CN113864391A - Elastic support piece, vibration reduction design method and projection equipment - Google Patents
Elastic support piece, vibration reduction design method and projection equipment Download PDFInfo
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- CN113864391A CN113864391A CN202111146384.4A CN202111146384A CN113864391A CN 113864391 A CN113864391 A CN 113864391A CN 202111146384 A CN202111146384 A CN 202111146384A CN 113864391 A CN113864391 A CN 113864391A
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- housing
- shell
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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
- F16F15/08—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 rubber springs ; with springs made of rubber and metal
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- G—PHYSICS
- G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
- G03B—APPARATUS OR ARRANGEMENTS FOR TAKING PHOTOGRAPHS OR FOR PROJECTING OR VIEWING THEM; APPARATUS OR ARRANGEMENTS EMPLOYING ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ACCESSORIES THEREFOR
- G03B21/00—Projectors or projection-type viewers; Accessories therefor
- G03B21/14—Details
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- G—PHYSICS
- G03—PHOTOGRAPHY; CINEMATOGRAPHY; ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ELECTROGRAPHY; HOLOGRAPHY
- G03B—APPARATUS OR ARRANGEMENTS FOR TAKING PHOTOGRAPHS OR FOR PROJECTING OR VIEWING THEM; APPARATUS OR ARRANGEMENTS EMPLOYING ANALOGOUS TECHNIQUES USING WAVES OTHER THAN OPTICAL WAVES; ACCESSORIES THEREFOR
- G03B29/00—Combinations of cameras, projectors or photographic printing apparatus with non-photographic non-optical apparatus, e.g. clocks or weapons; Cameras having the shape of other objects
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- General Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The utility model relates to an elastic support piece, damping design method and projection equipment, elastic support piece are used for the cover to establish on the fastener of connecting first casing and second casing, wherein, install the speaker on one in first casing and the second casing, install the ray apparatus on the other, elastic support piece has: a main body part which is arranged in the first shell in a penetrating way; a first limit part formed on the main body part and used for being abutted against the fastening piece and the first shell; the second limiting part is formed at one end of the main body part, which is back to the first limiting part, and is used for being abutted against the first shell and the second shell; wherein, the first spacing portion, the main body portion and the second spacing portion are all provided with a cavity. Through reducing elastic support's bulk rigidity, make the resonant frequency of first casing and second casing reduce, avoid ray apparatus galvanometer and first casing, second casing to produce the resonance to reach the purpose of damping, guarantee the definition of projection picture.
Description
Technical Field
The disclosure relates to the technical field of projection equipment, in particular to an elastic support piece, a vibration reduction design method and projection equipment.
Background
The intelligent projector is integrated with a wireless internet function and is provided with an intelligent operating system, a user can directly surf the internet to watch videos without connecting an external device, user experience is improved to a great extent, the intelligent projector is usually provided with a sound box, and the requirement of consumers for high-quality audio-visual enjoyment can be met. Specifically, the speaker is installed on the sound chamber casing, and the ray apparatus is installed on the ray apparatus casing, and sound chamber casing and ray apparatus casing establish the silica gel cushion on the fastener through fastener and cover and are connected to reduce the vibration of sound chamber casing, reach the purpose that improves tone quality. In the related art, the silica gel cushion is of a solid structure, so that the whole rigidity is high, the vibration reduction effect is general, and the optical machine vibrating mirror of the projector generates resonance with the sound cavity shell and the projector shell, so that the projection picture is shaken and unclear.
Disclosure of Invention
The disclosure aims to provide an elastic support member, a vibration damping design method and projection equipment, so as to solve the technical problem that the vibration damping effect of a silica gel cushion in the related art is poor.
In order to achieve the above object, the present disclosure provides an elastic supporting member for being sleeved on a fastening member connecting a first housing and a second housing, wherein one of the first housing and the second housing is provided with a speaker, and the other is provided with an optical device, the elastic supporting member has:
a main body portion inserted into the first housing;
a first stopper portion formed on the main body portion and adapted to abut against the fastening member and the first housing; and
a second stopper portion formed at an end of the main body portion opposite to the first stopper portion, and adapted to abut against the first housing and the second housing;
wherein the first limiting part, the main body part and the second limiting part are all provided with a cavity.
