CN112855835A - Vibration damper for weapon station vibration damping alloy - Google Patents
Vibration damper for weapon station vibration damping alloy Download PDFInfo
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- CN112855835A CN112855835A CN202011529245.5A CN202011529245A CN112855835A CN 112855835 A CN112855835 A CN 112855835A CN 202011529245 A CN202011529245 A CN 202011529245A CN 112855835 A CN112855835 A CN 112855835A
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- disc spring
- weapon station
- vibration
- damping
- guide rod
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/073—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only leaf springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2224/00—Materials; Material properties
- F16F2224/02—Materials; Material properties solids
- F16F2224/0208—Alloys
Abstract
The invention provides a vibration damping device of a weapon station vibration damping alloy. The method comprises the following steps: the damper comprises a base, a sleeve, a guide rod and a disc spring structure; a cradle and a gun body; the cradle and the sleeve are fixedly connected with the base respectively, one end of the guide rod is fixedly connected with the gun body, and the launching direction of the gun body is consistent with the extending direction of the guide rod; the disc spring structure and the other end of the guide rod are arranged in the sleeve, one end, far away from the guide rod, of the sleeve is provided with a limiting end, when the gun body launches a cannonball, the guide rod drives the disc spring structure to move towards the limiting end, and the limiting end is used for compressing the disc spring structure. The vibration damping device of the weapon station vibration damping alloy solves the problems that the rectangular spiral spring of the damper in the prior art has overlarge recoil displacement, secondary impact and low energy absorption rate.
Description
Technical Field
The invention relates to the technical field of weapon station vibration reduction, in particular to a vibration reduction device for a weapon station vibration reduction alloy.
Background
The vibration-damping alloy is widely applied to metal damping materials in the fields of precision machinery, rail transit, nuclear power, high-rise buildings, automobiles, marine equipment and aerospace, has an energy consumption mechanism generated by unique bicrystal activity of the vibration-damping alloy, can effectively absorb vibration and achieve the effects of vibration and noise reduction;
violent vibration can be generated when the weapon station shoots, so that the direction of a muzzle is changed, the shooting precision is seriously influenced, and the vibration can be effectively reduced by installing the vibration reduction device for the weapon station. The damping device of the existing weapon station mainly depends on a spring damper, a rectangular spiral spring is arranged in the damping device, the damping effect is not ideal, the muzzle vibration of the weapon station is still severe, and particularly the rectangular spiral spring has the problems of large recoil displacement, obvious secondary impact phenomenon, low energy absorption rate and the like.
The vibration-damping alloy belongs to a novel damping alloy material, has the characteristics of high damping, high strength, easiness in processing and the like, and is widely applied to the aspects of mechanical equipment vibration-damping supports, submarine propellers, nuclear power equipment vibration absorbers and the like at present. The damping performance of the damping material is close to that of rubber, but the strength of the damping material is comparable to that of structural steel, and the damping material has a plurality of advantages which cannot be achieved by the traditional damping material. Therefore, the vibration-damping alloy is applied to a weapon station, and a novel vibration-damping alloy vibration damping device is designed to reduce the influence of vibration on a muzzle and has important significance for improving the shooting precision.
Disclosure of Invention
The invention aims to provide a vibration damping device for a weapon station vibration damping alloy, which can solve the problems of large recoil displacement, obvious secondary impact phenomenon and low energy absorption rate of a rectangular spiral spring of a damper in the prior art.
In order to achieve the above purpose, the invention provides the following technical scheme:
a damping device for a weapon station damping alloy, comprising: the damper comprises a base, a sleeve, a guide rod and a disc spring structure;
a cradle and a gun body; the cradle and the sleeve are fixedly connected with the base respectively, one end of the guide rod is fixedly connected with the gun body, and the launching direction of the gun body is consistent with the extending direction of the guide rod; the disc spring structure is made of vibration-damping alloy;
the disc spring structure and the other end of the guide rod are arranged in the sleeve, one end, far away from the guide rod, of the sleeve is provided with a limiting end, when the gun body launches a cannonball, the guide rod drives the disc spring structure to move towards the limiting end, and the limiting end is used for compressing the disc spring structure.
