CN105445883B - Optical lens bracket device - Google Patents
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- CN105445883B CN105445883B CN201510306928.7A CN201510306928A CN105445883B CN 105445883 B CN105445883 B CN 105445883B CN 201510306928 A CN201510306928 A CN 201510306928A CN 105445883 B CN105445883 B CN 105445883B
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- 230000003287 optical effect Effects 0.000 title claims abstract description 63
- 239000006096 absorbing agent Substances 0.000 claims abstract description 99
- 238000013016 damping Methods 0.000 claims abstract description 50
- 238000001816 cooling Methods 0.000 claims abstract description 47
- 239000002826 coolant Substances 0.000 claims abstract description 26
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 claims description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 6
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 claims description 4
- 239000003570 air Substances 0.000 claims description 4
- 229910052757 nitrogen Inorganic materials 0.000 claims description 4
- PXGOKWXKJXAPGV-UHFFFAOYSA-N Fluorine Chemical compound FF PXGOKWXKJXAPGV-UHFFFAOYSA-N 0.000 claims description 3
- 229910052731 fluorine Inorganic materials 0.000 claims description 3
- 239000011737 fluorine Substances 0.000 claims description 3
- 239000001307 helium Substances 0.000 claims description 3
- 229910052734 helium Inorganic materials 0.000 claims description 3
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 claims description 3
- 238000010521 absorption reaction Methods 0.000 abstract description 8
- 230000017525 heat dissipation Effects 0.000 abstract description 3
- 230000010354 integration Effects 0.000 abstract description 3
- 230000005284 excitation Effects 0.000 description 13
- 230000009467 reduction Effects 0.000 description 10
- 230000008859 change Effects 0.000 description 6
- 239000000110 cooling liquid Substances 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000002955 isolation Methods 0.000 description 4
- 239000008367 deionised water Substances 0.000 description 3
- 229910021641 deionized water Inorganic materials 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 229910000737 Duralumin Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 125000003158 alcohol group Chemical group 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- APFVFJFRJDLVQX-UHFFFAOYSA-N indium atom Chemical compound [In] APFVFJFRJDLVQX-UHFFFAOYSA-N 0.000 description 1
- 230000031700 light absorption Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000002310 reflectometry Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000003190 viscoelastic substance Substances 0.000 description 1
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- Vibration Prevention Devices (AREA)
- Instruments For Measurement Of Length By Optical Means (AREA)
Abstract
The invention relates to the technical field of optical machines, and provides an optical frame device. The device comprises a spectacle frame body, a cooling unit and a vibration absorption unit; the cooling unit comprises a cooling channel arranged in the mirror bracket body; the vibration absorption unit is a dynamic vibration absorber and is arranged in the cooling channel; and the damping medium of the dynamic vibration absorber is a cooling medium injected into the cooling channel. The optical frame controls vibration through the dynamic vibration absorber, and has the advantages of small initial amplitude of a main vibration system and small interference of a vibration source. On this basis, place the power bump leveller in the cooling channel of cooling unit in for the cooling medium among the cooling channel not only is used for mirror holder body and sets up the heat dissipation of the optical element on the mirror holder body, can do the damping medium of power bump leveller simultaneously, and can cool off the power bump leveller, thereby on the basis that does not improve optical mirror holder structure complexity, integrated and inhaled and cool off the function, promoted the integration degree of optical mirror holder.
Description
Technical Field
The invention relates to the technical field of optical machines, in particular to an optical frame device, and more particularly to an optical frame device integrating vibration absorption and cooling functions.
Background
The optical frame is an important component in optical machine products, and mainly solves the problems of clamping and adjusting optical elements. In practical applications, the optical frame is affected by vibration and thermal interference, which may cause the position of the optical element to be held to change, and the thermal interference may affect the relevant optical performance of the optical element, such as reflectivity and wavefront distortion. The changes of the position and the optical performance of the optical element in the optical-mechanical system directly affect important parameters of the whole system, such as beam direction, optical power, beam quality and the like, and even cause the system to be incapable of normal operation due to serious changes. Therefore, how to reduce the influence of vibration and thermal interference on the optical frame is an important research topic in the field of optical machine technology.