Optionally, the first limiting part and the second limiting part are larger than the main body part in radial dimension, and the cavities of the first limiting part and the second limiting part are all annular cavities.
Optionally, the resilient support has a mounting hole for the fastener to pass through, the centre line of the annular cavity being collinear with the axis of the mounting hole.
Optionally, at least one of the first limiting part and the second limiting part and the main body part are of a split structure, and cavities of the first limiting part and the second limiting part are communicated.
Optionally, the main body portion includes an inner ring and an outer ring which are coaxially arranged at an interval, the inner ring protrudes in an axial direction relative to the outer ring, an end portion of the outer ring close to one end of the inner ring protruding extends in a radial direction to form a boss, a stepped structure is formed on an inner peripheral wall of the first limiting portion and/or the second limiting portion, and the boss and one end of the inner ring protruding abut against a stepped surface of the stepped structure.
Optionally, the area of the longitudinal cross-section of the cavity is 32.1mm2～42.2mm2。
Optionally, the cavity is filled with a buffer medium.
According to a second aspect of the present disclosure, there is also provided a vibration damping design method applied to a projection apparatus, where the projection apparatus includes a first housing, a second housing, a speaker mounted on the first housing, an optical engine mounted on the second housing, a fastener connecting the first housing and the second housing, and an elastic support member sleeved on the fastener, the elastic support member has a cavity, and the vibration damping design method includes:
obtain the optical-mechanical galvanometer of the optical-mechanicalOperating frequency f0；
Acquiring the resonant frequency f of the first shell and the second shell1(ii) a And
adjusting the parameters of the elastic support member to change the resonance frequency f1So that the operating frequency f0Is not equal to the resonance frequency f1Wherein the parameters of the elastic support comprise: at least one of a material, a thickness in a direction of support, a size of the cavity, and a pressure within the cavity.
Optionally, said resonant frequency f is changed during said adjusting of a parameter of said elastic support1In the step (2), the vibration damping design method further includes:
obtaining a maximum resonant frequency f of the fastener2Wherein the maximum resonance frequency f2＝k*f1K > 0 and is a constant; and
adjusting the area x of the longitudinal section of the cavity to the maximum resonance frequency f2Less than a first threshold value, and the maximum deformation y of the elastic support in the supporting direction is less than a second threshold value;
preferably, the maximum resonance frequency of the fastener is: f. of2＝A1x+B1，A1< 0, and A1、B1Is a constant; maximum deformation amount of the elastic support in the supporting direction: y is A2x+B2，A2> 0, and A2、B2Is a constant.
Optionally, the area x of the longitudinal section of the cavity satisfies: x is the number ofmin＜x＜xmaxWherein, in the step (A),
xmin＝A3M2-B3M+C，A3、B3c is a constant, M is the weight of the first housing;
xmax＝21±0.8mm。
according to a third aspect of the present disclosure, there is also provided a projection apparatus, including a first housing, a second housing, a speaker mounted on the first housing, an optical engine mounted on the second housing, a fastener connecting the first housing and the second housing, and an elastic supporting member sleeved on the fastener, where the elastic supporting member is the above elastic supporting member; and/or
The projection device is obtained by the vibration reduction design method.
Through the technical scheme, the cavities are respectively arranged in the main body part, the first limiting part and the second limiting part, the integral rigidity of the elastic support piece is reduced, the resonance frequency of the first shell and the second shell is reduced, resonance of the optical machine vibrating mirror, the first shell and the second shell is avoided, the purpose of vibration reduction is achieved, the definition of a projected picture is guaranteed, and picture shaking is avoided.
