WO2020181763A1 - 电涡流调谐质量阻尼器、压缩机组件和空调器 - Google Patents

电涡流调谐质量阻尼器、压缩机组件和空调器 Download PDF

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Publication number
WO2020181763A1
WO2020181763A1 PCT/CN2019/110736 CN2019110736W WO2020181763A1 WO 2020181763 A1 WO2020181763 A1 WO 2020181763A1 CN 2019110736 W CN2019110736 W CN 2019110736W WO 2020181763 A1 WO2020181763 A1 WO 2020181763A1
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WIPO (PCT)
Prior art keywords
eddy current
damping
conductor plate
tuned mass
hole
Prior art date
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Ceased
Application number
PCT/CN2019/110736
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English (en)
French (fr)
Inventor
陈骏达
高旭
王现林
高智强
程诗
刘江驰
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of WO2020181763A1 publication Critical patent/WO2020181763A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/08—Compressors specially adapted for separate outdoor units
    • F24F1/12—Vibration or noise prevention thereof

Definitions

  • the application belongs to the technical field of air conditioning, and specifically relates to an eddy current tuned mass damper, a compressor assembly and an air conditioner.
  • the compressor is one of the core components of the air conditioner and an important source of vibration and noise outside the air conditioner.
  • the compressor vibration damping method in the prior art mainly uses a vibration damping foot pad to attenuate the vibration energy generated during the compressor working process and is transmitted to the bottom plate.
  • the vibration of the compressor itself is still obvious, and the vibration will also propagate along the path to the pipes and sheet metal parts connected to it.
  • the existing eddy current tuned mass damper has the defect that the damping cannot be adjusted, resulting in poor adaptability and general performance, and the installation of the existing eddy current tuned mass damper is limited, and usually can only perform vibrations in a specific direction. Vibration reduction, and the installation method cannot be changed according to the actual situation, so the vibration reduction adaptability is often limited and the vibration reduction effect is not good.
  • the technical problem to be solved by this application is to overcome the defect that the eddy current tuned mass damper in the prior art cannot be adjusted, resulting in poor adaptability and general performance, thereby providing an eddy current tuned mass damper, Compressor components and air conditioners.
  • This application provides an eddy current tuned mass damper, which includes:
  • the conductor plate is provided with a first through hole penetrating its two-phase back wall surface, the inner wall of the first through hole is provided with an internal thread, and the outer peripheral wall of the damping adjusting screw is provided with an external thread, and
  • the first through hole can allow the damping adjustment screw to pass therethrough, so that when the damping adjustment screw rotates, the conductor plate can be driven to move closer or away from the magnet.
  • the first end of the damping adjusting screw is connected to the first side wall of the damper housing, and the second end of the damping adjusting screw is connected to the first side wall of the damper housing.
  • the first side wall is opposite to the second side wall.
  • the position on the damping adjustment screw that matches the conductor plate is located between the first end and the second end.
  • the magnet is a permanent magnet; and/or, the damping adjustment screw is a cylinder, and when the damping adjustment screw rotates, the conductor plate can be aligned with the axis of the damping adjustment screw Consistent movement.
  • a stiffness adjustment screw is connected to the magnet, and when the damper housing includes a first side wall, the first side wall of the damper housing also penetrates through A second through hole is provided, the stiffness adjusting screw can be inserted into the second through hole, and the outer peripheral wall of the stiffness adjusting screw is provided with an external thread, and the inner peripheral wall of the second through hole is provided with The internal thread matched with the external thread of the rigidity adjusting screw enables the distance between the magnet and the first side wall to be changed when the rigidity adjusting screw rotates.
  • the damper housing when the damper housing includes a first side wall and a second side wall, it is inside the damper housing and located on the first side wall and the second side wall A guide rod is also provided in between, and a third through hole is provided on the conductor plate to penetrate through its two-phase back wall surface.
  • the guide rod can penetrate through the third through hole so that the conductor The plate can slide in the direction of the guide rod.
  • one end of the guide rod is connected to the first side wall, and the other end of the guide rod is connected to the second side wall.
  • the guide rod when the damping adjustment screw is a cylinder, the guide rod is also a cylinder, and the axis of the guide rod is parallel to the axis of the damping adjustment screw.
  • a first boss is provided at the lower end of the conductor plate and connected to the first through hole, and the first boss has a third boss that penetrates the first through hole.
  • the through hole can allow the damping adjustment screw to pass therethrough.
  • a second boss is provided at the lower end of the conductor plate and connected to the third through hole, and the second boss has a fourth boss that penetrates the third through hole.
  • the through hole can allow the guide rod to pass through.
  • This application also provides a compressor assembly, which includes the eddy current tuned mass damper described in any one of the preceding items, and also includes a compressor, and the eddy current tuned mass damper is arranged on the top and/or side of the compressor On the wall.
  • the present application also provides an air conditioner, which includes the aforementioned compressor assembly.
  • the eddy current tuned mass damper, compressor assembly, and air conditioner provided in this application have the following beneficial effects:
  • the magnet and the conductor plate inside the damper housing are made into a structure in which the spacing can be adjusted as required, and the damping of the eddy current tuned mass damper can be adjusted as required, thereby effectively improving the eddy current tuned mass damper
  • the adaptability and versatility especially the structure of the damping adjustment screw, the damping adjustment screw is inserted into the first through hole of the conductor plate, and through the threaded fit, it can make the conductor plate through the rotation of the damping adjustment screw Adjust and change the position of the conductor plate, so as to realize the movement of the conductor plate closer or away from the magnet, and realize the damping adjustment function and effect of the damper;
  • the eddy current tuned mass damper of the present application realizes the generation of non-contact damping force through the eddy current effect, which greatly enhances the service life of the damper.
  • the eddy current tuned mass damper is in a form of stepless frequency and variable damping
  • the structure can be adjusted and matched for different types of compressors; the eddy current tuned mass damper has strong robustness and can have a good damping effect for the variable frequency damping structure; the external damper structure , Simplifies assembly and subsequent maintenance work, and does not affect the working state of the compressor itself; it can absorb and consume the vibration energy of fixed-frequency and variable-frequency compressors, and suppress the vibration and noise of the compressor itself. This can make the compressor run more smoothly and improve the comfort of the air conditioner.
  • Figure 1 is a schematic diagram of the front structure of the eddy current tuned mass damper of the present application installed on a compressor (Embodiment 1);
  • Figure 2 is a schematic top view of the structure in Figure 1;
  • FIG. 3 is a schematic diagram of the front internal sectional view of the eddy current tuned mass damper in FIG. 1;
  • Figure 4 is a top structural view of Figure 3;
  • Figure 5 is a schematic diagram of the front structure of the eddy current tuned mass damper of the present application installed on the compressor (Embodiment 2);
  • Fig. 6 is a schematic top view of the structure in Fig. 5.
