WO2014180009A1 - 旋转机械转子液力多频动力吸振器 - Google Patents

旋转机械转子液力多频动力吸振器 Download PDF

Info

Publication number
WO2014180009A1
WO2014180009A1 PCT/CN2013/076372 CN2013076372W WO2014180009A1 WO 2014180009 A1 WO2014180009 A1 WO 2014180009A1 CN 2013076372 W CN2013076372 W CN 2013076372W WO 2014180009 A1 WO2014180009 A1 WO 2014180009A1
Authority
WO
WIPO (PCT)
Prior art keywords
frequency
rotor
mass
vibration absorber
vibration
Prior art date
Application number
PCT/CN2013/076372
Other languages
English (en)
French (fr)
Inventor
何立东
张震坤
张炳康
杨秀峰
高金吉
Original Assignee
北京化工大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 北京化工大学 filed Critical 北京化工大学
Publication of WO2014180009A1 publication Critical patent/WO2014180009A1/zh

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies

Definitions

  • the invention relates to a rotor dynamic vibration absorber used in a rotating machine, which is mainly used for controlling vibration problems of a rotating machine rotor such as a fan, a compressor, a steam turbine, a machining machine spindle system, and belongs to the technical field of vibration control.
  • Rotating machines such as fans, compressors, steam turbines, gas turbines, and machine tools have always been key equipment in modern large-scale industries.
  • High-speed rotating rotors are the core components.
  • the vibration size and system stability affect the performance and reliability of rotating machinery products. An important factor in the service life. Therefore, how to reduce the vibration of the rotor system, improve the life of the rotor, and ensure the safe and reliable operation of the mechanical equipment is of great significance in the research of rotating machinery.
  • TMD tuned mass damper
  • the main system for the rotor main system mass, for the rotor main system stiffness, for the TMD subsystem mass, for the TMD subsystem stiffness, the main system
  • the forced vibration is carried out under the action of sinusoidal disturbance.
  • the working principle of the TMD subsystem is: Add a subsystem (absorber) to the vibration system (main vibration system), and reasonably select the structural parameters, dynamic characteristics and subsystems of the subsystem.
  • connection form of the system makes the subsystem and the frequency of the main system coincide, the two generate resonance, the vibration energy is transferred from the main system to the subsystem, the subsystem is forced to respond and react to the main system, and the vibration state of the main system is changed. Damping purpose.
  • the rotating machine rotor Since the frequency of the TMD subsystem must be the same or very close to the frequency of the main system to reduce the vibration, the rotating machine rotor has the characteristics of various vibration frequency changes and frequent changes throughout the operation.
  • the working speed is about 3000r/min
  • the first-order critical speed is about 1750 r/min
  • the vibration at the critical speed is 29Hz when the rotor is overcritical
  • the vibration corresponds to the frequency under the working speed when the rotor is stable. 50Hz
  • shafting misalignment vibration causes twice the frequency of the working speed, 100Hz
  • TMD frequency conversion devices for stationary equipment or structures are as follows: Li Jianfeng et al. studied the mechanical frequency shifting in "Active Frequency Shift Dynamic Vibration Absorber” (Experimental Mechanics, Vol. 20, No. 4, pp. 507-514). Dynamic vibration absorber, through The motor-driven screw changes the span between the two elastic rods to change the stiffness of the tuning quality subsystem, realizes the frequency change, and applies for a patent (CN1978939A); Sun Wanquan et al., "Semi-active control of TMD based on shape memory alloy” (Harbin Industry) Journal of University Journal, Vol.41, No.6, pp.
  • TMD dampers to textile machinery high-speed winders and applied for invention patents (CN202048137U).
  • the damper can reduce the vibration response of the bobbin during the operation of the winder, but only has a damping effect corresponding to the frequency at the working speed, and does not adapt to the frequency change of the rotor system.
  • Song Fangqi et al. “Methods for Controlling Multi-Frequency Unbalance Response of Rotors Using Electromagnetic Suspension Dynamic Vibration Absorbers” (Mechanical Science and Technology, Vol. 23, No. 2, pp. 170-173, 2004). Controlling Electromagnetic Suspension Dynamic Vibration Absorbers by Controlling Electromagnetic Forces The stiffness thus changes its frequency to account for changes in the rotor system frequency and is patented (CN201078433Y).
  • the present invention maintains the frequency of the TMD subsystem consistent with the frequency of the main rotor system through the online real-time continuous adjustment of the quality, and is unique to the design.
  • the structure meets the demand of the current rotating machinery rotor for the vibration of various frequency components to form a continuous real-time vibration suppression.
  • a rotary mechanical rotor hydraulic multi-frequency dynamic vibration absorber the device comprises a connection transfer mechanism, an adjustable tuning quality mechanism and a control system.
  • connection transmission mechanism realizes the connection between the main vibration system of the rotor and the TMD subsystem, and its function is to transfer the vibration energy generated during the rotation of the rotor to the TMD subsystem without affecting the normal operation of the rotor.
  • the connecting transmission mechanism of the device comprises a bushing and a rolling bearing, the bushing is fixed at a suitable position on the rotating shaft by a set screw, and a rolling bearing is mounted thereon, and the vibration generated when the rotor is working is transmitted to the inner ring of the bearing and passes through the bearing Pass vibration to adjustable tuning quality Institution.
  • the characteristic of the connection transmission mechanism is that it does not act as a support for the rotor system, does not interfere with the normal rotation of the rotor, and at the same time can well play the role of vibration energy transfer.
  • the body of the adjustable tuning mass mechanism is a spring set and a mass.
  • the mass provides the quality of the subsystem
  • the spring group provides the stiffness of the subsystem
  • the natural frequency of the subsystem lj ⁇ , thus adjusting the mass can adjust the solidity of the subsystem
  • the mass of the device is a closed hollow hollow chamber filled with a high-density liquid medium, and connected to the pump and the circulating liquid tank through the pipeline system, and the quality of the mass chamber is changed by pumping and spraying the pump.
  • the frequency is a high-density liquid medium, and connected to the pump and the circulating liquid tank through the pipeline system, and the quality of the mass chamber is changed by pumping and spraying the pump.
  • the frequency is a closed hollow hollow chamber filled with a high-density liquid medium, and connected to the pump and the circulating liquid tank through the pipeline system, and the quality of the mass chamber is changed by pumping and spraying the pump.
  • the frequency In order to ensure that the liquid is relatively evenly distributed in the annular cavity, the circumference of the annular cavity is divided into a plurality of small closed cavities by 360°, and the number can be four, six, eight, etc., and the fluid medium adopts a high-density liquid to increase the unit volume of the closed cavity.
  • the amount of mass change, to broaden the range of frequency adjustment, the liquid in the circulating tank is enough to ensure that the liquid can be recycled.
  • the spring set of the device is also arranged in a ring shape, embedded between the outer ring of the rolling bearing and the annular mass chamber.
  • the annular mass chamber of the adjustable tunable mass mechanism of the device is connected to the pumping and spraying pump through a hose, and the pumping and discharging pump is connected with a common circulating tank.
