WO2021135069A1 - 一种复合电磁式动力吸振器 - Google Patents

一种复合电磁式动力吸振器 Download PDF

Info

Publication number
WO2021135069A1
WO2021135069A1 PCT/CN2020/094111 CN2020094111W WO2021135069A1 WO 2021135069 A1 WO2021135069 A1 WO 2021135069A1 CN 2020094111 W CN2020094111 W CN 2020094111W WO 2021135069 A1 WO2021135069 A1 WO 2021135069A1
Authority
WO
WIPO (PCT)
Prior art keywords
mover
coil
vibration absorber
dynamic vibration
composite electromagnetic
Prior art date
Application number
PCT/CN2020/094111
Other languages
English (en)
French (fr)
Inventor
张维
李东昱
闫政涛
陈凡
杨预立
Original Assignee
中科振声（苏州）电子科技有限公司
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 中科振声（苏州）电子科技有限公司 filed Critical 中科振声（苏州）电子科技有限公司
Publication of WO2021135069A1 publication Critical patent/WO2021135069A1/zh

Links

Images

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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1005—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass
    • F16F7/1011—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass by electromagnetic means
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • 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
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on metal springs
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/0029—Location, co-location
    • 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
    • F16F2238/00—Type of springs or dampers
    • F16F2238/02—Springs
    • F16F2238/022—Springs leaf-like, e.g. of thin, planar-like metal
    • 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
    • F16F2238/00—Type of springs or dampers
    • F16F2238/02—Springs
    • F16F2238/026—Springs wound- or coil-like

