the weighted part at the bottom in the correction plane. Then the balancing plate is attached and tied with thin wire at a distance of 10 mm from the weld, the machine is started, and the balance of the driveshaft end with the plate is checked. The imbalance should be no more than 70 g·cm (700 g·mm). Then, releasing one end and securing the other end of the pendulum frame with the fixator stand, dynamic balancing of the other end of the driveshaft is performed according to the technological sequence described above.
传动轴具有一些平衡特性。对于大多数零件来说，动平衡的基础是支撑颈（如电机转子、涡轮机、主轴、曲轴等），但对于传动轴来说，基础是法兰。在装配过程中，不同连接处不可避免地会出现间隙，从而导致不平衡。如果在平衡过程中无法达到最小的不平衡，轴就会被剔除。平衡精度受以下因素影响：
- 传动轴法兰着陆带与左右支撑头架夹紧法兰内孔之间的连接间隙；
- 法兰基面的径向和端面跳动；
- 铰链和花键连接处存在间隙。花键连接腔内如果存在润滑脂，则会导致“浮动”不平衡。如果这会影响达到所需的平衡精度，则驱动轴无需润滑脂即可进行平衡。
有些不平衡可能完全无法纠正。如果传动轴万向节的摩擦力增加，校正平面的相互影响也会增加。这会导致平衡性能和精度下降。
根据 OST 37.001.053-74，建立了以下不平衡标准：具有两个接头（双支撑）的传动轴需要动态平衡，具有三个接头（三支撑）的传动轴需要与中间支撑一起组装；在组装轴或联轴器之前，重量超过 5 公斤的传动轴和联轴器的法兰（轭）需要静态平衡；三关节传动轴两端或中间支撑处的传动轴残余不平衡标准通过特定的不平衡进行评估；
传动轴两端或中间支撑处的最大允许特定残余不平衡量标准，以及平衡台上任何位置的三节传动轴，均不得超过：乘用车、轻载卡车（1吨以下）和超小型客车的变速器不得超过6g-cm/kg，其余车辆不得超过10g-cm/kg。传动轴或三节传动轴的最大允许残余不平衡量标准，应在平衡台上以与最高车速下变速器中传动频率一致的转速进行测量。
Note: OST 37.001.053-74 is a Soviet automotive-industry standard from 1974 and is quoted here as a historical reference. In modern terms, 6 g·cm/kg at 3,000 rpm corresponds to about G 19 and 10 g·cm/kg to about G 31 — the OST requirement sits between G 16 and G 40, consistent with the ISO 21940-11 (formerly ISO 1940-1) grades for drive shafts. Specify new work in ISO 21940-11 grades.
对于载重量为4吨及以上的卡车、小型和大型客车的传动轴和三节传动轴，允许将平衡台上的转速降低至最高车速下传动轴转速的70%。根据OST 37.001.053-74，传动轴的平衡转速应等于：
nb = (0.7 ... 1.0) nr,
其中 nb – 平衡旋转频率（应与机架的主要技术数据相对应，n=3000 min-1); nr – 最大工作旋转频率，分钟-1.
在实际应用中，由于接头和花键连接处存在间隙，驱动轴无法在建议的旋转频率下保持平衡。在这种情况下，可选择另一种旋转频率，并在该频率下实现平衡。
4.用于传动轴的现代平衡机
图 8.用于长达 2 米、重达 500 千克传动轴的平衡机
该模型有 2 个支架，可在 2 个校正平面上保持平衡。
图 9.用于长达 4200 毫米、重达 400 千克传动轴的平衡机
该模型有 4 个支架，可同时在 4 个校正平面上进行平衡。
图 10.用于传动轴动平衡的卧式硬轴承平衡机
1 – Balancing item (driveshaft); 2 – Machine base; 3 – Machine supports; 4 – Machine drive; The structural elements of the machine supports are shown in Figure 11.