The influence of vibration on the optical frame mainly results from environmental vibration, such as a water-cooled engine pump source, building operation or underground traffic trains and the like. Currently, in opto-mechanical systems, vibration isolation methods such as vibration isolation rubber, hydraulic damping, and air springs are mainly used for vibration control. Since the vibration isolation system mainly uses an elastic element, the amplitude of vibration by the vibration source gradually decreases from a large value to a small value, but the amplitude at the initial stage of vibration is large. On the other hand, the thermal interference on the optical frame is mainly caused by stray light absorption and optical element absorption in the high-power laser system, and the working environment with high temperature or severe change. Therefore, the optical frame must be cooled by a temperature-controlled cooling device. For a high-power optical-mechanical system running in a vibration environment or an optical-mechanical system with the characteristics of high temperature or severe change due to existing vibration of a working environment, the system needs to be subjected to vibration prevention and temperature control design respectively, so that the structure of the optical-mechanical system is complicated.
The dynamic vibration absorber is also called as tuned mass damper, and the basic principle is as follows: by adding a substructure (namely a dynamic vibration absorber) on a target vibration system (namely a main vibration system), properly selecting the structural form, dynamic parameters and the coupling relation with the main vibration system, the vibration state of the main vibration system is changed, and the forced vibration response of the main vibration system is reduced on a desired frequency band. Because there is no elastic element between the main vibration system and the vibration source, the vibration amplitude of the main vibration system at the initial stage of vibration is smaller than that of the vibration isolation method under the action of the same vibration source. Because the vibration suppression device has a simple structure, is easy to implement, and can effectively suppress the vibration of equipment with small frequency change, the vibration suppression device is widely applied to various mechanical equipment in various industries such as transportation, industrial machinery, building bridges and the like, and becomes one of important means for implementing vibration control.
Disclosure of Invention
Technical problem to be solved
The invention aims to provide an optical lens bracket device which integrates vibration control and temperature control and has a simple structure.
(II) technical scheme
In order to solve the above technical problem, the present invention provides an optical frame, comprising a frame body, a cooling unit and a vibration absorbing unit; the cooling unit comprises a cooling channel disposed in the frame body; the vibration absorption unit is a dynamic vibration absorber and is arranged in the cooling channel; and the damping medium of the dynamic vibration absorber is a cooling medium injected into the cooling channel.
Preferably, the cooling passages include a transverse passage through which the cooling medium flows in a transverse direction, and a longitudinal passage through which the medium flows in a longitudinal direction; the dynamic vibration absorber comprises a transverse dynamic vibration absorber and a longitudinal dynamic vibration absorber; the damping medium of the transverse dynamic vibration absorber is the cooling medium which flows transversely in the transverse channel, and the damping medium of the longitudinal dynamic vibration absorber is the cooling medium which flows longitudinally in the longitudinal channel.
Preferably, the mirror frame body comprises a mirror frame, a mirror rod and a mirror base; the mirror frame is used for clamping optical elements and is connected with the mirror base through the mirror rod.
Preferably, the optical element is a mirror, a lens, a wave plate, a prism or an aperture stop.
Preferably, the cooling passage and the dynamic vibration absorber are both provided in the mirror frame.
Preferably, the cooling channel is provided in the mirror frame, mirror stem and mirror base, and the dynamic vibration absorber is provided in the mirror stem/mirror base.
Preferably, the spring element of the dynamic vibration absorber is a coil spring, a cantilever beam, a parallel plate spring, a torsion spring, or a laminated rubber.
Preferably, the cooling medium introduced into the cooling channel is water, alcohol, fluorine, air, nitrogen or helium.
