CN218028288U - Ultra-high frequency tuned mass damper - Google Patents
Ultra-high frequency tuned mass damper Download PDFInfo
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- CN218028288U CN218028288U CN202222187690.9U CN202222187690U CN218028288U CN 218028288 U CN218028288 U CN 218028288U CN 202222187690 U CN202222187690 U CN 202222187690U CN 218028288 U CN218028288 U CN 218028288U
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Abstract
The application relates to an ultrahigh frequency tuned mass damper, which comprises a shell, a mass block and a stiffness element; the mass is located within the housing; the stiffness element comprises a cantilever beam extending along a first direction and a compression spring arranged along a second direction, and the cantilever beam, the compression spring and the mass block are connected; and, the first direction is different from the second direction. The method and the device can solve the technical problems that in the related art, under the ultrahigh frequency condition, the requirement on rigidity of the spiral pressure spring of the tuned mass damper is high, the using amount is large, and the vibration requirement under the frequency is difficult to meet.
Description
Technical Field
The application relates to the technical field of damper devices, in particular to an ultrahigh frequency tuned mass damper.
Background
The civil engineering structure is different from a mechanical member, and the natural vibration frequency is not too high generally, and the high-frequency vibration problem is not outstanding, but when the mechanical equipment is installed on the civil engineering structure, the high-frequency vibration problem is generated. These high frequency vibrations not only can have great influence to the fatigue life of structure and equipment and normal use, also can produce great noise, have reduced staff's travelling comfort.
At present, the main solutions to the high-frequency vibration of civil engineering structures are as follows: (1) The method is characterized in that the method is used for reinforcing the structural rigidity, and is the most common solution for designers at the present stage, namely the rigidity of a main beam, a secondary beam or a floor slab is increased, so that the vibration frequency of the floor slab is far away from the vibration frequency of main working equipment, but the method influences the normal production of the civil structure, influences the attractiveness and prolongs the construction period, and in addition, new high-order modal vibration of the floor slab can be caused after the rigidity is increased; (2) The floor plate is subjected to overall vibration isolation, vibration energy transmission of power equipment to a civil structure is reduced through the vibration isolation device, but the vibration isolation device is only suitable for a newly-built civil engineering structure, and the reconstruction of the existing civil engineering structure is difficult to realize, so that the cost is high; (3) Mechanical equipment vibration isolation, namely, the coefficient of transmission of the equipment vibration to the civil engineering structure is reduced, but in consideration of cost, the prior art mainly adopts simple devices such as springs and rubber vibration isolators to deal with the equipment vibration isolation, the vibration attenuation effect is limited, the normal operation of the equipment is influenced, and the rubber vibration isolators are short in service life and need to be replaced frequently.
Compared with the solution, the energy-absorbing vibration-damping measure based on the tuned mass damper is particularly suitable for the steady-state vibration of the single frequency of the civil structure caused by mechanical equipment. However, the traditional tuned mass damper adopts a helical compression spring, and under the ultrahigh frequency condition, the requirement on the rigidity of the helical compression spring is high, the using amount is large, and the vibration requirement under the frequency is difficult to meet.
Disclosure of Invention
The embodiment of the application provides an ultrahigh frequency tuned mass damper, and aims to solve the technical problems that in the related art, under the ultrahigh frequency condition, the requirement on rigidity of a helical compression spring of the tuned mass damper is high, the usage amount is large, and the vibration requirement under the frequency is difficult to meet.
The application provides harmonious mass damper of hyperfrequency, it includes:
a housing;
a mass located within the housing;
the stiffness element comprises a cantilever beam extending along a first direction and a compression spring arranged along a second direction, and the cantilever beam, the compression spring and the mass block are connected; and also,
the first direction is different from the second direction.
In some embodiments, the cantilever beam is disposed on one inner wall of the housing and connected to the mass, and the compression spring is disposed on the other inner wall of the housing and connected to the mass.