On the basis of the technical scheme, the invention can be further improved as follows:
furthermore, the damper is provided with a first nut, a second nut and a compression nut, the first nut is fixedly connected with the sleeve, the guide rod is connected with the sleeve in a sliding manner, and the second nut is fixedly connected with the sleeve and sleeved on the compression nut; the compression nut is fixedly connected with the guide rod.
Further, the weapon station also comprises an incomplete gear structure, and the incomplete gear structure is fixedly connected with the cradle.
Furthermore, the incomplete gear structure comprises a damping fin, an incomplete gear fixing frame and an incomplete gear, wherein the damping fin is arranged between the incomplete gear fixing frame and the incomplete gear and used for damping.
Further, the incomplete gear fixing frame is fixedly connected with the cradle.
Further, the damping fin, the incomplete gear fixing frame and the incomplete gear are fixedly connected.
Furthermore, the vibration damper further comprises a gasket structure, the gasket structure comprises a first flange gasket and a second flange gasket, the weapon station is provided with a weapon station base, the first flange gasket is fixedly connected with the weapon station base, and a flange plate is arranged between the first flange gasket and the second flange gasket.
Further, the gasket structure further comprises a damping plug, and the damping plug is arranged between the first flange gasket and the second flange gasket.
Furthermore, the dish spring structure includes 8 dish springs, and 2 adjacent dish spring structures are involutory each other.
Furthermore, the disc spring structure formed by the mutual involution of the 8 disc springs comprises a single-layer disc spring structure and a three-layer composite disc spring structure.
The invention has the following advantages:
according to the vibration damping device for the vibration damping alloy of the weapon station, the disc spring structure formed by the mutual involution of 8 disc springs is arranged in the sleeve, so that when a gun body launches a cannonball, the guide rod drives the disc spring structure to move towards the limiting end, the disc spring structure is pressed by the limiting end, and the actual working condition of the damper can be met; the problems that a rectangular spiral spring of the damper in the prior art is large in recoil displacement, obvious in secondary impact phenomenon and low in energy absorption rate are solved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a schematic diagram of the overall configuration of a weapon station according to an embodiment of the invention;
FIG. 2 is an enlarged view of the structure at A;
FIG. 3 is a view showing the internal structure of the structure at A;
FIG. 4 is a schematic illustration of the position of the partial gear structure at the weapon station in an embodiment of the present invention;
FIG. 5 is a schematic illustration of a partial gear configuration in an embodiment of the present invention;
FIG. 6 is a schematic structural diagram of a 5000N disc spring according to an embodiment of the present invention;
FIG. 7 is a schematic structural diagram of a 3000N disc spring according to an embodiment of the present invention;
FIG. 8 is a schematic diagram of a computational model of a spring single piece without a support surface according to an embodiment of the invention;
FIG. 9 is a diagram of a finite element mesh model of a weapon station in an embodiment of the present invention;
FIG. 10 is a diagram illustrating input parameters of a 3000N disc spring in accordance with an embodiment of the present invention;
FIG. 11 is a schematic view of a laminated combination disc spring according to an embodiment of the present invention;
FIG. 12 is a schematic view of a sectional combination spring according to an embodiment of the present invention;
FIG. 13 is a schematic diagram of 5000N disc spring input parameters according to an embodiment of the present invention;
FIG. 14 is a table showing the effectiveness of damping at 47.5Hz for different X-direction schemes in an embodiment of the present invention;
FIG. 15 is a table showing the vibration damping effect at 47.5Hz in different Z-direction schemes in the embodiment of the present invention;
FIG. 16 is a table showing the effective damping effect of different schemes in the X direction at 0-500Hz in the embodiment of the present invention;
FIG. 17 is a table showing the effective damping effect of effective damping values of 0-500Hz in different Z-direction schemes in the embodiment of the present invention.