图 11.用于传动轴动平衡的机器支撑元件
1 - 左侧不可调支撑；2 - 中间可调支撑（2 件）；3 - 右侧不可调固定支撑；4 - 支撑架锁定手柄；5 - 可移动支撑平台；6 - 支撑垂直调节螺母；7 - 垂直位置锁定手柄；8 - 支撑夹紧支架；9 - 中间轴承活动夹钳；10 - 夹钳锁定手柄；11 - 夹紧支架锁定；12 - 用于物品安装的驱动（前导）主轴；13 - 驱动主轴
5.传动轴平衡的准备工作
下面，我们将讨论机器支架的设置以及在机器支架上安装平衡部件（四支撑传动轴）的问题。
图 12.在平衡机主轴上安装过渡法兰
图 13.在平衡机支架上安装传动轴
图 14.使用气泡水平仪水平校准平衡机支架上的传动轴
图 15.固定平衡机的中间支架以防止传动轴垂直位移
手动旋转物品一圈。确保旋转自如，不会卡在支架上。之后，机器的机械部分安装完毕，物品安装也就完成了。
6.传动轴平衡程序
Which kit do I need? A two-support machine correcting in two planes (Figure 8) needs the two-channel Balanset-1A. A four-support machine correcting in four planes simultaneously (Figure 9, and the procedure below) needs the four-channel Balanset-4A. The measurement and calculation workflow is identical; only the channel count differs. The procedure below is described for a four-plane setup, while the software screenshots show the same workflow on the two-plane Balanset-1A — on the Balanset-4A the same screens simply add planes 3 and 4.
The process of driveshaft balancing on the balancing machine will be considered using the Balanset-4A measuring system as an example. The Balanset-4A is a portable balancing kit designed for balancing in one, two, three, and four correction planes of rotors, either rotating in their own bearings or mounted on a balancing machine. The device includes up to four vibration sensors, a phase angle sensor, a four-channel measuring unit, and a portable computer.
The entire balancing process, including measurement, processing, and display of information on the magnitude and location of corrective weights, is performed automatically and does not require the user to have additional skills and knowledge beyond the provided instructions. The results of all balancing operations are saved in the Balancing Archive and can be printed as reports if necessary. In addition to balancing, the Balanset-4A can also be used as a regular vibro-tachometer, allowing measurement on four channels of the root mean square (RMS) value of total vibration, RMS of the rotational component of vibration, and control of rotor rotation frequency.
此外，该设备还可显示时间函数图和按振动速度绘制的振动频谱图，有助于评估平衡机械的技术状况。
Figure 16. External View of the Balanset-4A Device for Use as a Measuring and Computing System of the Driveshaft Balancing Machine
Figure 17. Example of Using the Balanset-4A Device as a Measuring and Computing System of the Driveshaft Balancing Machine
Figure 18. Main window of the Balanset software: F1 - About, F5 - Vibration Meter, F7 - Balancing, F8 - Charts, F6 - Reports
The Balanset-4A device is supplied with vibration sensors. The sensors are accelerometer-based; the software integrates their signal and displays vibration velocity in mm/s RMS.
Figure 19. Installation of Balanset-4A Vibration Sensors on the Supports of the Balancing Machine
The direction of the sensors' sensitivity axis should match the direction of the support's vibration displacement, in this case – horizontal. For additional information on sensor installation, see BALANCING ROTORS IN OPERATING CONDITIONS.
- 在平衡机支架上安装振动传感器 1、2、3、4。
- 将振动传感器连接至连接器 X1、X2、X3 和 X4。
- 安装相位角传感器（激光转速计）5，使平衡转子的径向（或端面）与传感器外壳之间的标称间隙在 10 至 300 毫米之间。
- 在转子表面贴上宽度至少为 10-15 毫米的反光胶带标记。
- 将相角传感器连接至连接器 X5。
- 将测量装置连接到计算机的 USB 端口。
- 使用市电时，请将计算机连接至电源装置。
- 将供电装置连接至 220 伏 50 赫兹的网络。
- Turn on the computer and start the Balanset software.