In some embodiments, the first direction and the second direction are perpendicular to each other.
In some embodiments, the damping device further comprises two damping elements, one end of each damping element is connected with the inner wall of the shell, on which the cantilever beam is fixed, and the other end of each damping element is connected with the mass block, and the two damping elements are arranged on two sides of the cantilever beam and are parallel to the cantilever beam.
In some embodiments, the damping element is made of damping rubber, and the damping rubber is attached to the surface of the cantilever beam.
In some embodiments, the damping element is a steel strand damper that is spaced apart from the cantilevered beam.
In some embodiments, the damper further comprises a viscous damper, one end of the viscous damper is connected with the inner wall of the shell, on which the pressure spring is fixed, and the other end of the viscous damper is connected with the mass block.
In some embodiments, the eddy current damping comprises a permanent magnet disposed on a wall surface of the mass opposite the cantilever beam and a conductor disposed on an inner wall of the housing opposite the permanent magnet.
In some embodiments, the number of the compressed springs is one, and the compressed springs are arranged on one inner wall of the shell and connected with the mass block;
or the number of the pressure springs is multiple, the pressure springs are arranged on two opposite inner walls of the shell and connected with the mass block, and the number of the pressure springs on the two inner walls is equal.
In some embodiments, the cross-sectional form of the cantilever is a circular, square tube or circular ring, and the number of the cantilever is one or more.
The beneficial effect that technical scheme that this application provided brought includes:
the embodiment of the application provides an ultrahigh frequency tuned mass damper, which comprises a shell, a mass element and a rigidity element, wherein the shell provides a supporting and fixing space for other elements, the mass element performs reciprocating motion when vibrating externally, and the rigidity element provides rigidity meeting frequency requirements for a device. When the mechanical equipment is installed on a civil structure, ultrahigh frequency vibration occurs outside, the control frequency of the damper is adjusted to be the same as the vibration frequency of the outside, the force generated by the relative motion of the damper and the damper is reacted to the outside, so that the vibration of the outside is eliminated, and the energy of the vibration of the outside can be considered to be consumed and absorbed by the damper.
The rigidity element adopts the combination of a cantilever beam and a pressure spring, the cantilever beam can freely bend and move, and the cantilever beam has higher rigidity, so that the defect of insufficient rigidity of the pressure spring is effectively overcome, the rigidity requirement and the dosage requirement on the pressure spring are reduced, and the control frequency of ultrahigh frequency vibration is met. In addition, the combination of the cantilever beam and the pressure spring reduces the supporting rigidity of the shell, so that the compression of the pressure spring is facilitated, and the damper is easy to assemble. In addition, the combination of the cantilever beam and the pressure spring reduces the supporting rigidity of the shell, so that the compression of the pressure spring is facilitated, and the damper is easy to assemble. Therefore, the technical problems that the requirement on the rigidity of the spiral compression spring of the tuned mass damper is high, the using amount is large and the vibration requirement under the frequency is difficult to meet under the ultrahigh frequency condition in the related technology are solved.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic diagram of a viscous damping scheme provided by an embodiment of the present application;
FIG. 2 is a schematic view of a damping rubber solution provided in an embodiment of the present application;
FIG. 3 is a schematic diagram of a steel strand damping scheme provided in an embodiment of the present application;
fig. 4 is a schematic view of an eddy current damping scheme provided in an embodiment of the present application.
In the figure: 1. a housing; 2. a cantilever beam; 3. a pressure spring; 4. a mass block; 5. viscous damping; 6. damping rubber; 7. damping the steel strand; 8. a permanent magnet; 9. a conductor.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
The embodiment of the application provides an ultrahigh frequency tuned mass damper, which can solve the technical problems that in the related technology, under the ultrahigh frequency condition, the stiffness requirement of a helical compression spring of the tuned mass damper is high, the using amount is large, and the vibration requirement under the frequency is difficult to meet.