Definitions

  • the invention belongs to the technical field of vibration absorption, and specifically relates to a composite electromagnetic dynamic vibration absorber.
  • Vibration absorber is widely used as a common vibration control method, and active vibration absorber, as the ultimate form of vibration absorber, can suppress vibration to the greatest extent.
  • the traditional active electromagnetic vibration absorber produces electromagnetic force mainly in the following ways: (1) Amp force type vibration absorber: Most of this type of vibration absorber has wires around the circumference, and the energized wires generate ampere force under the action of the radial magnetic field. This type of vibration absorber requires the coil to be placed between the air gap, and the coil is energized to generate ampere force in the air gap magnetic field; (2) Electromagnet type vibration absorber: energize the energized wire around the iron core to turn the iron core into an electromagnet , The electromagnet and the mover attract or repel to produce electromagnetic force.
  • the disadvantages of the active electromagnetic vibration absorbers of the above two principles are as follows.
  • the electromagnetic output force density is relatively small, and it cannot generate enough electromagnetic force in a limited space.
  • the reason is that there is a contradiction between the air gap magnetic field strength and the coil space: for example, an electromagnetic electromechanical coupling circuit tuned vibration absorber disclosed in Chinese invention patent CN107339352B, the coil is installed in the air gap between the housing and the mover, if the number of coil turns is increased Therefore, the output force is increased. The more the number of turns, the greater the radial width of the coil, the larger the air gap will inevitably be.
  • the increase of the air gap will weaken the strength of the air gap magnetic field, which will weaken the output force; if the air gap is increased by reducing the air gap
  • the strength of the magnetic field will increase the output force, which will inevitably compress the installation space of the coil, forcing the reduction of the number of coil turns, thereby reducing the coil flow area, and weakening the output force instead.
  • the number of coil layers of this type of vibration absorber is often 1-3. Therefore, electromagnetic vibration absorbers that mainly generate ampere force are often relatively large in size and have a relatively large output force volume density. small.
  • the distance between the permanent magnet and the electromagnet will change with the displacement of the mover, so the output force will change with the change of the mover; on the other hand, in order to ensure that the permanent magnet does not collide with the electromagnet, the permanent magnet will not collide with the electromagnet.
  • the magnet and the electromagnet need to ensure a large gap, which will also lead to a reduction in output force.
  • Another example is an electromagnetic active vibration absorber disclosed in Chinese Patent Document CN106641087B.
  • the technical problem to be solved by the present invention is that the existing ampere force type vibration absorber or electromagnet type vibration absorber cannot balance the output force density and the output force linearity.
  • the present invention provides a composite electromagnetic dynamic vibration absorber, including
  • the vibration absorber unit includes:
  • Two cover plates are arranged opposite to each other and cover both ends of the housing, and enclose an installation cavity with the housing;
  • the mover is installed in the installation cavity; the mover includes:
  • Three mover iron cores and two main permanent magnets, the mover iron cores and the main permanent magnets are sequentially spaced apart;
  • a vibration guide assembly the mover is mounted in the installation cavity coaxially with the housing through the vibration guide assembly;
  • the coil is wound between the housing and the mover
  • the coil groove is opened on the inner wall surface of the housing around the mover; when the mover is in the equilibrium position, along the axial direction of the mover, the edge of the upper notch of the coil groove is located above the Between the N-pole surface and the S-pole surface of the main permanent magnet; the lower notch edge of the coil slot is located between the N-pole surface and the S-pole surface of the main permanent magnet below;
  • the coil is fixedly installed in the coil slot
  • the housing is made of soft magnetic material.
  • the coil fills the coil slot, and the side surface of the coil facing the mover is flush with the inner wall surface of the housing.
  • the axial cross section of the coil groove is square.
  • At least two secondary permanent magnets are respectively fixed on the end faces of the mover cores located at both ends of the mover facing the cover plate;
  • the adjacent secondary permanent magnets and the main permanent magnets are arranged opposite to each other with the same pole.
  • the outer diameter of the secondary permanent magnet is the same as the outer diameter of the mover core.
  • a retaining ring is fixed on the outer circumference of any of the main permanent magnets.
  • Any one of the mover cores and the main permanent magnet of the reinforced retaining ring have the same outer diameter.
  • vibration guide components includes:
  • the limit part is arranged on the mover coaxially with the mover;
  • One end of the elastic member is fixed on the inner wall of the installation cavity, and the other end is fixed on the limiting part.
  • At least two linear bearings coaxial with the mover and fixedly mounted on the mover cores at both ends of the mover;
  • the guide rod penetrates the mover along the central axis of the mover, and its two ends are respectively connected to the cover plates on two opposite sides;
  • the mover is slidably mounted on the guide rod through the linear bearing.
  • Any one of the limiting portions is a first groove, which is opened on the end surface of the mover facing the cover plate;
  • Any one of the elastic members is a compression spring
  • a second groove is formed on the cover plate corresponding to the first groove
  • Both ends of the compression spring are respectively fixed in the first groove and the second groove.
  • Any one of the limiting parts is a flange; the flange is fixed on the mover;
  • Any one of the elastic members is at least one leaf spring, which is evenly distributed along the circumference of the flange;
  • One end of any one of the leaf springs is fixed on the flange, and the other end is fixed on the inner wall of the installation cavity.
  • the leaf spring has a circular ring shape, the inner ring edge of the circular ring shape is fixed on the flange, and the outer ring edge is fixed on the inner wall of the installation cavity.
  • Any one of the mover core and the outer shell is made of silicon steel sheets stacked or wound.
  • a heat sink is installed on the mover core located in the middle.
  • the installation cavity is filled with grease.
  • the outer shell is made of soft magnetic material
  • the inner wall of the outer shell surrounds the mover in the installation cavity to open a coil slot, when the mover is in the equilibrium position, along the mover In the axial direction, the upper slot edge of the coil slot is located between the N pole surface and the S pole surface of the upper main permanent magnet; the lower slot edge of the coil slot is located between the N pole surface and the S pole surface of the lower main permanent magnet;