  • an eddy current tuned mass damper which includes:
  • the spacing between 3 can be adjusted; it also includes a damping adjustment screw 4, which can drive the conductor plate 3 to move closer or away from the magnet 2 when the damping adjustment screw 4 rotates.
  • the magnet and the conductor plate inside the damper housing are made into a structure in which the spacing can be adjusted as required, and the damping of the eddy current tuned mass damper can be adjusted as required, thereby effectively improving the adaptability of the eddy current tuned mass damper Versatility and versatility; especially the structure of the damping adjustment screw is used, the damping adjustment screw is inserted into the first through hole of the conductor plate, and through the threaded fit, the position of the conductor plate can be changed by the rotation of the damping adjustment screw Adjust and change, so as to realize the movement of the conductor plate closer to or away from the magnet, and realize the damping adjustment function and effect of the damper.
  • the eddy current tuned mass damper of the present application realizes the generation of non-contact damping force through the eddy current effect, which greatly enhances the service life of the damper.
  • the eddy current tuned mass damper has a structure with variable frequency and variable damping. It can be adjusted and matched for different types of compressors; the eddy current tuned mass damper has strong robustness and can have a good damping effect for the variable frequency damping structure; the external damper structure is simplified
  • the assembly and subsequent maintenance work will not affect the working state of the compressor itself; the vibration energy of the fixed frequency and variable frequency compressors can be well absorbed and consumed, and the vibration and noise of the compressor itself can be suppressed. Make the compressor run more smoothly and improve the comfort of the air conditioner.
  • This application designs an eddy current tuned mass damper for damping the compressor itself.
  • the action mode of the damper is that when its natural frequency is consistent with the vibration frequency of the compressor, the energy of the compressor will be transferred to the magnet inside the damper Above, the magnet and the conductor plate produce relative displacement to form an eddy current in the conductor plate, and finally the kinetic energy is converted into heat energy for dissipation, thereby suppressing the vibration of the compressor.
  • This application proposes a new type of damper structure that combines traditional tuned mass damper and eddy current energy dissipation principle for compressor vibration reduction.
  • This damper achieves the purpose of adjusting the equivalent mass and the equivalent stiffness of the damper by matching the weights of different masses to the permanent magnets and adjusting the stiffness of the adjustment screw.
  • the damping adjustment screw is used to adjust the position gap between the conductor plate and the permanent magnet to achieve the purpose of changing the eddy current damping.
  • the conductor plate 3 is provided with a first through hole 31 penetrating its two-phase back wall surface, the inner wall of the first through hole 31 is provided with internal threads, and the outer peripheral wall of the damping adjusting screw 4 is provided with Externally threaded, and the first through hole 31 can allow the damping adjustment screw 4 to pass therethrough, so that when the damping adjustment screw 4 rotates, the conductor plate 3 can be driven closer to or away from the magnet 2 exercise.
  • the structure of the damping adjustment screw is adopted, the damping adjustment screw is inserted into the first through hole of the conductor plate, and through the threaded fit, the position of the conductor plate can be adjusted and changed by the rotation of the damping adjustment screw, thereby achieving The conductor plate moves closer or away from the magnets to realize the damping adjustment function and effect of the damper.
  • the working principle of the damper the compressor 200 installed with the damper can be regarded as a two-degree-of-freedom vibration system, where the compressor 200 is the main system and the damper is its subsystem.
  • the main system works at a certain frequency. When its working frequency is consistent with the frequency of the subsystem, the vibration energy will be transferred, and the damper will absorb the vibration of the compressor 200.
  • the vibration energy will be transferred to the cantilever beam- On the magnet 2 of the mass system, the compressor 200 stops vibrating due to anti-resonance at this time, and the relative displacement between the magnet 2 and the conductor plate 3 will excite eddy currents on the conductor plate 3, thereby generating damping As a result of the force, finally, the kinetic energy of the magnet 2 will also be dissipated in the form of heat energy by the eddy current effect, thereby completing the vibration reduction work of the compressor.
  • the cantilever beam extension can be adjusted by the stiffness adjustment screw 5, so as to adjust the natural frequency of the entire cantilever beam-mass system.
  • the damping adjustment screw 4 can be adjusted to make the conductor plate 3 move up and down along the damping adjustment screw 4 and the guide rod 6 inside the damper, thereby changing the magnet 2 and the conductor plate 3 Air gap, thereby adjusting the damping force of different sizes.
  • the precise adjustment of the mass size of the mass block can be realized by replacing the mass blocks of different sizes with the gaskets of different specifications.
  • the damper housing 1 is detachable, so that the conductor plate 3 of different thickness and material can be replaced.
  • the material of the conductor plate 3 can be copper, aluminum and other metals without limitation. However, the higher the conductivity of the conductor plate, the higher the electrical conductivity. The stronger the eddy current effect, the greater the corresponding damping force.
  • the cantilever beam-mass system can also be replaced. By replacing magnets of different sizes, various dampers can be designed.
  • the shape of the damper housing 1, the internal magnet 2 and the conductor plate 3 of the damper are not fixed. It can be the cylindrical structure shown in this model, or any other structure, such as: cuboid, cube, polyhedron, etc., or even It is an irregular structure.
  • the first end of the damping adjusting screw 4 is connected to the first side wall 11 of the damper housing 1, and the second end of the damping adjusting screw 4 is connected to the damping On the second side wall 12 of the device housing 1, and the first side wall 11 is opposite to the second side wall 12.
  • This is the preferred connection method of the damping adjustment screw of the present application that is, one end is connected to the first side wall (preferably fixed), and the other end is connected to the second side wall (preferably fixed), so that the damping adjustment screw can be rotated during rotation.
  • the position of itself does not change, but simply rotates, and through this rotation, the position of the conductor plate screwed with it is moved to realize the change of the distance between the magnet and the damping adjustment.
  • the position on the damping adjusting screw 4 that matches the conductor plate 3 is located between the first end and the second end.
  • the magnet 2 is a permanent magnet; and/or, the damping adjustment screw 4 is a cylinder, and when the damping adjustment screw 4 rotates, the conductor plate 3 can interact with the damping The axis of the adjustment screw 4 moves in unison.
  • the permanent magnet can generate a constant magnetic field, which interacts with the conductor plate to generate eddy currents; the damping adjustment screw is a cylindrical body for sleeve and rotation, so that the conductor plate is sleeved on Movement occurs on the screw of the cylinder.