- Open the balancing workspace with the “F7 - Balancing” button and set the required number of correction planes in the “Plane count” field, so that vibration is measured simultaneously by the vibration sensors connected to the inputs of the measuring unit.
- A mnemonic diagram illustrating the connection of the sensors and the measuring unit appears on the computer display, as shown in Figure 18.
在进行平衡之前，建议使用测振仪模式（F5 按钮）进行测量。
Figure 20. Vibration Meter mode (F5): total vibration V1s, V2s and rotational components V1o, V2o with phases F1, F2, displayed as vibration velocity in mm/s RMS
如果总振动幅值 V1s (V2s) 与旋转分量幅值 V1o (V2o) 大致匹配，则可以推断机构振动的主要贡献来自转子不平衡。如果总振动幅值 V1s (V2s) 明显超过旋转分量 V1o (V2o)，建议检查机构——检查轴承状况，确保其牢固地安装在基础上，确认转子在旋转过程中不会接触固定部件，并考虑其他机构振动的影响等。
Studying the time function graphs and vibration spectra in the charts mode (“F8 - Charts”, the “F5-Spectrum (Hz)” tab) can be useful here.
图 21.振动时间函数和频谱图
该图显示了振动水平最高的频率。如果这些频率与平衡机构转子的旋转频率不同，则需要在平衡之前确定这些振动成分的来源并采取措施消除它们。
Reading the spectrum of a driveshaft: 1x is unbalance, 2x may be the joint itself. A dominant peak at the rotational frequency (1x) points to unbalance — this is what balancing removes. A dominant peak at twice the rotational frequency (2x), especially together with strong axial vibration, points to the joint angles, worn crosses or splines, or 错位: a universal (cardan) joint working at an angle γ makes the driven yoke lead and lag twice per revolution, so it produces a 2x component even when the shaft is perfectly balanced. Balancing will not remove it — equalise the joint angles (γ1 = γ2) and check the joints first. In the charts mode (“F8 - Charts”) the “F5-Spectrum (Hz)” tab shows the spectrum and the “F3-1x vibration” tab the rotational component; at 3000 min-1 1x = 50 Hz and 2x = 100 Hz.
同样重要的是要注意测振仪模式下读数的稳定性--测量过程中振动幅度和相位的变化不应超过 10-15%。否则，机械装置可能会在共振区附近运行。在这种情况下，应调整转子速度。
When performing four-plane balancing of a new rotor, five calibration runs and at least one trim run (Run T) of the balanced machine are required. Vibration measurement during the first machine run without a trial weight is performed as Run 0 in the balancing workspace. Subsequent runs are performed with a trial weight, sequentially installed on the driveshaft in each correction plane (in the area of each balancing machine support).
以后每次运行前，都应采取以下步骤：
- 停止平衡机器转子的旋转。
- 取下之前安装的试重。
- 在下一个平面安装试重。
Figure 22. Balancing workspace (“F7 - Balancing”) during a measurement run: Run 0 - Initial, trial-mass runs Run 1 and Run 2, and the trim run Run T
每次测量完成后，转子旋转频率（Nob）以及有效值（Vo1, Vo2, Vo3, Vo4）和相位（F1, F2, F3, F4) of the vibration at the rotational frequency of the balanced rotor are saved in the corresponding fields in the program window. After the fifth run (Weight in Plane 4), the balancing results with the polar plot (see Figure 23) appear, displaying the calculated values of the masses (M1, M2, M3, M4）和安装角度（f1, f2, f3, f4) 的校正砝码，这些砝码需要安装在转子的四个平面上，以补偿转子的不平衡。
Figure 23. Polar plot of the balancing result: calculated correction masses and angles for each plane, measured from the trial weight position in the direction of rotation
请注意！ 在平衡机第五次运行期间完成测量过程后，必须停止转子旋转并移除之前安装的试配重块。只有在此之后，才能继续在转子上安装（或移除）校正配重块。
在极坐标系中，转子上添加（或移除）校正配重的角位置是从试配重安装位置测量的。角度测量方向与转子旋转方向一致。在按叶片平衡的情况下，平衡转子中条件上视为第一个叶片的叶片与试配重安装位置一致。计算机显示屏上显示的叶片编号方向与转子旋转方向一致。
In this version of the program, it is assumed by default that the corrective weight will be added to the rotor. This is indicated by the mark set in the “Add mass” field. If correcting the imbalance by removing the weight (e.g., by drilling) is necessary, set the mark in the “Remove mass” field using the mouse, after which the angular position of the corrective weight will automatically change by 180 degrees.