Additional features and advantages of the disclosure will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description serve to explain the disclosure without limiting the disclosure. In the drawings:
fig. 1 is a schematic structural view of a first housing mounted with an elastic support provided in an exemplary embodiment of the present disclosure;
fig. 2 is a schematic structural view of an elastic support member provided in the related art;
FIG. 3 is a plot of the frequency sweep vibration spectrum of the Ming-Yi 47 galvanometer;
fig. 4 to 7 are partial detailed views of a first housing mounted with an elastic support provided in an exemplary embodiment of the present disclosure;
fig. 8 to 11 are schematic structural views of elastic supports provided in various exemplary embodiments of the present disclosure;
FIGS. 12 and 13 are flow charts of a damping design method provided by an exemplary embodiment of the present disclosure;
FIGS. 14a and 14b show the maximum deformation and the maximum resonance frequency f2A plot of the fit relationship to the area of the longitudinal section of the cavity;
FIG. 15 isLower limit value x of the area of the longitudinal section of the cavityminA fitted relationship graph with the weight of the first housing.
Description of the reference numerals
1-first shell, 11-lug, 2-elastic support, 20-cavity, 21-main body, 211-inner ring, 2110-protruding end of inner ring, 212-outer ring, 213-boss, 200-step structure, 22-first limiting part, 23-second limiting part, 24-mounting hole, 3-fastener, 4-loudspeaker.
Detailed Description
The following detailed description of specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.
In the present disclosure, where not otherwise stated, the use of directional words such as "upper", "lower", "top", "bottom" generally means defined in the normal assembly of the elastic support provided by the present disclosure, and in particular with reference to the drawing direction shown in fig. 5, "inner", "outer" means inner and outer of the respective component profiles, and "axial" means the axial direction of the fastener and mounting hole, the same as the deformation direction of the elastic support. Furthermore, the terms "first," "second," and the like, as used in this disclosure, are intended to distinguish one element from another, and not necessarily for order or importance. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated.
As shown in fig. 1, the speaker 4 is installed on the first casing 1, the first casing 1 and the second casing (not shown) installed with the optical engine are connected with the elastic support member 2 sleeved on the fastening member 3 through the fastening member 3, as shown in fig. 2 and 3, for the silica gel cushion with a solid structure, the peak value of the whole resonance frequency of the first casing 1 is basically contained within 20 to 20000Hz of the speaker 4, and the resonance risk is large. In addition, for a solid silica gel cushion, in a complete machine test, XYZ three-direction frequency sweep excitation is applied at the position of a loudspeaker 4, four optical machine support columns on a second shell are selected as response points, the resonance frequency of an optical machine installation support column is 60Hz, and a frequency doubling relation exists between the resonance frequency of an optical machine vibrating mirror and the resonance frequency (240Hz), that is, the resonance frequency of the optical machine vibrating mirror is the fourth harmonic frequency of the second shell, and the optical machine vibrating mirror generates resonance with the first shell 1 and the second shell, in addition, as shown in fig. 3, the vibrating mirror itself has a resonance peak at 60Hz, so that a projection picture of projection equipment is jittered and unclear.
In view of the above problems, as shown in fig. 4 to 11, the present disclosure provides an elastic support member, the elastic support member is configured to be sleeved on a fastening member 3 connecting a first housing 1 and a second housing, wherein one of the first housing 1 and the second housing is provided with a speaker 4, the other is provided with an optical engine, the elastic support member 2 has a main body portion 21, a first limiting portion 22, and a second limiting portion 23, the main body portion 21 is configured to penetrate through the first housing 1; the first stopper 22 is formed on the body 21 and is adapted to abut against the fastening member 3 and the first housing 1; the second stopper portion 23 is formed at an end of the main body portion 21 facing away from the first stopper portion 22, and is adapted to abut against the first housing 1 and the second housing; the first stopper 22, the body 21, and the second stopper 23 each have a cavity 20 therein.
