CN104712697B - Intensive-impact-resistant and inclination-resistant vibration isolator for ship display and control console - Google Patents

Abstract

The invention provides an intensive-impact-resistant and inclination-resistant vibration isolator for a ship display and control console. A base serves as a main frame, and the base, an upper cover and a bottom plate together form a shell. The upper cover is internally provided with a check ring. An adjusting bolt is inserted into the upper cover and is sequentially sleeved with a hexagonal ring, a cap, an adjusting nut, spiral springs and conical springs from top to bottom. Damping reeds and buffer reeds are arranged in an inner circle of the base at intervals and shaped like a cylinder to surround the cap. The upper portion of the adjusting bolt is connected with equipment, and a steel wire net pad is arranged between the lower portion of the adjusting bolt and the bottom plate and used for buffering and limiting of impact below the equipment. A cap outer circle is sleeved with a rubber gasket and used for limiting and buffering impact on the equipment. The cap and the conical springs of the bottom plate are used for enhancing the inclination-resistant performance of the equipment; the damping reeds are different from the buffer reeds in the working curve, and the damping reeds can avoid intensive impact. The safe stress range of the buffer reeds is larger than the actual displacement of the intensive impact. The intensive-impact-resistant and inclination-resistant vibration isolator is capable of being resistant to intensive impact and capable of resetting automatically and maintaining vibration isolation.

Description

Naval vessel indication control board resisting strong impact, vibration isolator resisting inclination

Technical field

The present invention relates to vibration of electronic equipment, impact noise control field, specifically a kind of naval vessel anti-strong punching of indication control board Hit, vibration isolator resisting inclination.

Background technology

Naval vessel indication control board is the terminal presentation facility of electronic apparatus system, is that operator exchange boundary with equipment (people-machine) The key equipment in face, its vibrating isolation system vibration isolator should meet following requirement:

1st, in ship sway, display device vibrating isolation system should have resistance to tilting it is desirable to man-machine relative displacement very little, To ensure that operator remain to see the figure on display and symbol.

At present, in hjb 204-1999 " vessels equipments anti-adverse environment design requirement ", regulation adopts backrest vibration isolation system System, installs 2 backrest vibration isolators at rack back and improves its stability, such as Fig. 2 (a).When indication control board cannot or not allow to pacify During dress backrest vibration isolator, then it is changed into no backrest vibrating isolation system, such as Fig. 2 (b), therefore it is required that bottom vibration isolator is retaining former function Meanwhile, also should increase the function of backrest vibration isolator, that is, there is anti-inclination and preferable self-resetting capability.

2nd, the interfering frequency scope very little being produced due to naval vessel itself, according to the vibration test amount of table c9 in gjb150.16a Value requires, and general surface vessel and submarine sinusoidal vibration frequency are 1-60hz (1-16hz amplitude 1mm；16-60hz1g), it is terrible To preferable vibration isolating effect, its vibration isolator natural frequency fn must be low, general fn≤6hz, in 8hz about start vibration isolation.Test Show, steel-wire isolator (fn ≈ 15hz, start vibration isolation to 21hz), rubber shock absorber (fn ≈ 20hz, 28.3hz start every Shake), when human eye distinguishable pattern modifying frequency fn≤24hz (i.e. per second change 24 times), it is in amplifying or effectiveness in vibration suppression In very poor frequency range, cause the operator cannot resolution graphics and letter symbol.

3rd, not yet promulgated so far due to the relevant criterion of gjb 150.30a-2009 naval vessel impact test and carry out, its thump Test is still carried out by test ten " impact tests of ship's fitting " in gjb150.18-86.Display panel control is a level equipment, that is, such Equipment is naval vessel to be fighted one battle after another and the requisite equipment of safety, and its performance is in impact and should no significant change after impact. It is therefore desirable to the vibrating isolation system of this kind equipment has preferable damping characteristics, in impact and after impact, the flexible member of vibration isolator With the stress of structural member all in the range of safe stress (i.e. elastic limit), its elastic characteristic and damping characteristic all should no substantially become Change.