After installing the corrective weights on the balanced rotor, carry out the trim run (Run T) to check the effectiveness of the balancing operation. After completing the trim run, the results of the rotor's rotation frequency (Nob）和有效值（Vo1, Vo2, Vo3, Vo4）和相位（F1, F2, F3, F4) of the vibration at the rotational frequency of the balanced rotor are saved. Simultaneously, the balancing results (see Figure 23) are updated, displaying the calculated parameters of additional corrective weights that need to be installed (or removed) on the rotor to compensate for its residual imbalance. Additionally, this workspace shows the values of the residual imbalance achieved after balancing. If the values of residual vibration and/or residual imbalance of the balanced rotor meet the tolerance requirements specified in the technical documentation, the balancing process can be completed. Otherwise, the balancing process can be continued. This method allows for correcting possible errors through successive approximations that may occur when installing (removing) the corrective weight on the balanced rotor.
If the balancing process continues, additional corrective weights must be installed (or removed) on the balanced rotor according to the calculated parameters shown in the balancing results.
The rotor balancing coefficients (dynamic influence coefficients) calculated from the results of the five calibration runs are saved in the computer's memory and can be reused with the “Load Coefficients” function when balancing rotors of the same type.
7.推荐的刚性转子平衡精度等级
The grades below are the balance quality grades G of ISO 1940-1, superseded without change of values by ISO 21940-11:2016. The grade is defined as G = e每·Ω, where e每 is the permissible specific residual unbalance (g·mm/kg = µm) and Ω = 2πn/60 is the service angular velocity (rad/s). The permissible residual unbalance follows as U每 = 9549·G·M/n [g·mm], split between the correction planes. See our ISO 1940-1 glossary entry.
The default grade for a road-vehicle driveshaft is G 40; G 16 applies when the drawing or the OEM specification calls for special requirements. Note that residual unbalance and vibration are separate acceptance criteria: the vibration of the assembled machine is assessed to ISO 20816 (formerly ISO 10816) — see our ISO 10816-1 glossary entry.
The G-grade table applies to rigid rotors only — rotors whose service speed stays below roughly 0.5…0.7 of the first bending critical speed. Long driveshafts (2 m and above, and any shaft with an intermediate support) can approach that limit: check the shaft's first critical speed against both the service speed and the balancing speed. If the shaft is flexible at speed, use a modal / multi-speed procedure (ISO 21940-12) — a two-plane rigid-rotor correction will not hold.