  • the magnet 2 is further connected with a stiffness adjustment screw 5, and when the damper housing 1 includes the first side wall 11, the first side of the damper housing 1
  • the wall 11 is also provided with a second through hole 13 therethrough, the stiffness adjusting screw 5 can be inserted into the second through hole 13, and the outer peripheral wall of the stiffness adjusting screw 5 is provided with an external thread, the The inner peripheral wall of the second through hole 13 is provided with internal threads that match the external threads of the rigidity adjusting screw 5, so that when the rigidity adjusting screw 5 rotates, the magnet 2 and the first side wall 11 The spacing can be changed.
  • the length of the section of the stiffness adjustment screw inside the damper housing can be changed, so that the natural frequency of the damper can be effectively adjusted, preferably as the screw inside the housing
  • the natural frequency decreases, and when the screw section in the casing is shortened, the natural frequency increases.
  • the application preferably adjusts the natural frequency of the damper to a value equal to or close to the vibration frequency of the compressor;
  • the structural form makes the magnet form a cantilever beam structure, which enables the damper to be effectively fixed to a suitable position, and the installation position or position of the damper can be changed as needed (for example, installed on the top of the compressor (Example 1, see Figure 1-2) or installed on the side wall of the compressor (embodiment 2, see Figure 5-6)), so that the adaptability of the damper is higher, and it can dampen resistance in multiple directions .
  • the eddy current tuned mass damper 100 of the present application is mainly composed of three parts, the damper housing 1, the cantilever beam-mass system with adjustable stiffness (including the magnet 2 and the stiffness adjustment screw 5) and the conductor plate 3, etc.;
  • the working principle of the damper the compressor 200 installed with the damper can be regarded as a two-degree-of-freedom vibration system, where the compressor 200 is the main system and the damper is its subsystem.
  • the main system works at a certain frequency. When its working frequency is consistent with the frequency of the subsystem, the vibration energy will be transferred, and the damper will absorb the vibration of the compressor 200.
  • the vibration energy will be transferred to the cantilever beam- On the magnet 2 of the mass system, the compressor 200 stops vibrating due to anti-resonance at this time, and the relative displacement between the magnet 2 and the conductor plate 3 will excite eddy currents on the conductor plate 3, thereby generating damping As a result of the force, finally, the kinetic energy of the magnet 2 will also be dissipated in the form of heat energy by the eddy current effect, thereby completing the vibration reduction work of the compressor.
  • the damper housing 1 when the damper housing 1 includes a first side wall 11 and a second side wall 12, it is inside the damper housing 1 and located between the first side wall 11 and the A guide rod 6 is also provided between the second side walls 12, and a third through hole 32 is provided on the conductor plate 3 to penetrate through its two-phase back wall.
  • the guide rod 6 can penetrate through the In the third through hole 32, the conductor plate 3 can slide along the direction of the guide rod 6.
  • the guide rod can support and guide the movement of the conductor plate.
  • the cantilever beam extension can be adjusted by the stiffness adjustment screw 5, so as to adjust the natural frequency of the entire cantilever beam-mass system.
  • the damping adjustment screw 4 can be adjusted to make the conductor plate 3 move up and down along the damping adjustment screw 4 and the guide rod 6 inside the damper, thereby changing the magnet 2 and the conductor plate 3 Air gap, thereby adjusting the damping force of different sizes.
  • the precise adjustment of the mass size of the mass block can be realized by replacing the mass blocks of different sizes with the gaskets of different specifications.
  • the optimal damping is designed by adjusting the position of the conductor plate 3, so that the damper can dampen vibration in a frequency range and has better robust performance, and when the target is fixed frequency compression
  • the conductor plate 3 is moved to the inner space of the damper farthest from the magnet 2. The bottom end is enough.
  • the damper can minimize the vibration amplitude of the compressor at the fixed frequency point, but this method reduces the robust performance of the damper, so the frequency offset of the compressor will cause the vibration reduction effect Great influence.
  • one end of the guide rod 6 is connected to the first side wall 11 and the other end of the guide rod 6 is connected to the second side wall 12.
  • This is the preferred connection form of the guide rod of the present application that is, one end is connected to the first side wall (preferably fixed), and the other end is connected to the second side wall (preferably fixed), so that the conductor plate can be connected to the first side wall and the second side wall. Guide sliding between the two side walls.
  • the guide rod 6 is also a cylinder, and the axis of the guide rod 6 is parallel to the axis of the damping adjustment screw 4.
  • This is a further preferred structural form of the guide rod of the present application.
  • the cylindrical body is convenient to be sleeved and guided, and it is convenient to make the conductor plate sleeve on the guide rod of the cylindrical body to move.
  • a first boss 33 is provided at the lower end of the conductor plate 3 and grounded to the first through hole 31, and the first boss 33 is connected to the first through hole 31.
  • the intersecting third through hole (not shown) can allow the damping adjusting screw 4 to pass therethrough.
  • the first boss is connected to the lower end of the first through hole of the conductor plate, and the first boss has a third through hole communicating with the first through hole.
  • the driving efficiency is improved.
  • the first boss and the conductor plate are integrally formed.
  • a second boss 34 is provided at the lower end of the conductor plate 3 and grounded to the third through hole 32, and the second boss 34 has a connection with the third through hole 32.
  • the intersecting fourth through hole (not shown) can allow the guide rod 6 to pass therethrough.
  • the second boss is connected to the lower end of the third through hole of the conductor plate, and the second boss has a fourth through hole that communicates with the third through hole.
  • the length of the through hole section connected with the guide rod is increased, and the guiding driving efficiency is improved.
  • the second boss and the conductor plate are integrally formed.
  • the present application also provides a compressor assembly, which includes the eddy current tuned mass damper 100 described in any one of the preceding items, and further includes a compressor 200, and the eddy current tuned mass damper is disposed on the top of the compressor 200 and / Or on the side wall.
  • the magnet and the conductor plate inside the damper housing are made into a structure in which the spacing can be adjusted as required, and the damping of the eddy current tuned mass damper can be adjusted as required, thereby effectively improving the adaptability of the eddy current tuned mass damper Versatility and versatility; especially the structure of the damping adjustment screw is used, the damping adjustment screw is inserted into the first through hole of the conductor plate, and through the threaded fit, the position of the conductor plate can be changed by the rotation of the damping adjustment screw Adjust and change, so as to realize the movement of the conductor plate closer to or away from the magnet, and realize the damping adjustment function and effect of the damper.
  • the eddy current tuned mass damper of the present application realizes the generation of non-contact damping force through the eddy current effect, which greatly enhances the service life of the damper.
