CN203361392U - High-frequency tuning mass vibration absorber - Google Patents
High-frequency tuning mass vibration absorber Download PDFInfo
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- CN203361392U CN203361392U CN 201320410293 CN201320410293U CN203361392U CN 203361392 U CN203361392 U CN 203361392U CN 201320410293 CN201320410293 CN 201320410293 CN 201320410293 U CN201320410293 U CN 201320410293U CN 203361392 U CN203361392 U CN 203361392U
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Abstract
The utility model belongs to a high-frequency tuning mass vibration absorber which comprises a connecting plate, elastic elements, damping elements and a mass block. The mass block is arranged between the connecting plate and a pre-fastening connecting piece, the elastic elements are arranged between the mass block and the pre-fastening connecting piece and between the mass block and the connecting plate respectively, the damping elements are arranged between the mass block and the pre-fastening connecting piece or/and between the mass block and the connecting plate, pre-fastening structures are arranged between the connecting plate and the pre-fastening connecting piece, pre-fastening force is exerted on the elastic elements through the pre-fastening structures, the elastic elements are compressed until the end portions of the elastic elements are in sufficient contact with the mass block, the pre-fastening connecting piece or the connecting plate adjacent to the elastic elements, and the linear variation stage when external force borne by the elastic elements and the compressed displacement of the elastic elements are in the direct proportion begins. The high-frequency tuning mass vibration absorber is compact in spatial structure, suitable for controlling vibration of structures with the frequency of 15Hz or more, excellent in cost performance and wide in market application prospect.
Description
Technical field
The utility model belongs to the civil engineering structure antivibration area, is specifically related to a kind of for controlling the tuning mass bumper of building structure dither.
Background technology
Development along with urban construction, various high levels, super highrise building and thin and tall structure, long span building thing are increasing, the realistic problem of having to address in becoming engineering construction in this class large span of control, the resonance of low frequency configuration thing failure, facts have proved, tuning mass bumper (also has in document and claims tuned mass damper, or title mass tuning damper, also be called for short TMD herein) be a kind of effective vibration control apparatus, its intrinsic frequency is adjusted to the natural frequency that approaches structure, then installed structurally.When structure is subject to exciting force interference vibration-generating, cause the resonance of mass tuning damper, utilize the vibrating inertia force of tuning quality to react on structure itself, thereby offset exciting force, reach the purpose that reduces structural response.Want to bring into play to greatest extent the damping effect of mass tuning damper, require its intrinsic frequency consistent with the natural frequency of main structure as far as possible, otherwise the effectiveness in vibration suppression of TMD will decline to a great extent.The Chinese patent that for example patent No. is 200410087664.2 discloses a kind of like this oriented vertical adjustable tuning mass bumper, the resonance that can cause under People's Bank of China's incentive action for controlling the building structure such as overpass or harbour trestle.
The TMD of this spline structure is applicable to the following application scenario of 15Hz, and when being applied to the high frequency occasion, (15Hz and more than) can meet difficulty.Reason is, because the rigidity of rubber elastomeric material is nonlinear, in therefore existing high-quality mass tuning damper product, mostly adopts steel spring as flexible member.According to theoretical mechanics general knowledge, the relation of the global stiffness of the intrinsic frequency of this type of tuning mass bumper and whole springs and the quiet distortion of integral body under the mass Action of Gravity Field of whole springs is as shown in formula (1) and formula (2):
Wherein: f is frequency, and unit is Hz; K is the global stiffness of whole springs; M is quality; π is pi; G is acceleration of gravity; δ is the quiet distortion of the integral body of whole springs, and unit is mm.
Design formulas (1) by intrinsic frequency can be known, existing this type of tuning mass bumper can provide good control to the low frequency vibrations such as people's row energization of 2Hz left and right, roughly go for the vibration damping of the structural vibration of 10Hz left and right after expansion, but but being difficult to be suitable for vibrates such as the high-frequency structure more than 15Hz.This be because, from design formulas (1), suppose under the condition identical at quality m, when the intrinsic frequency of tuning mass bumper is 3Hz, the global stiffness of required whole springs is K, when intrinsic frequency is 15Hz, the global stiffness of required whole springs is 25K, all the global stiffness of spring need improve 25 times, if directly utilize the spring of large rigidity, cost of production improves greatly, if utilize a large amount of low rigid spring parallel connections, the product plane size is very large, needs larger plane space to put layout simultaneously, and applicability is poor; In addition, by formula (2), can be drawn, when the intrinsic frequency of tuning mass bumper is 3Hz, the quiet 27.6mm that is deformed into of integral body of whole springs; And intrinsic frequency is while being 15Hz, all the quiet distortion of integral body of springs is only 1.1mm; Admittedly, while for frequency, being 20Hz, all the quiet distortion of integral body of spring is only 0.6mm.Single spring will inevitably have height error adding man-hour, and the tuning mass bumper that four springs are set of take is example, and due to the existence of working height error, as shown in Figure 1, the stiffness curve of first spring is as K
1shown in, spring deflection reaches S
1the time, the stiffness K of this spring
1start to enter the linear change stage; In like manner, second spring deflection reaches S
2the time, the stiffness K of this spring
2start to enter the linear change stage; The 3rd spring deflection reaches S
3the time, the stiffness K of this spring
3start to enter the linear change stage; The 4th spring deflection reaches S
4the time, the stiffness K of this spring
4start to enter the linear change stage, therefore, in theory, when four spring assemblies are used, at least make compress variation reach S
4also to deduct amplitude in addition, just can make all springs change at the rigidity linear stage when vibration, the intrinsic frequency of the tuning mass bumper now consisted of above-mentioned spring is only a stationary value, in practice, take spiral cylinder spring as example, S1～S4 can reach 0.5～4mm, take the 2mm amplitude as example, when amount of spring compression reaches 2.5～6mm, during the vibration of guarantee mass, at the rigidity linear stage, change, corresponding TMD operating frequency is 10～6.5Hz.