Referring to fig. 1, 2, 3 and 4, as a preferred example, the present application provides an ultra-high frequency tuned mass damper comprising a housing 1, a mass 4 and a stiffness element; the mass block 4 is positioned in the shell 1; the rigidity element comprises a cantilever beam 2 extending along a first direction and a compression spring 3 arranged along a second direction, and the cantilever beam 2, the compression spring 3 and the mass block 4 are connected; and, the first direction is different from the second direction.
The damper comprises a shell 1, a mass element and a rigidity element, wherein the shell 1 provides a supporting and fixing space for other elements, the mass element performs reciprocating motion when vibrating externally, and the rigidity element provides rigidity meeting frequency requirements for the device. When the mechanical equipment is installed on the civil structure, ultrahigh frequency vibration occurs outside, the control frequency of the damper is adjusted to be the same as the vibration frequency of the outside, the force generated by the relative motion of the damper and the damper is reacted to the outside, so that the vibration of the outside is eliminated, and the energy of the vibration of the outside can be considered to be consumed and absorbed by the damper.
In the application, the rigidity element adopts the combination of the cantilever beam 2 and the pressure spring 3, the cantilever beam 2 can freely bend and move, and has high rigidity, the defect that the rigidity of the pressure spring 3 is insufficient is effectively overcome, the rigidity requirement and the dosage requirement on the pressure spring 3 are reduced, and the control frequency of ultrahigh frequency vibration is met. In addition, the combination of the cantilever beam and the pressure spring reduces the supporting rigidity of the shell, so that the compression of the pressure spring is facilitated, and the damper is easy to assemble. Therefore, the technical problems that the requirement on the rigidity of the spiral compression spring of the tuned mass damper is high, the using amount is large and the vibration requirement under the frequency is difficult to meet under the ultrahigh frequency condition in the related technology are solved.
In some preferred embodiments, the cantilever beam 2 is disposed on one inner wall of the housing and is connected to the mass 4, and the compression spring 3 is disposed on the other inner wall of the housing and is connected to the mass 4.
Specifically, the first direction and the second direction are perpendicular to each other. However, the first direction and the first direction may be two different directions, and only the mass block 4 needs to be in a balanced state.
The device can adopt different damping elements to solve the problem of high-frequency vibration caused by mechanical vibration of the civil engineering structure through various energy consumption forms.
For example, in some preferred embodiments, the device further comprises two damping elements, one end of each damping element is connected to the inner wall of the housing 1 to which the outrigger 2 is fixed, the other end of each damping element is connected to the mass 4, and the two damping elements are arranged on both sides of the outrigger 2, parallel to the outrigger 2.
Specifically, the damping element adopts damping rubber 6, and the damping rubber 6 is attached to the surface of the cantilever beam 2. The device consumes energy through damping rubber 6 along with cantilever beam 2 deformation, sets up thickness and the area of damping rubber 6 to different cross-sectional forms and power consumption demand.
Specifically, the damping element adopts a steel strand damper 7, and the steel strand damper 7 and the cantilever beam 2 are arranged at intervals. StatorThe number of the false steel strand dampers 7 is i, and the additional rigidity of the steel strand dampers 7 to the dampers is K 3 Wherein the value range of i is 1 or more. The device consumes energy through the friction of the steel wires in the steel strand damper 7, and the quantity and the size specification of the steel strand damper 7 are set according to energy consumption requirements.
For example, in other preferred embodiments, the device further comprises a viscous damper 5, one end of the viscous damper 5 being connected to the inner wall of the housing 1 to which the compression spring 3 is fixed, and the other end being connected to the mass 4. The amount of viscous damping 5 is 1 and above. The device consumes energy through viscous damping 5 both ends relative motion, sets up the quantity and the parameter of viscous damping 5 through the power consumption demand.