  • the eddy current tuned mass damper has a structure with variable frequency and variable damping. It can be adjusted and matched for different types of compressors; the eddy current tuned mass damper has strong robustness and can have a good damping effect for the variable frequency damping structure; the external damper structure is simplified
  • the assembly and subsequent maintenance work will not affect the working state of the compressor itself; the vibration energy of the fixed frequency and variable frequency compressors can be well absorbed and consumed, and the vibration and noise of the compressor itself can be suppressed. Make the compressor run more smoothly and improve the comfort of the air conditioner.
  • the compressor eddy current tuned mass damper 100 of the present application is preferably bonded to the top surface of the compressor 200 to form a stable rigid connection.
  • the bonding position is as far away as possible from the center axis of the compressor 200, because the compressor 200 is far away from the center axis.
  • the positional vibration displacement is large, and the damper can exert the best damping effect.
  • placing the damper on the top of the compressor 200 can also suppress the vibration of the compressor in the two larger directions of tangential and radial (Example 1, Figure 1-2).
  • the present application also provides an air conditioner, which includes the aforementioned compressor assembly.
  • the eddy current tuned mass damper of the present application realizes the generation of non-contact damping force through the eddy current effect, which greatly enhances the service life of the damper.
  • the eddy current tuned mass damper has a structure with variable frequency and variable damping. It can be adjusted and matched for different types of compressors; the eddy current tuned mass damper has strong robustness and can have a good damping effect for the variable frequency damping structure; the external damper structure is simplified
  • the assembly and subsequent maintenance work will not affect the working state of the compressor itself; the vibration energy of the fixed frequency and variable frequency compressors can be well absorbed and consumed, and the vibration and noise of the compressor itself can be suppressed. Make the compressor run more smoothly and improve the comfort of the air conditioner.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

一种电涡流调谐质量阻尼器，包括：阻尼器壳体(1)，以及设置于阻尼器壳体(1)内部的磁体(2)和导体板(3)，磁体(2)和导体板(3)之间间隔设置，且磁体(2)和导体板(3)之间的间距能够进行调节；还包括阻尼调节螺杆(4)，当阻尼调节螺杆(4)旋转时能够驱动导体板(3)相对于磁体(2)做靠近或远离的运动。还提供一种包括该电涡流调谐质量阻尼器的压缩机组件和空调器。能够根据需要调节阻尼器的阻尼，有效提高电涡流调谐质量阻尼器的适应性和通用性；拥有较强的鲁棒性，可针对变频率被减振结构起到很好的减振效果；对于定频和变频压缩机的振动能量均能进行很好的吸收消耗。

Description

电涡流调谐质量阻尼器、压缩机组件和空调器
相关申请的交叉引用
本申请要求于2019年3月13日提交中国专利局，申请号为201910187850.X，申请名称为“一种电涡流调谐质量阻尼器、压缩机组件和空调器”的中国专利申请的优先权,在此将其全文引入作为参考。