We can find thus, the TMD:1 that is this class in 200410087664.2 " directly supporting type " for the patent No.) when amplitude is greater than the quiet deflection under Gravitative Loads, the intrinsic frequency parameter of TMD is a variable, cisco unity malfunction; 2) be greater than the quiet deflection sum under amplitude and Gravitative Loads when the initial nonlinearity erron of spring, the intrinsic frequency parameter of TMD is a variable, can not work.
In addition, except the working height error of spring self, when being assemblied in tuning mass bumper, spring also has rigging error, thus in practical application, as shown in Figure 2, the global stiffness K of all springs in tuning mass bumper
0at at least compressed S of all springs
0shi Caihui enters the linear change stage, and in the linear change stage that the external force that namely flexible member described in the utility model bears is directly proportional to the compression displacement of flexible member, now, the intrinsic frequency of tuning mass bumper is only a stationary value.The tuning mass bumper of existing structure only relies on the deadweight of mass to be difficult to eliminate fully working height error and the rigging error of all springs, reach the linear change stage that external force that flexible member bears is directly proportional to the compression displacement of flexible member, especially when dither, the working amplitude of spring is very little again, even may occur that the final error scope after the height error of all springs and rigging error accumulative total has exceeded the situation of the number range after the quiet distortion of spring superposes with working amplitude, when tuning mass bumper is worked in this case, all the global stiffness of spring is nonlinear change, therefore the intrinsic frequency of tuning mass bumper is difficult to accurate control, can't make the intrinsic frequency of tuning mass bumper be consistent or approach with the natural frequency of structure all the time, so its damping property can't meet the engineering application requirements.
In summary it can be seen, the existing tuning mass bumper that utilizes steel spring directly to support mass is difficult to be applicable to the above dither of 15Hz.And the structural vibration caused such as much huge revolving equipment such as steam turbine generators now, natural frequency is all more than 15Hz, even surpassed 20Hz, so the market an urgent demand provides a kind of mass tuning damper product that goes for the high-frequency structure vibration isolation.
Summary of the invention
The purpose of this utility model is to overcome above-mentioned defect, and a kind of space structures compactness is provided, and goes for the even high frequency mass tuning damper of higher frequency structural vibration control of 15Hz.
The utility model high frequency mass tuning damper is to realize like this, comprise junction plate, flexible member, damping element and mass, characterized by further comprising pre-clamping joint, mass is arranged between junction plate and pre-clamping joint, reach between mass and junction plate flexible member is set respectively between mass and pre-clamping joint, damping element is arranged between mass and pre-clamping joint or/and between mass and junction plate, between junction plate and pre-clamping joint, pre-pressing structure is set, by pre-pressing structure, flexible member is applied to pretightning force, compression elastic element is until flexible member end and adjacent mass, preload piece or junction plate fully contact, enter the linear change stage that external force that flexible member bears is directly proportional to the compression displacement of flexible member.
Described pre-pressing structure comprises the concrete forms such as pretension connecting rod, pretension hook, pretension chain and pre-locking bracket, as long as can realize locking the relative position of pre-clamping joint and junction plate, can realize same effect.
For saving assembly space, can be provided with cavity at the middle part of flexible member, the pretension connecting rod passes from the cavity at flexible member middle part.In the utility model high frequency mass tuning damper, the structure of pretension connecting rod and assembling mode can be varied, for example, the two ends of pretension connecting rod are respectively equipped with helicitic texture, the pretension connecting rod runs through pre-clamping joint and junction plate setting, utilize nut to coordinate with helicitic texture, lock the relative position of pre-clamping joint and junction plate; Perhaps an end of pretension connecting rod is provided with helicitic texture, and the other end is fixed on pre-clamping joint, and the end that the pretension connecting rod is threaded structure runs through the junction plate setting, utilizes nut to coordinate with helicitic texture, locks the relative position of pre-clamping joint and junction plate; Perhaps an end of pretension connecting rod is provided with helicitic texture, and the other end is fixed on junction plate, and the end that the pretension connecting rod is threaded structure runs through pre-clamping joint setting, utilizes nut to coordinate with helicitic texture, locks the relative position of pre-clamping joint and junction plate.
As a kind of special case, pre-clamping joint and nut can also become one.