(III) advantageous effects
The technical scheme of the invention has the following advantages: the optical frame controls vibration through the dynamic vibration absorber, and has the advantages of small initial amplitude of a main vibration system and small interference of a vibration source. On this basis, place the power bump leveller in the cooling channel of cooling unit in for the cooling medium among the cooling channel not only is used for mirror holder body and sets up the heat dissipation of the optical element on the mirror holder body, can do the damping medium of power bump leveller simultaneously, and can cool off the power bump leveller, thereby on the basis that does not improve optical mirror holder structure complexity, integrated and inhaled and cool off the function, promoted the integration degree of optical mirror holder.
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, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1: the dynamic vibration absorber is a schematic diagram of a vibration reduction principle;
FIG. 2: a schematic structural view of an optical frame in which a dynamic vibration absorber is provided in a frame according to the first embodiment;
FIG. 3: a characteristic curve of the longitudinal vibration amplitude of the main vibration system of the first embodiment changing with the excitation frequency;
FIG. 4: a schematic structural view of an optical frame in which a dynamic vibration absorber is provided in a mirror bar according to a second embodiment;
FIG. 5: a characteristic curve of the longitudinal vibration amplitude of the main vibration system of the second embodiment changing with the excitation frequency;
FIG. 6: a schematic structural view of an optical frame in which a dynamic vibration absorber is disposed in a lens holder according to a third embodiment;
Detailed Description
The embodiments of the present invention will be described in further detail with reference to the drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The application provides an optical frame, including mirror holder body, cooling unit and inhale the unit of shaking. The cooling unit includes a cooling channel disposed in the frame body. The vibration absorption unit is a dynamic vibration absorber, so that the vibration absorption unit has the advantages of small initial amplitude of a main vibration system and small interference of a vibration source. The dynamic vibration absorber is arranged in the cooling channel, so that the cooling medium in the cooling channel is used for heat dissipation of the mirror bracket body and the optical element arranged on the mirror bracket body, and can be simultaneously used as a damping medium of the dynamic vibration absorber and can cool the dynamic vibration absorber, thereby integrating vibration absorption and cooling functions on the basis of not improving the complexity of the structure of the optical mirror bracket, and improving the integration degree of the optical mirror bracket.
Referring to fig. 1, the dynamic vibration absorber is generally composed of a mass, a spring element, and a damping element. The spring element includes a coil spring, a cantilever beam, a parallel plate spring, a torsion spring, a laminated rubber, and the like. The damping elements include hydraulic damping, magnetic damping, viscoelastic material, friction damping, etc. In fig. 1, 1-1 is the equivalent mass of the dynamic vibration absorber, 1-2 is the equivalent stiffness of the dynamic vibration absorber, and 1-3 is the equivalent damping of the dynamic vibration absorber. 1-4 is the equivalent mass of the main vibration system, 1-5 is the equivalent stiffness of the main vibration system, and 1-6 is the ground or the bearing platform.
The vibration control principle of the dynamic vibration absorber is that an additional dynamic system is formed besides a vibration object, namely a main vibration system, and a resonance system formed by mass and springs absorbs vibration of the vibration object and then amplifies the vibration, and the vibration is consumed in damping elements of the vibration object to convert vibration energy into heat energy.
To achieve efficient conversion of vibrational energy to thermal energy, two conditions need to be satisfied: first, the ratio of the natural frequency of the vibration-suppressing object to the natural frequency of the dynamic vibration absorber satisfies the optimum homodyne condition, i.e., the ratio
Secondly, the damping requirement of the dynamic vibration absorber meets the optimal damping condition, namely
Wherein,being the natural angular frequency of the dynamic vibration absorber,and the mu is the ratio of the equivalent mass M of the dynamic vibration absorber to the equivalent mass M of the main vibration system.
When the main vibration system and the dynamic vibration absorber simultaneously meet the optimal homodyne condition and the optimal damping condition, the maximum amplitude ratio of the system is as follows:
when the vibration of the environment causes the main vibration system 1-4 to generate micro displacement, and the main vibration system 1-4 and the dynamic vibration absorber 1-1 simultaneously meet the optimal homodyne condition and the optimal damping condition, the dynamic vibration absorber 1-1 can absorb the vibration of the main vibration system 4 very well, at the moment, the main vibration system stops vibrating very fast, the dynamic vibration absorber generates displacement change and is consumed in the damping elements 1-3, and the main vibration system 1-4 is subjected to vibration reduction. Here, the vibration energy of the dynamic vibration absorber 1-1 is converted into heat in the damping motion.
By combining the working principle of the dynamic vibration absorber, the dynamic vibration absorber is arranged in the cooling channel, and the dynamic vibration absorber is arranged differently according to the different flow directions of the cooling medium in the cooling channel, so that the vibration in different directions can be controlled. When the vibration of the optical lens frame in a plane needs to be controlled, the vibration in two vector directions which are perpendicular to each other in the plane only needs to be controlled respectively.
In the present application, the transverse channels and the longitudinal channels are preferably arranged such that the transverse channels are supplied with a cooling medium flowing in the transverse direction and the longitudinal channels are supplied with a cooling medium flowing in the longitudinal direction. The dynamic vibration absorber is specifically set so as to obtain a lateral dynamic vibration absorber that can reduce lateral vibration and a longitudinal dynamic vibration absorber that can reduce longitudinal vibration. The transverse dynamic vibration absorber is a dynamic vibration absorber which adopts a cooling medium flowing along the transverse direction as a damping medium; the longitudinal dynamic vibration absorber refers to a dynamic vibration absorber that employs a cooling medium flowing in the longitudinal direction as a damping medium.
Further, the damping medium of the dynamic vibration absorber is limited by the cooling medium, and water, alcohol, fluorine, air, nitrogen, helium, or the like may be selected.
The optical lens frame can be used for clamping optical elements such as a reflector, a lens, a wave plate, a prism or an aperture diaphragm, and the position of the optical elements can be adjusted.
The solution of the present application is illustrated below by means of three different examples.
Example one
Referring to fig. 2, in the optical frame of the first embodiment, the frame body includes a frame, a frame rod and a frame base; the mirror frame is used for clamping optical elements and is connected with the mirror base through the mirror rod. The dynamic vibration absorber is arranged in the mirror frame, and the cooling medium is deionized water. In the figure, 2-1 is a mirror frame, 2-2 is a mirror plate, 2-3 is a heat sink around the mirror plate, 2-4 is a cooling channel inside the mirror frame, 2-5 is a longitudinal dynamic vibration absorber with a longitudinal damping medium distributed on the inner wall of the mirror frame, 2-6 is a lateral dynamic vibration absorber with a lateral damping medium distributed on the inner wall of the mirror frame, 2-7 is a cooling liquid inlet, 2-8 is a cooling liquid outlet, 2-9 is a mirror shaft, and 2-10 is a mirror base.
The entire frame body is fixed to the optical platform together with the cooling unit and the vibration absorbing unit provided on the frame body. Deionized water flowing out of the water cooler and having a constant temperature and a stable flow rate enters from a cooling liquid inlet 2-7, passes through a cooling channel 2-4 and flows out from a cooling liquid outlet 2-8. Indium foil is wound on the side face of the lens 2-2, so that the lens can be fully in good contact with the surrounding heat sink 2-3, and the heat conduction efficiency is improved. When the system is actually operated, the heat generated by the part of incident light absorbed by the lens 2-2 is continuously conducted to the heat sink 2-3, and the heat sink 2-3 absorbing the heat exchanges heat with the deionized water in the cooling channel 2-4 to finally take away the heat on the lens 2-2, so that the lens 2-2 is cooled.
Taking the longitudinal dynamic vibration absorbers 2-5 with longitudinal damping media distributed on the inner wall of the mirror frame as an example to calculate the vibration reduction effect of the dynamic vibration absorbers: the spectacle frame body is made of stainless steel, the integral equivalent mass is 1kg, and the equivalent rigidity is 2N/m; the inner wall of the mirror frame 2-1 is provided with a longitudinal dynamic vibration absorber 2-5; the longitudinal dynamic vibration absorber 2-5 adopts a cantilever beam structure, the equivalent mass is 0.1kg, namely the mass ratio is 0.1, the longitudinal equivalent stiffness is 0.2N/m, and the equivalent damping is 0.5 N.s/m. If the external excitation frequency caused by the external environment is changed from 0.6Hz to 1.4Hz, the vibration amplitude of the main vibration system is changed along with the external excitation frequency, and the characteristic is shown as a thick solid line in fig. 3, wherein the abscissa of fig. 3 corresponds to the external excitation frequency value, and the ordinate corresponds to the amplitude ratio.
It can be seen that the main vibration system has a resonance peak in the variation range of the external excitation frequency, and the maximum amplitude ratio is 28.94. After the longitudinal dynamic vibration absorber 2-5 is added in the spectacle frame 2-1, the amplitude of the resonance peak can be obviously reduced, the system is subjected to vibration reduction, and when the equivalent damping is smaller, the system has second-order natural frequency, namely double resonance peaks; the damping ratio and the fixed frequency ratio of the longitudinal dynamic vibration absorber 2-5 are further optimized by the formula (1) and the formula (2), the optimal damping ratio is 0.1679, the optimal fixed frequency ratio is 0.9091, and the characteristic curve of the main vibration system vibration amplitude changing along with the excitation frequency is shown as a thin solid line in fig. 3. It can be known from the figure that the maximum value of the amplitude of the formant of the main vibration system is reduced to the lowest value, the maximum amplitude ratio is 4.588, the amplitude values of the two formants are equal, the system is optimal at the moment, and the vibration damping performance is the best.
Similarly, in the transverse direction, the transverse dynamic vibration absorber 2-6 with a transverse damping medium is arranged on the inner wall of the mirror frame 2-1, the transverse dynamic vibration absorber 2-6 adopts a cantilever beam structure, and when the mass of the transverse dynamic vibration absorber 2-6 is determined, the optimal vibration reduction is obtained through the formula (1) and the formula (2).
Example two
Referring to fig. 4, the optical frame of the second embodiment is different from the first embodiment in that the cooling channel 2-4 is located inside the entire frame body, and the cooling medium is alcohol. And the longitudinal dynamic vibration absorbers 2-5 are distributed on the inner wall of the mirror rod 2-9, and the transverse dynamic vibration absorbers 2-6 are distributed on the inner wall of the mirror base 2-10. In addition, cooling liquid inlets 2-7 and cooling liquid outlets 2-8 are respectively arranged at two ends of the lens bases 2-10.
The longitudinal dynamic vibration absorbers 2-5 and the transverse dynamic vibration absorbers 2-6 in the second embodiment satisfy two conditions of optimal harmony and optimal damping.
Taking the longitudinal dynamic vibration absorbers 2-5 with longitudinal damping media distributed on the inner walls of the mirror rods 2-9 as an example to calculate the vibration reduction effect of the dynamic vibration absorbers: the spectacle frame body is made of duralumin, the integral equivalent mass is 0.4kg, and the equivalent stiffness is 1N/m; the longitudinal dynamic vibration absorber 2-5 is arranged on the inner wall of the mirror rod 2-9, the longitudinal dynamic vibration absorber 2-5 adopts a cantilever beam structure, the equivalent mass is 0.04kg, namely the mass ratio is 0.1, the longitudinal equivalent stiffness is 0.1N/m, and the equivalent damping is 0.5 N.s/m. When the external excitation frequency caused by the external environment changes from 0.7Hz to 1.3Hz, the vibration amplitude of the main vibration system changes along with the external excitation frequency, and the characteristic is shown as a thick solid line in FIG. 5, wherein the abscissa of FIG. 5 corresponds to the external excitation frequency value and the ordinate corresponds to the amplitude ratio.
It can be seen that the main vibration system has a resonance peak within the variation range of the external excitation frequency, and the maximum amplitude ratio is 112.9. After the longitudinal dynamic vibration absorber 2-5 is added in the mirror rod, the amplitude of the resonance peak can be obviously reduced, the system is subjected to vibration reduction, and when the equivalent damping is smaller, the system has second-order natural frequency, namely double resonance peaks; the damping ratio and the fixed frequency ratio of the longitudinal dynamic vibration absorber 2-5 are further optimized by the formula (1) and the formula (2), the optimal damping ratio is 0.1273, the optimal fixed frequency ratio is 0.9524, and the characteristic curve of the vibration amplitude of the main vibration system changing along with the excitation frequency is shown as a thin solid line in fig. 5. It can be known from the figure that the maximum value of the amplitude of the formant of the main vibration system is reduced to the lowest value, the maximum amplitude ratio is 6.407, the amplitude values of the two formants are equal, the system is optimal at the moment, and the vibration damping performance is the best.
When the spectacle frame body provided with the lenses vibrates under the influence of the environment, the spectacle frame body can generate small displacement in the transverse direction and the longitudinal direction, and the longitudinal dynamic vibration absorbers 2-5 and the transverse dynamic vibration absorbers 2-6 can well absorb the vibration of the spectacle frame body in the transverse direction and the longitudinal direction to enable the spectacle frame body to generate displacement and consume the displacement in a damping element, namely a cooling medium in the cooling channel 2-4, so that the change of the transmission direction of a light path is reduced to the maximum extent, and the spectacle frame body is damped. The vibration energy of the dynamic vibration absorber is converted into heat in the damping motion, and the heat is exchanged with the alcohol in the cooling channels 2-4, so that the dynamic vibration absorber is cooled.
EXAMPLE III
Referring to fig. 6, the optical frame of the third embodiment is different from the first embodiment in that the cooling channels 2-4 are located inside the whole frame body, and the cooling medium is liquid nitrogen. And the longitudinal dynamic vibration absorber 2-5 and the transverse dynamic vibration absorber 2-6 are distributed on the inner wall of the lens base 2-10. In addition, coolant inlets 2-7 and coolant outlets 2-8 are provided on both sides of the mirror bar 2-9, respectively.
The longitudinal dynamic vibration absorbers 2-5 and the transverse dynamic vibration absorbers 2-6 in the third embodiment satisfy two conditions of optimal harmony and optimal damping.
Taking the longitudinal dynamic vibration absorbers 2-5 with longitudinal damping media distributed on the inner walls of the mirror bases 2-10 as an example to calculate the vibration reduction effect of the dynamic vibration absorbers: the spectacle frame body is made of stainless steel, the integral equivalent mass is 2kg, and the equivalent rigidity is 2N/m; the inner wall of the mirror base 2-10 is provided with a transverse dynamic vibration absorber 2-6, the transverse dynamic vibration absorber 2-6 adopts a cantilever beam structure, the equivalent mass is 0.15kg, namely the mass ratio is 0.075, the transverse equivalent stiffness is 0.1N/m, and the equivalent damping is 0.5 N.s/m. Assuming that the external excitation frequency caused by the external environment is changed from 0.65Hz to 1.25Hz, the maximum amplitude ratio of the resonance peak of the main vibration system is 49.77. After the transverse dynamic vibration absorber 2-6 is added in the mirror base 2-10, the amplitude of the resonance peak of the transverse dynamic vibration absorber can be obviously reduced, the system can be subjected to vibration reduction, the damping ratio and the fixed frequency ratio of the transverse dynamic vibration absorber 2-6 are further optimized by the formula (1) and the formula (2), the optimal damping ratio is 0.1505, the optimal fixed frequency ratio is 0.9302, the maximum value of the vibration amplitude of the main vibration system is reduced to the minimum value, the maximum amplitude ratio is 5.265, the amplitude values of the two resonance peaks are equal, and the system is optimal and has the best vibration reduction performance.