技术领域
本申请属于空调技术领域，具体涉及一种电涡流调谐质量阻尼器、压缩机组件和空调器。
背景技术
压缩机是空调的核心组成部件之一，也是空调外机振动噪音的重要来源。压缩机工作时，由于其内部偏心转子的周期性运动，必然产生一定频率的振动噪音。现有技术中的压缩机减振方式，主要是通过减振脚垫衰减压缩机工作过程中产生的振动能量传递到底板。但是压缩机本身的振动仍然很明显，并且振动还会随路径向其所连接的管道，钣金件等进行传播。
专利号为CN103983054A和CN204373285U的专利均公开了一种压缩机组件及其储液器，在其储液器内部结构中设计加装一种质量调谐阻尼器装置，用以减小储液器自身的振动，从而降低空调外机的整体噪音振动。但是此申请均存在以下几点问题：(1)结构位于储液器内部，会影响储液器内部流体的走向，并由于对通道形成一定阻碍，有产生再生噪音的可能(2)阻尼器整体结构频率为定值，只能满足小范围特定频率的振动抑制，在频率波动较大(特别针对变频机)时，其减振作用并不明显甚至没有减振效果(3)阻尼器无阻尼调节装置，很难满足最优调谐质量阻尼器的设计要求(4)结构位于缸体内部，装配及后期维护保养均较困难，并且整体结构形式难以调节。
并且现有的电涡流调谐质量阻尼器存在阻尼无法调节的缺陷，导致其适应性能和通用性能较差，并且现有电涡流调谐质量阻尼器的安装受到限制、通常只能对特定方向的振动进行减振，并不能根据实际情况更改安装方式，因此减振适应性往往较为局限，减振效果不佳。
由于现有技术中的现有的电涡流调谐质量阻尼器存在阻尼无法调节、导致其适应性能和 通用性能较差，并且现有电涡流调谐质量阻尼器通常只能对特定方向的振动进行减振、减振适应性局限，减振效果不佳等技术问题，因此本申请研究设计出一种电涡流调谐质量阻尼器、压缩机组件和空调器。
发明内容
因此，本申请要解决的技术问题在于克服现有技术中的电涡流调谐质量阻尼器存在阻尼无法调节、导致其适应性能和通用性能较差的缺陷，从而提供一种电涡流调谐质量阻尼器、压缩机组件和空调器。
本申请提供一种电涡流调谐质量阻尼器，其包括：
阻尼器壳体，以及设置于所述阻尼器壳体内部的磁体和导体板，所述磁体和所述导体板之间间隔设置，且所述磁体和所述导体板之间的间距能够进行调节；还包括阻尼调节螺杆，当所述阻尼调节螺杆旋转时能够驱动所述导体板相对于所述磁体做靠近或远离的运动。
在其中一个实施例中，所述导体板设置有贯穿其两相背壁面的第一通孔，所述第一通孔内壁设置有内螺纹、所述阻尼调节螺杆外周壁设置有外螺纹，且所述第一通孔能够容许所述阻尼调节螺杆从中穿过，使得当所述阻尼调节螺杆旋转时能够驱动所述导体板相对于所述磁体做靠近或远离的运动。
在其中一个实施例中，所述阻尼调节螺杆的第一端连接于所述阻尼器壳体的第一侧壁上、所述阻尼调节螺杆的第二端连接设置于所述阻尼器壳体的第二侧壁上，且所述第一侧壁与所述第二侧壁相对。
在其中一个实施例中，所述阻尼调节螺杆上与所述导体板相配合的位置位于所述第一端和所述第二端之间。
在其中一个实施例中，所述磁体为永磁体；和/或，所述阻尼调节螺杆为圆柱体，当所述阻尼调节螺杆旋转时、所述导体板能够做与所述阻尼调节螺杆的轴线相一致的运动。
在其中一个实施例中，所述磁体上还连接设置有刚度调节螺杆，当所述阻尼器壳体包括第一侧壁时，所述阻尼器壳体的所述第一侧壁上还贯穿地设置有第二通孔，所述刚度调节螺杆能够穿设于所述第二通孔中，且所述刚度调节螺杆的外周壁设置有外螺纹、所述第二通孔的内周壁设置有与所述刚度调节螺杆的外螺纹相匹配的内螺纹，使得所述刚度调节螺杆转动时、所述磁体与所述第一侧壁之间的间距能够发生改变。
在其中一个实施例中，当所述阻尼器壳体包括第一侧壁和第二侧壁时，在所述阻尼器壳体内部、且位于所述第一侧壁和所述第二侧壁之间还设置有导杆，所述导体板上还以贯 穿其两相背壁面的方式设置有第三通孔，所述导杆能够穿设于所述第三通孔中、使得所述导体板能够沿着所述导杆的方向滑动。
在其中一个实施例中，所述导杆的一端连接于所述第一侧壁上、所述导杆的另一端连接于所述第二侧壁上。
在其中一个实施例中，当所述阻尼调节螺杆为圆柱体时，所述导杆也为圆柱体，且所述导杆的轴线与所述阻尼调节螺杆的轴线平行。
在其中一个实施例中，所述导体板的下端且与所述第一通孔相接地设置有第一凸台，所述第一凸台具有与所述第一通孔相贯通的第三通孔、能够容许所述阻尼调节螺杆从中穿过。
在其中一个实施例中，所述导体板的下端且与所述第三通孔相接地设置有第二凸台，所述第二凸台具有与所述第三通孔相贯通的第四通孔、能够容许所述导杆从中穿过。
本申请还提供一种压缩机组件，其包括前任一项所述的电涡流调谐质量阻尼器，还包括压缩机，所述电涡流调谐质量阻尼器设置于所述压缩机的顶部和/或侧壁上。
本申请还提供一种空调器，其包括前述的压缩机组件。
本申请提供的一种电涡流调谐质量阻尼器、压缩机组件和空调器具有如下有益效果：
1.本申请通过将阻尼器壳体内部的磁体和导体板制作成间距能够根据需要进行调节的结构形式，能够根据需要调节电涡流调谐质量阻尼器的阻尼，从而有效提高电涡流调谐质量阻尼器的适应性和通用性；尤其是采用阻尼调节螺杆的结构形式、将阻尼调节螺杆穿设于导体板的第一通孔中，并且通过螺纹配合，能够使得通过阻尼调节螺杆的旋转而将导体板的位置进行调节和改变，从而实现导体板相对于磁体之间做靠近或远离的运动，实现阻尼器的阻尼调节功能和效果；
2.本申请的电涡流调谐质量阻尼器通过电涡流效应，实现非接触式阻尼力的产生，大大增强了阻尼器的使用寿命，电涡流调谐质量阻尼器为无极频率可变、阻尼可变形式结构，可针对不同类型的压缩机进行调节匹配；电涡流调谐质量阻尼器拥有较强的鲁棒性，可针对变频率被减振结构起到很好的减振效果；外置式的阻尼器结构，简化了装配和后期的保养维护工作，并且不会影响压缩机本身的工作状态；对于定频和变频压缩机的振动能量均能进行很好的吸收消耗，抑制压缩机自身的振动噪音，由此可以使得压缩机运行更加平稳，提升空调舒适性。
附图说明
图1是本申请的电涡流调谐质量阻尼器安装于压缩机上的正面结构示意图(实施例1)；
图2是图1中的俯视结构示意图；
图3是图1中电涡流调谐质量阻尼器的正面内部剖视结构示意图；
图4是图3的俯视结构图；
图5是本申请的电涡流调谐质量阻尼器安装于压缩机上的正面结构示意图(实施例2)；
图6是图5中的俯视结构示意图。
图中附图标记表示为：
1、阻尼器壳体；11、第一侧壁；12、第二侧壁；13、第二通孔；2、磁体；3、导体板；31、第一通孔；32、第三通孔；33、第一凸台；34、第二凸台；4、阻尼调节螺杆；5、刚度调节螺杆；6、导杆；100、电涡流调谐质量阻尼器；200、压缩机。
具体实施方式
如图1-6所示，本申请提供一种电涡流调谐质量阻尼器，其包括：