In the utility model, applicable flexible member and damping element are varied.For example, flexible member comprises helical spring, dish spring, leaf spring, metal rubber composite spring, rubber spring (comprising shear-type rubber spring) and elastic polyurethane spring etc.; Damping element comprises orifice restriction type damper, viscous damper, frcition damper and directly utilizes damping capacity the damper that good macromolecular material is made etc., such as block rubber, elastic polyurethane piece etc.It is worth mentioning that, flexible member can also become one with damping element.At this, the described implication become one comprises that flexible member can firmly link together by sulfuration, thermal-adhering, the connection technique such as bonding and damping element, perhaps flexible member and damping element are same element, for example, block rubber not only can provide good elasticity, can also effectively improve the damping ratio of system, so it can use as flexible member and damping element simultaneously.
In the utility model high frequency mass tuning damper, owing between junction plate and pre-clamping joint, being provided with pre-pressing structure, by pre-pressing structure, flexible member has been carried out to pretension, eliminated the initial nonlinear impact of flexible member, make the flexible member linear change stage that the external force in bearing is directly proportional to the compression displacement of flexible member all the time, the global stiffness of high frequency mass tuning damper Elastic element and the operating frequency of high-frequency tuning mass bumper remain stable, therefore it goes for the above dither control of 15Hz, the oscillation damping and energy dissipating effect is very stable.
The space structures compactness of the utility model high frequency mass tuning damper, go for the even control of higher frequency structural vibration of 15Hz, cost performance is very superior, and it has effectively enlarged the scope of application of tuning mass bumper product, and market application foreground is very wide.
The accompanying drawing explanation
The curve map that the rigidity that Fig. 1 is single steel spring changes with compress variation.
The curve map that the rigidity that Fig. 2 is existing mass tuning damper changes with compress variation
One of structural representation that Fig. 3 is the utility model high frequency mass tuning damper.
The upward view that Fig. 4 is Fig. 3.
Two of the structural representation that Fig. 5 is the utility model high frequency mass tuning damper.
The top view that Fig. 6 is Fig. 5.
Three of the structural representation that Fig. 7 is the utility model high frequency mass tuning damper.
The top view that Fig. 8 is Fig. 7.
Four of the structural representation that Fig. 9 is the utility model high frequency mass tuning damper.
The top view that Figure 10 is Fig. 9.
Five of the structural representation that Figure 11 is the utility model high frequency mass tuning damper.
Six of the structural representation that Figure 12 is the utility model high frequency mass tuning damper.
Seven of the structural representation that Figure 13 is the utility model high frequency mass tuning damper.
Eight of the structural representation that Figure 14 is the utility model high frequency mass tuning damper.
The top view that Figure 15 is Figure 14.
Nine of the structural representation that Figure 16 is the utility model high frequency mass tuning damper.
The specific embodiment
Embodiment mono-
The utility model high frequency mass tuning damper, comprise junction plate 2, flexible member, damping element 6 and mass 3 as shown in Figure 3 and Figure 4, in addition, also comprises pre-clamping joint 1, between junction plate 2 and pre-clamping joint 1, pre-pressing structure 7 is set.Wherein, pre-clamping joint 1 is made by steel plate, and size is identical with junction plate 2, and mass 3 is arranged between junction plate 2 and pre-clamping joint 1; Flexible member comprises helical steel springs 4 and 5, and helical steel springs 4 is arranged between mass 3 and pre-clamping joint 1, and helical steel springs 5 is arranged between mass 3 and junction plate 2; Damping element 6 adopts the hole throttle type damper, and damping element 6 is fixedly installed on respectively between mass 3 and pre-clamping joint 1 and between mass 3 and junction plate 2.In addition, in this example, between junction plate 2 and pre-clamping joint 1, pre-pressing structure 7 is set and is specially six roots of sensation pretension connecting rod, an end of pretension connecting rod is provided with helicitic texture, and the other end is weldingly fixed on pre-clamping joint 1, the end that the pretension connecting rod is threaded structure runs through junction plate 2 settings, utilize nut 8 to coordinate with helicitic texture, lock the relative position of pre-clamping joint 1 and junction plate 2, for the ease of handling nut 8, also be fixedly installed four legs 9 in junction plate 2 bottom surfaces, leg 9 is made by square steel pipe.Apply pretightning force by 7 pairs of helical steel springs of pre-pressing structure 4 and 5, compression helical steel springs 4 and 5, until helical steel springs 4 and 5 ends fully contact with adjacent mass 3, pre-clamping joint 1 or junction plate 2, the linear change stage that the external force that each helical steel springs in the utility model high frequency mass tuning damper is entered bear is directly proportional to the compression displacement of himself.In order to prevent in use occurred level slip of flexible member, pre-clamping joint 1, junction plate 2 reach on the mass 3 adjacent with flexible member and are fixed with respectively limit base 20, and during assembling, limit base 20 embeds in the inner ring of helical steel springs.