Description of reference numerals:
the damper comprises a damper 10, a base 101, a sleeve 102, a guide rod 103, a first nut 104, a second nut 105, a compression nut 106, a disc spring structure 20, a disc spring 201, a cradle 30, a gun body 40, an incomplete gear structure 50, a damping sheet 501, an incomplete gear fixing frame 502, an incomplete gear 503, a gasket structure 60, a first flange gasket 601 and a second flange gasket 602.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the following embodiments, and it should be understood that the described embodiments are some, but not all, embodiments of the present invention. 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 invention.
Example 1
As shown in fig. 1 to 6, the present invention provides a damping device for a weapon station damping alloy, comprising:
a damper 10 including a base 101, a sleeve 102, a guide rod 103, and a disc spring structure 20;
the disc spring structure 20 and the other end of the guide rod 103 are disposed in the sleeve 102, one end of the sleeve 102, which is away from the guide rod 103, is provided with a limiting end, when the gun body 40 fires the shell, the guide rod 103 drives the disc spring structure 20 to move towards the limiting end, and the limiting end is used for compressing the disc spring structure 20.
The vibration-damping alloy is a metal damping material which fills up the domestic blank and can be widely applied to the fields of precision machinery, rail transit, nuclear power, high-rise buildings, automobiles, ship equipment and aerospace. Is also one of the special metals with the highest manganese content (Mn > 72%) known at present. The vibration-damping alloy belongs to a high-strength damping material with a twin-crystal structure, and under the action of periodic stress, a large number of coherent twin-crystal interfaces closely related to thermoelastic martensite phase change are rearranged and generate inelastic strain to relax the stress, so that external vibration energy is dissipated, and the effects of vibration reduction and noise reduction are achieved.
That is, when pressure is applied to the crystals, the crystals will undergo a certain degree of elastic deformation; increasing the pressure, and generating double crystals in the crystallization; on the basis of this, when the applied pressure is increased, the growth of twins is causedAnd expansion, and even new twins in other areas. However, when the pressure is released, the twins will automatically shrink until they disappear, and the crystal shape will return to the original state. The damping alloy has an energy consumption mechanism generated by the unique twinning activity, so that vibration can be effectively absorbed, and the effects of vibration reduction and noise reduction are achieved. The material parameters of the vibration-damping alloy are shown in FIG. 1, and the density of the vibration-damping alloy is 7.25g/cm3Poisson's ratio is 0.338, elastic modulus is 80Gpa, yield strength is 240MPa, and tensile strength is 540 MPa.
The strength of the disc spring 201 is calculated based on an empirical formula for the disc spring 201 design in the manual sixth edition of the mechanical design, and a calculation model of the disc spring 201 is shown in fig. 8.
The load calculation formula of the disc spring 201 is:
the stress calculation formula of the disc spring 201 is as follows:
wherein F is the load of a single disc spring, N; t is the thickness of the disc spring, mm; d is the outer diameter of the disc spring, mm; f is the deformation of the single disc spring, mm; h is0-the calculated value of the deflection when the disc spring is flattened, mm; e-the elastic modulus of the disc spring material, MPa; μ -Poisson's ratio; calculating coefficients
Wherein
For disc spring K without supporting surface4＝1。
Fig. 10 is a schematic diagram of input parameters of a 3000N disc spring according to an embodiment of the present invention.
The load F of the single disc spring 201 is 1103N by substituting the formula 1 and the formula 2, the stress of the disc spring 201 is 222.4Mpa, which is smaller than the yield strength 240Mpa of the vibration damping alloy, and the strength requirement is met. The load of the disc spring 201 can not meet the strength requirement of the original damper.
As shown in fig. 7, the combination of the combined disc springs is adopted, and three pieces of the combined disc springs are firstly overlapped, and eight pairs of the combined disc springs are firstly combined.
Wherein the load and deformation of the disc spring overlap are calculated, as shown in fig. 11, the load F of the disc spring overlap is calculated without counting the frictional forceZThe deformation amount is the same as that of the single sheet.