For example, in other preferred embodiments, the device further comprises eddy current damping comprising a permanent magnet 8 and a conductor 9, the permanent magnet 8 being arranged on the wall of the mass 4 opposite the cantilever beam 2, the conductor 9 being arranged on the inner wall of the housing 1 opposite the permanent magnet 8. Specifically, the permanent magnets 8 are two magnets with opposite magnetic pole directions, and the conductor 9 is a copper sheet. The device causes the magnetic field change through the motion of the mass block 4, so that the conductor 9 cuts the magnetic induction line to generate electric energy, and the electric energy is finally converted into the vibration energy of a heat energy dissipation structure, and the specifications of the permanent magnet 8 and the conductor 9 are set according to the energy consumption requirement.
In some preferred embodiments, the number of the compression springs 3 is one, and the compression springs are arranged on one inner wall of the shell 1 and connected with the mass block 4; or, the number of the pressure springs 3 is multiple, the pressure springs 3 are arranged on two opposite inner walls of the shell 1 and connected with the mass block 4, and the number of the pressure springs 3 on the two inner walls is equal. Defining the number of the pressure springs 3 as m, and the additional rigidity of the pressure springs 3 to the damper as K 2 The calculation formula of the rigidity of a single pressure spring is
Wherein, G is the shear modulus of pressure spring material, and D is pressure spring silk diameter, and D is the pressure spring diameter, and N is the effective number of turns of pressure spring.
In some preferred embodiments, the cantilever beam 2 has a cross-sectional form of a circle, a square tube or a circular ring, and the number thereof is one or more. Defining the number of the cantilever beams 2 as nThe additional rigidity of the cantilever beam 2 to the damper is K 1 The calculation formula of the stiffness of the single cantilever beam is
Wherein E is the elastic modulus of the cantilever beam material, L is the length of the cantilever beam, and I is the section inertia moment of the cantilever beam.
Defining the section inertia moment of the circular cantilever beam as I 1 The calculation formula is
Wherein d is the diameter of the circular section; defining the section inertia moment of the square cantilever beam as I 2 The calculation formula is
Wherein b is the width of the square section, and h is the height of the square section; defining the section inertia moment of the square tubular cantilever beam as I 3 The calculation formula is
B is the outer width of the square pipe-shaped section, H is the outer height of the square pipe-shaped section, B is the inner hole width of the square pipe-shaped section, and H is the inner hole height of the square pipe-shaped section; the section inertia moment of the circular cantilever beam is defined as I 4 The calculation formula is
Wherein D is the outer diameter of the circular section and D is the inner diameter of the circular section. Will I 1 、I 2 、I 3 And I 4 Substituting into the above calculation formula of single cantilever beam rigidity to obtain K 1 The numerical value of (c).
The mass of the mass block is defined as M, and the calculation formula of the control frequency of the ultrahigh frequency tuned mass damper is as follows
According to the number n of the cantilever beams 2 and the additional rigidity K of the cantilever beams 2 to the damper 1 The number m of the compressed springs 3 and the additional rigidity K of the compressed springs 3 to the damper 2 To obtainThe ultra-high frequency tuned mass damper controls the frequency f.
However, in the scheme that the damping element adopts the steel strand damper 7, the steel strand damper 7 has rigidity property, so that the calculation formula of the control frequency of the ultrahigh frequency tuned mass damper is as follows
According to the number n of the cantilever beams 2 and the additional rigidity K of the cantilever beams 2 to the damper 1 The number m of the pressure springs 3 and the additional rigidity K of the pressure springs 3 to the damper 2 The number i of the steel strand dampers 7 and the additional stiffness K of the steel strand dampers 7 to the dampers 3 And obtaining the control frequency f of the ultrahigh frequency tuned mass damper.
According to the calculation method, the control frequency f of the ultrahigh frequency tuned mass damper is adjusted to be the same as the external vibration frequency, so that the effects of energy absorption and vibration reduction can be achieved under the condition that the mechanical equipment causes ultrahigh frequency vibration of the civil structure.