It should be noted that, in design process, can determine the global stiffness k of the utility model high frequency mass tuning damper Elastic element according to formula (1) and formula (2), preferably, be arranged on the global stiffness of all helical steel springs 4 between mass 3 and pre-clamping joint 1 and be arranged on mass 3 and junction plate 2 between the global stiffness of all helical steel springs 5 identical, be respectively half of required flexible member global stiffness k, in the course of work, the distortion of each helical steel springs 4 and each helical steel springs 5 is basically identical like this, in like manner, be arranged on the damping element 6 between mass 3 and pre-clamping joint 1 and be arranged on mass 3 and junction plate 2 between damping element 6 also identical on performance, like this, in the utility model high frequency mass tuning damper, all helical steel springs 4 and all helical steel springs 5 form in parallel, its rigidity sum total just in time reaches the global stiffness k of required flexible member.During application, by leg 9, the utility model high frequency mass tuning damper is arranged on the structure of easy generation dither, when structure is subject to excitation generation dither, spring in the utility model high frequency mass tuning damper---the mass tuning system is started working automatically, utilize the vibrating inertia force of tuning quality to react on structure itself, thereby the counteracting exciting force, reach the purpose that reduces structural response.Owing in the utility model high frequency mass tuning damper, being provided with pre-pressing structure, under the pretightning force effect provided at pre-pressing structure, the linear change stage that all flexible members all are directly proportional to the compression displacement of himself in born external force, therefore can guarantee that the global stiffness of flexible member is constant in the course of the work, in the situation that mass of vibration is also constant, the intrinsic frequency of the utility model high frequency mass tuning damper is a steadiness parameter, be conducive to accurately regulate the intrinsic frequency of the utility model high frequency mass tuning damper, make it more approach the natural frequency of structure, and then raising damping property, meet better the engineering instructions for use, in addition, due to the global stiffness of all helical steel springs 4 between mass 3 and pre-clamping joint 1 and be arranged on mass 3 and junction plate 2 between the global stiffness of all helical steel springs 5 identical, be arranged on the damping element 6 between mass 3 and pre-clamping joint 1 and be arranged on mass 3 and junction plate 2 between damping element 6 also identical on performance, therefore the distortion of each helical steel springs 4 and each helical steel springs 5 is basically identical in the course of the work, more simple and convenient while adjusting parameter, in addition, owing to flexible member being arranged to connect in parallel with upside and downside two groups, can effectively utilize space, in number of springs, under identical condition, takies less plane space, the mounting arrangements of being more convenient for, have, at plane space, under identical condition, due to the flexible member that can arrange greater number, the quantity of also being convenient to by increasing flexible member reduces the rigidity of single flexible member, thereby reduces difficulty of processing and the cost of flexible member again.
The TMD of the existing direct supporting construction of the initial employing under study for action of inventor of the present utility model finds while controlling 15Hz and above dither, after meticulously selecting spring assembling TMD, even spring parameter is very accurate, the frequency of TMD is still unstable, found it is because there is initial nonlinear reason in flexible member through repeatedly detecting and testing, increase pre-pressing structure in TMD after, realize the frequency stabilization of TMD, obtained good oscillation damping and energy dissipating effect.In the utility model high frequency mass tuning damper, alternative pre-pressing structure is varied; except already mentioned pretension connecting rod in this example; can also be the structures such as pretension hook, pretension chain or pre-locking bracket; or even the combination of said structure; as long as can realize flexible member is applied to enough pretightning forces; can realize same effect, among the protection domain all required at the utility model.In addition, in the utility model, applicable flexible member and damping element are also varied, and for example, flexible member comprises helical spring, dish spring, leaf spring, metal rubber composite spring, rubber spring (comprising shear-type rubber spring) and elastic polyurethane spring etc.; Damping element comprises orifice restriction type damper, viscous damper, frcition damper and directly utilizes damping capacity the damper that good macromolecular material is made etc., such as block rubber, elastic polyurethane piece etc.It is worth mentioning that, flexible member can also become one with damping element.At this, the described implication become one comprises that flexible member can firmly link together by sulfuration, thermal-adhering, the connection technique such as bonding and damping element, perhaps flexible member and damping element are same element, for example, block rubber not only can provide good elasticity, can also effectively improve the damping ratio of system, so it can use as flexible member and damping element simultaneously.These flexible members and damping element can be applicable in the utility model high frequency mass tuning damper, among the protection domain all required at the utility model.In addition, in this routine described technical scheme, one end of pretension connecting rod 7 is provided with helicitic texture, utilize helicitic texture and nut 8 to coordinate the relative position of the pre-clamping joint 1 of locking and junction plate 2, the meaning that nut 8 wherein is set is to adjust at any time as required the pretightning force be applied on flexible member, and can split at any time the utility model high frequency mass tuning damper each building block is safeguarded to replacing, if do not consider to safeguard and do not need to regulate pretightning force yet, also can be directly by pretension connecting rod 7 with together with junction plate 2 is welded and fixed, thereby realize the relative position of the pre-clamping joint 1 of locking and junction plate 2, also can realize good effect, among the protection domain also required at the utility model.Have again; in these row, pre-pressing structure comprises six roots of sensation pretension connecting rod; flexible member comprises that six helical steel springs 4 and six spiral shells execute steel spring 5; damping element 6 arranges two between pre-clamping joint 1 and mass 3; also arrange two between mass 3 and junction plate 2; only, for know-why of the present utility model is described better, the position of the quantity of pretension connecting rod, flexible member and damping element can arrange as required in actual applications, among the protection domain all required at the utility model.In this example, limit base 20 embeds the inner ring of helical steel springs 4 and 5; it can't be moved horizontally; in actual applications; also can enlarge the size of limit base; the outer ring of helical steel springs is embedded in limit base; thereby realizing making its purpose that can't move horizontally, is all the simple replacement of common technology, among the protection domain also required at the utility model.These characteristics is applicable to all technical schemes of the utility model, at this, is described in the lump.