  • the liquid pump operates to inject liquid into the annular mass chamber, the mass of the annular cavity increases, and the frequency of the subsystem decreases accordingly.
  • the frequency of the main system of the rotor rises, the corresponding rise is required.
  • the pumping pump works to extract part of the liquid in the annular mass chamber, the quality of the annular chamber decreases, and the subsystem frequency increases accordingly.
  • the natural frequency of the tuning quality subsystem is adjusted so that the frequency of the subsystem is consistent with the frequency of the main vibration system of the rotor to adapt to the frequency variation of the rotor under actual conditions.
  • the control system is used to monitor the vibration and speed of the rotor, and the mass of the annular mass chamber is adjusted to adapt to the frequency change of the rotor, thereby achieving the best damping effect.
  • the device control system includes a real-time signal acquisition and analysis system and an execution system.
  • the real-time signal acquisition and analysis system consists of a laser speedometer, an eddy current displacement sensor, a terminal block, a signal conditioning module, a data acquisition card, and a computer.
  • the laser speedometer and the eddy current displacement sensor convert the rotor speed signal and the vibration signal into an electrical signal, and the electrical signal enters the signal conditioning module through the connection terminal, and the conditioned signal is connected to the signal acquisition card, and converted into a computer identifiable number.
  • the pre-compiled control program in the computer analyzes and calculates the collected speed signal and vibration signal, determines the real-time frequency and vibration of the rotor, and combines the parameters of the annular mass chamber to calculate the mass change of the corresponding annular mass chamber.
  • the control signal is then passed to the execution system.
  • the execution system consists of a pump, a liquid pump, a circulating fluid tank, a piping system and a valve. According to the quality change given by the control signal, it is decided whether the pump is working or the pump is working and the corresponding valve is opened.
  • the system draws or injects liquid into the annular mass chamber to maintain the adjustable tuning mass mechanism at a frequency consistent with the rotor system, thereby forming a real-time continuous closed loop control loop.
  • the basic principle of vibration damping of the present invention is: Rotating mechanical rotor generates vibration of different frequencies for various reasons during operation, A suitable position of the rotor (not necessarily at the bearing support) is provided with a hydraulic multi-frequency dynamic vibration absorber, wherein the connection transmission mechanism mounted on the rotor transmits the vibration energy generated by the rotor to the adjustable tuning mass mechanism, and the adjustable tuning mass mechanism is The timing of the control system is consistent with the frequency of the main rotor system, causing resonance, and the annular mass chamber on it generates a dynamic response and reacts to the rotor main system to cancel and suppress the vibration of the rotor.
  • the invention Compared with the existing vibration damping method, the invention has the following advantages:
  • I Adapt to the vibration of various frequency components of the rotor system. If the main system of the rotor vibrates sharply in the critical speed region, the frequency of the TMD subsystem corresponding to the critical speed of the main system is required, and the vibration damping function is used to ensure the safety of the rotor. When the rotor enters the stable working phase after passing through the critical speed zone, the TMD is required. The system corresponds to the frequency at the working speed of the main system and plays a role in damping.
  • the device of the invention can flexibly adjust the frequency, adapt to the vibration of various frequency components of the rotor system, ensure the frequency consistent with the main vibration system of the rotor, and avoid the occurrence of TMD.
  • the problem of imbalance Compared with the TMD damper (CN202048137U) used for the hollow rotor of textile machinery, the device of the invention can flexibly adjust the frequency, adapt to the vibration of various frequency components of the rotor system, ensure the frequency consistent with the main vibration system of the rotor, and avoid the occurrence of TMD.
  • the problem of imbalance is flexibly adjust the frequency, adapt to the vibration of various frequency components of the rotor system, ensure the frequency consistent with the main vibration system of the rotor, and avoid the occurrence of TMD.
  • the characteristic main frequency is the frequency at the working speed during stable operation; after a period of time, the difference in elevation caused by the unit heating is easy to induce the shaft system misalignment vibration, and the characteristic main frequency rises to twice the working speed frequency; The medium vibration may cause the oil film to whirl, and the characteristic frequency drops to about half of the working speed.
  • the frequent changes of the main frequency of the rotor system also require the vibration absorber to flexibly adjust its own frequency to adapt to the complex conditions of real-time changes. Ensure that the vibration absorber works effectively.
  • the hydraulic multi-frequency dynamic vibration absorber of the invention has strong stability and high reliability, and requires no complicated electromagnetic device and power amplifier, and no signal electromagnetic interference, etc. compared with the electromagnetic suspension dynamic vibration absorber (CN201078433Y). Problem with a longer service life. At the same time, the device does not need to change the original mechanical structure, and can complete the vibration reduction transformation of large new and old equipment, especially for the mechanical equipment that is forced to stop due to excessive vibration amplitude in the current petrochemical enterprises, which can play a good role. The vibration damping effect ensures the safe operation of mechanical equipment and promptly resumes production.
  • the control system of the invention can continuously adjust the quality of the adjustable tuning quality mechanism in real time online, and the computer automatically calculates the mass change amount according to the speed signal and the vibration signal, so that the adjustable tuning quality can be adjusted in time according to the real-time change of the rotor speed and the vibration.
  • the mass of the mechanism is kept consistent with the frequency of the main rotor system to better control the vibration of the rotor.
  • a hydraulic multi-frequency dynamic vibration absorber can be installed at a suitable position on the rotor according to actual conditions and needs to achieve various purposes. If you want to achieve the purpose of protecting the bearing, you can install a hydraulic multi-frequency power absorber near the bearing; if you want to reduce the vibration at the coupling or the impeller, you can install the hydraulic multi-frequency power absorber at the corresponding position.
  • the number of vibration absorbers can be one, two or even more depending on the actual situation.
  • the installation position can be installed not only in the vicinity of the bearing and the impeller, but also in any position along the entire length of the rotor, as long as the space permits.
  • the hydraulic multi-frequency dynamic vibration absorber of the present invention has unique structure, high reliability and stable performance; no wear parts, Therefore, the maintenance is small and the service life is long; the position of the vibration absorber is flexible and the adaptability is good; the control system is excellent, and the active control is facilitated.