The Chinese patent of Application No. 03131862.2 discloses a kind of Modular-Type Non-Peak Shock Isolator, this vibration isolation Device is as shown in Figure 3 although also have certain shock resistance, but it has the disadvantages that

1st, adopt linear coil spring as main loaded spring, vibration isolator rigidity is less, reset difficult.

2nd, the metal dry-friction damping needed for resonance free peak transmission characteristic that vibration isolator requires is by between straight reed and cap Dry friction produce, during vertical thump, after cap displacement increases, bending spring piece and straight reed work simultaneously, cause straight reed Stress is excessive and there is permanent deformation, make vibration damping lose it is impossible to keep resonance free peak character.And cap outward flange with During the straight switch jaw contact of this spring combination, between bending spring piece and cap outward flange, gap is now 1.5mm, because gap is excessive, water Flat impact easily cause directly, bending spring piece permanent deformation.Between contact point between cap and straight reed, surface extrusion stress is easily impacted into Indenture.

3rd, only there is buffer limit mat structure during the vertical downward impact of equipment, lack that reply equipment is vertical to be impacted upwards Buffer limit structure.

Content of the invention

The present invention is in order to solve problem of the prior art, there is provided a kind of naval vessel indication control board of no backrest vibrating isolation system is with resisting Thump, vibration isolator resisting inclination, have the anti-tilt function of elastic self-resetting, remain to keep original vibration isolation after standing thump Energy.

The present invention includes base, and base inner circle bottom is fixed with base plate, and the top of base is fixed with lid, base, base plate Collectively constitute the shell of this vibration isolator with upper lid；It is inserted with a regulating bolt, regulating bolt top is fixed with upper lid centre bore Cap, cap bottom stretch into chassis interior along regulating bolt axial direction it is characterised in that: cap lower end be outward flange structure, It is connected with circular cone spring between outward flange and base plate；Regulating bolt bottom is cased with adjusting nut, is connected between adjusting nut and base plate There is spiral spring, spiral spring forms parallel-connection structure with circular cone spring；It is provided with the damping that the outward flange of cap is surrounded in the inner circle of base Buffering reed.

In parallel using non-linear cone spring and linear coil spring, as seen from Figure 10, under the effect of wo load, parallel springs work Make to put at for o, work as δ_νDuring≤2mm, approximately linear characteristic, rigidity ko in parallel of the o point fn required by vibration isolator determines, k₁、k₂ Slope k in o point₁₀、k₂₀By equipment gravity center eccentric situation reasonable distribution, eccentric big, k₁₀<k₂₀, eccentric little, k₁₀≈k₂₀.When inclining When tiltedly, Fig. 8 the right and left spring-loaded point exists respectively | δ_m| a point and b point position, its slope is that rigidity k ≈ df/d δ then differs Very big, k_b＞ ＞ k_a.Therefore, in Fig. 8 (c), indication control board is tilted to the right, and the rigidity of right side parallel springs is k_b, counter-force is f_b, And the rigidity of left side parallel springs is k_a, counter-force is f_aIt can be seen that, f_b＞ ＞ f_a.

According to a rigidity be ko linear principal screw spring when, then in δ_mB' point at counter-force be f_b' it is clear that f_b＞ f_b', then righting moment can increase δ m=(f_b-f_b')atgθ.When vibration isolator is subject to larger horizontal impact, due to increasing Add righting moment, reach elastic self-resetting and the effect of anti-inclination.

Improve further, damping buffering reed includes spaced straight reed and bending spring piece, by opening regulation ring, cone Ring is compressed with vibration isolator shell；When static between the distance between straight reed and cap outward flange and bending spring piece and cap outward flange Range difference be less than or equal to 0.5mm, deformed most 0.5mm palintrope reeds by straight reed during horizontal impact and work.Will be curved Gap between reed and straight reed is reduced to δ≤0.5mm by δ >=1.5mm, can greatly reduce straight reed extrusion stress and Bending stress.