The utility model high frequency mass tuning damper, flexible member is arranged to connect in parallel with upside and downside two groups, set up pre-clamping joint and pre-tightening apparatus simultaneously, by flexible member is applied to pretightning force, effectively eliminate before use the mismachining tolerance of flexible member height, make the global stiffness of flexible member become a constant parameter, and then can be by the natural frequency that approaches most structure of the intrinsic frequency adjustment of the utility model high frequency mass tuning damper, realize good damping property, reach the purpose that reduces structural response.This advantage is applicable to the technical scheme of all the utility model high frequency mass tuning dampers.In addition, in application process, the pretension connecting rod can also play the effect of guiding, makes the more stable work of the utility model high frequency mass tuning damper reliable.In addition, based on the utility model know-why, the technical scheme of the utility model high frequency mass tuning damper equally also goes for the low frequency vibration of control structure.Especially it is to be noted, in the utility model, junction plate also can be integrated in the structure for the treatment of vibration damping, or for treating the part of vibration-proof structure, in the middle of the protection domain all required at the utility model.
In sum, the utility model high frequency mass tuning damper simple and compact for structure, its damping property is good, cost is low, long service life, and the scope of application is wider, go for the even control of higher frequency structural vibration of 15Hz, market application foreground is very wide.
Embodiment bis-
The utility model high frequency mass tuning damper, be with the difference of embodiment mono-as shown in Figure 5 and Figure 6, and damping element 6 only is arranged between mass 3 and junction plate 2, comprises two hole throttle type dampers.In addition, in pre-pressing structure 7, the two ends of each root pretension connecting rod are respectively equipped with helicitic texture, and the pretension connecting rod runs through pre-clamping joint 1 and junction plate 2 arranges, and utilizes nut 8 to coordinate with helicitic texture, locks the relative position of pre-clamping joint 1 and junction plate 2.For prevent flexible member in use occurred level slide, be fixed with respectively limit base 23 on pre-clamping joint 1, junction plate 2 and the mass 3 adjacent with flexible member, during assembling, helical steel springs 4 and 5 outer ring are placed in limit base 23.
With embodiment mono-, compare, in this routine described technical scheme, damping element 6 only is arranged between mass 3 and junction plate 2, utilized space between therefore pre-clamping joint 1 and mass 2 is larger, its meaning is to select the helical steel springs 4 of low rigidity, meet the global stiffness requirement by increasing usage quantity, be conducive to like this reduce difficulty of processing and the product cost of helical steel springs 4, the quantity that reduces in addition damping element also can reduce the workload of maintaining.Based on above-mentioned know-why, although still take in this example and six helical steel springs 4 and six helical steel springs 5 are set describe as example, but in actual applications, the quantity that flexible member is set between the quantity of flexible member and mass and connector is set between pre-clamping joint and mass also can be different, as long as meet the global stiffness requirement, can realize good effect; In addition, except the quantity difference, the rigidity sum of flexible member is set between pre-clamping joint and mass, and the rigidity sum that flexible member is set between mass and connector also can be different, as long as the global stiffness after parallel connection meets the demands, also can play good effect, but when design should note controlling the pretension amount of flexible member, guarantee institute have elastic component in the course of the work two ends all the time with mass, pre-clamping joint or junction plate close contact.In this technique scheme, only with word, describe, the different structure that all is based on the utility model know-why is arranged, among the protection domain all required at the utility model.
Embodiment tri-
The utility model high frequency mass tuning damper, be with the difference of embodiment bis-as shown in Figure 7 and Figure 8, and damping element 10 only is arranged between mass 3 and pre-clamping joint 1, is specially two viscous dampers.In addition, one end of pretension connecting rod 7 is provided with helicitic texture, the other end is weldingly fixed on junction plate 2, the end that the pretension connecting rod is threaded structure runs through pre-clamping joint 1 setting, utilize nut 8 to coordinate with helicitic texture, lock the relative position of pre-clamping joint 1 and junction plate 2, pretension connecting rod 7 passes from the cavity at flexible member middle part, from the cavity at the helical steel springs 4 of upper and lower correspondence and 5 middle parts, passes.
With embodiment mono-, compare, except having reduced damping element quantity, maintenance workload still less outside, because nut 8 is arranged on the top of pre-clamping joint 1, so junction plate can omit leg, the structure of product is simpler.In addition, limit base 20 no longer is fixed together with pre-clamping joint 1, junction plate 2 or mass 3, has saved welded connection technology, safeguards that replacing is easier, is convenient to recycling.In addition, pretension connecting rod 7 passes from the cavity at flexible member middle part, does not take additional space, therefore is conducive to arrange the flexible member of greater number, thereby reduce the rigidity of single flexible member, reach the purpose that reduces single flexible member difficulty of processing and overall cost.