  • Figure 1 is a simplified diagram of the motion equation of the TMD system.
  • Figure 2 is a schematic view of the structure of the present invention in a rotor system
  • FIG. 3 is a schematic structural view of a hydraulic multi-frequency dynamic vibration absorber of the present invention
  • FIG. 4 is a block diagram of the control system of the hydraulic multi-frequency dynamic vibration absorber of the present invention
  • Figure 5 is a diagram of the closed loop control system of the present invention
  • Embodiment 6 is a schematic view of Embodiment 1.
  • Figure 7 is a schematic view of Embodiment 2
  • Figure 8 is a schematic view of Embodiment 3
  • Embodiment 9 is a schematic view of Embodiment 4.
  • Figure 10 is a schematic view of Embodiment 5
  • Fig. 2 the motor 14 is powered, and the shaft 1 is rotated by the coupling 13, which is the most basic structure in the rotary machine.
  • the rotor system support 12 generally supports the shaft 1 through bearings and bearing blocks.
  • a hydraulic multi-frequency dynamic vibration absorber is applied at a certain position, which mainly comprises a sleeve 2, a rolling bearing 3, a spring group 4, an annular mass chamber 5, a mass chamber valve 6, a pump valve 7, a pumping pump 8, and a liquid discharging pump 9. , circulating fluid tank 10 and piping system 11.
  • FIG. 3 is a schematic view showing the structure of the hydraulic multi-frequency dynamic vibration absorber.
  • the specific working process is as follows: When the rotating machine is running, the rotating shaft 1 will vibrate for various reasons, and the sleeve 2 is fixed to the rotating shaft 1 by a set screw. Upper, the rolling bearing 3 is mounted on the sleeve 2, and the sleeve 2 and the rolling bearing 3 constitute a connection transmission mechanism, which can function to transmit vibration energy without affecting the normal operation of the rotating shaft 1.
  • the tuning mass mechanism comprises a spring group and an annular mass chamber, and the spring group 4 is fixed between the outer ring of the rolling bearing 3 and the annular mass chamber 5.
  • the annular mass chamber 5 When the vibration energy is transmitted, the annular mass chamber 5 generates a forced response due to the rotor system. The same frequency, causing resonance, and reaction to the rotor system, to reduce vibration.
  • the mass adjustment system of Figure 3 operates as follows:
  • the annular mass chamber 5 of the present invention is divided into four closed chambers in the circumferential direction, each having a respective cavity valve 6 (a), 6 (b) , 6 (c) and 6 (d), and connected to the liquid pump 8 and the liquid discharge pump 9 through the piping system 11, the liquid pump 8 and the liquid discharge pump 9 are connected to the common circulating liquid tank 10, and each has a corresponding Valves 7 (a) and 7 (b). If the actual situation needs to increase the frequency of the TMD subsystem, then the ring should be reduced accordingly.
  • the liquid is withdrawn, the mass is reduced, and the frequency rises to the target frequency, the pump 8 and the associated valve are closed; otherwise, if the actual situation needs to reduce the frequency of the TMD subsystem, the quality of the annular mass chamber 5 is increased.
  • the real-time signal detection and analysis system includes a laser speedometer 15, an eddy current displacement sensor 16, a terminal 18, a signal conditioning module 19, a data acquisition card 20, and a computer 21. .
  • the laser speed measuring device 15 and the eddy current displacement sensor 16 respectively connect the rotational speed signal and the vibration signal 17 of the rotating shaft 1 to the signal conditioning module 19 through the terminal 18, and the signal conditioning module 19 rectifies, filters and amplifies the disordered signal, and extracts
  • a signal useful for analysis is sent to the data acquisition card 20, and the data acquisition card 20 converts the analog electrical signal into a digital electrical signal, and sends the signal to a control analysis system in the computer 21, and the control analysis system passes the speed signal and
  • the vibration signal is analyzed, the real-time frequency and vibration of the rotor are determined, and the mass change amount is calculated in combination with the parameters of the annular mass chamber 5 to form a control signal 22.
  • the execution system is composed of an annular mass chamber 5, a cavity valve 6, a pump valve 7, a liquid pump 8, a liquid discharge pump 9, a circulating fluid tank 10, and a piping system 11, and a control signal 22 provided by the signal detection and analysis system controls the chamber.
  • the opening and closing of the body valve 6 and the pump valve 7 determines the operation of the liquid pump 8 and the liquid discharge pump 9, and the amount of liquid in the annular mass chamber 5 is ensured, thereby adjusting the mass of the annular mass chamber 5, so that the tuning quality subsystem Maintain consistency in the frequency of the rotor system.
  • Figure 5 is a diagram of a closed loop control system of the present invention. If the laser speedometer and the eddy current displacement sensor monitor the frequency of the rotor system, the signal is sent to the computer, and the computer automatically calculates the mass increase required to adjust the frequency, forms a control signal, and turns on the spray pump under the control signal.
  • the hydraulic multi-frequency dynamic vibration absorber is installed at two different positions on the rotating shaft 1, that is, inside the two supports 12, and the vibration energy is transferred to the TMD vibration absorber.
  • the vibration of the rotating shaft 1 is reduced to achieve the purpose of protecting the bearing.
  • the two supports 12 of the rotating shaft 1 there is not enough space between the two supports 12 of the rotating shaft 1 to install the hydraulic multi-frequency dynamic vibration absorber, and the same purpose is to protect the bearing, and the two supports 12 can also be selected.
  • the outer position is installed. Although the installation position of the hydraulic multi-frequency power absorber is slightly changed, it can also protect the bearing. Therefore, the actual engineering application can flexibly select the installation position of the hydraulic multi-frequency power absorber according to the specific situation and needs.
  • the deflection at the midpoint between the two supports 12 is the largest, so the amount of unbalance here is relatively large.
  • the vibration here will also Larger, in order to reduce the vibration here, the hydraulic multi-frequency dynamic vibration absorber can be installed here.
  • the cantilever end is usually caused to vibrate greatly, so that it can be moved away from the support 12 on the rotating shaft 1, that is, the cantilever having the largest vibration amplitude.
  • the hydraulic multi-frequency dynamic vibration absorber is installed at the end to reduce the vibration of the cantilever structure rotor system and protect the rotor system from stable operation.
  • the coupling 13 causes vibrations that are not caused by moderate problems, it can be mounted on both sides of the coupling 13, that is, on two different shafts A and B.
  • the hydraulic multi-frequency dynamic vibration absorber is used to reduce the vibration caused by the misalignment of the rotating shaft A and the rotating shaft B, and the protective coupling 13 and the two rotating shafts are stably operated.
  • the flutter caused by the cutting force of the turning tool greatly affects the machining accuracy of the workpiece.
  • the feed amount is limited, which also affects the work. effectiveness.
  • the hydraulic multi-frequency dynamic vibration absorber is mounted on the outside of the chuck clamp to reduce chattering during workpiece machining and improve machining accuracy and work efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Support Of The Bearing (AREA)