In the middle part of straight reed, damping area is linear structure, and top and the bottom non-damping area is curvilinear structures, and the outward flange of cap only exists With straight switch jaw contact during the motion of damping area.Change originally straight bending spring piece and simultaneously participate in setting of work when vertical impact displacement is larger Meter theory, that is, after vertical impact displacement is more than vibration displacement, straight reed retreats away from cap outward flange, is not involved in work, directly Do not produce impact stress in reed, reach the stability of damping force needed for suppression resonance.

Improve further, described cap outward flange outer surface is sphere, its arc radius is equal to damping buffering reed group Synthesis cylinder inside radius it is ensured that cap main shaft is all contacted with cap outward flange with straight reed during base axis run-off the straight, Reduce the every straight stress of reed and the stability of total frictional force.

Improve further, be cased with back-up ring and rubber blanket on described cap is cylindrical, fitted with upper lid in its guide ring top, rubber Being fitted with the outward flange of cap bottom in rubber cushion bottom, leaves gap between back-up ring and rubber blanket.When cap impacts upwards, act on The power of rubber blanket passes to upper lid by inner shield ring, then passes to basic installing plate by base attachment screw.Running into can during thump To play the effect of suppression bounce-back and limiting displacement impact impact.Gap between inner shield ring and cap also can limit cap axle center Inclination angle between lid axial line on line.

Improve further, between described regulating bolt and base plate, be provided with steel net pad.Using upper and lower two buffer limits Module rubber blanket and steel net pad limit impact displacement, by bending spring piece with rebounce, can be made during thump stress all the time In safe range of stress.

Improve further, in whole damping buffering one layer of horizontal buffering ring rubber tube of spring assembly outer layer bag, cap is applied Impulsive force suffered by reed is directly delivered to base by buffering ring, can substantially reduce the bending stress in reed.

Brief description

Fig. 1 is present configuration schematic diagram.

Fig. 2 (a) is the naval vessel indication control board structural representation using backrest vibrating isolation system.

Fig. 2 (b) is the naval vessel indication control board structural representation not adopting backrest vibrating isolation system.

Fig. 3 is a kind of structural scheme of mechanism of Modular-Type Non-Peak Shock Isolator.

Fig. 4 (a) is that in a kind of Modular-Type Non-Peak Shock Isolator, cap outward flange structure and straight switch jaw contact are illustrated Figure.

Fig. 4 (b) is cap outward flange structure when being subject to vertical thump in a kind of Modular-Type Non-Peak Shock Isolator With straight switch jaw contact schematic diagram.

Fig. 4 (c) is subject to cap outward flange structure and straight switch jaw contact schematic diagram during vertical thump for the present invention.

Fig. 5 is reed mechanics model schematic.

Fig. 6 (a) is straight reed schematic diagram in a kind of Modular-Type Non-Peak Shock Isolator.

Fig. 6 (b) is bending spring piece schematic diagram in a kind of Modular-Type Non-Peak Shock Isolator.

Fig. 6 (c) is the impulsive force schematic diagram that in a kind of Modular-Type Non-Peak Shock Isolator, damping buffering reed is subject to.

Fig. 7 (a) is straight reed schematic diagram in the present invention.

Fig. 7 (b) is bending spring piece schematic diagram in the present invention.

Fig. 7 (c) is the impulsive force schematic diagram that in the present invention, damping buffering reed is subject to.

Fig. 8 (a) is that when assuming that the no backrest vibrating isolation system of indication control board is made up of 4 bottom vibration isolator, height of center of mass is illustrated Figure.Fig. 8 (b) is center of gravity schematic diagram when assuming that the no backrest vibrating isolation system of indication control board is made up of 4 bottom vibration isolator.