  • the coil is fixedly installed in the coil slot.
  • the shell forms an electromagnet, which generates an interaction force with the mover. For example, when the coil passes a forward current, the mover receives a downward electromagnetic force.
  • the wire in the middle of the coil is affected by the magnetic field inward in the radial direction.
  • the coil will receive an upward ampere force.
  • the mover will receive a downward reaction force. That is, when the coil passes forward current, the mover will receive downward electromagnetic force and ampere force at the same time. When the coil passes reverse current, the mover will receive upward electromagnetic force and ampere force at the same time. When a single-frequency harmonic current occurs, the mover will receive a single-frequency force.
  • the mover is excited by electromagnetic force and responds to the inertial force in the spring-vibrator-damping system as the output force of the active vibration absorber to counteract the vibration of the equipment.
  • a composite electromagnetic dynamic vibration absorber provided by the present invention, the coil is installed in the coil slot, and the inner wall surface of the coil is flush with the inner wall surface of the housing, and the air gap between the inner wall surface of the housing and the circumferential wall surface of the mover can be Adjust to the minimum to increase the strength of the air gap magnetic field to increase the output force density.
  • a vibration guide assembly is arranged between the mover cores at both ends of the mover and the opposite cover plate, and any vibration guide assembly is suitable for applying the movement along the shell axis
  • the elastic biasing force of the forward movement restricts the movement of the mover to the axial direction of the housing through the vibration guide assembly, which ensures the linearity of the output force.
  • auxiliary permanent magnets are respectively arranged on the end faces of the mover iron cores at both ends of the mover facing the cover plate, that is, the upper mover iron core is sandwiched between the upper main permanent magnets Between the secondary permanent magnet and the secondary permanent magnet, the lower mover core is sandwiched between the lower main permanent magnet and the secondary permanent magnet.
  • the main permanent magnet and the secondary permanent magnet are arranged opposite to each other to form a magnetic field barrier, avoiding the magnetic field at the upper and lower ends of the mover. Leakage increases the strength of the magnetic field.
  • Figure 1 is a schematic structural diagram of Embodiment 1 of the composite electromagnetic dynamic vibration absorber of the present invention
  • Embodiment 2 is a schematic structural diagram of Embodiment 2 of the composite electromagnetic dynamic vibration absorber of the present invention
  • Figure 3 is a schematic diagram of the mover structure of the composite electromagnetic dynamic vibration absorber of the present invention.
  • Figure 4 is a schematic diagram of a local magnetic circuit in the composite electromagnetic dynamic vibration absorber of the present invention.
  • This embodiment provides a composite electromagnetic dynamic vibration absorber, which includes a housing 1, two cover plates 2, a mover, a vibration guide assembly, a coil 5, and a coil slot 11.
  • the two cover plates 2 are an upper cover plate and a lower cover plate.
  • the cover plate 2 is a flat plate structure.
  • the housing 1 is closed in the circumferential direction and has an open structure at both ends.
  • the upper cover plate and the lower cover plate are sealed and arranged on the housing respectively. 1
  • a closed installation cavity is enclosed with the housing 1.
  • the upper and lower openings of the housing 1 are provided with stepped surfaces respectively, and the corresponding two cover plates are provided with matching steps in the circumferential direction. The two stepped surfaces are attached together to form a seal.
  • the housing 1 is made of soft magnetic material.
  • the cover plate 2 can also be provided with mounting holes to facilitate the installation of various adapters and sensors.
  • One of the cover plates 2 is also provided with an assembling part, and assembling holes 22 are provided on the assembling part, which is convenient for installing the vibration absorber on other equipment to counteract the vibration of the equipment.
  • the mover is composed of three mover iron cores 3, two main permanent magnets 4, and at least two auxiliary permanent magnets 6.
  • the mover iron core 3, the main permanent magnet 4 and the auxiliary The permanent magnets 6 are of cylindrical structure, that is, the shaft section is square.
  • the two main permanent magnets 4 are respectively installed between the two mover cores 3, and the outer circumference of the two main permanent magnets 4 is fixedly installed with a retaining ring 41, the retaining ring 41 is made of non-magnetic material to avoid the influence of the magnetic field on the outer edge of the main permanent magnet 4 on the magnetic field of the energized coil.
  • two auxiliary permanent magnets 6 are provided, and the two auxiliary permanent magnets 6 are respectively fixed on the two movers.
  • the outer end surface of the mover iron core 3 at the end, as shown in Figure 3, the mover from top to bottom is: the upper secondary permanent magnet 6, the upper mover iron core 3, the upper main permanent magnet 4, the middle mover iron core 3.
  • Four auxiliary permanent magnets can also be arranged, which are attracted and stacked together, and fixed on the outer end surfaces of the mover core 3 at both ends of the mover, depending on specific needs.
  • the outer diameters of the mover iron core 3, the auxiliary permanent magnet 6 and the retaining ring 41 are the same, the upper auxiliary permanent magnet 6, the upper mover iron core 3, the upper main permanent magnet 4, the middle mover iron core 3, and the lower main permanent magnet 4 ,
  • the lower mover iron core 3, the lower auxiliary permanent magnet 6 and the retaining ring 41 are connected as a whole by screws or glue, and the mover is cylindrical in shape, which is suitable for reducing the damping of the mover.
  • the adjacent secondary permanent magnet 6 is opposite to the main permanent magnet 4, and the magnetic poles between the two main permanent magnets 4 are opposite to each other. As shown in FIG. 3, the polarity of the lower end surface of the upper secondary permanent magnet 6 is the same as that of the upper main permanent magnet 4.
  • the upper end faces have the same polarity, for example, both are N poles; the polarity of the lower end face of the upper main permanent magnet 4 is the same as the upper end face of the lower main permanent magnet 4, both are S poles; the poles on the lower end face of the lower main permanent magnet 4 The polarity is the same as the polarity of the upper end surface of the lower secondary permanent magnet 6 and both are N poles.
  • the secondary permanent magnet 6 and the main permanent magnet 4 have the same poles to form a magnetic field barrier.
  • the secondary permanent magnets 6 at both ends avoid the leakage of the magnetic field at the upper and lower ends of the mover and increase the magnetic field strength.
  • Both the mover core 3 and the shell 1 are made of materials with high permeability and low conductivity, such as soft magnetic materials.
  • the mover core 3 and the shell 1 are made of silicon steel sheets stacked or wound. , It can also be made from a whole piece of silicon steel by machining.