Wherein the load and deformation of the involution of the disc spring are calculated, as shown in fig. 12, the deformation f of the involution of the disc spring is calculated without counting the friction forceZThe load is the same as for the single sheet.
The combined spring used this time is shown in fig. 7: firstly, overlapping three layers of disc springs, and then overlapping eight groups of overlapped groups for involution, so that the deformation of the combined disc spring is 0.25X 2X 4-2 mm; the bearing load is 1103X 3-3309N, the stress is 222.37Mpa, which is less than the yield strength of the vibration-damping alloy material, and the strength requirement is satisfied.
Due to the damping effect of the friction force between the disc springs 201, the rigidity of the superposed combined disc spring is increased compared with theoretical calculation, the deformation amount of the superposed disc springs is sequentially decreased, and the transmission of the external force of the combined disc spring used under the impact load is also sequentially decreased for each plate, so that the number of the adopted combined disc springs is not too large, in addition, a 5000N impact load damper with higher requirement is provided for the damper 10, and 8 superposed combined disc springs are designed.
The load F of the single disc spring 201 is 5355.7N by substituting the formula 1 and the formula 2, the stress of the disc spring 201 is 226.8MPa, which is smaller than the yield strength 240MPa of the vibration damping alloy, and the strength requirement is met. Because the load of the disc spring 201 can not meet the strength requirement of the original damper 10, a combination form of eight involutory disc springs 201 is adopted.
Fig. 13 is a schematic diagram of input parameters of a 5000N disc spring 201 according to an embodiment of the present invention.
The combined spring adopted by the scheme is shown in figure 6: the 8 disc springs 201 are firstly combined, so that the deformation of the combined disc spring is 0.17 × 2 × 4 to 1.36 mm; the bearing load is 5355N, the stress is 226.82Mpa, and the stress is smaller than the yield strength of the vibration-damping alloy material, so that the strength requirement is met.
The damper 10 is provided with a first nut 104, a second nut 105 and a compression nut 106, the first nut 104 is fixedly connected with the sleeve 102, the guide rod 103 is slidably connected with the sleeve 102, and the second nut 105 is fixedly connected with the sleeve 102 and sleeved on the compression nut 106; the compression nut 106 is fixedly connected with the guide rod 103.
The weapon station also comprises an under-gear structure 50 and a pinion, said under-gear structure 50 being solidly connected to said cradle 30. The pinion gear meshes with the incomplete gear 503.
The incomplete gear structure 50 includes a damping plate 501, an incomplete gear fixing frame 502 and an incomplete gear 503, wherein the damping plate 501 is disposed between the incomplete gear fixing frame 502 and the incomplete gear 503.
The incomplete gear fixing frame 502 is fixedly connected with the cradle 30.
The damping plate 501, the incomplete gear fixing frame 502 and the incomplete gear 503 are fixedly connected.
The damping device further comprises a gasket structure 60, wherein the gasket structure 60 comprises a first flange gasket 601 and a second flange gasket 602, the weapon station is provided with a weapon station base, the first flange gasket 601 is fixedly connected with the weapon station base, and a flange plate is arranged between the first flange gasket 601 and the second flange gasket 602.
The gasket structure 60 further comprises a damping plug, which is arranged between the first flange gasket 601 and the second flange gasket 602. The disc spring structure 20 includes 8 disc springs 201, and 2 adjacent disc spring structures 20 are mutually involuted. The disc spring structure 20 formed by the mutual involution of the 8 disc springs 201 comprises a single-layer disc spring structure and a three-layer composite disc spring structure.
Because the vibration degree of the weapon station has important influence on the design precision, the vibration characteristics of different vibration-making alloy schemes on the muzzle of the weapon station are qualitatively compared by combining the high damping advantage of alloy manufacturing based on an ANSYS Workbench simulation platform and by using the syntropy harmonic response vibration analysis.
A simplified original model of the vibration analysis of the weapon station is shown in fig. 9, in which the X-axis is the horizontal direction of the gun shaft and the Z-axis is the vertical direction of the gun shaft; in order to ensure the accuracy of vibration analysis, the grid division of the weapon station is controlled, the main body adopts hexahedron units, the total node number of the grid is 837518, and the total unit number of the grid is 308146.