Fig. 8 (c) is that the no backrest vibrating isolation system assuming indication control board is made up of 4 bottom vibration isolator, when naval vessel has α to tilt, Barycenter deflects schematic diagram.

Fig. 9 is a kind of vibration isolator resisting inclination structural representation.

Figure 10 is linear coil spring and cone spring characteristic curve.

Specific embodiment

The invention will be further described below in conjunction with the accompanying drawings.

The primary structure of the present invention is as shown in figure 1, include base 14, base 14 inner circle bottom is fixed with base plate 15, base 14 top is fixed with lid 6, and base 14, base plate 15 and upper lid 6 collectively constitute the shell of this vibration isolator；Upper lid 6 center in the holes It is inserted with a regulating bolt 2, regulating bolt 2 top is fixed with cap 3, bottom is stretched into along regulating bolt 2 axial direction in cap 3 bottom Seat 14 internal it is characterised in that: cap 3 lower end is outward flange structure, is connected with circular cone spring 12 between outward flange and base plate 15；Adjust Section bolt 2 bottom is cased with adjusting nut 4, is connected with spiral spring 13, spiral spring 13 and circular cone spring between adjusting nut 4 and base plate 15 12 formation parallel-connection structures；It is provided with the damping buffering reed 9 that the outward flange of cap 3 is surrounded, damping buffering in the inner circle of base 14 The cylinder sleeve that reed 9 is constituted has rubber tube 10.

Described damping buffering reed 9 includes spaced straight reed and bending spring piece, by opening regulation ring 8, conical ring 7 With vibration isolator shell compression；When static between the distance between straight reed and cap 3 outward flange and bending spring piece and cap 3 outward flange Range difference be less than or equal to 0.5mm, deformed most 0.5mm palintrope reeds by straight reed during horizontal impact and work；Straight spring In the middle part of piece, damping area is linear structure, and top and the bottom non-damping area is curvilinear structures, and the outward flange of cap 3 is only when damping area's motion With straight switch jaw contact.

Described cap 3 outward flange outer surface is sphere, the cylinder that its arc radius is combined into equal to damping buffering reed 9 Inside radius.

It is cased with back-up ring 5 and rubber blanket 11, fitted with upper lid 6 in its guide ring 5 top, rubber blanket on described cap 3 is cylindrical Being fitted with the outward flange of cap 3 bottom in 11 bottoms, leaves gap between back-up ring 5 and rubber blanket 11.Described regulating bolt 2 and bottom It is provided with steel net pad 16 between plate 15.

The designing points of the present invention are as follows:

1st, anti-inclination and elastic self-resetting design

Linear coil spring is adopted in the Modular-Type Non-Peak Shock Isolator of Application No. 03131862.2 shown in Fig. 3 As main loaded spring, due to fn≤5-6hz, so its vibration isolator rigidity is less.

K=(2 π f_n)²×m₁n/m

In formula, f_n-- the low natural frequency that vibration isolation needs

m₁-- the actual bearer amount of each vibration isolator

Assume that the no backrest vibrating isolation system of indication control board is made up of 4 bottom vibration isolator, height of center of mass is hc (Fig. 8 a), center of gravity C is overlapped (Fig. 8 b) with vibration isolator supporting plane center o, and when naval vessel has α to tilt, barycenter c is biased to c'(Fig. 8 c) δ_On=δ_Under=atg θ, tilting moment is m_a=mg h_cTg θ, righting moment is m_k=4k δ_On=4katg θ.Spring reset condition m_k＞ m_a.

During using linear main spring, if improve rigidity k can be limited by fn, increase righting moment m for this_k, just need to increase a (or b) size, such as a, b is restricted, then reset highly difficult.For this reason, we employ the Application No. shown in Fig. 9 There is provided in a kind of 201320211180.9 Chinese patent " vibration isolator resisting inclination " carries out the spacing design concept of construction forces.