  • a heat sink (not shown in the figure) is added to the mover core 3 located in the middle to facilitate heat dissipation.
  • Through holes (not shown in the figure) can be provided on the mover to facilitate adjustment of mover damping. Of course, in order to ensure the greater mass of the mover, the number of through holes is determined according to specific needs.
  • the mover is restricted in the installation cavity by a vibration guide assembly.
  • Two sets of vibration guide assemblies are provided.
  • the two sets of vibration guide assemblies are respectively arranged between the two ends of the mover and the corresponding cover plate 2.
  • the vibration guide assembly includes a limit part and an elastic part.
  • the limiting portion is a first groove 71
  • the auxiliary permanent magnet 6 is in an annular shape as a whole
  • the first groove 71 is enclosed between the annular inner ring and the upper surface of the upper mover iron core 3
  • a second groove 21 is opened on the inner wall of the cover plate 2 directly opposite to the first groove 71.
  • the elastic member adopts a compression spring 72.
  • the two ends of the compression spring 72 are respectively fixedly installed in the first groove 71 and the second groove.
  • the compression springs 72 at both ends have an elastic biasing force on the mover along the axial direction of the mover.
  • the guide rod 82 is coaxially pierced on the mover.
  • the two ends of the guide rod 82 are respectively fixed on the cover plate 2 at both ends.
  • the linear bearings 81 are respectively fixed on the upper mover iron core 3 and the lower mover iron core 3, and the mover
  • the upper and lower linear bearings 81 are slidably arranged on the guide rod 82.
  • the linearity of the output force is ensured through the limit of the limit part and the guide rod 82.
  • the upper main permanent magnet 4, the central mover core 3 and the lower main permanent magnet 4 and the guide rod 82 are spaced apart, and there is oil 10 in the space.
  • the inner wall of the housing 1 has a coil slot 11 around the mover.
  • the cross section of the coil slot 11 in the axial direction of the mover is rectangular, and the edge of the upper slot of the coil slot 11 Located between the N pole surface and the S pole surface of the upper main permanent magnet 4, the lower slot edge of the coil slot 11 is located between the N pole surface and the S pole surface of the lower main permanent magnet 4, and the coil 5 is filled with the coil slot 11 and fixed In the coil slot 11, and the ring structure enclosed by the coil 5 faces the inner side of the mover and is flush with the inner wall surface of the housing 1. Since the housing 1 is made of soft magnetic material, it is shared with the coil 5 embedded on it. The stator is formed and interacts with the mover. The air gap between the inner wall surface of the housing 1 and the circumferential wall surface of the mover can be adjusted to a minimum, and the strength of the air gap magnetic field is increased to increase the output force density.
  • the installation cavity is filled with grease 9.
  • the grease 9 can better transfer the heat generated by the mover when the vibration absorber is working to the housing 1; second, the grease 9 It can play a good lubrication effect on the linear bearing 81; thirdly, the grease 9 provides fluid resistance when the mover moves up and down to provide necessary damping for the vibration absorber.
  • the output principle of the composite electromagnetic dynamic vibration absorber in this embodiment is formed by the superposition of electromagnetic force and ampere force.
  • the N poles of the upper secondary permanent magnet 6 and the lower primary permanent magnet 4 are set downward, and the N poles of the upper primary permanent magnet 4 and the lower secondary permanent magnet 6 are set upward.
  • the upper mover core 3 and the lower The outer edge of the mover core 3 induces an "N" pole (as shown in Figure 4). Since the edge of the upper notch of the coil slot 11 is located below the lower surface of the upper mover iron core 3; the "N" pole of the outer edge of the upper mover iron core 3 is attracted by the "S" pole of the upper part of the coil slot 11, and the mover produces a downward movement. Electromagnetic force component. The edge of the lower notch of the coil slot 11 is located above the upper surface of the lower mover iron core 3.
  • the "N" pole of the outer edge of the lower mover iron core 3 is repelled by the "N" pole at the lower part of the coil slot 11, and the mover generates downward electromagnetic waves. Force component. Therefore, when the coil 5 passes a forward current, the mover receives a downward electromagnetic force. At the same time, the wire in the middle of the coil 5 is affected by the radially inward magnetic field. According to the left-hand rule, the coil 5 will receive an upward ampere force. According to Newton's third law, the mover will receive a downward reaction force. In summary, when the coil 5 passes a forward current, the mover will simultaneously receive a downward electromagnetic force and ampere force.
  • the mover When the coil 5 passes a reverse current, the mover will receive an upward force, so the coil 5 passes a certain In the case of single-frequency harmonic current, the mover will receive a single-frequency force.
  • the mover As the mass of the active vibration absorber, the mover is excited by electromagnetic force and responds to the inertial force in the spring-vibrator-damping system as the output force of the active vibration absorber to counteract the equipment vibration.
  • the secondary permanent magnets 6 at both ends may not be provided.
  • the grease 9 may not be provided in the installation cavity.
  • This embodiment provides a composite electromagnetic dynamic vibration absorber.
  • the limit part in the vibration guide assembly adopts a flange 73, which is coaxial. Pass through the guide rod 82 and fixed on the mover core 3 at both ends of the mover. Flanges 73 are located in the inner rings of the secondary permanent magnets 6 at both ends.
  • the elastic parts are plate springs 74 which are symmetrically distributed about the flanges 73.
  • the leaf spring 74 has a circular ring shape, the inner ring edge of the circular ring shape is fixed on the outer peripheral surface of the flange 73, and the outer ring edge is fixed on the inner step of the seal between the cover plate 2 and the housing 1, and the mover When in a balanced state, the surface of the leaf spring 74 is arranged perpendicular to the axial direction of the mover.
  • the guide rod 82 and the two linear bearings 81 located on the upper mover core 3 and the lower mover core 3 may not be provided, and only the plate spring 74 and the method are used.
  • the Lan 73 concentric limit ensures the linearity of the mover's movement.
  • the shape of the leaf spring 74 may be a fan shape, and multiple fan-shaped leaf springs 74 are provided, and any fan-shaped leaf spring 74 is radiated and distributed along the flange 73 toward the housing 1, for example, a fan shape
  • the leaf spring 74 can be provided with four, eight, nine, ten, etc., evenly distributed in the circumferential direction of the flange 73, and one end is fixed on the flange 73 and one end is fixed on the inner wall of the installation cavity.
  • a single fan-shaped leaf spring The area of 74 and the number of settings only need to meet a certain mechanical strength, depending on specific needs.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)