It should be noted that the elastic supporting member 2 provided by the present disclosure may be made of different materials such as natural rubber, silicon rubber, etc., and the shape of the elastic supporting member 2 and the size of the cavity 20 may be designed according to the actual vibration reduction requirement, which is not limited by the present disclosure. In addition, in consideration of the scheme of additionally arranging the cavity, the integral rigidity of the elastic supporting piece can be reduced, and meanwhile, the deformation of the elastic supporting piece in the supporting direction is increased. In addition, the present disclosure includes an embodiment in which the elastic support 2 is inserted into the first housing 1, the speaker 4 is installed on the first housing 1, and the optical engine is installed on the second housing, and also includes an embodiment in which the elastic support 2 is inserted into the first housing 1, the optical engine is installed on the first housing 1, and the speaker 4 is installed on the second housing, which all belong to the protection scope of the present disclosure, and the former is taken as an example for detailed description in the following. In this embodiment, as shown in fig. 1, 4 and 5, the speaker 4 is mounted on the first housing 1, the first housing 1 is formed with a lug 11, the main body 21 is accommodated in an opening of the lug 11, the first position-limiting portion 22 abuts against an end of the fastening member 3 and a top surface of the lug 11, the second position-limiting portion 23 abuts against a bottom surface of the lug 11 and the second housing, and the elastic support member 2 changes a rigid contact between the fastening member 3 and the first housing 1 and between the first housing 1 and the second housing into a soft contact, thereby playing a role of vibration damping.
Through the technical scheme, the cavities 20 are respectively arranged in the main body part 21, the first limiting part 22 and the second limiting part 23, the integral rigidity of the elastic support piece 2 is reduced, the resonance frequency of the first shell 1 and the second shell is reduced, and the optical machine galvanometer, the first shell 1 and the second shell are prevented from generating resonance, so that the aim of vibration reduction is fulfilled, the definition of a projected picture is ensured, and the picture is prevented from shaking.
In an exemplary embodiment of the present disclosure, as shown in fig. 8 to 11, the first position-limiting portion 22 and the second position-limiting portion 23 are larger than the main body portion 21 in the radial direction, and the cavities of the three are all annular cavities, for example, the first position-limiting portion 22, the main body portion 21, and the second position-limiting portion 23 are respectively cylindrical structures, the longitudinal section (the section cut along the diameter and height of the bottom surface of the cylinder) of the elastic supporting member 2 may be configured as an i-shape, and in the longitudinal section, the cavity 20 includes two rectangles of equal size located at both sides of the axis. The elastic support part 2 can be integrally formed by adopting an injection molding process, and the cavity 20 is directly processed in the forming process, so that the integral strength and the service life of the elastic support part 2 can be improved.
As shown in fig. 8 to 11, the elastic support member 2 has a mounting hole 24 through which the fastening member 3 passes, and the center lines of the annular cavities in the first stopper portion 22, the main body portion 21, and the second stopper portion 23 are collinear with the axis of the mounting hole 24. Therefore, the deformation of the whole elastic support piece 2 can be ensured to be positioned on the same axis, and the elastic support piece is easy to process and convenient to form.
The elastic support member 2 provided by the present disclosure may also be designed as a split structure, at least one of the first limiting portion 22 and the second limiting portion 23 and the main body portion 21 are split structures, and the cavities 20 of the three are communicated, that is, in the present disclosure, the main body portion 21, the first limiting portion 22 and the second limiting portion 23 may be processed separately, and the connection and fixation in the axial direction of the three are realized by the fastening member 3; as shown in fig. 10 and 11, it is also possible to manufacture the first stopper portion 22 separately and design the second stopper portion 23 and the main body portion 21 as an integral structure, or manufacture the second stopper portion 23 separately and design the first stopper portion 22 and the main body portion 21 as an integral structure, all of which belong to the protection scope of the present disclosure. Specifically, in an exemplary embodiment of the present disclosure, as shown in fig. 5, 6, 10 and 11, the second position-limiting portion 23 and the main body portion 21 may be an integral structure, the main body portion 21 includes an inner ring 211 and an outer ring 212 coaxially arranged at an interval, the inner ring 211 axially protrudes the outer ring 212 by a predetermined height, an end portion of the outer ring 212 close to the protruding end 2110 of the inner ring radially extends to form a boss 213, the inner circumferential wall of the first position-limiting portion 22 is formed with a stepped structure 200, and the boss 213 and the protruding end 2110 of the inner ring are all abutted against a stepped surface of the stepped structure 200, so that the closed cavity 20 can be formed while supporting in the axial direction, and the purpose of reducing the rigidity and controlling the deformation amount in the axial direction can be achieved at the same time.