Connecting bolt bottom in Fig. 9 is extended, is inserted in axle bed, and in addition spacing using spacing collar, that is, utilize frame for movement Limit the corner displacement of vibration isolator itself.Practical application proves, this structure limits and reset function is obvious, but in thump Under effect, the downward shaft distortion easily causing connecting bolt is stuck, makes vibration isolator follow the string characteristic it is impossible to vibration damping.

Patent of the present invention adopts non-linear cone spring and linear coil spring in parallel, to increase righting moment m_kTechnology, with When retain 03131862.2 Modular-Type Non-Peak Shock Isolator bearing capacity adjustable characteristics.Its operation principle is:

Patent of the present invention adopts linear coil spring k₁Cone spring k non-linear with taper₂Parallel-connection structure.

k₁For linear coil spring characteristic curve, its effect is regulation actual bearer amount wo when equipment has bias, and to plan Closing curve shape is matching stiffness effect very little.

(1)k₂For bore spring characteristic curve, as seen from Figure 10, wo load effect under, parallel springs operating point for o at, Work as δ_νDuring≤2mm, approximately linear characteristic, rigidity ko in parallel of the o point fn required by vibration isolator determines, k₁、k₂Oblique in o point Rate k₁₀、k₂₀By equipment gravity center eccentric situation reasonable distribution, eccentric big, k₁₀<k₂₀, eccentric little, k₁₀≈k₂₀.When inclined, Fig. 8 is left Right both sides spring-loaded point exists respectively | δ_m| a point and b point position, its slope is that rigidity k ≈ df/d δ then differs greatly, k_b＞ ＞ k_a.Therefore, in Fig. 8 (c), indication control board is tilted to the right, and the rigidity of right side parallel springs is k_b, counter-force is f_b, and left side parallel connection bullet The rigidity of spring is k_a, counter-force is f_aIt can be seen that, f_b＞ ＞ f_a.

It is k according to a rigidity_oLinear principal screw spring when, then in δ_mB' point at counter-force be f_b' it is clear that f_b＞ f_b', then righting moment can increase δ m=(f_b-f_b') atg θ, make vibrating isolation system be easy to reset.

According to defined f_nObtain k_o, required righting moment δ m size, and vibration isolator installs a and b size, then may be used By k_oValue reasonable distribution k₁、k₂Shared ratio and the nonlinear characteristic of cone spring.

2nd, damping buffering spring component stress optimizes

2.1 straight reed stress optimization

A) in the Modular-Type Non-Peak Shock Isolator of Application No. 03131862.2 shown in Fig. 3, claim 1 Described damping buffering spring assembly is resonance free peak transmission characteristic η requiring vibration isolator_νMetal dry-friction damping needed for≤1 Produced by the dry friction between straight reed and cap, such as shown in Fig. 6 (a).During vertical thump, such as shown in Fig. 6 (c), cap After displacement increases, bending spring piece and straight reed work simultaneously, cause straight reed stress excessive and permanent deformation occurs, and so that vibration is hindered Buddhist nun loses it is impossible to keep resonance free peak character, such as shown in Fig. 4 (b).

B) during the straight switch jaw contact of cap outward flange and this spring combination, gap delta between bending spring piece and cap outward flange >= 1.5mm, so easily causing in horizontal impact, straight bending spring piece flexural deformation is excessive, its stress is more than allowable stress, and leads to forever Deform long.

Due to r≤3mm Fig. 4 (b) of cap lug, between the contact point between cap and straight reed, surface extrusion stress increases Greatly, easily impact into indenture.

Circumferentially equally distributed straight reed inner surface be a radius be r02 (approximate cap r01) cylindrical drum, cap Outward flange is the circular arc of r≤3mm, then as shown in Fig. 4 (a), when table periphery run-off the straight in cap main shaft with straight reed When, only two or several straight reed participation work in theory, so that the stress in these straight reeds is increased, and always rub Power reduces, and causes damping characteristic unstable.