Abstract

一种旋转机械转子液力多频动力吸振器，包括连接传递机构、可调式调谐质量机构和控制系统。在旋转机械转子系统的转轴外侧套有连接传递机构，包括用紧定螺钉固定在转轴（1）上的轴套（2）和安装在轴套（2）上的滚动轴承（3），可以起到传递振动能量的作用，同时又不会影响转轴的正常运转。可调式调谐质量机构包括弹簧组（4）和质量块，质量块为环形空心的密闭质量腔（5），其内充有水、油或其他一些高密度液体介质，并通过管路系统（11）与泵及循环液箱（10）连接，通过泵的抽液、喷液，改变质量腔（5）的质量从而起到调节频率的作用；弹簧组（4）环形布置，嵌在滚动轴承（3）外圈与环形质量腔（5）之间，提供调谐质量阻尼器子系统刚度；控制系统监测转子转速及振动情况，对环形质量腔（5）进行质量调节以适应转子的频率变化，使调谐质量阻尼器子系统的频率与转子主系统频率保持一致，由此达到最佳的减振效果。

Description

旋转机械转子液力多频动力吸振器
技术领域
本发明涉及一种在旋转机械中使用的转子动力吸振器， 主要用于控制风机、 压缩机、 汽 轮机、 加工机床主轴系统等旋转机械转子的振动问题， 属于振动控制技术领域。 技术背景
风机、 压缩机、 汽轮机、 燃气轮机、 加工机床等旋转机械一直都是现代大型工业的关键 设备， 高速旋转的转子作为核心部件， 其振动的大小和系统稳定性是影响旋转机械产品性能、 可靠性及使用寿命的重要因素。 因而如何减小转子系统的振动， 提高转子寿命， 保证机械设 备安全可靠运行在旋转机械的研究中具有重要意义。
调谐质量阻尼器 （TMD)， 作为一种动力吸振器， 具有结构简单， 性能稳定， 且易于实现 工程应用等优点， 已广泛应用于建筑结构、 道路桥梁、 交通工具 （舰船、 飞机、 汽车)、 工业 机械等诸多领域， 结构示意图见附图 1， 其运动方程为：
Mc + Kx + k(x - x{ ) - F sin(<¾>i) 式中： 为转子主系统质量， 为转子主系统刚度， 为 TMD子系统质量， 为 TMD子系 统刚度， 主系统在正弦扰力的作用下进行强迫振动， 则 TMD子系统的工作原理是： 在振动系 统（主振系）上附加一个子系统（吸振器）， 合理选择子系统的结构参数、 动力特性以及与主 系统的连接形式， 使子系统与主系统的频率相一致， 二者产生共振， 振动能量从主系统转移 到子系统， 子系统受迫响应并反作用于主系统， 改变主系统的振动状态， 达到减振目的。
由于 TMD子系统频率必须与主系统频率相同或非常接近才能起到减振作用， 而旋转机械 转子在整个运转过程中具有振动频率成分多样且变化频繁的特点。 以 200MW汽轮机组为例， 工作转速约为 3000r/min， 一阶临界转速约为 1750 r/min, 转子过临界时振动对应临界转速 下的频率 29Hz; 转子稳定工作时振动对应工作转速下的频率 50Hz; 轴系不对中振动造成工作 转速下频率的二倍 100Hz; 轴承油膜涡动引起的半频成分 25Hz等等。 即使在稳定的工作转速 下工作， 其转速也并非严格固定不变， 难以保证转速始终维持 3000r/min不变。 以上种种造 成转子系统频率的变化和波动， 因此就要求 TMD系统必须能够跟随转子系统频率的变化而相 应的改变自身频率， 保持与转子系统频率相一致， 这样才能发挥 TMD系统减振的作用。
目前用于静止设备或结构的 TMD变频装置有以下几种： 李剑锋等在 《主动移频式动力吸 振器》 （实验力学 2005年第 20卷第 4期第 507〜514页）研究了机械移频式动力吸振器， 通 过电机驱动螺杆改变两弹性杆之间跨距从而改变调谐质量子系统的刚度， 实现频率的变化， 并申请专利 （CN1978939A) ; 孙万泉等在 《基于形状记忆合金的 TMD半主动控制》 （哈尔滨工 业大学学报 2009年第 41卷第 6期第 164〜168页）提出了形状记忆合金 SMA-TMD振动控制装 置， 并从理论上探讨了形状记忆合金在变刚度 TMD中的应用； 康存军等在 《磁流变弹性体主 动式自调谐吸振器控制系统的研究》 （振动与冲击 2012年第 31卷第 6期第 27〜31页） 中利 用磁流变材料在外加磁场控制下产生刚度变化的特性制作调谐减振器的弹簧元件， 实现调谐 减振器频率的自适应变化； 汪志昊在其博士学位论文 《自供电磁流变阻尼减振系统与永磁式 电涡流 TMD的研制及应用》 （湖南大学 2011年） 中实验研究了永磁式电涡流 TMD， 通过悬臂 结构的长度变化改变刚度以调节频率， 通过永磁体与铜板的间距变化调节阻尼， 实现变刚度 和变阻尼的双重控制；奇瑞汽车公司的一项专利（CN201747858 )中多个质量铁块用螺栓连接， 通过质量铁块数量的变化实现频率变化， 但其无法实现连续的频率调控。
对于旋转机械中使用的 TMD装置主要有以下几种： 侯曦、 王生泽等人将 TMD减振器应用 于纺织机械高速卷绕机， 并申请发明专利（CN202048137U)。 该减振器可以减少卷绕机运转时 筒管的振动响应， 但只对应工作转速下的频率有减振作用， 不适应转子系统的频率变化。 宋 方臻等在《用电磁悬浮动力吸振器控制转子多频不平衡响应的方法》 （机械科学与技术 2004 年第 23卷第 2期第 170〜173页） 中通过控制电磁力改变电磁悬浮动力吸振器的刚度从而改 变其频率， 以应对转子系统频率的变化， 并申请专利 （CN201078433Y)。
综上所述， 目前的 TMD变频装置大多是通过刚度的变化或阻尼的变化来改变固有频率， 也有用于车辆悬挂的改变质量的变频 TMD， 但无法实现频率的实时在线连续调控， 在旋转机 械转子系统上还未见通过质量变化调节频率的 TMD装置。 针对旋转机械转子工作过程中频率 成分多样且特征主频的出现随机性较强等特点， 本发明通过质量的在线实时连续调节使 TMD 子系统的频率始终与转子主系统频率保持一致， 设计特有的结构， 以满足目前旋转机械转子 对多种频率成分振动期望形成连续实时抑振的需求。 发明内容
本发明采取如下技术方案： 一种旋转机械转子液力多频动力吸振器， 该装置包括连接传 递机构、 可调式调谐质量机构和控制系统三部分。