Abstract

一种复合电磁式动力吸振器，外壳（1）采用软磁材料制成，线圈槽（11）开设在外壳的内壁面上，动子处于平衡位置时，沿动子的轴向，线圈槽的上方槽口边缘位于上方主永磁体（4）的N极表面与S极表面之间，线圈槽的下方槽口边缘位于下方主永磁体的N极表面与S极表面之间；线圈（5）安装在线圈槽内，在线圈通正向电流时，动子受到向下的电磁力。同时，在线圈中间部分导线受到沿径向朝里的磁场的影响，根据左手定则，线圈会受到向上的安培力，根据牛顿第三定律，动子会受到一个向下的反作用力。即当线圈通正向电流时，动子同时会受到向下的电磁力和安培力，当线圈通反向电流时，动子同时会受到向上的电磁力和安培力，通过电磁力和安培力共同作用抵消振动。

Description

一种复合电磁式动力吸振器 技术领域
本发明属于吸振技术领域，具体涉及一种复合电磁式动力吸振器。
背景技术
在众多工业领域，机械振动是一种不可忽视的工程问题。吸振器作为一种常用的振动控制手段被广泛应用，而主动式吸振作为吸振器的终极形式，可以最大程度抑制振动。
传统的主动式电磁吸振器产生电磁力的方式主要是：(1)安倍力型吸振器：此类吸振器大多导线周向环绕，通电导线在径向磁场的作用下产生安培力。此类吸振器，需要将线圈置于气隙间，线圈通电在气隙磁场中产生安培力；(2)电磁铁型吸振器：给围绕铁芯的通电导线通电，使铁芯变成电磁铁，电磁铁与动子吸引或排斥产生电磁力。上述两种原理的主动式电磁吸振器各存在弊端如下。
对于安培力型吸振器而言，其缺点是电磁输出力密度相对较小，不能在有限的空间产生足够的电磁力。原因是气隙磁场强度与线圈空间之间存在矛盾：如中国发明专利CN107339352B公开的一种电磁机电耦合电路调谐吸振器，线圈安装在外壳与动子之间的气隙中，若提高线圈匝数从而提高输出力，匝数越多线圈的径向宽度越大，则气隙势必变大，气隙增大导致气隙磁场强度变弱，反而削弱输出力；若通过减小气隙提高气隙磁场强度从而提高输出力，势必会压缩线圈的安装空间，迫使减少线圈匝数，从而减小线圈过流面积，反而削弱输出力。实际应用中，为保证足够的气隙磁场强度，此类吸振器线圈层数往往在1-3层，因此对于产生安培力为主的电磁吸振器，往往体积相对较大，输出力体积密度较小。
对于电磁铁型吸振器而言，虽然其电磁输出力密度相较于上述原理电 磁吸振器而言较大，但其输出力往往会随动子位移的变化而变化，这会导致电磁力输出线性度较差(当给吸振器通单频电流时，吸振器输出力会产生谐波)。这往往直接影响振动主动控制的效果，甚至导致控制失败。如中国专利文献CN108916301B公开的一种电磁式主动控制吸振器中动子电磁铁与定子永磁铁作用原理。一方面，其永磁铁与电磁铁间距离会随着动子的位移变化而变化，因此输出力会随动子的变化而变化；另一方面，为保证永磁铁与电磁铁不碰撞，其永磁铁与电磁铁需要保证较大的间隙，这还会导致输出力减小。又如中国专利文献CN106641087B公开的一种电磁式主动吸振器，当动子偏离中心平衡位置越大时，定子对动子的作用力就越强，这会造成一定程度的非线性性，当吸振器工作电流较大、工作频率较低时，此非线性性体现的愈加明显，这限制了此类作动器的下限工作频率。
发明内容
因此，本发明所要解决的技术问题在于现有的安培力型吸振器或电磁铁型吸振器无法兼顾输出力密度与输出力线性度。
为此，本发明提供一种复合电磁式动力吸振器，包括
所述吸振器单体包括：
外壳；
两个盖板，相对设置并罩设在所述外壳的两端，并与所述外壳围成安装腔；
动子，安装在所述安装腔内；所述动子包括：
三块动子铁芯和两块主永磁体，所述动子铁芯和主永磁体依次间隔设置；
振动导向组件，所述动子通过所述振动导向组件与所述外壳同轴安装在所述安装腔内；
线圈，绕设在所述外壳与所述动子之间；
其特征在于，
线圈槽，围绕所述动子开设在所述外壳的内壁面上；在所述动子处于 平衡位置时，沿所述动子的轴向，所述线圈槽的上方槽口边缘位于上方所述主永磁体的N极表面与S极表面之间；所述线圈槽的下方槽口边缘位于下方所述主永磁体的N极表面与S极表面之间；
所述线圈固定安装在所述线圈槽内；
所述外壳由软磁材料制成。
所述线圈充满所述线圈槽，且所述线圈朝向所述动子的侧面与所述外壳的内壁面齐平。
所述线圈槽的轴向截面为方形。
还包括：
至少两个副永磁体，分别固定在位于所述动子两端的动子铁芯朝向所述盖板的端面上；
相邻的所述副永磁体与所述主永磁体同极相对设置。
所述副永磁体的外径和所述动子铁芯的外径相同。
任一所述主永磁体的外周固定挡圈。
任一所述动子铁芯和加固挡圈的主永磁体的外径相同。
任一所述振动导向组件包括：
限位部，与所述动子同轴设置在所述动子上；
弹性件，其一端固定在所述安装腔的内壁上，另一端固定在所述限位部上。
还包括：
至少两个直线轴承，与所述动子同轴且分别固定安装在所述动子两端的所述动子铁芯上；
导杆，沿着所述动子的中心轴贯穿所述动子，且两端分别连接在相对的两侧所述盖板上；
所述动子通过所述直线轴承可滑动地安装在所述导杆上。
任一所述限位部为第一凹槽，开设在所述动子朝向所述盖板的端面上；
任一所述弹性件为压缩弹簧；
所述盖板上对应所述第一凹槽开设第二凹槽；
所述压缩弹簧的两端分别固定在所述第一凹槽和所述第二凹槽内。
任一所述限位部为法兰；所述法兰固定在所述动子上；
任一所述弹性件为至少一个板簧，沿所述法兰周向均匀分布；
任一所述板簧一端固定在所述法兰上，另一端固定在所述安装腔的内壁上。
所述板簧为圆环形，其圆环形的内圈边缘固定在所述法兰上，其外圈边缘固定在所述安装腔的内壁上。
任一所述动子铁芯与所述外壳由硅钢片堆叠或卷绕制成。
位于中间的所述动子铁芯上安装散热片。
所述安装腔内充满润滑脂。
本发明的技术方案，具有如下优点：
1.本发明提供的一种复合电磁式动力吸振器，外壳采用软磁材料制成，在外壳的内壁面上围绕安装腔内的动子开设线圈槽，动子处于平衡位置时，沿动子的轴向，线圈槽的上方槽口边缘位于上方主永磁体的N极表面与S极表面之间；线圈槽的下方槽口边缘位于下方主永磁体的N极表面与S极表面之间；线圈固定安装在线圈槽内，线圈通电时，外壳形成电磁铁，与动子之间产生相互作用力，例如，在线圈通正向电流时，动子受到向下的电磁力。同时，在线圈中间部分导线受到沿径向朝里的磁场的影响，根据左手定则可知线圈会受到向上的安培力，根据牛顿第三定律可知动子会受到一个向下的反作用力。即当线圈通正向电流时，动子同时会受到向下的电磁力和安培力，当线圈通反向电流时，动子同时会受到向上的电磁力和安培力，因此，在线圈通某一单频简谐波电流时，动子会受到一个单频的力。动子作为主动吸振器的质量块，受到电磁力激励，会在弹簧-振子-阻尼系统响应惯性力，作为主动式吸振器的输出力，从而抵消设备振动。
2.本发明提供的一种复合电磁式动力吸振器，线圈安装在线圈槽内，且线圈的内壁面与外壳的内壁面齐平，外壳内壁面与动子周向壁面之间的 气隙可以调整至最小，增大气隙磁场强度从而提高了输出力密度。
3.本发明提供的一种复合电磁式动力吸振器，在动子两端的动子铁芯与其相对的盖板之间设置振动导向组件，任一振动导向组件适于对动子施加沿外壳轴向运动的弹性偏压力，通过振动导向组件将动子的运动限制在沿外壳的轴向上，保证了输出力的线性度。
4.本发明提供的一种复合电磁式动力吸振器，在动子两端的动子铁芯朝向盖板的端面上分别设置副永磁体，即位于上方的动子铁芯夹在上方主永磁体与副永磁体之间，位于下方的动子铁芯夹在下方主永磁体与副永磁体之间，主永磁体与副永磁体同极相对设置形成磁场屏障，避免了动子上下两端的磁场泄漏，提高了磁场强度。
附图说明
为了更清楚地说明本发明具体实施方式或现有技术中的技术方案，下面将对具体实施方式或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图是本发明的一些实施方式，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本发明复合电磁式动力吸振器的实施例1结构示意图；
图2为本发明复合电磁式动力吸振器的实施例2结构示意图；
图3为本发明复合电磁式动力吸振器中动子结构示意图；
图4为本发明复合电磁式动力吸振器中局部磁路示意图。
附图标记说明：
1-外壳；11-线圈槽；2-盖板；21-第二凹槽；22-装配孔；3-动子铁芯；4-主永磁体；41-挡圈；5-线圈；6-副永磁体；71-第一凹槽；72-压缩弹簧；73-法兰；74-板簧；81-直线轴承；82-导杆；9-润滑脂；10-油液。