Therefore cap outer flange surface is changed to the sphere that radius is r02 by patent of the present invention, when cap and straight reed inner core It is ensured that all straight reeds are contacted with cap when axis tilts, thus reducing the stress and strain in every straight reed, such as Fig. 4 (c).Simultaneously as the outward flange arc radius r≤3mm in cap (2) increases to the sphere of r=r02, greatly reduce level Contact squeeze stress between cap and straight reed and holding damping characteristic during impact, as shown in Figure 4.

C) gap between bending spring piece and straight reed is reduced to δ≤0.5mm by δ >=1.5mm, that is, straight when horizontal impact Reed deforms 0.5mm, and bending spring piece is worked, and can greatly reduce extrusion stress and the bending stress of straight reed.

In the middle part of the straight reed (as shown in Figure 7a) that the present invention uses, damping area is linear structure, the non-damping in top and the bottom Qu Weiqu Line structure, with straight switch jaw contact when the outward flange of cap only moves in damping area.Change originally straight bending spring piece in vertical impact position Simultaneously participate in the design concept of work when moving larger, that is, after vertical impact displacement is more than vibration displacement, straight reed retreat away from Cap outward flange, is not involved in work, does not produce impact stress in straight reed.

D) reed Mechanics Calculation

Reed mechanical model is shown in Fig. 5, and in figure c point is equilibrium point under nominal load, and p is due to cap and reed mistake during design It is full of and deform f_cAnd the normal pressure producing, 3 points of moments of flexure of a, b, c are:

$\begin{array}{ccc}{m}_a=\frac{p\&centerdot;x{(l-x)}^2}{l^2}& m_b=\frac{p\&centerdot;x^2(l-x)}{l^2}& m_c=\frac{2p\&centerdot;x^2{(l-x)}^2}{l^3}\end{array}---\left(1\right)$

Equilibrium point is deformed into:

$f_c=\frac{p\&centerdot;x^3{(l-x)}^3}{3{\mathrm{ej}}_z{l}^3}---\left(2\right)$

Material can allow the maximal bending moment to be:

${\mathrm{\&sigma;}}_{max}=\frac{m_{max}}{w}\&le;\&lsqb;\mathrm{\&sigma;}\&rsqb;$

m_max=[σ] w (3)

In formula, e elastic modelling quantity；

j_zThe moment of inertia；

W composite bending modulus；

[σ] material allowable stress.

Formula (3) is substituted into (2) and obtains bending spring piece permission deformation formula

$f_c=\frac{\&lsqb;\mathrm{\&sigma;}\&rsqb;w\&centerdot;x(l-x)}{6{\mathrm{ej}}_z}---\left(4\right)$

As x=l/2, maximum allowable it is deformed into

$f_{max}=\frac{\&lsqb;\mathrm{\&sigma;}\&rsqb;w{(l/2)}^2}{6{\mathrm{ej}}_z}---\left(5\right)$

Reed other each point permission deformation equation formula is:

$f_c=\frac{\&lsqb;\mathrm{\&sigma;}\&rsqb;w\&centerdot;x^2(l-x)}{3{\mathrm{ej}}_{z}l}---\left(6\right)$

Accordingly, reed can be optimized with design, that is, control reed to produce maximum distortion in safe range of stress, from And so that reed both can have most effectively been dissipated impact energy and its stress is safe in operation interval.

2.2 bending spring piece stress optimization

Shown in bending spring piece such as Fig. 6 (b) in Modular-Type Non-Peak Shock Isolator.The present invention adopts upper and lower two bufferings Spacing module rubber blanket and steel net pad limit impact displacement, and the stress making bending spring piece (shown in Fig. 7 b) is all the time in safe stress model In enclosing, shown in schematic diagram such as Fig. 7 (a), (b), (c).Its structure chart is as shown in Figure 1.