阻尼器壳体1，以及设置于所述阻尼器壳体1内部的磁体2和导体板3，所述磁体2和所述导体板3之间间隔设置，且所述磁体2和所述导体板3之间的间距能够进行调节；还包括阻尼调节螺杆4，当所述阻尼调节螺杆4旋转时能够驱动所述导体板3相对于所述磁体2做靠近或远离的运动。
本申请通过将阻尼器壳体内部的磁体和导体板制作成间距能够根据需要进行调节的结构形式，能够根据需要调节电涡流调谐质量阻尼器的阻尼，从而有效提高电涡流调谐质量阻尼器的适应性和通用性；尤其是采用阻尼调节螺杆的结构形式、将阻尼调节螺杆穿设于导体板的第一通孔中，并且通过螺纹配合，能够使得通过阻尼调节螺杆的旋转而将导体板的位置进行调节和改变，从而实现导体板相对于磁体之间做靠近或远离的运动，实现阻尼器的阻尼调节功能和效果。
本申请的电涡流调谐质量阻尼器通过电涡流效应，实现非接触式阻尼力的产生，大大增强了阻尼器的使用寿命，电涡流调谐质量阻尼器为无极频率可变、阻尼可变形式结构，可针对不同类型的压缩机进行调节匹配；电涡流调谐质量阻尼器拥有较强的鲁棒性，可针对变频率被减振结构起到很好的减振效果；外置式的阻尼器结构，简化了装配和后期的保养维护工作，并且不会影响压缩机本身的工作状态；对于定频和变频压缩机的振动能量均能进行很好的吸收消耗，抑制压缩机自身的振动噪音，由此可以使得压缩机运行更加平稳，提升空调舒适性。
本申请设计一种针对压缩机本身减振的电涡流调谐质量阻尼器，该阻尼器作用方式为当其固有频率与压缩机的振动频率一致时，压缩机的能量将被转移到阻尼器内部磁铁上，磁铁与导体板产生相对位移而在导体板内形成电涡流，最后动能转换成热能的形式进行耗散，由此抑制压缩机的振动。
本申请提出了一种用于压缩机减振的融合传统调谐质量阻尼器及电涡流耗能原理的新型阻尼器结构。此阻尼器通过给永磁体搭配不同质量的重物、调节刚度调节螺杆的伸长量从而达到调节阻尼器等效质量及等效刚度的目的。利用阻尼调节螺杆，调节导体板与永磁体之间的位置间隙从而起到改变电涡流阻尼大小的目的。
在其中一个实施例中，所述导体板3设置有贯穿其两相背壁面的第一通孔31，所述第一通孔31内壁设置有内螺纹、所述阻尼调节螺杆4外周壁设置有外螺纹，且所述第一通孔31能够容许所述阻尼调节螺杆4从中穿过，使得当所述阻尼调节螺杆4旋转时能够驱动所述导体板3相对于所述磁体2做靠近或远离的运动。
采用阻尼调节螺杆的结构形式、将阻尼调节螺杆穿设于导体板的第一通孔中，并且通过螺纹配合，能够使得通过阻尼调节螺杆的旋转而将导体板的位置进行调节和改变，从而实现导体板相对于磁体之间做靠近或远离的运动，实现阻尼器的阻尼调节功能和效果。
阻尼器的工作原理：安装了阻尼器的压缩机200可看成一个二自由度振动系统，其中压缩机200为主系统，而阻尼器为其子系统。主系统以一定的频率进行工作，当其工作频率与子系统频率一致的时候，振动能量将会发生转移，阻尼器将会吸收压缩机200的振动，由此，振动能量将转移到悬臂梁-质量块系统的磁体2上，此时压缩机200由于受到反共振作用而停止振动，而磁体2与导体板3之间产生的相对位移又会在导体板3上激发出电涡流，从而产生阻尼力的作用，最终，磁体2的动能也将被电涡流效应以热能的形式耗散掉，从而完成对压缩机的减振工作。
为了应对不同频率的压缩机200振动，可通过刚度调节螺杆5调节其悬臂梁伸长量，从而对整个悬臂梁-质量块系统的固有频率大小进行调节。而为了设计满足最优的阻尼器减振效果，可通过调节阻尼调节螺杆4使得导体板3沿阻尼调节螺杆4和导杆6在阻尼器内部进行上下移动，从而改变磁体2和导体板3的空气间隙，由此调节不同大小的阻尼力。通过更换不同大小的质量块配合不同规格的垫片实现质量块质量大小的精确调节。
阻尼器壳体1可拆卸，由此可以更换不同厚度、材质的导体板3，导体板3的材质可以为铜、铝等多种金属，不局限，但导体板所用材质电导率越高，电涡流效应越强，相应的阻尼力也会越大。悬臂梁-质量块系统也可以进行更换，通过更换不同规格大小的磁铁可 设计多种规格的阻尼器。
阻尼器的阻尼器壳体1、内部磁体2和导体板3的形状均不定，可以为本模型所展示的圆柱体结构，也可为其他任意结构，如：长方体、正方体、多面体等，甚至可以是不规则结构。
在其中一个实施例中，所述阻尼调节螺杆4的第一端连接于所述阻尼器壳体1的第一侧壁11上、所述阻尼调节螺杆4的第二端连接设置于所述阻尼器壳体1的第二侧壁12上，且所述第一侧壁11与所述第二侧壁12相对。这是本申请的阻尼调节螺杆的优选连接方式，即一端连接于第一侧壁上(优选固定)，另一端连接于第二侧壁上(优选固定)，能够使得阻尼调节螺杆在旋转过程中本身的位置不发生变化，只是单纯的自转，而通过这种转动促使与其螺纹连接的导体板的位置发生移动，实现与磁体之间间距的改变，实现阻尼调节的作用。
在其中一个实施例中，所述阻尼调节螺杆4上与所述导体板3相配合的位置位于所述第一端和所述第二端之间。这是本申请的阻尼调节螺杆的进一步优选结构形式，即导体板位于第一端和第二端之间，这样能够使得导体板在阻尼调节螺杆的第一端和第二端之间发生移动，如图3所示优选为上下运动。
在其中一个实施例中，所述磁体2为永磁体；和/或，所述阻尼调节螺杆4为圆柱体，当所述阻尼调节螺杆4旋转时、所述导体板3能够做与所述阻尼调节螺杆4的轴线相一致的运动。这是本申请的磁体的优选结构形式，通过永磁体能够产生恒定的磁场，从而与导体板之间作用而产生电涡流；阻尼调节螺杆为圆柱体便于套设和转动，使得导体板套设于圆柱体的螺杆上发生运动。
在其中一个实施例中，所述磁体2上还连接设置有刚度调节螺杆5，当所述阻尼器壳体1包括第一侧壁11时，所述阻尼器壳体1的所述第一侧壁11上还贯穿地设置有第二通孔13，所述刚度调节螺杆5能够穿设于所述第二通孔13中，且所述刚度调节螺杆5的外周壁设置有外螺纹、所述第二通孔13的内周壁设置有与所述刚度调节螺杆5的外螺纹相匹配的内螺纹，使得所述刚度调节螺杆5转动时、所述磁体2与所述第一侧壁11之间的间距能够发生改变。
通过所述刚度调节螺杆的转动能够使得处于所述阻尼器壳体内部的刚度调节螺杆的部分段的长度进行改变，从而能够有效地调节该阻尼器的固有频率，优选地当壳体内部的螺杆段增长时其固有频率降低、壳体内的螺杆段缩短时其固有频率升高，本申请优选将阻尼器的固有频率调节到与压缩机的振动频率相等或接近的数值；并且本申请通过螺杆的结构 形式使得磁体形成悬臂梁的结构，能够使得阻尼器能够被有效地固定到合适的位置，并且能够根据需要变换阻尼器的安装方位或位置(例如安装到压缩机的顶部(实施例1，见图1-2)或安装到压缩机的侧壁(实施例2，见图5-6))，从而使得阻尼器的适应性能更高，并且使其能够对多个方向的阻力进行减振作用。
本申请的电涡流调谐质量阻尼器100主要由三部分组成，阻尼器壳体1、可调节刚度的悬臂梁-质量块系统(包括磁体2和刚度调节螺杆5)和导体板3等；