具体实施方式
下面将结合附图对本发明的技术方案进行清楚、完整地描述，显然， 所描述的实施例是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
在本发明的描述中，需要说明的是，术语“中心”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
在本发明的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本发明中的具体含义。
实施例1
本实施例提供一种复合电磁式动力吸振器，包括外壳1、两个盖板2、动子、振动导向组件、线圈5和线圈槽11。两个盖板2分别为上盖板和下盖板，盖板2为平板状板材结构，外壳1呈周向封闭，两端开口型结构，上盖板和下盖板分别密封罩设在外壳1两端开口上，与外壳1围成封闭的安装腔，如图1所示，外壳1上下两端开口处分别设置台阶面，对应的两个盖板2周向设置与之相匹配的台阶面，两个台阶面贴合在一起形成密封，本实施例中，外壳1由软磁材料制成。盖板2上还可以设置安装孔，以便 于安装各种转接件与传感器等。其一盖板2上还设置装配部，装配部上开设装配孔22，便于将吸振器装设到其它设备上以抵消设备振动。
如图1所示，本实施例中，动子由三块动子铁芯3、两块主永磁体4、至少两块副永磁体6组成，动子铁芯3、主永磁体4和副永磁体6均为圆柱状结构，即轴截面为方形，两块主永磁体4分别安装在两块动子铁芯3之间，两块主永磁体4的外周固定安装挡圈41，挡圈41由非导磁材料制成，避免主永磁体4外沿的磁场对通电线圈磁场的影响，本实施例中，副永磁体6设置两块，两块副永磁体6分别固定在动子两端的动子铁芯3的外端面上，如图3所示，动子自上而下依次为：上方副永磁体6、上方动子铁芯3、上方主永磁体4、中部动子铁芯3、下方主永磁体4、下方动子铁芯3、下方副永磁体6。副永磁体还可以设置四块，两两相吸叠置在一起，并固定在动子两端的动子铁芯3的外端面上，视具体需要而定。动子铁芯3、副永磁体6和挡圈41的外径相同，上方副永磁体6、上方动子铁芯3、上方主永磁体4、中部动子铁芯3、下方主永磁体4、下方动子铁芯3、下方副永磁体6及挡圈41通过螺钉或胶水连接为一个整体，动子整体呈圆柱状，适于降低动子阻尼。相邻的副永磁体6与主永磁体4、两个主永磁体4之间的磁极同极相对设置，如图3所示，上方副永磁体6下端面的极性与上方主永磁体4上端面的极性相同，例如均为N极；上方主永磁体4下端面的极性与下方主永磁体4上端面的极性相同，均为S极；下方主永磁体4下端面的极性与下方副永磁体6上端面的极性相同，均为N极。副永磁体6与主永磁体4的磁极同极相对设置形成磁场屏障，两端的副永磁体6避免了动子上下两端的磁场泄漏，提高了磁场强度。
动子铁芯3与外壳1均采用高导磁率、低导电率的材料制成，如软磁材料，本实施例中，动子铁芯3和外壳1均采用硅钢片堆叠或卷绕制成，也可以由整块硅钢通过机械加工制成。位于中部的动子铁芯3上加装散热片(图中未示出)，便于散出热量。动子上可以开设贯通孔(图中未示出)，便于调整动子阻尼，当然，为保证动子较大的质量，贯通孔开设的数量视 具体需要而定。
动子通过振动导向组件限制在安装腔内，振动导向组件设置两组，两组振动导向组件分别设置在动子两端与其对应的盖板2之间，振动导向组件包括限位部和弹性件，如图1所示，限位部为第一凹槽71，副永磁体6整体呈圆环形，圆环形内圈与上方动子铁芯3上表面之间围成第一凹槽71，与第一凹槽71正对的盖板2的内壁面上开设第二凹槽21，弹性件采用压缩弹簧72，压缩弹簧72的两端分别固定安装在第一凹槽71和第二凹槽21内，两端的压缩弹簧72对动子具有沿动子轴向的弹性偏压力。导杆82同轴穿设在动子上，导杆82两端分别固定在两端的盖板2上，直线轴承81分别固定在上方动子铁芯3和下方动子铁芯3上，动子通过上下两个直线轴承81滑动设置在导杆82上。通过限位部和导杆82的限位，保证输出力的线性度。上方的主永磁体4、中部的动子铁芯3与下方的主永磁体4与导杆82之间间隔设置，间隔腔内具有油液10。
再如图1所示，外壳1的内壁面上围绕动子开设一圈线圈槽11，本实施例中，线圈槽11在动子轴向上的截面为长方形，线圈槽11的上方槽口边缘位于上方主永磁体4的N极表面与S极表面之间，线圈槽11的下方槽口边缘位于下方主永磁体4的N极表面与S极表面之间，线圈5充满线圈槽11并固定在线圈槽11内，且线圈5围成的环状结构朝向动子的内侧面与外壳1的内壁面齐平，由于外壳1采用软磁材料制成，与嵌设在其上的线圈5共同形成定子，并与动子产生相互作用。外壳1内壁面与动子周向壁面之间的气隙可以调整至最小，增大气隙磁场强度从而提高输出力密度。
本实施例中，安装腔内充满润滑脂9，其一，相比较空气而言，润滑脂9可以更好的将吸振器工作时动子产生的热量传递至外壳1；其二，润滑脂9可以对直线轴承81起到良好的润滑作用；其三，润滑脂9在动子上下运动时提供液阻从而给吸振器提供必要的阻尼。
本实施例中的复合电磁式动力吸振器的出力原理由电磁力与安培力叠 加形成。以上方副永磁体6与下方主永磁体4的N极向下设置，上方主永磁体4与下方副永磁体6的N极向上设置。
当线圈5内导线通正向电流时(“正向”为垂直纸面向里的方向)，如图4所示，根据电磁感应定律，在中部动子铁芯3中生成感应磁场，根据右手螺旋定则，磁感线由外壳1下端发出并由上端进入。所以，线圈槽11上部形成电磁铁“S”极，线圈槽11下部形成电磁铁“N”极。对于动子，由于上方副永磁体6与下方主永磁体4的N极向下设置，上方主永磁体4与下方副永磁体6的N极向上设置，所以在上方动子铁芯3和下方动子铁芯3的外缘感应均形成“N”极(如图4所示)。由于线圈槽11的上方槽口边缘位于上方动子铁芯3下表面的下方；上方动子铁芯3外缘“N”极受到线圈槽11上部“S”极吸引，动子产生向下的电磁力分力。线圈槽11的下方槽口边缘位于下方动子铁芯3上表面的上方，下方动子铁芯3外缘“N”极受到线圈槽11下部“N”极排斥，动子产生向下的电磁力分力。因此，在线圈5通正向电流时，动子受到向下的电磁力。同时，在线圈5中间部分导线受到沿径向朝里的磁场的影响，根据左手定则可知线圈5会受到向上的安培力，根据牛顿第三定律可知动子会受到一个向下的反作用力。综上，当线圈5通正向电流时，动子同时会受到向下的电磁力和安培力，当线圈5通反向电流时，动子会受向上的力，因此在线圈5通某一单频简谐波电流时，动子会受到一个单频的力。动子作为主动吸振器的质量块，受到电磁力激励，会在弹簧-振子-阻尼系统响应惯性力，作为主动式吸振器的输出力，从而抵消设备振动。
作为实施例1的第一个可替换的实施方式，可以不设置两端的副永磁体6。
作为实施例1的第二个可替换的实施方式，安装腔内可以不设置润滑脂9。
实施例2
本实施例提供一种复合电磁式动力吸振器，与实施例1的技术方案相比，区别在于，如图2所示，振动导向组件中的限位部采用法兰73，法兰73同轴穿设在导杆82上并固定在动子两端的动子铁芯3上，法兰73位于两端副永磁体6的内圈中，弹性件采用板簧74，关于法兰73对称分布，本实施例中，板簧74为圆环形，其圆环形的内圈边缘固定在法兰73外周面上，其外圈边缘固定在盖板2与外壳1密封的内侧台阶上，动子处于平衡状态时，板簧74的表面垂直于动子的轴向设置。
作为实施例2的第一个可替换的实施方式，可以不设置导杆82和位于上方动子铁芯3与下方动子铁芯3上的两个直线轴承81，仅通过板簧74与法兰73同心限位保证动子移动的线性度。
作为实施例2的第二个可替换的实施方式，板簧74的形状可以为扇形，扇形板簧74设置多个，任一扇形板簧74沿法兰73朝向外壳1辐射分布，例如，扇形板簧74可以设置四片、八片、九片、十片等等，均匀分布在法兰73周向，且一端固定在法兰73上，一端固定在安装腔的内壁上，单个扇形板簧74的面积大小和设置的数量满足一定的机械强度即可，视具体需要而定。
显然，上述实施例仅仅是为清楚地说明所作的举例，而并非对实施方式的限定。对于所属领域的普通技术人员来说，在上述说明的基础上还可以做出其它不同形式的变化或变动。这里无需也无法对所有的实施方式予以穷举。而由此所引伸出的显而易见的变化或变动仍处于本发明创造的保护范围之中。