( 1 )连接传递机构实现转子主振系与 TMD子系统的连接， 其功能是将转子旋转过程中产 生的振动能量转移到 TMD子系统， 同时又不影响转子的正常工作。 本装置的连接传递机构包 括一个轴套和一个滚动轴承， 轴套用紧定螺钉固定在转轴的合适位置上， 并在其上安装一个 滚动轴承， 转子工作时产生的振动传递到轴承内圈， 并通过轴承将振动传给可调式调谐质量 机构。 连接传递机构的特点就是不作为转子系统的支撑， 不干扰转子的正常旋转， 同时能够 很好的起到振动能量传递转移的作用。
(2) 可调式调谐质量机构的主体为弹簧组和质量块。 质量块提供子系统的质量 ， 弹簧 组提供子系统的刚度 子系统固有频率 = lj^， 因而调节质量 可以调节子系统的固
2π Μ
有频率 /与转子主振系频率相一致， 通过动力吸振达到转子减振的目的。 本装置的质量块为 环形空心的密闭腔， 其内充有高密度液体介质， 并通过管路系统与泵及循环液箱连接， 通过 泵的抽液、 喷液， 改变质量腔的质量从而起到调节频率的作用。 为保证液体在环形腔内分布 相对均匀， 将环形腔圆周 360° 分隔为多个小封闭腔， 数量可以是 4个、 6个、 8个等， 流体 介质采用高密度液体可以提高密闭腔单位体积的质量变化量， 以拓宽频率调节的范围， 循环 液箱中的液体足够多保证液体能够循环利用。 本装置的弹簧组同样环形布置， 嵌在滚动轴承 外圈与环形质量腔之间。
(3)可调式调谐质量机构的调节。本装置可调式调谐质量机构的环形质量腔通过软管与 抽、 喷液泵连接， 抽、 喷液泵与共同的循环液箱连接。 当转子主系统频率下降， 需要相应降 低子系统的频率时， 喷液泵工作向环形质量腔内喷入液体， 环形腔质量增加， 子系统频率相 应降低； 当转子主系统频率上升， 需要相应升高子系统的频率时， 抽液泵工作将环形质量腔 内的部分液体抽出， 环形腔质量下降， 子系统频率相应提高。 由此对调谐质量子系统的固有 频率进行调节， 使子系统的频率与转子主振系频率保持一致， 以适应实际情况下转子的频率 变化。
(4)控制系统， 用来监测转子振动情况和转速， 对环形质量腔进行质量调节以适应转子 的频率变化， 由此达到最佳的减振效果。 本装置控制系统包括实时信号采集分析系统和执行 系统。 实时信号采集分析系统由激光测速仪、 电涡流位移传感器、 接线端子、 信号调理模块、 数据采集卡及计算机构成。 其中激光测速仪、 电涡流位移传感器将转子的转速信号和振动信 号转换为电信号， 电信号通过接线端子进入信号调理模块， 调理后的信号接入信号采集卡内， 转换为计算机可识别的数字信号， 计算机内事先编译好的控制程序对采集的转速信号和振动 信号进行分析计算， 确定转子的实时频率和振动大小， 结合环形质量腔的参数， 计算出相应 环形质量腔的质量变化量， 形成控制信号， 然后将控制信号传给执行系统。 执行系统由抽液 泵、 喷液泵、 循环液箱、 管路系统和阀门组成， 根据控制信号给出的质量变化情况， 决定抽 液泵工作还是喷液泵工作并打开相应阀门， 通过管路系统向环形质量腔内抽出或喷入液体， 使可调式调谐质量机构保持与转子系统相一致的频率， 由此形成实时连续闭环的控制回路。
本发明的减振基本原理是： 旋转机械转子在工作中因各种原因产生不同频率的振动， 在 转子的合适位置 （无需一定在轴承支撑处） 安装液力多频动力吸振器， 其中装在转子上的连 接传递机构将转子产生的振动能量传递给可调式调谐质量机构， 可调式调谐质量机构在控制 系统的调节下时刻与转子主系统频率保持一致， 引发共振， 其上的环形质量腔产生动力响应 并反作用于转子主系统， 抵消和抑制转子的振动。
本发明与现有的减振方法相比具有以下的优势：
一. 适应转子系统多种频率成分的振动。 如转子主系统在临界转速区振动剧烈， 就需要 TMD 子系统对应主系统临界转速下的频率， 发挥减振作用保证转子安全过临界； 转子通过临 界转速区后进入稳定工作阶段， 就需要 TMD子系统对应主系统工作转速下的频率， 发挥减振 作用。 与用于纺织机械空心转子的 TMD减振器 （CN202048137U) 相比本发明装置能够对频率 进行灵活调整， 适应转子系统多种频率成分的振动， 保证与转子主振系频率保持一致， 避免 TMD出现失调问题。
二. 适应转子系统特征主频变化频繁的复杂工况。 以汽轮机组为例， 稳定工作时特征主 频为工作转速下的频率； 一段时间后机组发热造成标高差异容易诱发轴系不对中振动， 特征 主频上升为工作转速频率的二倍； 强烈的不对中振动有可能会造成油膜涡动， 特征主频下降 到约工作转速频率的一半； 转子系统特征主频的频繁变化同样需要吸振器能够对自身频率进 行灵活调整， 适应实时变化的复杂工况， 保证吸振器能够有效工作。
三. 可靠性高。 本发明的液力多频动力吸振器具有很强的稳定性以及很高的可靠性， 与 电磁悬浮动力吸振器 （CN201078433Y) 相比， 无需复杂的电磁装置及功放， 也不存在信号电 磁干扰等问题， 具有更长的使用寿命。 同时本装置不需要改变原有的机械结构， 可以完成大 型新、 老设备的减振改造， 尤其是针对目前石化企业中一些由于振动幅值过大被迫停工的机 械设备， 能起到良好的减振效果， 保障机械设备的安全运行， 迅速的恢复生产。
四. 能够形成实时闭环连续的自适应控制。 本发明的控制系统可以使可调式调谐质量机 构的质量实时在线连续调节， 计算机根据转速信号和振动信号自动计算出质量变化量， 这样 就可以根据转子转速和振动的实时变化及时调整可调式调谐质量机构的质量， 保持与转子主 系统频率相一致， 更好的控制转子的振动。
五. 安装数量及位置灵活。 可以根据实际情况和需要， 在转子上的合适位置安装液力多 频动力吸振器， 以实现各种目的。 如希望达到保护轴承的目的， 那么可以在轴承附近安装液 力多频动力吸振器； 如希望减小联轴器或叶轮处振动， 那么可以在相应的位置安装液力多频 动力吸振器。 吸振器的安装数量根据实际情况可以是一个、 两个甚至是多个， 安装位置不仅 可以在轴承、 叶轮附近， 只要空间允许， 根据实际情况可以安装在沿转子全长的任意位置。
总之， 本发明所述的液力多频动力吸振器结构独特， 可靠性高， 性能稳定； 无磨损部件， 因此维修少、 寿命长； 吸振器施加位置灵活， 适应性好； 控制系统优良， 便于实现主动控制。 附图说明
图 1为 TMD系统运动方程简图
图 2为本发明在转子系统中的结构简图
图 3为本发明液力多频动力吸振器的结构示意图
图 4为本发明液力多频动力吸振器控制系统框图
图 5为本发明闭环控制系统图
图 6为实施例 1的示意图
图 7为实施例 2的示意图
图 8为实施例 3的示意图
图 9为实施例 4的示意图
图 10为实施例 5的示意图
图 11为实施例 6的示意图 具体实施方式
以下结合附图具体说明本发明旋转机械转子液力多频动力吸振器。 附图 2中， 电机 14提 供动力， 通过联轴器 13使转轴 1旋转， 这是旋转机械中最基本的结构。 转子系统支撑 12— 般通过轴承、 轴承座来支撑转轴 1。 在某位置施加液力多频动力吸振器， 其主要包括轴套 2、 滚动轴承 3、 弹簧组 4、 环形质量腔 5、 质量腔阀门 6、 泵阀门 7、 抽液泵 8、 喷液泵 9、 循环 液箱 10和管路系统 11。
附图 3给出了液力多频动力吸振器的结构示意图， 具体的工作过程是： 旋转机械运转时， 转轴 1由于各种原因将会产生振动， 轴套 2用紧定螺钉固定在转轴 1上， 滚动轴承 3安装在 轴套 2上， 轴套 2与滚动轴承 3组成连接传递机构， 可以起到传递振动能量的作用， 同时又 不会影响转轴 1的正常运转。 调谐质量机构包括弹簧组和环形质量腔， 弹簧组 4固定在滚动 轴承 3的外圈和环形质量腔 5之间， 当振动能量传递过来后， 环形质量腔 5产生受迫响应， 由于与转子系统的频率相同， 引发共振， 并反作用于转子系统， 起减振作用。
附图 3中质量调节系统是如下工作的： 本发明的环形质量腔 5在圆周方向上分隔成 4个 封闭腔， 每个封闭腔都有各自的腔体阀门 6 ( a)、 6 (b)、 6 ( c ) 和 6 ( d)， 并通过管路系统 11与抽液泵 8和喷液泵 9相连， 抽液泵 8和喷液泵 9连接共同的循环液箱 10， 并且各自也有 相应的阀门 7 ( a) 和 7 (b)。 若实际情况需要增大 TMD子系统的频率， 那就要相应减小环形 质量腔 5的质量， 那么根据控制信号打开阀门 6 ( a)、 6 (b)、 6 ( c ) 和 6 ( d)， 并开启抽液 泵 8和相应阀门 7 ( a), 从封闭腔中抽出液体， 质量减小， 频率升高达到目标频率后， 关闭 抽液泵 8和相关阀门； 反之若实际情况需要降低 TMD子系统的频率， 同理就要增大环形质量 腔 5的质量， 于是打开阀门 6 ( a)、 6 (b)、 6 ( c ) 和 6 ( d)， 并开启喷液泵 9和相应阀门 7 (b)， 向封闭腔中喷入液体， 质量增加， 频率降低到目标频率时， 关闭喷液泵 9和相关阀门， 完成控制操作。
附图 4为液力多频动力吸振器控制系统框图， 图中实时信号检测分析系统包括激光测速 仪 15、 电涡流位移传感器 16、 接线端子 18、 信号调理模块 19、 数据采集卡 20和计算机 21。 其中激光测速仪 15与电涡流位移传感器 16分别将转轴 1的转速信号和振动信号 17， 通过接 线端子 18接入信号调理模块 19， 信号调理模块 19将杂乱的信号进行整流、 滤波及放大， 提 取出对于分析有用的信号并送入数据采集卡 20， 数据采集卡 20将模拟电信号转换成数字电 信号， 并将信号送入计算机 21中的控制分析系统中， 控制分析系统通过对转速信号和振动信 号的分析， 确定转子的实时频率和振动， 结合环形质量腔 5的参数， 计算出质量变化量， 形 成控制信号 22。 执行系统由环形质量腔 5、 腔体阀门 6、 泵阀门 7、 抽液泵 8、 喷液泵 9、 循 环液箱 10和管路系统 11组成，信号检测分析系统提供的控制信号 22控制腔体阀门 6和泵阀 门 7的开闭并决定抽液泵 8和喷液泵 9的工作情况， 保证环形质量腔 5内的液体量， 从而调 整环形质量腔 5的质量， 使调谐质量子系统保持对转子系统频率的一致性。
附图 5为本发明闭环控制系统图。 如激光测速仪和电涡流位移传感器监测到转子系统的 频率减小， 将信号输送到计算机， 计算机自动计算出调节频率需要的质量增大量， 形成控制 信号， 在控制信号的作用下开启喷液泵和相关阀门， 向环形质量腔喷液， 当喷入液体的量达 到控制信号给定的量时， 关闭喷液泵和相关阀门， 完成频率调节； 如激光测速仪和电涡流位 移传感器监测到转子系统的频率增大， 将信号输送到计算机， 计算机自动计算出调节频率需 要的质量减小量， 形成控制信号， 在控制信号的作用下开启抽液泵和相关阀门， 将环形质量 腔内的液体抽出， 当抽出液体的量达到控制信号给定的量时， 关闭抽液泵和相关阀门， 完成 频率调节。 由此可以形成实时连续闭环的控制回路。 实施例 1
参见附图 6， 某些场合需要保护转子系统支撑 12处的轴承， 避免轴承出现损伤和破坏， 那么就需要在支撑 12附近位置安装液力多频动力吸振器。充分发挥本发明吸振器施加位置灵 活多样的优势， 在转轴 1上的两个不同位置， 即在两处支撑 12的内侧安装液力多频动力吸振 器， 将振动能量转移到 TMD吸振器上， 减小转轴 1的振动， 达到保护轴承的目的。 实施例 2
参见附图 7， 与实施例 1相比， 某些转轴 1两支撑 12之间没有足够的空间来安装液力多 频动力吸振器， 同样要达到保护轴承的目的， 也可以选择在两支撑 12的外侧位置安装。尽管 液力多频动力吸振器的安装位置略有变化， 但也可以起到保护轴承的作用， 因而实际工程应 用中可以根据具体情况和需要， 灵活选择液力多频动力吸振器的安装位置。
实施例 3
参见附图 8， 对于作用载荷对称的挠性转子， 两支撑 12之间的中点处其挠度最大， 因而 此处的不平衡量也相对较大， 当转轴 1旋转时， 此处的振动也会比较大， 为了降低此处的振 动， 可以在此处安装液力多频动力吸振器。
实施例 4
参见附图 9， 对于悬臂转子系统， 由于不平衡量以及悬臂结构的相对不稳定通常会引起 的悬臂端剧烈大幅振动， 因此可以在转轴 1上远离支撑 12的位置， 即在振动幅值最大的悬臂 末端安装液力多频动力吸振器， 以减小悬臂结构转子系统的振动， 保护转子系统稳定工作。 实施例 5
参见附图 10， 对于两转子系统或多转子系统， 由于联轴器 13造成不对中等问题引起的 振动，可以在联轴器 13的两侧，即在两根不同的转轴 A和转轴 B上安装液力多频动力吸振器， 以减小由于转轴 A和转轴 B不对中带来的振动， 保护联轴器 13和两根转轴稳定工作。
实施例 6
参见附图 11， 对于加工机床， 如车床主轴系统， 车刀对工件切削力引起的颤振会大大影 响工件的加工精度， 为了避免较大的振动， 会限制进给量， 这也影响了工作效率。 在卡盘夹 具的外侧安装液力多频动力吸振器， 可以减小工件加工时的颤振， 提高加工精度和工作效率。