In whole damping buffering one layer of horizontal buffering ring rubber tube of spring assembly outer layer bag, by the impulsive force suffered by bending spring piece Directly base is delivered to by buffering ring, the bending stress in reed can be substantially reduced, such as shown in Fig. 7 (c).

3rd, anti-rebounce design during thump

When the Modular-Type Non-Peak Shock Isolator of Application No. 03131862.2 only has equipment vertical downward impact Buffer limit mat structure, in a kind of vibration isolator resisting inclination of Application No. 201320211180.9 vertical up and down impact when all no Buffer limit pad component.The present invention (Fig. 1) increases the buffer limit pad component rubber blanket and back-up ring during the vertical impact upwards of equipment, When cap impacts upwards, the power acting on rubber blanket passes to upper lid by back-up ring, then passes to basis peace by base attachment screw Dress plate.Gap between back-up ring and cap also can limit the inclination angle between lid axial line on cap axial line.

Concrete application approach of the present invention is a lot, the above be only the preferred embodiment of the present invention it is noted that for For those skilled in the art, under the premise without departing from the principles of the invention, some improvement can also be made, this A little improvement also should be regarded as protection scope of the present invention.

Claims (5)

1. a kind of naval vessel indication control board resisting strong impact, vibration isolator resisting inclination, including base (14), base (14) inner circle bottom is fixed Have base plate (15), the top of base (14) is fixed with lid (6), base (14), base plate (15) and upper lid (6) collectively constitute this every Shake the shell of device；It is inserted with a regulating bolt (2), regulating bolt (2) top is fixed with cap (3), cap in upper lid (6) centre bore Lid (3) bottom along regulating bolt (2) axially stretch into base (14) internal it is characterised in that: cap (3) lower end is that outward flange is tied It is connected with circular cone spring (12) between structure, outward flange and base plate (15)；Regulating bolt (2) bottom is cased with adjusting nut (4), adjusts spiral shell It is connected with spiral spring (13), spiral spring (13) forms parallel-connection structure with circular cone spring (12) between female (4) and base plate (15)；Base (14) it is provided with the damping buffering reed (9) that the outward flange of cap (3) is surrounded in inner circle, outside described cap (3) outward flange Surface is sphere, the cylinder inside radius that its arc radius is combined into equal to damping buffering reed (9).

2. naval vessel according to claim 1 indication control board resisting strong impact, vibration isolator resisting inclination it is characterised in that: described Damping buffering reed (9) includes spaced straight reed and bending spring piece, by opening regulation ring (8), conical ring (7) and vibration isolator Shell compresses；When static between the distance between straight reed and cap (3) outward flange and bending spring piece and cap (3) outward flange away from Deviation is less than or equal to 0.5mm, is deformed most 0.5mm palintrope reeds by reed straight during horizontal impact and works；In straight reed Damping area of portion is linear structure, and top and the bottom non-damping area is curvilinear structures, the outward flange of cap (3) only when damping area's motion with Straight switch jaw contact.

3. naval vessel according to claim 1 and 2 indication control board resisting strong impact, vibration isolator resisting inclination it is characterised in that: described Cap (3) cylindrical on be cased with back-up ring (5) and rubber blanket (11), fitted with Shang Gai (6) in its guide ring (5) top, rubber blanket (11) fitted with the outward flange of cap (3) bottom in bottom, leaves gap between back-up ring (5) and rubber blanket (11).

4. naval vessel according to claim 3 indication control board resisting strong impact, vibration isolator resisting inclination it is characterised in that: described It is provided with steel net pad (16) between regulating bolt (2) and base plate (15).

5. naval vessel according to claim 1 and 2 indication control board resisting strong impact, vibration isolator resisting inclination it is characterised in that: described The cylinder sleeve that constitutes of damping buffering reed (9) have rubber tube (10).