阻尼器的工作原理：安装了阻尼器的压缩机200可看成一个二自由度振动系统，其中压缩机200为主系统，而阻尼器为其子系统。主系统以一定的频率进行工作，当其工作频率与子系统频率一致的时候，振动能量将会发生转移，阻尼器将会吸收压缩机200的振动，由此，振动能量将转移到悬臂梁-质量块系统的磁体2上，此时压缩机200由于受到反共振作用而停止振动，而磁体2与导体板3之间产生的相对位移又会在导体板3上激发出电涡流，从而产生阻尼力的作用，最终，磁体2的动能也将被电涡流效应以热能的形式耗散掉，从而完成对压缩机的减振工作。
在其中一个实施例中，当所述阻尼器壳体1包括第一侧壁11和第二侧壁12时，在所述阻尼器壳体1内部、且位于所述第一侧壁11和所述第二侧壁12之间还设置有导杆6，所述导体板3上还以贯穿其两相背壁面的方式设置有第三通孔32，所述导杆6能够穿设于所述第三通孔32中、使得所述导体板3能够沿着所述导杆6的方向滑动。通过设置导杆能够对导体板的运动起到支承和导向的作用。
为了应对不同频率的压缩机200振动，可通过刚度调节螺杆5调节其悬臂梁伸长量，从而对整个悬臂梁-质量块系统的固有频率大小进行调节。而为了设计满足最优的阻尼器减振效果，可通过调节阻尼调节螺杆4使得导体板3沿阻尼调节螺杆4和导杆6在阻尼器内部进行上下移动，从而改变磁体2和导体板3的空气间隙，由此调节不同大小的阻尼力。通过更换不同大小的质量块配合不同规格的垫片实现质量块质量大小的精确调节。
当作用对象为变频压缩机时，通过调节导体板3的位置设计最优阻尼，使得阻尼器可在一个频率段范围进行减振，拥有较好的鲁棒性能，而当作用对象为定频压缩机时，只需将悬臂梁-质量块系统的固有频率大小调节和压缩机一致即可，而不用加上导体板3，此时将导体板3移到离磁体2最远的阻尼器内部空间最下端即可，此时阻尼器能最大程度减小固定频率点的压缩机振动幅值大小，但此做法降低了阻尼器的鲁棒性能，因此压缩机的频率偏移将对减振效果造成很大影响。
在其中一个实施例中，所述导杆6的一端连接于所述第一侧壁11上、所述导杆6的另 一端连接于所述第二侧壁12上。这是本申请的导杆的优选连接形式，即一端连接于第一侧壁(优选固定)、另一端连接于第二侧壁(优选固定)，能够使得导体板能够在第一侧壁和第二侧壁之间进行导向滑动。
在其中一个实施例中，当所述阻尼调节螺杆4为圆柱体时，所述导杆6也为圆柱体，且所述导杆6的轴线与所述阻尼调节螺杆4的轴线平行。这是本申请的导杆的进一步优选结构形式，圆柱体便于套设和导向，便于使得导体板套设于圆柱体的导杆上发生运动。
在其中一个实施例中，所述导体板3的下端且与所述第一通孔31相接地设置有第一凸台33，所述第一凸台33具有与所述第一通孔31相贯通的第三通孔(未示出)、能够容许所述阻尼调节螺杆4从中穿过。这是本申请的导体板的进一步优选结构形式，即在导体板的第一通孔下端相接第一凸台、并且第一凸台具有与第一通孔相连通的第三通孔，能够使得与螺杆相接的内螺纹段得到增长，提高驱动效率，优选第一凸台与导体板一体成型。
在其中一个实施例中，所述导体板3的下端且与所述第三通孔32相接地设置有第二凸台34，所述第二凸台34具有与所述第三通孔32相贯通的第四通孔(未示出)、能够容许所述导杆6从中穿过。这是本申请的导体板的进一步优选结构形式，即在导体板的第三通孔下端相接第二凸台、并且第二凸台具有与第三通孔相连通的第四通孔，能够使得与导杆相接的通孔段得到增长，提高导向驱动效率，优选第二凸台与导体板一体成型。
本申请还提供一种压缩机组件，其包括前任一项所述的电涡流调谐质量阻尼器100，还包括压缩机200，所述电涡流调谐质量阻尼器设置于所述压缩机200的顶部和/或侧壁上。
本申请通过将阻尼器壳体内部的磁体和导体板制作成间距能够根据需要进行调节的结构形式，能够根据需要调节电涡流调谐质量阻尼器的阻尼，从而有效提高电涡流调谐质量阻尼器的适应性和通用性；尤其是采用阻尼调节螺杆的结构形式、将阻尼调节螺杆穿设于导体板的第一通孔中，并且通过螺纹配合，能够使得通过阻尼调节螺杆的旋转而将导体板的位置进行调节和改变，从而实现导体板相对于磁体之间做靠近或远离的运动，实现阻尼器的阻尼调节功能和效果。
本申请的电涡流调谐质量阻尼器通过电涡流效应，实现非接触式阻尼力的产生，大大增强了阻尼器的使用寿命，电涡流调谐质量阻尼器为无极频率可变、阻尼可变形式结构，可针对不同类型的压缩机进行调节匹配；电涡流调谐质量阻尼器拥有较强的鲁棒性，可针对变频率被减振结构起到很好的减振效果；外置式的阻尼器结构，简化了装配和后期的保养维护工作，并且不会影响压缩机本身的工作状态；对于定频和变频压缩机的振动能量均能进行很好的吸收消耗，抑制压缩机自身的振动噪音，由此可以使得压缩机运行更加平稳， 提升空调舒适性。
本申请的压缩机电涡流调谐质量阻尼器100优选与压缩机200的顶部表面粘接在一起，形成稳定的刚性连接，所粘接位置尽量远离压缩机200中心轴线，由于压缩机200远离中心轴线的位置振动位移较大，阻尼器可以发挥最好的减振效果，同时将此阻尼器置于压缩机200顶部也可以抑制压缩机切向和径向两个较大方向的振动(实施例1，图1-2)。
本申请还提供一种空调器，其包括前述的压缩机组件。本申请的电涡流调谐质量阻尼器通过电涡流效应，实现非接触式阻尼力的产生，大大增强了阻尼器的使用寿命，电涡流调谐质量阻尼器为无极频率可变、阻尼可变形式结构，可针对不同类型的压缩机进行调节匹配；电涡流调谐质量阻尼器拥有较强的鲁棒性，可针对变频率被减振结构起到很好的减振效果；外置式的阻尼器结构，简化了装配和后期的保养维护工作，并且不会影响压缩机本身的工作状态；对于定频和变频压缩机的振动能量均能进行很好的吸收消耗，抑制压缩机自身的振动噪音，由此可以使得压缩机运行更加平稳，提升空调舒适性。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请的保护范围之内。以上所述仅是本申请的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本申请技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本申请的保护范围。

Claims (13)

  1. 一种电涡流调谐质量阻尼器，其特征在于，包括：
    阻尼器壳体(1)，以及设置于所述阻尼器壳体(1)内部的磁体(2)和导体板(3)，所述磁体(2)和所述导体板(3)之间间隔设置，且所述磁体(2)和所述导体板(3)之间的间距能够进行调节；还包括阻尼调节螺杆(4)，当所述阻尼调节螺杆(4)旋转时能够驱动所述导体板(3)相对于所述磁体(2)做靠近或远离的运动。
  2. 根据权利要求1所述的电涡流调谐质量阻尼器，其特征在于：