Claims

WO 2014/180009 权 利 要 求 书 PCT/CN2013/076372
1、 一种旋转机械转子液力多频动力吸振器， 其特征在于： 该装置包括连接传递机构、 可调式 调谐质量机构和控制系统， 连接传递机构套置在旋转机械转子系统的转轴外侧， 可调式调谐 质量机构包括弹簧组和质量块， 其中， 质量块为环形空心密闭腔， 其内充有液体介质， 并通 过管路系统与泵及循环液箱连接； 控制系统包括实时信号采集分析系统和执行系统， 其用于 控制改变环形空心密闭腔内的液体介质的质量， 从而改变液力多频动力吸振器的固有频率。
2、 根据权利要求 1所述的旋转机械转子液力多频动力吸振器， 其特征在于： 连接传递机构包 括用紧定螺钉固定在转轴上的轴套和安装在轴套上的滚动轴承； 所述可调式调谐质量机构的 弹簧组呈环形布置， 嵌在滚动轴承外圈与环形质量腔之间。
3、根据权利要求 1所述的旋转机械转子液力多频动力吸振器， 其特征在于： 所述的环形空心 密闭腔具有在圆周方向平均分隔开的多个小封闭腔， 小封闭腔的数量可以是 4个、 6个、 8个 或多个， 使得密闭腔内的液体介质的质量在圆周方向上均匀分布。
4、根据权利要求 1所述的旋转机械转子液力多频动力吸振器， 其特征在于： 所述的环形空心 密闭腔内充有的液体介质为水、 油或者其他一些高密度液体， 采用高密度液体介质可以提高 密闭腔单位体积的质量变化量。
5、根据权利要求 1所述的旋转机械转子液力多频动力吸振器， 其特征在于： 所述的控制系的 实时信号采集分析系统由激光测速仪、 电涡流位移传感器、 接线端子、 信号调理模块、 数据 采集卡及计算机构成， 其中激光测速仪、 电涡流位移传感器固定在基础或壳体上， 垂直于转 轴， 将转轴的转速信号和振动位移信号转换为电信号并通过接线端子接入信号调理模块， 调 理后的信号接入数据采集卡内， 转换为计算机可识别的数字信号， 计算机内事先编译好的控 制程序对采集的转速信号和振动位移信号进行分析计算， 确定转子的实时频率和振动大小， 结合环形空心密闭腔的参数形成控制信号， 然后将控制信号传给执行系统。
6、根据权利要求 5所述的旋转机械转子液力多频动力吸振器， 其特征在于： 所述的控制系的 执行系统由抽液泵、 喷液泵、 循环液箱、 管路系统和阀门组成， 根据所述控制信号给出的质 量变化情况， 决定抽液泵工作还是喷液泵工作并打开相应阀门， 通过管路系统向环形空心密 闭腔内抽出或喷入液体， 使可调式调谐质量机构保持与转子系统相一致的频率， 由此形成实 时连续闭环的控制回路。
7、 一种使用权利要求 1所述的旋转机械转子液力多频动力吸振器的减振方法， 其特征在于， 将液力多频动力吸振器安装于旋转机械转子靠近支撑轴承的转轴处。
8、 一种使用权利要求 1所述的旋转机械转子液力多频动力吸振器的减振方法， 其特征在于， 将液力多频动力吸振器安装于加工机床的卡盘夹具上， 减小工件切削加工时的颤振， 提高加 工精度， 提高工作效率。
9、 一种权利要求 1所述的旋转机械转子液力多频动力吸振器的应用， 其特征在于， 该液力多 频动力吸振器可用于减小旋转机械转子轴承处的振动， 也可用于减小悬臂转子系统悬臂端的 振动， 还可用于减小双转子或多转子系统由于联轴器不对中引起的振动。
PCT/CN2013/076372 2013-05-07 2013-05-29 旋转机械转子液力多频动力吸振器 WO2014180009A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201310163488.5A CN103267085B (zh) 2013-05-07 2013-05-07 旋转机械转子液力多频动力吸振器
CN201310163488.5 2013-05-07

Publications (1)

Publication Number Publication Date
WO2014180009A1 true WO2014180009A1 (zh) 2014-11-13

Family

ID=49010730

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2013/076372 WO2014180009A1 (zh) 2013-05-07 2013-05-29 旋转机械转子液力多频动力吸振器

Country Status (2)

Country Link
CN (1) CN103267085B (zh)
WO (1) WO2014180009A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11603903B2 (en) 2020-12-21 2023-03-14 Toyota Motor Engineering & Manufacturing North America, Inc. Vibration isolation for rotating machines
US11927236B2 (en) 2020-12-21 2024-03-12 Toyota Motor Engineering & Manufacturing North America, Inc. Vibration isolation for rotating machines

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103511554B (zh) * 2013-10-17 2015-10-14 北京化工大学 一种旋转机械转子变质量调频动力吸振器
CN103659502A (zh) * 2013-12-04 2014-03-26 天水星火机床有限责任公司 双砂轮车轴磨削装置
CN103742591B (zh) * 2013-12-25 2016-01-13 北京化工大学 旋转机械转子自适应连续移频调谐质量阻尼器
CN103982635B (zh) * 2014-06-11 2017-01-04 北京化工大学 齿轮轴系减振降噪的组合阻尼装置
CN105526294B (zh) * 2016-01-20 2018-05-29 上海交通大学 基于磁激励的运动粒子吸振单元及组合装置与方法
US11686369B2 (en) * 2017-03-31 2023-06-27 Tmt Machinery, Inc. Vibration damping device and bobbin holder system
CN106904497B (zh) * 2017-04-05 2019-08-02 北京中丽制机工程技术有限公司 一种摩擦辊固有频率调节方法及装置
CN107387652B (zh) * 2017-06-05 2019-11-19 上海交通大学 一种推进轴系分布式主动减振器
CN107542628B (zh) * 2017-09-30 2020-05-08 株洲时代新材料科技股份有限公司 一种减振设备
CN108331882B (zh) * 2018-02-08 2019-12-06 东北大学 一种利用非线性能量阱机制的转子系统动力吸振器
CN108547913B (zh) * 2018-05-14 2019-08-23 东北大学 一种带变刚度杆的转子系统动力吸振器
CN108916316B (zh) * 2018-06-27 2020-09-11 东北大学 一种抑制转子系统振动的二级非线性能量阱
CN108825718B (zh) * 2018-07-19 2020-02-11 东北大学 一种抑制转子系统振动的接地式非线性能量阱
CN109654157B (zh) * 2018-12-19 2023-11-10 上海齐耀动力技术有限公司 一种外置式动平衡装置及系统
CN110259881A (zh) * 2019-06-17 2019-09-20 石家庄铁道大学 一种动力吸振器
CN110594132B (zh) * 2019-09-17 2021-05-04 万江新能源集团有限公司 一种空气源机组中间泵
CN110630475B (zh) * 2019-09-27 2023-11-24 珠海格力电器股份有限公司 一种电动车空调压缩机主动调频吸振装置及方法
CN112576457B (zh) * 2019-09-27 2022-08-26 北京金风科创风电设备有限公司 调频阻尼器、风力发电机组及调频阻尼器的调频方法
CN112555289B (zh) * 2020-12-08 2022-02-22 宁波捷成轴业有限公司 一种用于汽车转向系统的降噪传动轴
CN113700794B (zh) * 2021-05-25 2023-03-31 北京化工大学 一种适用于转子轴承系统阻尼器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0467427A2 (en) * 1990-07-20 1992-01-22 General Motors Corporation Mass impact damper for rotors
JP2001349380A (ja) * 2000-06-09 2001-12-21 Nok Vibracoustic Kk ダンパ
CN1666035A (zh) * 2002-05-31 2005-09-07 株式会社富国 粘性阻尼器
CN101254748A (zh) * 2007-02-27 2008-09-03 汽车配件控股有限责任公司 用于传动轴中心支撑轴承的可转动质量阻尼器
CN101639109A (zh) * 2009-08-20 2010-02-03 长安大学 一种固有频率可调的吸振装置及具有该吸振装置的发动机

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2899673B2 (ja) * 1988-05-28 1999-06-02 ナガセインテグレックス 回転体のオートバランサー用制御装置
CA2187890A1 (en) * 1994-04-18 1995-10-26 Ming-Lai Lai Tuned mass damper
CN102183338A (zh) * 2011-01-18 2011-09-14 西安交通大学 一种用于高转速的注液式在线动平衡头结构
CN102758874B (zh) * 2012-07-17 2014-10-15 北京化工大学 旋转机械转子多频率成分振动自适应变阻尼变刚度减振器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0467427A2 (en) * 1990-07-20 1992-01-22 General Motors Corporation Mass impact damper for rotors
JP2001349380A (ja) * 2000-06-09 2001-12-21 Nok Vibracoustic Kk ダンパ
CN1666035A (zh) * 2002-05-31 2005-09-07 株式会社富国 粘性阻尼器
CN101254748A (zh) * 2007-02-27 2008-09-03 汽车配件控股有限责任公司 用于传动轴中心支撑轴承的可转动质量阻尼器
CN101639109A (zh) * 2009-08-20 2010-02-03 长安大学 一种固有频率可调的吸振装置及具有该吸振装置的发动机

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11603903B2 (en) 2020-12-21 2023-03-14 Toyota Motor Engineering & Manufacturing North America, Inc. Vibration isolation for rotating machines
US11927236B2 (en) 2020-12-21 2024-03-12 Toyota Motor Engineering & Manufacturing North America, Inc. Vibration isolation for rotating machines

Also Published As

Publication number Publication date
CN103267085A (zh) 2013-08-28
CN103267085B (zh) 2015-12-23

Similar Documents

Publication Publication Date Title
WO2014180009A1 (zh) 旋转机械转子液力多频动力吸振器
CN103511554B (zh) 一种旋转机械转子变质量调频动力吸振器
WO2019137026A1 (zh) 一种推力轴承、转子系统及推力轴承的控制方法
CN102758874B (zh) 旋转机械转子多频率成分振动自适应变阻尼变刚度减振器
CN105443857B (zh) 一种用于阀门的变阻尼减振降噪装置
CN103742591B (zh) 旋转机械转子自适应连续移频调谐质量阻尼器
WO2019137028A1 (zh) 轴承、转子系统及轴承的控制方法
CN105526180A (zh) 磁悬浮复合分子泵
CN103471824B (zh) 一种汽轮机叶轮旋转试验平台及方法
Wenzhi et al. Active control and simulation test study on torsional vibration of large turbo-generator rotor shaft
CN108223580A (zh) 一种燃气轮机用耦合弹支油膜阻尼器轴承系统
CN208935164U (zh) 一种转子系统
CN103075420A (zh) 一种可变支点智能型径向可倾瓦滑动轴承装置
CN103143971A (zh) 一种滚珠丝杆预拉伸结构
WO2019137025A1 (zh) 一种径向轴承、转子系统及径向轴承的控制方法
CN106894851B (zh) 中心架减振调节汽轮机气封间隙的方法及减振装置
CN207906294U (zh) 一种燃气轮机用耦合弹支油膜阻尼器轴承系统
CN205217182U (zh) 一种基于磁悬浮轴承永磁同步电机的高速雾化器
CN203594785U (zh) 随动式釜用双端面机械密封
CN209294325U (zh) 一种一体化主动隔振作动器
CN104696520A (zh) 一种随动式釜用双端面机械密封
CN105363585A (zh) 一种基于磁悬浮轴承永磁同步电机的高速雾化器
CN105422732B (zh) 一种用于细长回转轴的复合阻尼减振胀棒结构
CN107591988A (zh) 一种可紧急制动的高精度永磁耦合调速器
CN204419959U (zh) 非接触式管路振动控制装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13883865

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13883865

Country of ref document: EP

Kind code of ref document: A1