In addition, the ultrahigh frequency tuned mass damper can be transversely arranged or longitudinally arranged to control the vibration of the structure in the vertical direction and the horizontal direction.
In the description of the present application, it should be noted that the terms "upper", "lower", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, which are merely for convenience of describing the present application and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be configured and operated in a specific orientation, and thus, should not be construed as limiting the present application. Unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are intended to be inclusive and mean, for example, that they may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.
It is noted that, in the present application, relational terms such as "first" and "second", and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrases "comprising a," "8230," "8230," or "comprising" does not exclude the presence of additional like elements in a process, method, article, or apparatus that comprises the element.
The previous description is only an example of the present application, and is provided to enable any person skilled in the art to understand or implement the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. An ultra high frequency tuned mass damper, comprising:
a housing (1);
a mass (4), the mass (4) being located within the housing (1);
the stiffness element comprises a cantilever beam (2) extending along a first direction and a compression spring (3) arranged along a second direction, and the cantilever beam (2), the compression spring (3) and the mass block (4) are connected; and also,
the first direction is different from the second direction.
2. The uhf tuned mass damper of claim 1, wherein:
the cantilever beam (2) is arranged on one inner wall of the shell and connected with the mass block (4), and the pressure spring (3) is arranged on the other inner wall of the shell and connected with the mass block (4).
3. The uhf tuned mass damper of claim 1, wherein:
the first direction and the second direction are perpendicular to each other.
4. The uhf tuned mass damper of claim 1, wherein:
the damping device is characterized by further comprising two damping elements, wherein one end of each damping element is connected with the inner wall, fixed with the cantilever beam (2), of the shell (1), the other end of each damping element is connected with the mass block (4), and the two damping elements are arranged on two sides of the cantilever beam (2) and are parallel to the cantilever beam (2).
5. The uhf tuned mass damper of claim 4, wherein:
the damping element is made of damping rubber (6), and the damping rubber (6) is attached to the surface of the cantilever beam (2).
6. The uhf tuned mass damper of claim 4, wherein: the damping element adopts a steel strand damping (7), and the steel strand damping (7) and the cantilever beam (2) are arranged at intervals.
7. The uhf tuned mass damper of claim 1, wherein:
still include viscous damping (5), viscous damping (5) one end with shell (1) is fixed with the inner wall of pressure spring (3) links to each other, the other end with quality piece (4) link to each other.
8. The uhf tuned mass damper of claim 1, wherein:
still include electric eddy current damping, electric eddy current damping includes permanent magnet (8) and conductor (9), permanent magnet (8) set up in quality piece (4) with on the wall that cantilever beam (2) are relative, conductor (9) set up on the inner wall of shell (1) relative with permanent magnet (8).
9. The uhf tuned mass damper of claim 1, wherein:
the number of the pressure springs (3) is one, and the pressure springs are arranged on one inner wall of the shell (1) and connected with the mass block (4);
or the number of the pressure springs (3) is multiple, the pressure springs are arranged on two opposite inner walls of the shell (1) and connected with the mass block (4), and the number of the pressure springs (3) on the two inner walls is equal.
10. The uhf tuned mass damper of any of claims 1-9, wherein: the cross section of the cantilever beam (2) is in a circular, square tube or circular ring shape, and the number of the cantilever beams is one or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202222187690.9U CN218028288U (en) | 2022-08-17 | 2022-08-17 | Ultra-high frequency tuned mass damper |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202222187690.9U CN218028288U (en) | 2022-08-17 | 2022-08-17 | Ultra-high frequency tuned mass damper |
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| CN218028288U true CN218028288U (en) | 2022-12-13 |
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| CN202222187690.9U Active CN218028288U (en) | 2022-08-17 | 2022-08-17 | Ultra-high frequency tuned mass damper |
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