This time, mainly three vibration damping scheme vibration analyses are performed, as shown in fig. 1:
the scheme of the weapon station base of the weapon station is shown in figure 1, and a 3mm flange gasket, a damping plug and two combined actions are arranged on the upper part and the lower part of the weapon station base;
the damping plug and damping fin weapon station base scheme of the incomplete gear structure 50 in the weapon station pitching mechanism is shown in FIG. 5, and a damping plug and a damping fin 501 are adopted; wherein, the weapon station damper scheme adopts a disc spring 201 and a damper damping gasket scheme.
In order to analyze the inherent vibration characteristics of the weapon station, the simplified weapon is subjected to modal analysis, the modal analysis boundary conditions of the weapon station are applied to the base of the weapon station, the 1 st order and the 2 nd order are respectively bending vibration of the gun rod in the X direction and the Z direction, the frequency is low, and the bending vibration of the first 2 nd order is emphasized to be reduced because the excitation frequency is 10 Hz.
In order to analyze whether the natural frequency of the weapon station after the vibration damping scheme is added has influence, the modal frequencies of different vibration damping schemes are respectively calculated, the natural frequency and the vibration mode of the first two orders of the whole weapon station provided with the vibration damping alloy structural scheme are basically unchanged, therefore, the provided structural scheme basically does not change the natural vibration characteristic of the original weapon station, in addition, the natural frequency of different schemes is analyzed and compared in the range of 0-500H, and the influence of different vibration damping alloy vibration damping schemes on the natural frequency and the vibration mode of the weapon station is basically unchanged.
The boundary condition of the harmonic response analysis of the weapon station adopts the fixed constraint of the bottom surface of a base of the weapon station, the axial direction of a gun rod applies 9600N sine exciting force, and different vibration reduction effects are compared by extracting the accelerated speeds of different schemes of the end part of the gun head.
The modal analysis shows that the first two-step vibration of the weapon station is mainly concentrated on the vibration in the X-axis direction and the Z-axis direction, the resonance frequency of the X-direction vibration acceleration obtained through harmonic response is 47.5Hz, and the resonance frequency is basically consistent with the first-order 46.79Hz and the second-order 47.497Hz of the original weapon station obtained through the previous modal analysis, so that the first two-step frequency of the weapon station generates coupling in the X-direction vibration and is close to the excitation frequency of 10Hz, the calculation result shows that the vibration damping effect of the scheme of the common damper bolt gasket and the weapon station base damping plug is basically not existed, and the X-direction acceleration is reduced by 0.04dB under 47.5 Hz; the vibration reduction effect is optimal under 47.5Hz frequency of a common damper bolt gasket, an incomplete gear damping plug and a 3mm damping fin, and is reduced by 41.13 dB; the X-direction acceleration of the weapon station base with the flange gaskets of 3mm up and down is reduced by 6.05 dB; the combination scheme of the upper and lower 3mm flange gaskets and the weapon station base damping plug is reduced by 6.22 dB. The vibration reduction effect of the damping plug is basically unchanged; the damping effect of the scheme of adding the damper damping gasket and the 3000N disc spring is basically unchanged and is about 31 dB; the scheme of adding the damper damping gasket and the 5000N disc spring is reduced by 9.48dB compared with the scheme of the 5000N disc spring; the damping effect of the other solutions is shown in fig. 14.
The resonance frequency of Z-direction vibration acceleration obtained by harmonic response is 47.5Hz, and is basically consistent with the first-order 46.79Hz and the second-order 47.497Hz of the original weapon station obtained by the previous modal analysis, which shows that the first two-order frequency of the weapon station generates coupling in X-direction vibration and is close to the excitation frequency of 10Hz, and the calculation result shows that the vibration damping effect of the scheme of the common damper bolt gasket and the weapon station base damping plug is basically not existed, and the X-direction acceleration is reduced by 0.04dB under 47.5 Hz; the vibration reduction effect is optimal under the 50147.5Hz frequency of the bolt gasket, the incomplete gear damping plug and the 3mm damping sheet of the common damper, and 40.07dB is reduced; the X-direction acceleration of the weapon station base with the flange gaskets of 3mm up and down is reduced by 6.04 dB; the combination scheme of the upper and lower 3mm flange gaskets and the weapon station base damping plug is reduced by 6.21dB, which shows that the vibration reduction effect of the weapon station base damping plug is basically unchanged; the damping effect of the scheme of adding the damper damping gasket and the 3000N disc spring is basically unchanged and is about 31 dB; the scheme of adding the damper damping gasket and the 5000N disc spring is reduced by 9.23dB compared with the scheme of 5000N single disc spring; the damping effect of the other solutions is shown in fig. 15.
The vibration reduction effect of the X direction and the Z direction at the frequency of 47.5Hz can be qualitatively obtained, wherein the effect of a common damper bolt gasket, an incomplete gear damping plug and a 3mm damping sheet is the best, then the vibration reduction scheme of the damper bolt gasket and a disc spring 50000N is adopted, and finally the common damper bolt gasket and a weapon station base up-down 3mm flange gasket are adopted.
Harmonic response analysis calculates the weapon station 0-500Hz, and counts the effective value in the frequency range, and the calculation result shows that the damping effect is the best when the bolt gasket of the common damper and the damper 3000N are used, the effective value is reduced by 12.12dB, and the effect is 2.41dB lower than that of the scheme of adding the damping gasket of the damper, because the damping of the scheme of the damping gasket of the damper is better than that of the high frequency band at the low frequency, and in addition, the scheme of the damper 3000N is better than that of the damper 5000N within the frequency range of 0-500 Hz; the vibration reduction effect of the scheme of the bolt gasket of the common damper and the damping plug of the weapon station base is basically not existed, and the effective value of the X-direction acceleration is reduced by 0.06 dB; the vibration reduction effect of the common damper bolt gasket, the incomplete gear damping plug and the 1mm damping fin under the frequency of 0-500Hz is better than that of 3mm, and is reduced by 9.42 dB; the X-direction acceleration of the weapon station base with the flange gaskets of 3mm up and down is reduced by 6.11 dB; the combination scheme of the upper and lower 3mm flange gaskets and the weapon station base damping plug is reduced by 6.27dB, which shows that the vibration reduction effect of the weapon station base damping plug is basically unchanged; the damping effect of the other solutions is shown in fig. 16.
The comparison of the Z-direction vibration acceleration of the muzzle of the 0-500Hz weapon station shows that the vibration reduction effect of the damper vibration reduction gasket and the disc spring under 3000N is optimal, the vibration reduction effect is reduced by 11.08dB and is 1.12dB lower than that of the damper vibration reduction gasket and the disc spring with 5000N, and the vibration reduction effect of the damper scheme for mounting the vibration reduction gasket is better than that of the common damper gasket; the vibration reduction effect of the scheme of the bolt gasket of the common damper and the damping plug of the base of the weapon station is basically not existed, and the effective value of the Z-direction acceleration is reduced by 0.05 dB; the vibration reduction effect of the common damper bolt gasket, the incomplete gear damping plug and the 3mm damping fin under the frequency of 0-500Hz is better than that of 1mm, and is reduced by 9.95 dB; the X-direction acceleration of the weapon station base with the flange gaskets of 3mm up and down is reduced by 4.27 dB; the combination scheme of the upper and lower 3mm flange gaskets and the weapon station base damping plug is reduced by 4.39dB, which shows that the vibration reduction effect of the weapon station base damping plug is basically unchanged; the damping effect of the other solutions is shown in fig. 17.
According to the method, the weapon station is analyzed in two frequency ranges of 0-100Hz and 0-500Hz, and as the excitation frequency of the weapon station is 10Hz, the natural frequency which is closer to the excitation frequency is easy to cause resonance, the selected scheme has a good vibration reduction effect at low frequency as much as possible, and meanwhile, the 0-500Hz frequency also has a certain vibration reduction effect, so that the damper vibration reduction gasket scheme and the vibration reduction scheme of the 5000N disc spring structure 20 meet the requirements in conclusion; secondly, adopting a scheme of a common bolt, an incomplete gear damping plug and a 3mm damping fin; the upper and lower flange gasket scheme of the base of the weapon station and the damping plug scheme of the base of the weapon station have inferior damping effect.
The use process of the damping device of the weapon station damping alloy is as follows:
when the disc spring fixing frame is used, an operator mutually involutes 2 adjacent disc spring structures 20 to form the disc spring structures, the disc spring structures 20 and the other ends of the guide rods 103 are arranged in the sleeve 102, the disc spring structures 20 abut against the limiting ends, the damping sheet 501 is arranged between the incomplete gear fixing frame 502 and the incomplete gear 503, the damping sheet 501, the incomplete gear fixing frame 502 and the incomplete gear 503 are fixedly connected, and the incomplete gear fixing frame 502 and the cradle 30 are fixedly connected.
The damping plug is arranged between the first flange gasket 601 and the second flange gasket 602 to form a gasket structure 60.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include more than one of the feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise. Furthermore, the terms "mounted," "connected," and "connected" are to be construed broadly and may, for example, 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 meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.
Claims (10)
1. A vibration damping apparatus for a weapon station vibration damping alloy, comprising:
the damper comprises a base, a sleeve, a guide rod and a disc spring structure;
a cradle and a gun body; the cradle and the sleeve are fixedly connected with the base respectively, one end of the guide rod is fixedly connected with the gun body, and the launching direction of the gun body is consistent with the extending direction of the guide rod; the disc spring structure is made of vibration-damping alloy;
the disc spring structure and the other end of the guide rod are arranged in the sleeve, one end, far away from the guide rod, of the sleeve is provided with a limiting end, when the gun body launches a cannonball, the guide rod drives the disc spring structure to move towards the limiting end, and the limiting end is used for compressing the disc spring structure.
2. The vibration damping device for the weapon station vibration damping alloy according to claim 1, wherein the damper has a first nut, a second nut and a compression nut, the first nut is fixedly connected with the sleeve, the guide rod is slidably connected with the sleeve, the second nut is fixedly connected with the sleeve and is sleeved on the compression nut; the compression nut is fixedly connected with the guide rod.
3. The apparatus of claim 2, wherein the weapon station further comprises a partial gear structure, the partial gear structure being grounded to the cradle.
4. The vibration damping device for a weapon station vibration damping alloy according to claim 3, wherein said partial gear structure comprises a damper plate, a partial gear holder and a partial gear, said damper plate being provided between said partial gear holder and said partial gear for damping vibration.
5. The apparatus of claim 4, wherein the partial gear holder is fixedly connected to the cradle.
6. The vibration damping device for the weapon station vibration damping alloy according to claim 4, wherein the damping fin, the partial gear fixing frame and the partial gear are fixedly connected.
7. The vibration damping device for the weapon station vibration damping alloy according to claim 1, wherein the vibration damping device further comprises a gasket structure, the gasket structure comprises a first flange gasket and a second flange gasket, the weapon station has a weapon station base, the first flange gasket is fixedly connected with the weapon station base, and a flange plate is arranged between the first flange gasket and the second flange gasket.
8. The vibration damping apparatus for a weapon station vibration suppressing alloy as recited in claim 7, wherein said gasket structure further comprises a damping plug disposed between said first flange gasket and said second flange gasket.
9. The vibration damper for damping alloy in weapon station as set forth in claim 1, wherein said disc spring structure comprises 8 disc springs, and adjacent 2 of said disc spring structures are mutually engaged.
10. The vibration damper for damping alloy in weapon station as set forth in claim 9, wherein said disc spring structure formed by joining 8 disc springs to each other comprises a single-layer disc spring structure and a three-layer composite disc spring structure.
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