The dynamic vibration absorber of the embodiment is arranged in the cooling channel of the optical lens bracket, and turbulent heat exchange of the dynamic vibration absorber can be realized, so that the heat exchange efficiency of the dynamic vibration absorber is improved. In addition, the dynamic vibration absorber is internally arranged, so that no light path is influenced to the outside.
The optical frame of the embodiment has a simple structure, does not need precise adjustment, does not have strict requirements on an optical-mechanical system and the like, and is wide in application range.
The above embodiments are merely illustrative of the present invention and are not to be construed as limiting the invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications or equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and the technical solution of the present invention is covered by the claims of the present invention.
Claims (8)
1. An optical frame comprises a frame body and a cooling unit, wherein the cooling unit comprises a cooling channel arranged in the frame body; and the damping medium of the dynamic vibration absorber is a cooling medium injected into the cooling channel.
2. The optical frame of claim 1, wherein the cooling channel comprises a transverse channel in which a cooling medium flows in a transverse direction, and a longitudinal channel in which a medium flows in a longitudinal direction; the dynamic vibration absorber comprises a transverse dynamic vibration absorber and a longitudinal dynamic vibration absorber; the damping medium of the transverse dynamic vibration absorber is the cooling medium which flows transversely in the transverse channel, and the damping medium of the longitudinal dynamic vibration absorber is the cooling medium which flows longitudinally in the longitudinal channel.
3. The optical frame of claim 1, wherein the frame body comprises a frame, a stem, and a base; the mirror frame is used for clamping optical elements and is connected with the mirror base through the mirror rod.
4. An optical frame as in claim 3, wherein the optical element is a mirror, a lens, a wave plate, a prism, or an aperture stop.
5. An optical frame as claimed in claim 3, wherein the cooling channel and the dynamic vibration absorber are both provided in the frame.
6. An optical frame according to claim 3, wherein the cooling channel is provided in the frame, the stem and the base, and the dynamic vibration absorber is provided in the stem/base.
7. An optical frame according to any of claims 1 to 6, wherein the spring element of the dynamic vibration absorber is a coil spring, a cantilever beam, a parallel plate spring, a torsion spring or a laminated rubber.
8. An optical frame as claimed in any one of claims 1 to 6, wherein the cooling medium introduced into the cooling channel is water, alcohol, fluorine, air, nitrogen or helium.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510306928.7A CN105445883B (en) | 2015-06-05 | 2015-06-05 | Optical lens bracket device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510306928.7A CN105445883B (en) | 2015-06-05 | 2015-06-05 | Optical lens bracket device |
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| Publication Number | Publication Date |
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| CN105445883A CN105445883A (en) | 2016-03-30 |
| CN105445883B true CN105445883B (en) | 2018-01-26 |
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| CN201510306928.7A Active CN105445883B (en) | 2015-06-05 | 2015-06-05 | Optical lens bracket device |
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| CN106646804B (en) * | 2016-12-21 | 2023-09-19 | 中国工程物理研究院激光聚变研究中心 | Clamping device and optical instrument |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2586177Y (en) * | 2002-12-27 | 2003-11-12 | 天津市激光技术研究所 | Polarizing axis large power laser optical reflector mount |
| JP2005152972A (en) * | 2003-11-27 | 2005-06-16 | Mitsubishi Electric Corp | Laser beam machining apparatus |
| CN101470236A (en) * | 2007-12-26 | 2009-07-01 | 沈阳大陆激光柔性制造技术有限公司 | Optical regulation lens frame suitable for mobile process full-solid state high power laser |
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2015
- 2015-06-05 CN CN201510306928.7A patent/CN105445883B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2586177Y (en) * | 2002-12-27 | 2003-11-12 | 天津市激光技术研究所 | Polarizing axis large power laser optical reflector mount |
| JP2005152972A (en) * | 2003-11-27 | 2005-06-16 | Mitsubishi Electric Corp | Laser beam machining apparatus |
| CN101470236A (en) * | 2007-12-26 | 2009-07-01 | 沈阳大陆激光柔性制造技术有限公司 | Optical regulation lens frame suitable for mobile process full-solid state high power laser |
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