Specifically, in the present embodiment, the area of the longitudinal section of the cavity 20 may be 32.1mm2～42.2mm2And has an optimum vibration damping effect while the amount of deformation in the axial direction is less than a predetermined value, which will be described in detail later.
As shown in fig. 1, speakers 4 are respectively installed at two opposite sides of a first housing 1, the first housing 1 and a second housing are connected by a plurality of fastening members 3 which surround the circumference of the first housing 1 and are arranged at intervals, and each fastening member 3 is sleeved with an elastic supporting member 2 provided by the present disclosure to support at a plurality of positions where the first housing 1 and the second housing are connected, so as to reduce the resonant frequency of the first housing 1 and the second housing.
Further, in the present disclosure, the cavity 20 may be filled with a buffer medium, such as a buffer solution, to further achieve the effect of vibration damping.
According to a second aspect of the present disclosure, as shown in fig. 12, there is also provided a vibration damping design method applied to a projection apparatus includingThe vibration damping design method comprises the following steps of firstly, arranging a first shell 1, a second shell, a loudspeaker 4 arranged on the first shell 1, an optical machine arranged on the second shell, a fastener 3 connected with the first shell 1 and the second shell, and an elastic support member 2 sleeved on the fastener 3, wherein the elastic support member 2 is provided with a cavity 20, and the vibration damping design method provided by the disclosure comprises the following steps: step 1201, obtaining the working frequency f of the vibrating mirror of the optical machine0(ii) a Step 1202, acquiring resonance frequency f of the first shell and the second shell1(ii) a And step 1203, adjusting parameters of the elastic supporting member to change the resonant frequency f1To make the operating frequency f0Not equal to the resonance frequency f1Wherein the parameters of the elastic support comprise: at least one of a material, a thickness in a direction of support, a size of the cavity, and a pressure within the cavity.
In terms of materials, the elastic supporting piece 2 can be made of silicon rubber, and the silicon rubber is a super-elastic material and is softer, so that the effect of reducing the overall rigidity can be achieved; in the aspect of the design of the cavity, the size of the cavity, the internal pressure and the like can be designed, the overall rigidity is further reduced, the resonance frequency of structural members such as the first shell 1 and the second shell connected with the first shell 1 is reduced, the tone quality is improved, and the resonance effect of the optical engine is reduced. Varying the resonant frequency f of the first housing 1 and the second housing may be achieved by controlling one or more of the above parameters1To make it operate at the frequency f of the vibrating mirror of the optical machine0There is no frequency doubling relationship.
As shown in FIG. 13, the resonant frequency f is changed by adjusting the parameters of the elastic support member1In the step (b), the vibration damping design method provided by the present disclosure further includes: step 1301, obtaining the maximum resonance frequency f of the fastener2Wherein the maximum resonance frequency f2＝k*f1K > 0 and is a constant; and a step 1302 of adjusting the area x of the longitudinal section of the cavity to a maximum resonance frequency f2Less than a first threshold value and a maximum deformation y of the elastic support in the supporting direction is less than a second threshold value, wherein the maximum resonance frequency of the fastener is: f. of2＝A1x+B1，A1< 0, and A1、B1Is a constant; maximum deformation amount of the elastic support in the supporting direction: y is A2x+B2，A2> 0, and A2、B2Is a constant. Specifically, in the vibration damping design method provided by the present disclosure, the maximum resonance frequency f of the head response of the fastener 3 under the action of the sweep frequency is selected2To measure the damping effect, the maximum resonance frequency f2With resonant frequency f1In direct proportion, synchronously increasing or decreasing at the maximum resonance frequency f2Is equivalent to and acquires the resonance frequency f1And the maximum resonance frequency f can be obtained without disassembling the projector2And the testing efficiency of the whole machine is improved. In the vibration damping design method provided by the present disclosure, by adjusting the area of the longitudinal section of the cavity 20, it is fully considered that the maximum deformation amount y of the elastic support 2 in the supporting direction also satisfies a certain requirement under the action of the gravity of the first housing 1 while reducing the rigidity of the entire elastic support 2, and it is found that, as shown in fig. 14a and 14b, the maximum resonance frequency f of the fastener is shown2As a function of the area x of the longitudinal section, i.e. the maximum resonance frequency f, increases with increasing area x of the longitudinal section of the cavity2The maximum deformation y of the elastic support in the supporting direction is reduced in a proportional function relationship with the area x of the longitudinal section, that is, as the area x of the longitudinal section increases, the rigidity of the elastic support decreases and the deformation y in the supporting direction increases. By comprehensively considering the above factors, in the vibration damping design method, on the premise of ensuring the supporting function of the elastic supporting member 2, in order to ensure the optimal vibration damping effect, the range of the area of the longitudinal section of the cavity satisfying the conditions needs to be determined.
The following table shows a comparison of the areas of different longitudinal sections of the cavity, in the following schemes, on the premise that the weight M of the first housing 1 is constant, the original scheme is the scheme of fig. 2 using the elastic supporting member with a solid structure, and in the A, B, C, D scheme, simulation tests are performed by taking the case that the longitudinal section of the cavity 20 is two rectangles with equal width and height as an example, and the following table shows that:
for the data in the table above, the original scheme is the smallest for the maximum deformation y in the supporting direction, the maximum deformation y increases with the increase of the area of the longitudinal section of the cavity, the second threshold value is 0.05mm according to the design requirement, the maximum deformation y needs to be smaller than 0.05, the scheme D does not meet the requirement, and the scheme A, B, C meets the requirement. Maximum resonance frequency f of scheme A in terms of vibration damping effect2And in conclusion, the scheme C is an optimal scheme, the maximum deformation is less than 0.05mm, and the maximum resonance frequency is reduced by more than 100Hz, namely less than 1260Hz, the maximum resonance frequency of the scheme B is only reduced by 13Hz, the requirement is not met, the vibration reduction effect is not obvious, and the maximum resonance frequency is reduced by more than 100 Hz.
In addition, this disclosure has carried out complete machine simulation analysis and experimental verification to elastic support element 2 in scheme C, speaker 4 is located the both sides of first casing 1 as the vibration source, speaker 4 and vibrating diaphragm are at the vibration sound production of different directions, first casing 1 can appear the displacement vibration in different directions in the space, carry out full frequency response analysis through finite element simulation, exert the sweep frequency excitation of XYZ three direction in the lower part of speaker 4, obtain the frequency response spectrum of first casing 1, obtain the frequency response of four ray apparatus installation support columns on the second casing, through discovering, the resonant frequency and the response amplitude of first casing 1, second casing all reduce, and do not have the doubling of frequency relation with the resonant frequency 240Hz of ray apparatus galvanometer, can effectively avoid ray apparatus resonance, all reach good effect in the aspect of supporting effect and damping effect.
In addition, the maximum deformation amount y and the maximum resonance frequency f are fitted through the analysis of the data in the table2Longitudinal section of the cavityFurther explores the range of values of the area of the longitudinal section of the cavity that satisfy the conditions. Namely:
maximum resonant frequency of fastener: f. of2＝A1x+B1Wherein-29.162 < A1＜-13.724，1589.4＜B1＜1608.9；
Maximum deformation amount of the elastic support in the supporting direction: y is A2x+B2Wherein, 0.0012 < A2＜0.0023，0.0048＜B2< 0.0062; preferably:
as shown in FIGS. 14a and 14b, a curve fitted to the first casing 1 with a weight of 850g, A, was selected1＝-21.289，B1＝1601.6，A2＝0.0021，B20.0057, i.e.:
maximum resonance frequency: f. of2＝-21.289x+1601.6，
Maximum deformation: y is 0.021x +0.0057,
according to design requirements, the maximum deformation y is required to be less than 0.05mm, and the maximum resonance frequency f2Less than 1260Hz, it can be concluded that the area of the longitudinal section of the cavity satisfying the conditions is in the range 16.05 < x < 21.10.
In the same way as above, the first and second,
the range of the area of the longitudinal section of the cavity satisfying the condition can be obtained by selecting a first shell fitting curve with the weight of 650g as follows: x is more than 17.11 and less than 21.33;
the range of the area of the longitudinal section of the cavity satisfying the condition can be obtained by selecting a first shell fitting curve with the weight of 750g as follows: x is more than 16.04 and less than 21.19;
the range of the area of the longitudinal section of the cavity satisfying the condition can be obtained by selecting a fitting curve of the first shell with the weight of 1150g as follows: x is more than 15.59 and less than 21.70;
the range of areas of the longitudinal section of the cavity satisfying the conditions can be obtained by selecting a first shell fitting curve with the weight of 1450g as follows: x is more than 15.55 and less than 21.25;
the above data show that the upper limit value x of the weight of the first housing 1 to the area of the longitudinal section of the cavity is defined by the weight of the first housing 1maxLess influence, as shown in FIG. 15, of the first casing 1The lower limit value x of the weight M and the area of the longitudinal section of the cavityminFitting is performed, i.e. the area x of the longitudinal cross-section of the cavity satisfies xmin＜x＜xmaxWherein x ismin＝A3M2+B3M+C，A3、B3C is a constant, and M is the weight of the first shell; x is the number ofmax21 + -0.8 mm. Therefore, as the weight of the first housing 1 increases, the lower limit value of the area of the longitudinal section of the cavity gradually decreases and tends to converge, and the upper limit value is substantially unchanged. When designing the area of the longitudinal section of the cavity, a suitable cavity 20 can be designed according to the weight of the first housing 1 to ensure both the damping effect and the supporting effect. In addition, when the number of times of fitting the selected first shells with different weights is more, A in the fitting curve is larger3、B3C is more precise, 0.2468 < A in this embodiment3＜0.2673，-1.963＜B3< -1.724, 15.897 < C < 19.325, preferably, in the fitted curve shown in FIG. 15, A3＝0.2575，B3-1.8005, C18.642, i.e.,
xmin＝0.2575M2-1.8005M+18.642，
for the first shell 1 with heavier load, the area of the longitudinal section of the cavity can be directly designed to be the minimum value, so that the requirements on support and vibration reduction can be met without recalculation and design.
According to the third aspect of the present disclosure, there is also provided a projection apparatus, which includes a first housing 1, a second housing, a speaker 4 mounted on the first housing, an optical engine mounted on the second housing, a fastener connecting the first housing and the second housing, and an elastic support member sleeved on the fastener, where the elastic support member may be the elastic support member described above, and/or the projection apparatus is obtained by the above-described vibration reduction design method. The projection device has all the advantages of the elastic support member and the vibration reduction design method, and redundant description is not repeated here.
The preferred embodiments of the present disclosure are described in detail with reference to the accompanying drawings, however, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solution of the present disclosure within the technical idea of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.
It should be noted that, in the foregoing embodiments, various features described in the above embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, various combinations that are possible in the present disclosure are not described again.
In addition, any combination of various embodiments of the present disclosure may be made, and the same should be considered as the disclosure of the present disclosure, as long as it does not depart from the spirit of the present disclosure.
Claims (11)
1. An elastic support member for being sleeved on a fastener (3) connecting a first shell (1) and a second shell, wherein one of the first shell (1) and the second shell is provided with a loudspeaker (4), and the other is provided with a light machine, the elastic support member (2) is characterized in that:
a main body part (21) which is inserted into the first housing (1);
a first stopper portion (22) formed on the main body portion (21) and adapted to abut against the fastening member (3) and the first housing (1); and
a second stopper portion (23) formed at one end of the main body portion (21) facing away from the first stopper portion (22) and adapted to abut against the first housing (1) and the second housing;
wherein, the first limit part (22), the main body part (21) and the second limit part (23) are all provided with a cavity (20).
2. The elastic support according to claim 1, characterized in that the first limit stop portion (22) and the second limit stop portion (23) are radially larger than the main body portion (21), and the cavities (20) of the three are all annular cavities.
3. The elastic support according to claim 2, characterized in that it has a mounting hole (24) for the fastener (3) to pass through, the centre line of the annular chamber being collinear with the axis of the mounting hole (24).
4. The elastic support according to claim 1, wherein at least one of the first and second position-limiting portions (22, 23) and the main body portion (21) are of a split structure, and the cavities (20) of the first and second position-limiting portions are communicated with each other.
5. The elastic support according to claim 4, wherein the main body portion (21) includes an inner ring (211) and an outer ring (212) which are coaxially arranged at a distance from each other, the inner ring (211) protrudes in an axial direction with respect to the outer ring (212), and an end portion of the outer ring (212) near an end (2110) where the inner ring protrudes extends in a radial direction to form a boss (213), an inner peripheral wall of the first stopper portion (22) and/or the second stopper portion (23) is formed with a stepped structure (200), and the boss (213) and the end (2110) where the inner ring protrudes each abut against a stepped surface of the stepped structure (200).
6. Elastic support according to claim 1, characterized in that the area of the longitudinal section of the cavity (20) is 32.1mm2～42.2mm2。
7. Elastic support according to any one of claims 1 to 6, characterized in that said cavity (20) is filled with a buffer medium.
8. The damping design method is applied to projection equipment, the projection equipment comprises a first shell (1), a second shell, a loudspeaker (4) installed on the first shell (1), an optical machine installed on the second shell, a fastener (3) for connecting the first shell (1) and the second shell, and an elastic support member (2) sleeved on the fastener (3), and is characterized in that the elastic support member (2) is provided with a cavity (20), and the damping design method comprises the following steps:
obtaining the working frequency f of the vibrating mirror of the optical machine0；
Acquiring the resonant frequency f of the first shell and the second shell1(ii) a And
adjusting the parameters of the elastic support member to change the resonance frequency f1So that the operating frequency f0Is not equal to the resonance frequency f1Wherein the parameters of the elastic support comprise: at least one of a material, a thickness in a direction of support, a size of the cavity, and a pressure within the cavity.
9. The method of claim 8, wherein the resonant frequency f is varied by adjusting the parameters of the resilient support1In the step (2), the vibration damping design method further includes:
obtaining a maximum resonant frequency f of the fastener2Wherein the maximum resonance frequency f2＝k*f1K > 0 and is a constant; and
adjusting the area x of the longitudinal section of the cavity to the maximum resonance frequency f2Less than a first threshold value, and the maximum deformation y of the elastic support in the supporting direction is less than a second threshold value;
preferably, the first and second liquid crystal materials are,
maximum resonant frequency of the fastener: f. of2＝A1x+B1，A1< 0, and A1、B1Is a constant;
maximum deformation amount of the elastic support in the supporting direction: y is A2x+B2，A2> 0, and A2、B2Is a constant.
10. The vibration damping design method according to claim 8, characterized in that the area x of the longitudinal section of the cavity satisfies: x is the number ofmin＜x＜xmaxWherein, in the step (A),
xmin＝A3M2-B3M+C，A3、B3c is a constant, M isThe weight of the first housing;
xmax＝21±0.8mm。
11. a projection device, characterized in that the projection device comprises a first housing (1), a second housing, a speaker (4) mounted on the first housing (1), an optical machine mounted on the second housing, a fastener (3) connecting the first housing (1) and the second housing, and an elastic support member (2) fitted over the fastener (3), wherein the elastic support member (2) is according to any one of claims 1-7; and/or
The projection device is obtained by the vibration damping design method of any one of claims 8 to 10.
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| CN202111146384.4A CN113864391B (en) | 2021-09-28 | 2021-09-28 | Elastic support piece, vibration reduction design method and projection equipment |
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