Claims (15)

  1. 一种复合电磁式动力吸振器，包括：
    外壳(1)；
    两个盖板(2)，相对设置并罩设在所述外壳(1)的两端，并与所述外壳(1)围成安装腔；
    动子，安装在所述安装腔内；所述动子包括：
    三块动子铁芯(3)和两块主永磁体(4)，所述动子铁芯(3)和主永磁体(4)依次间隔设置；
    振动导向组件，所述动子通过所述振动导向组件与所述外壳同轴安装在所述安装腔内；
    线圈(5)，绕设在所述外壳(1)与所述动子之间；
    其特征在于，
    线圈槽(11)，围绕所述动子开设在所述外壳(1)的内壁面上；在所述动子处于平衡位置时，沿所述动子的轴向，所述线圈槽(11)的上方槽口边缘位于上方所述主永磁体(4)的N极表面与S极表面之间；所述线圈槽(11)的下方槽口边缘位于下方所述主永磁体(4)的N极表面与S极表面之间；
    所述线圈(5)固定安装在所述线圈槽(11)内；
    所述外壳(1)由软磁材料制成。
  2. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，所述线圈(5)充满所述线圈槽(11)，且所述线圈(5)朝向所述动子的侧面与所述外壳(1)的内壁面齐平。
  3. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，所述线圈槽(11)的轴向截面为方形。
  4. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，还包 括：
    至少两个副永磁体(6)，分别固定在位于所述动子两端的动子铁芯(3)朝向所述盖板(2)的端面上；
    相邻的所述副永磁体(6)与所述主永磁体(4)同极相对设置。
  5. 根据权利要求4所述的复合电磁式动力吸振器，其特征在于，所述副永磁体(6)的外径和所述动子铁芯(3)的外径相同。
  6. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，任一所述主永磁体(4)的外周固定挡圈(41)。
  7. 根据权利要求6所述的复合电磁式动力吸振器，其特征在于，任一所述动子铁芯(3)和加固挡圈(41)的主永磁体(4)的外径相同。
  8. 根据权利要求1-7中任一项所述的复合电磁式动力吸振器，其特征在于，任一所述振动导向组件包括：
    限位部，与所述动子同轴设置在所述动子上；
    弹性件，其一端固定在所述安装腔的内壁上，另一端固定在所述限位部上。
  9. 根据权利要求8所述的复合电磁式动力吸振器，其特征在于，
    还包括：
    至少两个直线轴承(81)，与所述动子同轴且分别固定安装在所述动子两端的所述动子铁芯(3)上；
    导杆(82)，沿着所述动子的中心轴贯穿所述动子，且两端分别连接在相对的两侧所述盖板(2)上；
    所述动子通过所述直线轴承(81)可滑动地安装在所述导杆(82)上。
  10. 根据权利要求9所述的复合电磁式动力吸振器，其特征在于，任一所述限位部为第一凹槽(71)，开设在所述动子朝向所述盖板(2)的端面上；
    任一所述弹性件为压缩弹簧(72)；
    所述盖板(2)上对应所述第一凹槽(71)开设第二凹槽(21)；
    所述压缩弹簧(72)的两端分别固定在所述第一凹槽(71)和所述第二凹槽(21)内。
  11. 根据权利要求8或9所述的复合电磁式动力吸振器，其特征在于，任一所述限位部为法兰(73)；所述法兰(73)固定在所述动子上；
    任一所述弹性件为至少一个板簧(74)，沿所述法兰(73)周向均匀分布；
    任一所述板簧(74)一端固定在所述法兰(73)上，另一端固定在所述安装腔的内壁上。
  12. 根据权利要求11所述的复合电磁式动力吸振器，其特征在于，所述板簧(74)为圆环形，其圆环形的内圈边缘固定在所述法兰(73)上，其外圈边缘固定在所述安装腔的内壁上。
  13. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，任一所述动子铁芯(3)与所述外壳(1)由硅钢片堆叠或卷绕制成。
  14. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，位于中间的所述动子铁芯(3)上安装散热片。
  15. 根据权利要求1所述的复合电磁式动力吸振器，其特征在于，所述安装腔内充满润滑脂(9)。
PCT/CN2020/094111 2019-12-31 2020-06-03 一种复合电磁式动力吸振器 WO2021135069A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201911421747.3 2019-12-31
CN201911421747.3A CN110985582A (zh) 2019-12-31 2019-12-31 一种复合电磁式动力吸振器

Publications (1)

Publication Number Publication Date
WO2021135069A1 true WO2021135069A1 (zh) 2021-07-08

Family

ID=70080311

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2020/094111 WO2021135069A1 (zh) 2019-12-31 2020-06-03 一种复合电磁式动力吸振器

Country Status (2)

Country Link
CN (1) CN110985582A (zh)
WO (1) WO2021135069A1 (zh)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110985582A (zh) * 2019-12-31 2020-04-10 中科振声（苏州）电子科技有限公司 一种复合电磁式动力吸振器
CN111810757B (zh) * 2020-07-23 2022-02-22 中国核动力研究设计院 一种适用于管路减振的主动吊架装置
CN112984039A (zh) * 2021-02-24 2021-06-18 武汉理工大学 一种轴系横向振动大力值惯性式电磁主动控制装置
CN113153949B (zh) * 2021-04-19 2022-05-13 中国人民解放军国防科技大学 非线性耦合共振单元及非线性声学超材料元胞结构
CN113669404B (zh) * 2021-06-25 2022-10-21 上海工程技术大学 一种含双振子结构的磁流变弹性体复合吸振器装置
CN114110290A (zh) * 2021-11-27 2022-03-01 北京工业大学 一种非线性自调谐管路振动噪声半主动控制方法及系统
CN115473404A (zh) * 2022-09-02 2022-12-13 哈尔滨工程大学 一种新型电磁作动器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000049309A2 (en) * 1999-02-22 2000-08-24 Cooper Tire & Rubber Company Apparatus for vibrations attenuation using electronic and electromagnetic actuation
CN102705414A (zh) * 2012-05-23 2012-10-03 西安交通大学 一种圆筒式电磁阻尼器
CN103791013A (zh) * 2014-02-19 2014-05-14 哈尔滨工程大学 集成式惯性电磁作动器
CN106641087A (zh) * 2015-11-04 2017-05-10 株洲时代新材料科技股份有限公司 一种电磁式主动吸振器
CN107339352A (zh) * 2017-08-21 2017-11-10 哈尔滨工程大学 一种电磁机电耦合电路调谐吸振器
CN108343694A (zh) * 2018-03-07 2018-07-31 武汉理工大学 一种采用双环串接式永磁铁的混合型动力吸振器
CN108361307A (zh) * 2018-01-11 2018-08-03 株洲时代新材料科技股份有限公司 一种消振装置
CN108916301A (zh) * 2018-07-23 2018-11-30 武汉理工大学 一种电磁式主动控制吸振器
CN110985582A (zh) * 2019-12-31 2020-04-10 中科振声（苏州）电子科技有限公司 一种复合电磁式动力吸振器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000049309A2 (en) * 1999-02-22 2000-08-24 Cooper Tire & Rubber Company Apparatus for vibrations attenuation using electronic and electromagnetic actuation
CN102705414A (zh) * 2012-05-23 2012-10-03 西安交通大学 一种圆筒式电磁阻尼器
CN103791013A (zh) * 2014-02-19 2014-05-14 哈尔滨工程大学 集成式惯性电磁作动器
CN106641087A (zh) * 2015-11-04 2017-05-10 株洲时代新材料科技股份有限公司 一种电磁式主动吸振器
CN107339352A (zh) * 2017-08-21 2017-11-10 哈尔滨工程大学 一种电磁机电耦合电路调谐吸振器
CN108361307A (zh) * 2018-01-11 2018-08-03 株洲时代新材料科技股份有限公司 一种消振装置
CN108343694A (zh) * 2018-03-07 2018-07-31 武汉理工大学 一种采用双环串接式永磁铁的混合型动力吸振器
CN108916301A (zh) * 2018-07-23 2018-11-30 武汉理工大学 一种电磁式主动控制吸振器
CN110985582A (zh) * 2019-12-31 2020-04-10 中科振声（苏州）电子科技有限公司 一种复合电磁式动力吸振器

Also Published As

Publication number Publication date
CN110985582A (zh) 2020-04-10

Similar Documents

Publication Publication Date Title
WO2021135069A1 (zh) 一种复合电磁式动力吸振器
US5896076A (en) Force actuator with dual magnetic operation
EP2550724B1 (en) Electromechanical conversion system with moving magnets; acoustic diffuser comprising said system and a moving member that generates sound waves
JP6036143B2 (ja) 発電装置
JP6317822B2 (ja) 一自由度磁力防振装置
CN109139760B (zh) 一种正负刚度并联的准零刚度隔振器
US4542311A (en) Long linear stroke reciprocating electric machine
Palomera-Arias et al. Feasibility study of passive electromagnetic damping systems
WO2021135174A1 (zh) 一种模块化吸振器、吸振器模组及机床
US20080285788A1 (en) Electrodynamic Transducer Including a Dome with a Ferrofluid Suspension
CN109707735B (zh) 磁轴承
US8781150B2 (en) Multiple magnetic air gap motor
CN112117861B (zh) 一种飞轮储能电机
CN111828525B (zh) 一种负刚度可调的新型电磁式隔振器
CN110994932A (zh) 基于混合气隙的高频直动式力马达
CN211501437U (zh) 一种复合电磁式动力吸振器
WO2021145334A1 (ja) 磁界発生装置、及び、磁気歯車
CN211127517U (zh) 基于混合气隙的高频直动式力马达
CN111810757B (zh) 一种适用于管路减振的主动吊架装置
CN102506989B (zh) 可调磁路的速度型振动传感器
JP2016025818A (ja) 発電機
CN108343694A (zh) 一种采用双环串接式永磁铁的混合型动力吸振器
WO2021087743A1 (zh) 一种圆筒型音圈电机磁性重力补偿器及音圈电机及其组件
CN104343873B (zh) 永磁柔性阻尼组件
WO2020042399A1 (zh) 一种永磁电机

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: 20910561

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: 20910561

Country of ref document: EP

Kind code of ref document: A1