In addition; be noted that; in the utility model high frequency mass tuning damper shown in Fig. 3 to Fig. 8; for convenient, mass of vibration is adjusted; mass 3 combines by plurality of steel plates; and the thickness specification of steel plate is different; in actual applications; if mass can accurately arrange; also can adopt the mass of monoblock or integral type, also can realize good effect, in the middle of the protection domain also required at the utility model; this point is equally applicable to, in the technical scheme of the utility model back, at this, be described in the lump.
Embodiment tetra-
The utility model high frequency mass tuning damper as shown in Figure 9 and Figure 10, with the difference of embodiment mono-, be, metal---the rubber-spring complex that flexible member 11 and flexible member 12 all adopt helical steel springs 14 and high-damping rubber 13 to form, because high-damping rubber 13 has good damping capacity simultaneously, therefore this metal---rubber-spring complex is flexible member, be also damping element, it becomes one damping element and flexible member simultaneously, therefore no longer another handicapping Buddhist nun element.In addition, pre-pressing structure 7 comprises eight pre-locking brackets, and the two ends of pre-locking bracket are respectively with together with pre-clamping joint 1 and junction plate 2 are welded and fixed.During assembling, in advance flexible member is compressed, until helical steel springs 14 ends fully contact with adjacent mass 3, pre-clamping joint 1 or junction plate 2, again that pre-locking bracket is soldered with pre-clamping joint 1 and junction plate 2, be continuously applied pretightning force by 7 pairs of flexible members of pre-pressing structure, compression elastic element, the linear change stage that the external force that each flexible member in the utility model high frequency mass tuning damper is all entered bear is directly proportional to the compression displacement of himself.In order to prevent in use occurred level slip of flexible member, utilize the rubber 13 in flexible member to make the two ends of flexible member reach the mass 3 adjacent with flexible member and be fixed together with pre-clamping joint 1, junction plate 2 respectively by sulfuration process.
In this example, owing to having adopted metal---rubber-spring complex, therefore the rigidity of single flexible member presents nonlinear variation, but after having applied suitable pretightning force, the flexible member stiffness variation in the course of the work that is positioned at the mass both sides forms complementation, therefore can be similar to and think that the composite rigidity of the two is linear, so the flexible member global stiffness of high frequency mass tuning damper is linear change, also applicable in the technical scheme of the flexible member that this point is made at nonlinear materials such as the utility model following adopted complex spring or rubber, no longer repeat, at this, be described in the lump.With embodiment tri-, compare, owing to having adopted metal---rubber-spring complex, flexible member and damping element integrate, so space utilization efficiency is higher, and the structure of the utility model product is also simpler.
It is to be noted, know-why based on the mass tuning damper of the utility model high frequency shown in Fig. 3 and Fig. 5 in this example, also can arrange limit base on pre-clamping joint, junction plate and corresponding mass, utilize limit base to realize the Horizontal limiting of flexible member, also can realize good effect; In addition, pre-locking bracket except with together with pre-clamping joint and junction plate are welded and fixed, can also utilize securing member that pre-locking bracket is fixedly connected with pre-clamping joint and junction plate, also can realize same effect, but also be more convenient for splitting maintenance; In addition except metal---rubber-spring complex; also can adopt metal---the elastic polyurethane complex spring; technique scheme is all simple change of this routine described technical scheme; in the middle of the protection domain also required at the utility model; only with word, be described accompanying drawing explanation no longer in addition at this.
Embodiment five
The utility model high frequency mass tuning damper as shown in figure 11, with the difference of embodiment tetra-, be, pre-pressing structure 7 comprises eight pretension chains, and pretension chain one end and junction plate 2 are welded and fixed, and the other end is connected with pre-clamping joint 1 by pretightning force adjusting screw(rod) structure 15.In addition, on pre-clamping joint 1, junction plate 2 and corresponding mass 3, limit base 20 is set, limit base 20 is embedded in the cavity at flexible member 11 and 12 middle parts, realize the Horizontal limiting of flexible member, so flexible member 11 and 12 is not fixedly linked with pre-clamping joint 1, junction plate 2 and adjacent mass 3.
With embodiment tetra-, compare, in this routine described technical scheme owing to being provided with pretightning force adjusting screw(rod) structure 15 in the pretension chain, utilize pretightning force adjusting screw(rod) structure 15 just can regulate the pretightning force be applied on flexible member, very convenient, also be convenient in addition split and safeguard.In addition, due to the Horizontal limiting that utilizes limit base 20 to realize flexible member, therefore flexible member needn't recycle sulfuration and waits complicated technology and pre-clamping joint 1, junction plate 2 and adjacent mass 3 to be fixedly linked, and its processing technology is easier, splits and safeguard to change also more easily realization.