    所述导体板(3)设置有贯穿其两相背壁面的第一通孔(31)，所述第一通孔(31)内壁设置有内螺纹、所述阻尼调节螺杆(4)外周壁设置有外螺纹，且所述第一通孔(31)能够容许所述阻尼调节螺杆(4)从中穿过，使得当所述阻尼调节螺杆(4)旋转时能够驱动所述导体板(3)相对于所述磁体(2)做靠近或远离的运动。
  3. 根据权利要求2所述的电涡流调谐质量阻尼器，其特征在于：
    所述阻尼调节螺杆(4)的第一端连接于所述阻尼器壳体(1)的第一侧壁(11)上、所述阻尼调节螺杆(4)的第二端连接设置于所述阻尼器壳体(1)的第二侧壁(12)上，且所述第一侧壁(11)与所述第二侧壁(12)相对。
  4. 根据权利要求3所述的电涡流调谐质量阻尼器，其特征在于：
    所述阻尼调节螺杆(4)上与所述导体板(3)相配合的位置位于所述第一端和所述第二端之间。
  5. 根据权利要求2所述的电涡流调谐质量阻尼器，其特征在于：
    所述磁体(2)为永磁体；和/或，所述阻尼调节螺杆(4)为圆柱体，当所述阻尼调节螺杆(4)旋转时、所述导体板(3)能够做与所述阻尼调节螺杆(4)的轴线相一致的运动。
  6. 根据权利要求1-5中任一项所述的电涡流调谐质量阻尼器，其特征在于：
    所述磁体(2)上还连接设置有刚度调节螺杆(5)，当所述阻尼器壳体(1)包括第一侧壁(11)时，所述阻尼器壳体(1)的所述第一侧壁(11)上还贯穿地设置有第二通孔(13)，所述刚度调节螺杆(5)能够穿设于所述第二通孔(13)中，且所述刚度调节螺杆(5)的外周壁设置有外螺纹、所述第二通孔(13)的内周壁设置有与所述刚度调节螺杆(5)的外螺纹相匹配的内螺纹，使得所述刚度调节螺杆(5)转动时、所述磁体(2)与所述第一侧壁(11)之间的间距能够发生改变。
  7. 根据权利要求1-6中任一项所述的电涡流调谐质量阻尼器，其特征在于：
    当所述阻尼器壳体(1)包括第一侧壁(11)和第二侧壁(12)时，在所述阻尼器壳体 (1)内部、且位于所述第一侧壁(11)和所述第二侧壁(12)之间还设置有导杆(6)，所述导体板(3)上还以贯穿其两相背壁面的方式设置有第三通孔(32)，所述导杆(6)能够穿设于所述第三通孔(32)中、使得所述导体板(3)能够沿着所述导杆(6)的方向滑动。
  8. 根据权利要求7所述的电涡流调谐质量阻尼器，其特征在于：
    所述导杆(6)的一端连接于所述第一侧壁(11)上、所述导杆(6)的另一端连接于所述第二侧壁(12)上。
  9. 根据权利要求7所述的电涡流调谐质量阻尼器，其特征在于：
    当所述阻尼调节螺杆(4)为圆柱体时，所述导杆(6)也为圆柱体，且所述导杆(6)的轴线与所述阻尼调节螺杆(4)的轴线平行。
  10. 根据权利要求2所述的电涡流调谐质量阻尼器，其特征在于：
    所述导体板(3)的下端且与所述第一通孔(31)相接地设置有第一凸台(33)，所述第一凸台(33)具有与所述第一通孔(31)相贯通的第三通孔、能够容许所述阻尼调节螺杆(4)从中穿过。
  11. 根据权利要求7所述的电涡流调谐质量阻尼器，其特征在于：
    所述导体板(3)的下端且与所述第三通孔(32)相接地设置有第二凸台(34)，所述第二凸台(34)具有与所述第三通孔(32)相贯通的第四通孔、能够容许所述导杆(6)从中穿过。
  12. 一种压缩机组件，其特征在于：
    包括权利要求1-11中任一项所述的电涡流调谐质量阻尼器(100)，还包括压缩机(200)，所述电涡流调谐质量阻尼器设置于所述压缩机(200)的顶部和/或侧壁上。
  13. 一种空调器，其特征在于：
    包括权利要求12所述的压缩机组件。
PCT/CN2019/110736 2019-03-13 2019-10-12 电涡流调谐质量阻尼器、压缩机组件和空调器 Ceased WO2020181763A1 (zh)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103775549A (zh) * 2014-01-22 2014-05-07 青岛科而泰环境控制技术有限公司 偏心式电涡流调谐质量阻尼装置
CN103983054A (zh) * 2014-05-13 2014-08-13 广东美芝精密制造有限公司 压缩机组件及其储液器
TW201439405A (zh) * 2013-04-03 2014-10-16 Jian-Zhi Chen 擺動式協調質量減幅系統
CN204373285U (zh) * 2014-12-19 2015-06-03 广东美芝制冷设备有限公司 压缩机及其储液器
CN206129960U (zh) * 2016-08-31 2017-04-26 柳州东方工程橡胶制品有限公司 一种摆式电涡流调谐质量阻尼器
CN209622966U (zh) * 2019-03-13 2019-11-12 珠海格力电器股份有限公司 一种电涡流调谐质量阻尼器、压缩机组件和空调器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102493573B (zh) * 2011-12-27 2013-10-23 中铁大桥局集团武汉桥梁科学研究院有限公司 一种多场耦合节能调谐质量减振装置
CN106948256B (zh) * 2017-04-26 2019-06-21 中铁大桥科学研究院有限公司 一种超低频液体质量调谐阻尼器及设计方法
CN206971873U (zh) * 2017-07-31 2018-02-06 中国铁路总公司 调谐质量阻尼器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW201439405A (zh) * 2013-04-03 2014-10-16 Jian-Zhi Chen 擺動式協調質量減幅系統
CN103775549A (zh) * 2014-01-22 2014-05-07 青岛科而泰环境控制技术有限公司 偏心式电涡流调谐质量阻尼装置
CN103983054A (zh) * 2014-05-13 2014-08-13 广东美芝精密制造有限公司 压缩机组件及其储液器
CN204373285U (zh) * 2014-12-19 2015-06-03 广东美芝制冷设备有限公司 压缩机及其储液器
CN206129960U (zh) * 2016-08-31 2017-04-26 柳州东方工程橡胶制品有限公司 一种摆式电涡流调谐质量阻尼器
CN209622966U (zh) * 2019-03-13 2019-11-12 珠海格力电器股份有限公司 一种电涡流调谐质量阻尼器、压缩机组件和空调器

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