表 2.推荐的刚性转子平衡精度等级。
| 机器类型（转子） | 平衡精度等级 | Balance quality grade G = e每·Ω, mm/s |
|---|---|---|
| 用于大型低速船用柴油机的驱动曲轴（结构不平衡）（活塞速度小于 9 米/秒） | G 4000 | 4000 |
| 用于大型低速船用柴油机的驱动曲轴（结构平衡）（活塞速度小于 9 米/秒） | G 1600 | 1600 |
| 安装在隔振器上的驱动曲轴（结构不平衡 | G 630 | 630 |
| 刚性支架上的驱动曲轴（结构不平衡 | G 250 | 250 |
| 为客车、卡车和机车组装的往复式发动机 | G 100 | 100 |
| 安装在隔振器上的驱动曲轴（结构平衡） | G 40 | 40 |
| Car wheels, wheel rims, wheel sets, drive shafts (cardan shafts) | G 40 | 40 |
| 农业机械 | G 16 | 16 |
| 刚性支架上的驱动曲轴（平衡的） | G 16 | 16 |
| 破碎机 | G 16 | 16 |
| Drive shafts (propeller / cardan shafts) with special requirements | G 16 | 16 |
| 飞机燃气轮机 | G 6.3 | 6.3 |
| 离心机（分离器、沉淀器） | G 6.3 | 6.3 |
| 电动机和发电机（轴高度至少为 80 毫米），最高额定转速可达 950 分钟-1 | G 6.3 | 6.3 |
| 轴高度小于 80 毫米的电机 | G 6.3 | 6.3 |
| 风机 | G 6.3 | 6.3 |
| 齿轮传动装置 | G 6.3 | 6.3 |
| 通用机械 | G 6.3 | 6.3 |
| 金属切割机 | G 6.3 | 6.3 |
| 造纸机 | G 6.3 | 6.3 |
| 水泵 | G 6.3 | 6.3 |
| 涡轮增压器 | G 6.3 | 6.3 |
| 水轮机 | G 6.3 | 6.3 |
| 压缩机 | G 6.3 | 6.3 |
| 计算机控制的驱动器 | G 2.5 | 2.5 |
| 最大额定转速超过 950 分钟的电动机和发电机（轴高度至少为 80 毫米）。-1 | G 2.5 | 2.5 |
| 燃气轮机和蒸汽轮机 | G 2.5 | 2.5 |
| 金属切割机驱动器 | G 2.5 | 2.5 |
| 纺织机械 | G 2.5 | 2.5 |
| 音频和视频设备驱动器 | G 1 | 1 |
| 磨床驱动装置 | G 1 | 1 |
| 高精密设备的主轴和驱动器 | G 0.4 | 0.4 |
关于驱动轴平衡的常见问题
什么是传动轴平衡？
驱动轴平衡是校正驱动轴中任何质量不平衡的过程，使其平稳旋转且不引起振动。这包括测量驱动轴一侧较重的位置，然后通过增加或减少少量重量（例如焊接平衡块）来抵消这种不平衡。平衡的驱动轴运转平稳，可防止车辆部件过度振动和磨损。
为什么传动轴平衡很重要？
不平衡的驱动轴会导致强烈的振动，尤其是在特定速度下，并且可能在加速或换挡时发出咔嗒声。随着时间的推移，这些振动会损坏轴承、万向节和其他传动系统部件。平衡驱动轴可以消除这些振动，确保更平稳的行驶，减少零件的负担，并避免代价高昂的损坏或停机。
传动轴不平衡的常见症状有哪些？
传动轴不平衡或故障的典型症状包括车辆地板或座椅明显振动或颤动，尤其是在车速增加时。换挡或加速减速时，您还可能会听到敲击声或咔哒声。在某些情况下，万向节可能会因不平衡而过热。如果您发现这些迹象，则很可能是传动轴需要平衡或维修。
如何平衡传动轴？
Drive shaft balancing is usually done using a specialized balancing machine. The drive shaft is mounted and spun at high speed while sensors detect any imbalance. A technician then attaches small weights to the drive shaft (or removes material) at specific positions based on the machine's readings. This process is repeated until the drive shaft rotates without significant vibration. Modern systems like the Balanset-4A can guide this process and calculate exactly where and how much weight to add for precise balancing.
结论
总之，适当的传动轴平衡对于安全、性能和成本节约至关重要。 By detecting and correcting imbalance, you prevent unnecessary wear on parts, avoid damaging breakdowns, and maintain optimal machine performance. Modern balancing systems like our Balanset-1A and Balanset-4A devices make the process efficient, helping even small workshops achieve professional results.
如果您遇到持续的传动轴振动问题，或需要可靠的平衡解决方案，请立即行动。请按照本指南中的步骤操作，或咨询我们的专家寻求帮助。采用正确的方法和设备，确保您的传动轴在未来数年内平稳可靠地运行。 联系我们 了解更多信息或探索最适合您需求的传动轴平衡设备。
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