Certainly be provided with pretightning force adjusting screw(rod) structure 15 in the pretension chain in this example; form detachable syndeton with pre-clamping joint 1; based on this routine described know-why; in actual applications; also pretightning force adjusting screw(rod) structure 15 can be set between pretension chain and junction plate 2; certainly pretension chain two ends can also be welded and fixed with pre-clamping joint 1 and connector 2 respectively, also can realize good effect, among the protection domain also required at the utility model.
Embodiment six
The utility model high frequency mass tuning damper, be with the difference of embodiment five as shown in figure 12, and pre-pressing structure 7 can also be the pretension hook, and lower end and the junction plate 2 of pretension hook are welded and fixed, and upper end crotch section and pretightning force adjusting screw(rod) structure 15 articulate.In addition, flexible member 11 and 12 consists of the high-damping rubber material.In addition, on pre-clamping joint 1, junction plate 2 and corresponding mass 3, limit base 23 is set, flexible member 11 and 12 is embedded in limit base 23, realizes the Horizontal limiting of flexible member 11 and 12.
Certainly based on this routine described know-why, also pretightning force adjusting screw(rod) structure 15 can be arranged on junction plate 2, an end of pretension hook is weldingly fixed on pre-clamping joint 1; Perhaps on pre-clamping joint 1 and junction plate 2, pretightning force adjusting screw(rod) structure 15 is set simultaneously, crotch section is set respectively at pretension hook two ends and pretightning force adjusting screw(rod) structure 15 articulates; In addition; as shown in figure 13; can also pretension hook 24 and 25 be set on pre-clamping joint 1 and junction plate 2 respectively accordingly and form pre-pressing structure; first compression elastic element during assembling; by all pretension hook 24 and 25 one by one correspondence articulate, after discharging flexible member, by pretension hook 24 and 25, cooperatively interact and be continuously flexible member pretightning force is provided; also can realize good effect, among the protection domain all required at the utility model.
Similar to the know-why of narration in embodiment tetra-, in this routine described technical scheme, flexible member is made by the high-damping rubber material, although the rigidity of single flexible member presents nonlinear variation, but after having applied suitable pretightning force, the flexible member stiffness variation in the course of the work that is positioned at the mass both sides forms complementation, therefore can be similar to and think that the composite rigidity of the two is linear, so the flexible member global stiffness of the utility model high frequency mass tuning damper is linear change, the intrinsic frequency of high frequency mass tuning damper is a stationary value, it can accurately be adjusted to the natural frequency for the treatment of vibration-proof structure approaching as far as possible, and then realize good effectiveness in vibration suppression, meet the needs of engineering.As can be seen here, the utility model high frequency mass tuning damper has been expanded the selection range of mass tuning damper product Elastic element greatly, so its applicability has obtained remarkable lifting.
Embodiment seven
The utility model high frequency mass tuning damper as shown in Figure 14 and Figure 15, with the difference of the mass tuning damper of high frequency shown in Fig. 7, be, metal---the rubber-spring complex that flexible member 11 and 12 all adopts helical steel springs 14 and high-damping rubber 13 to form, because high-damping rubber 13 has good damping capacity simultaneously, therefore this metal---rubber-spring complex is flexible member, also damping element simultaneously, it becomes one damping element and flexible member, therefore no longer another handicapping Buddhist nun element.In addition, the corresponding flexible member 11 of pre-clamping joint 1 is independent the setting respectively, and this routine Elastic element 11 is provided with four, and therefore pre-clamping joint 1 also arranges four.In addition, flexible member 12 also arranges four, corresponding, pretension connecting rod 7 also arranges four, and the size of corresponding junction plate 2 and mass 3 is different.
Compare with embodiment tri-, in this routine described technical scheme, adopted the pre-clamping joint 1 of absolute construction, be conducive to save material, also help the own wt that reduces product simultaneously, can avoid treating that the phenomenon that vibration-proof structure bears a heavy burden excessive occurs.Because the cavity size at flexible member middle part is less, pretension connecting rod 7 runs through the cavity setting at flexible member middle part, and it can effectively limit the horizontal movement of flexible member, so has omitted limit base in this example, its structure is simpler, is conducive to oversimplify manufacturing process and saves material.
Embodiment eight
The utility model high frequency mass tuning damper as shown in figure 16, with the difference of embodiment seven, be, the complex spring that flexible member 11 and 12 all adopts dish spring 16 and high-damping polyurethane material 17 to form, adopt in the course of the work the power equilibrium for guaranteeing dish spring 16, the upper and lower of complex spring corresponding dish spring 16 respectively arranges upper bearing plate 22 and the lower support plate 21 that steel plate is made, and upper bearing plate 22 and lower support plate 21 are integral with high-damping polyurethane material 17 thermal-adherings.In addition, as a kind of special case, nut 8 directly is used as pre-clamping joint and is used, and by controlling the relative position between nut 8 and junction plate 2, can control the pretightning force be applied in flexible member.
With embodiment seven, compare, this routine described the utility model high frequency mass tuning damper utilizes complex spring that metal stamper spring and elastane make as flexible member, can take full advantage of dish spring rigidity large, long service life, and the advantage such as take up room little.In addition, utilize nut 8 to use as pre-clamping joint, can further reduce the input of material, be conducive to reduce costs.This routine described technical scheme in sum, structure is compacter, takes up room still less, and material drops into still less.
The space structures compactness of the utility model high frequency mass tuning damper, go for the even control of higher frequency structural vibration of 15Hz, cost performance is very superior, it not only can adopt steel spring as flexible member, can also adopt the complex spring of steel spring and elasticity macromolecular material as flexible member, perhaps directly adopt elastic body that the elasticity macromolecular material makes as flexible member, effectively enlarged the scope of application of tuning mass bumper product, market application foreground is very wide.In addition, the embodiment in the utility model is only better explanation the technical solution of the utility model, should not be considered as restriction of the present utility model, and wherein the technical characterictic in many embodiment also can cross-reference.During practical application; quantity and position distribution that flexible member and damping element are used can design as required; pre-pressing structure also can be selected concrete form of structure as required; based on the utility model know-why; those skilled in the art can re-start combination or utilize similar technology simply to replace some element wherein the described technical scheme of above-described embodiment; as long as based on know-why of the present utility model, in the protection domain all required at the utility model.
Claims (8)
1. a high-frequency tuning mass bumper, comprise junction plate, flexible member, damping element and mass, characterized by further comprising pre-clamping joint, mass is arranged between junction plate and pre-clamping joint, reach between mass and junction plate flexible member is set respectively between mass and pre-clamping joint, damping element is arranged between mass and pre-clamping joint or/and between mass and junction plate, between junction plate and pre-clamping joint, pre-pressing structure is set, by pre-pressing structure, flexible member is applied to pretightning force, compression elastic element is until flexible member end and adjacent mass, preload piece or junction plate fully contact, enter the linear change stage that external force that flexible member bears is directly proportional to the compression displacement of flexible member.
2. high-frequency tuning mass bumper according to claim 1, is characterized in that pre-pressing structure comprises pretension connecting rod, pretension hook, pretension chain and pre-locking bracket.
3. high-frequency tuning mass bumper according to claim 2, is characterized in that the middle part of flexible member is provided with cavity, and the pretension connecting rod passes from the cavity at flexible member middle part.
4. high-frequency tuning mass bumper according to claim 2, the two ends that it is characterized in that the pretension connecting rod are respectively equipped with helicitic texture, the pretension connecting rod runs through pre-clamping joint and junction plate setting, utilizes nut to coordinate with helicitic texture, locks the relative position of pre-clamping joint and junction plate.
5. high-frequency tuning mass bumper according to claim 2, an end that it is characterized in that the pretension connecting rod is provided with helicitic texture, the other end is fixed on pre-clamping joint, the end that the pretension connecting rod is threaded structure runs through the junction plate setting, utilize nut to coordinate with helicitic texture, lock the relative position of pre-clamping joint and junction plate.
6. high-frequency tuning mass bumper according to claim 2, an end that it is characterized in that the pretension connecting rod is provided with helicitic texture, the other end is fixed on junction plate, the end that the pretension connecting rod is threaded structure runs through pre-clamping joint setting, utilize nut to coordinate with helicitic texture, lock the relative position of pre-clamping joint and junction plate.
7. high-frequency tuning mass bumper according to claim 6, is characterized in that pre-clamping joint and nut become one.
8. high-frequency tuning mass bumper according to claim 1, is characterized in that damping element and flexible member become one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320410293 CN203361392U (en) | 2013-07-10 | 2013-07-10 | High-frequency tuning mass vibration absorber |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320410293 CN203361392U (en) | 2013-07-10 | 2013-07-10 | High-frequency tuning mass vibration absorber |
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| CN203361392U true CN203361392U (en) | 2013-12-25 |
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| CN 201320410293 Withdrawn - After Issue CN203361392U (en) | 2013-07-10 | 2013-07-10 | High-frequency tuning mass vibration absorber |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334509A (en) * | 2013-07-10 | 2013-10-02 | 隔而固(青岛)振动控制有限公司 | High-frequency tuning mass damper |
| CN103792588A (en) * | 2014-01-20 | 2014-05-14 | 常州容大结构减振设备有限公司 | Cushioning and stabilizing platform of gravity testing equipment |
| CN109853301A (en) * | 2016-12-30 | 2019-06-07 | 青岛科而泰环境控制技术有限公司 | Plate-type ballastless railway roadbed with backpressure device |
-
2013
- 2013-07-10 CN CN 201320410293 patent/CN203361392U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103334509A (en) * | 2013-07-10 | 2013-10-02 | 隔而固(青岛)振动控制有限公司 | High-frequency tuning mass damper |
| CN103334509B (en) * | 2013-07-10 | 2016-03-16 | 隔而固(青岛)振动控制有限公司 | High-frequency tuning mass bumper |
| CN103792588A (en) * | 2014-01-20 | 2014-05-14 | 常州容大结构减振设备有限公司 | Cushioning and stabilizing platform of gravity testing equipment |
| CN109853301A (en) * | 2016-12-30 | 2019-06-07 | 青岛科而泰环境控制技术有限公司 | Plate-type ballastless railway roadbed with backpressure device |
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| C14 | Grant of patent or utility model | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20131225 Effective date of abandoning: 20160316 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |