CN219737969U - Ultra-high-speed rotating mirror device based on planetary speed change - Google Patents
Ultra-high-speed rotating mirror device based on planetary speed change Download PDFInfo
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Abstract
The utility model discloses an ultra-high-speed rotating mirror device based on a planetary gear assembly, which comprises a driving motor, a rotating mirror mechanism and a transmission ratio adjusting mechanism, wherein the rotating mirror mechanism comprises a rotating mirror and a rotating shaft, the transmission ratio adjusting mechanism is positioned between the driving motor and the rotating mirror mechanism and comprises a plurality of sets of planetary gear assemblies and corresponding clutches, and each set of planetary gear assembly is respectively connected between the driving motor and the rotating shaft in a transmission way; each set of planetary gear assembly has different transmission ratios, is axially and sequentially arranged on the rotating shaft, and is connected or disconnected with the rotating shaft through a corresponding clutch, and is simultaneously in transmission connection with the driving motor. The ultra-high-speed rotating mirror device realizes real-time speed change of the rotating mirror under different transmission ratios based on the planetary gear assembly.
Description
Technical Field
The present utility model relates to an ultra-high-speed imaging system, and more particularly, to an ultra-high-speed turning mirror device in an ultra-high-speed imaging system.
Background
The ultra-high-speed camera system is used for recording two-dimensional sequence images of some transient ultra-fast phenomena (such as high-voltage discharge, detonation and the like), and the obtained images can be used for researching the dynamic performance, process and mechanism of the phenomena. The ultra-high speed camera system has wide camera frequency, can be from tens of thousands per second to tens of thousands per second, and is a microsecond and sub microsecond image recording technology. The ultra-high speed image pickup frequency is obtained by sequential exposure of an ultra-high speed optical scanning shutter generated by an ultra-high speed rotating mirror. That is, the turning mirror is the core of the ultra-high speed camera system, and is a key technology for influencing the performance index of the system.
At present, a high-frequency motor is generally used for driving an ultra-high speed rotating mirror device. The high-frequency motor directly drives the rotary mirror by utilizing the frequency conversion of the high-frequency power supply to reach 2 x 10 per minute 5 However, the high-frequency power supply and the high-frequency motor are expensive, have large volumes and are inconvenient to maintain. The low-frequency motor is adopted, and the rotating speed of the rotating mirror is improved through the gear speed increasing mechanism, so that the ultra-high-speed rotating mirror with the advantages of simple structure, convenience in use, low cost and the like can be obtained.
The Chinese patent with the patent number of CN1499241A discloses an ultra-high-speed aluminum rotating mirror system, which comprises a supporting mechanism, a sealed shell, an aluminum rotating mirror arranged in the sealed shell, a speed increasing mechanism and a driving motor for driving the aluminum rotating mirror to rotate at an ultra-high speed through the speed increasing mechanism, wherein the speed increasing mechanism consists of a gear speed increasing mechanism and a large-speed-ratio coaxial speed increasing mechanism, the gear speed increasing mechanism comprises a large gear and a small gear, and the large gear is arranged on an output shaft of the driving motor and matched with the small gear so as to drive the small gear to rotate rapidly; the sealing shell comprises a body, a sealing cover and a sealing gasket which are arranged at the front end of the body, a sealing glass ball cover which is arranged on the side surface of the body and is opposite to the aluminum rotating mirror, a connecting plate which is used for fixedly connecting the driving motor with the tail end of the body, a sealing cover which is used for covering the driving motor and sealing the driving motor on the connecting plate, and a nozzle which is arranged on the connecting plate and is used for vacuumizing, wherein the high-speed-ratio coaxial speed-increasing mechanism comprises a friction sleeve, three high-speed wide bearings and a central shaft which are arranged at equal intervals, the friction sleeve and the pinion share the same rotating shaft, the tail end of the central shaft is positioned in the center of the friction sleeve, and the high-speed wide bearings are arranged in the friction sleeve and are tightly matched with the inner wall of the friction sleeve and the tail end of the central shaft; the aluminum rotating mirror is arranged in the middle of the central shaft; the friction sleeve can rotate at the same speed as the pinion, and drives the aluminum rotating mirror to rotate at an ultra-high speed through the high-speed wide bearing and the central shaft. The ultra-high-speed aluminum rotating mirror system adopts the gear speed increasing mechanism and the large-speed-ratio coaxial speed increasing mechanism to drive between the driving motor and the aluminum rotating mirror, and simultaneously realizes low-frequency output of the driving motor and high-speed rotation of the aluminum rotating mirror.
However, the ultra-high-speed aluminum rotary mirror system can only increase the rotating speed of the aluminum rotary mirror through a fixed transmission ratio by the gear speed increasing mechanism and the large-speed-ratio coaxial speed increasing mechanism, and cannot realize real-time speed change of the aluminum rotary mirror under different transmission ratios.
Disclosure of Invention
In order to solve the defects in the prior art, the utility model provides an ultra-high-speed rotating mirror device, which realizes real-time speed change of the rotating mirror under different transmission ratios based on a planetary gear assembly.
The technical problems to be solved by the utility model are realized by the following technical scheme:
the ultra-high-speed rotating mirror device based on the planetary gear assembly comprises a driving motor, a rotating mirror mechanism and a transmission ratio adjusting mechanism, wherein the rotating mirror mechanism comprises a rotating mirror and a rotating shaft, the transmission ratio adjusting mechanism is positioned between the driving motor and the rotating mirror mechanism and comprises a plurality of sets of planetary gear assemblies and corresponding clutches, and each set of planetary gear assembly is respectively connected between the driving motor and the rotating shaft in a transmission way; each set of planetary gear assembly has different transmission ratios, is axially and sequentially arranged on the rotating shaft, and is connected or disconnected with the rotating shaft through a corresponding clutch, and is simultaneously in transmission connection with the driving motor.
Further, each set of planetary gear assembly comprises an annular internal gear, a sun gear and a plurality of planetary gears, wherein the sun gear is sleeved outside the rotating shaft and is connected with or disconnected from the rotating shaft through a corresponding clutch, each planetary gear is arranged on the periphery of the sun gear at equal intervals and is meshed with the sun gear, and the annular internal gear is sleeved outside each planetary gear and is meshed with each planetary gear; the driving motor is connected with and drives the annular internal gears of the planetary gear assemblies to rotate simultaneously.
Further, there is at least one difference between the transmission ratio between the ring gear and the planet gears and the transmission ratio between the planet gears and the sun gear between the sets of planetary gear assemblies.
Further, a central through hole is formed in the sun gear of each set of planetary gear assembly, and a hollow pipe part extends out of the central through hole towards one side end surface of the central through hole; the rotating shafts sequentially penetrate through the central through holes of the sun gears, the clutches are sleeved outside the rotating shafts and the hollow pipe parts of the corresponding sun gears, one clutch ends of the clutches are fixedly connected with the rotating shafts, and the other clutch ends of the clutches are fixedly connected with the hollow pipe parts of the corresponding sun gears.
Further, the annular internal gear, the sun gear and the planet gears all adopt helical gears.
Further, each set of planetary gear assembly further comprises a gear baffle plate, the gear baffle plate is sleeved outside the rotating shaft and coaxially arranged with the sun gear, and a plurality of gear connecting shafts parallel to the rotating shaft are arranged at equal intervals on the same circumference of one side of the corresponding sun gear and one side of the planet gear; each planet wheel is rotatably sleeved outside the corresponding gear connecting shaft.
Further, the transmission ratio adjusting mechanism further comprises a rotating sleeve, a rotating cavity is arranged in the rotating sleeve, and the rotating shaft and each set of planetary gear assembly are arranged in the rotating cavity of the rotating sleeve; the annular internal gears of the planetary gear assemblies are axially formed on the inner wall of the rotating cavity; the end face of one side of the rotary sleeve is fixedly connected with the driving motor, and is driven to rotate by the driving motor.
Further, the rotating mirror mechanism further comprises two supporting components which are connected and used for supporting the rotating mirror, one supporting component is located at one axial end of the rotating mirror, and the other supporting component is located at the other axial end of the rotating mirror.
Further, each supporting component comprises a supporting seat and a plurality of friction wheels, a plurality of wheel cavities are formed in the end face of the supporting seat facing one side of the rotating mirror, and the wheel cavities are distributed around the center of the supporting seat at equal intervals; the center of each friction containing cavity is provided with a positioning pin shaft, and each friction wheel is rotatably sleeved outside the corresponding positioning pin shaft so as to be contained in the corresponding wheel cavity and in friction and propping against the outer wall of the rotating mirror shaft on the end face of the rotating mirror; the rotating shaft is formed by extending the center of a supporting seat of a supporting component facing one side of the transmission ratio adjusting mechanism into the transmission ratio adjusting structure.
Further, the speed measuring mechanism is arranged on the end face of the rotating mirror mechanism, which is opposite to one side of the transmission ratio adjusting mechanism.
The utility model has the following beneficial effects: the ultra-high speed rotating mirror device amplifies the low-frequency output of the driving motor through the planetary gear assembly in the transmission ratio adjusting mechanism and outputs the amplified low-frequency output to the rotating mirror through the rotating shaft, so that the rotating mirror can still realize ultra-high speed rotation under the low-frequency output of the driving motor, the planetary gear assembly in the transmission ratio adjusting mechanism is provided with a plurality of sets, and each set of planetary gear assembly is respectively connected between the driving motor and the rotating shaft in a transmission way; each set of planetary gear assembly has different transmission ratios and is connected with or disconnected from the rotating shaft through a corresponding clutch, when one clutch connects the corresponding planetary gear assembly with the rotating shaft, other clutches disconnect the corresponding planetary gear assembly from the rotating shaft, and each clutch can be controlled to be closed or separated according to the rotating speed required by the rotating mirror so as to select the planetary gear assembly with the proper transmission ratio to amplify the low-frequency output of the driving motor and output the amplified low-frequency output to the rotating mirror, thereby realizing real-time speed change of the rotating mirror under different transmission ratios.
Drawings
Fig. 1 is a schematic structural diagram of an ultra-high speed rotating mirror device provided by the utility model.
Fig. 2 is a schematic structural diagram of a driving motor in the ultra-high speed rotating mirror device provided by the utility model.
Fig. 3 is an exploded schematic view of a transmission ratio adjusting mechanism in the ultra-high speed rotating mirror device provided by the utility model.
Fig. 4 is an exploded schematic view of a turning mirror mechanism in the ultra-high speed turning mirror device provided by the utility model.
Fig. 5 is a schematic diagram of the friction wheel and the rotating mirror shaft in the ultra-high speed rotating mirror device provided by the utility model.
Detailed Description
The present utility model is described in detail below with reference to the drawings and the embodiments, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present utility model and should not be construed as limiting the utility model.
In the description of the present utility model, it should be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.
Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first", "a second", or a third "may explicitly or implicitly include one or more such feature. In the description of the present utility model, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," "disposed," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, or can be communicated between two elements or the interaction relationship between the two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.
Example 1
As shown in fig. 1, an ultra-high-speed rotating mirror device based on a planetary gear assembly comprises a driving motor 100, a transmission ratio adjusting mechanism 200 and a rotating mirror mechanism 300, wherein as shown in fig. 4, the rotating mirror mechanism 300 comprises a rotating mirror 301 and a rotating shaft 312, and the transmission ratio adjusting mechanism 200 is positioned between the driving motor 100 and the rotating mirror mechanism 300; as shown in fig. 3, the gear ratio adjusting mechanism 200 includes a plurality of sets of planetary gear assemblies 210 and corresponding clutches 220, and each set of planetary gear assemblies 210 is respectively connected between the driving motor 100 and the rotating shaft 312 in a transmission manner; each set of planetary gear assemblies 210 has different transmission ratios, is sequentially disposed on the rotation shaft 312 in the axial direction, and is connected to or disconnected from the rotation shaft 312 through a corresponding clutch 220, and is simultaneously connected to the driving motor 100 in a transmission manner.
The ultra-high speed rotating mirror device of the patent amplifies the low frequency output of the driving motor 100 through the planetary gear assembly 210 in the transmission ratio adjusting mechanism 200 and outputs the amplified low frequency output to the rotating mirror 301 through the rotating shaft 312, so that the rotating mirror 301 can still realize ultra-high speed rotation under the low frequency output of the driving motor 100, and the planetary gear assembly 210 in the transmission ratio adjusting mechanism is provided with a plurality of sets, and each set of planetary gear assembly 210 is respectively connected between the driving motor 100 and the rotating shaft 312 in a transmission way; each set of planetary gear assemblies 210 has different transmission ratios and is connected with or disconnected from the rotating shaft 312 through a corresponding clutch 220, when one clutch 220 connects the corresponding planetary gear assembly 210 with the rotating shaft 312, the other clutches 220 disconnect the corresponding planetary gear assembly 210 from the rotating shaft 312, and each clutch 220 can be controlled to be closed or separated according to the rotating speed required by the rotating mirror 301, so that the planetary gear assembly 210 with the proper transmission ratio is selected to amplify the low-frequency output of the driving motor 100 and output the amplified low-frequency output to the rotating mirror 301, and real-time speed change of the rotating mirror 301 under different transmission ratios is realized.
In this embodiment, two sets of planetary gear assemblies 210 are disposed in the gear ratio adjustment mechanism 200, each set of planetary gear assemblies includes a first set of planetary gear assemblies 210a having a first gear ratio and a second set of planetary gear assemblies 210b having a second gear ratio, the number of the clutches 220 is two, each set of planetary gear assemblies includes a first clutch 220a corresponding to the first set of planetary gear assemblies 210a and a second clutch 220b corresponding to the second set of planetary gear assemblies 210b, the first set of planetary gear assemblies 210a are connected to or disconnected from the rotating shaft 312 through the first clutch 220a, and the second set of planetary gear assemblies 210b are connected to or disconnected from the rotating shaft 312 through the second clutch 220 b; when the first clutch 220a is in a closed state, the second clutch 220b is in a separated state, the first clutch 220a connects the first set of planetary gear assemblies 210a with the rotating shaft 312, and the low-frequency output of the driving motor 100 is amplified according to a first transmission ratio and then provided to the rotating mirror 301; when the second clutch 220b is in the closed state, the first clutch 220a is in the disengaged state, the second clutch 220b connects the second set of planetary gear assemblies 210b with the rotating shaft 312, and the low frequency output of the driving motor 100 is amplified according to the second transmission ratio and then provided to the rotating mirror 301.
Preferably, the clutch 220 is an electromagnetic clutch 220, and the electromagnetic clutch 220 generates a pressing force by electromagnetic force so as to realize transmission or separation between shafts, thereby realizing remote control, having small control energy, being convenient for realizing machine tool automation, and simultaneously having the characteristics of quick response, good durability, easy assembly and maintenance and stable structure (being not loosened when being subjected to strong vibration), having simple structure and being widely applied.
Each set of planetary gear assemblies 210 comprises an annular inner gear 211, a sun gear 212 and a plurality of planetary gears 213, wherein the sun gear 212 is sleeved outside the rotating shaft 312 and is connected with or disconnected from the rotating shaft 312 through a corresponding clutch 220, each planetary gear 213 is arranged on the periphery of the sun gear 212 at equal intervals and is meshed with the sun gear 212, and the annular inner gear 211 is sleeved outside each planetary gear 213 and is meshed with each planetary gear 213; the driving motor 100 is connected to drive the ring gears 211 of the planetary gear sets 210 to simultaneously rotate.
When the driving motor 100 drives each set of planetary gear assemblies 210, the ring gears 211 of each set of planetary gear assemblies 210 rotate simultaneously, each ring gear 211 drives each planetary gear 213 in the same planetary gear assembly 210 to rotate first, each planetary gear 213 drives the sun gear 212 in the same planetary gear assembly 210 to rotate, the rotation output is transmitted to the planetary gear 213 in the same planetary gear assembly 210 by each ring gear 211, and then is transmitted to the sun gear 212 in the same planetary gear assembly 210 by each planetary gear 213; when one clutch 220 connects its corresponding sun gear 212 with the rotation shaft 312, the rotation shaft 312 obtains the rotation output amplified through the corresponding planetary gear assembly 210, while the other planetary gear assembly 210 is also transmitting, except that the other clutch 220 is not providing the rotation output of the other planetary gear assembly 210 to the rotation shaft 312 because it is in a disengaged state.
In this embodiment, the number of planetary gears 213 of each set of planetary gear assemblies 210 is three, and the three planetary gears 213 are distributed on the outer circumference of the corresponding sun gear 212 at 120 ° intervals.
Each set of planetary gear assemblies 210 employs a two-stage gearing, and the final gear ratio of each set of planetary gear assemblies 210 can be designed by the gear ratio between the ring gear 211 and the planet gears 213, and the gear ratio between the planet gears 213 and the sun gear 212.
There is at least one difference in the transmission ratio between the ring gear 211 and the planetary gear 213, and between the planetary gear 213 and the sun gear 212, such that the final transmission ratio between the sets of planetary gear assemblies 210 is different.
The final gear ratio i of each set of planetary gear assemblies 210 1 Depending on the number of teeth of its corresponding ring gear 211 and corresponding sun gear 212, since the planetary gear assembly 210 is an epicyclic train, the entire epicyclic train can be revolved around the rotational axis 312 by adding a common angular velocity- ωH to the entire epicyclic train, while the relative movement between the gears remains unchanged, and the angular velocity of each planet 213 becomes 0, which converts the epicyclic train into an epicyclic train, the transmission ratio of which can be expressed as:
wherein Z is 1 Z is the number of teeth of the annular internal gear 211 3 For the number of teeth of the sun gear 212, "-" indicates that the ring gear 211 is opposite in direction to the sun gear 212.
In this embodiment, the number of teeth of planetary gear 213 in first set of planetary gear assembly 210a is 90, the number of teeth of planetary gear 213 in second set of planetary gear assembly 210b is 120, and the gears of sun gear 212 of both first set of planetary gear assembly 210a and second set of planetary gear assembly 210b are 30; the number of teeth of the ring gear 211 and the sun gear 212 of the first set of planetary gear assemblies 210a and the second set of planetary gear assemblies 210b are respectively brought into the above formula, and the final gear ratio of the first set of planetary gear assemblies 210a is calculated to be 3, and the final gear ratio of the second set of planetary gear assemblies 210b is calculated to be 4.
Sun gears 212 of each set of planetary gear assemblies 210 are provided with a central through hole, and a hollow pipe 214 extends out of the central through hole towards one side end surface of the central through hole; the rotating shafts 312 sequentially penetrate through the central through holes of the sun gears 212, the clutches 220 are sleeved outside the rotating shafts 312 and the hollow pipe portions 214 of the corresponding sun gears 212, one clutch ends of the clutches are fixedly connected with the rotating shafts 312, and the other clutch ends of the clutches are fixedly connected with the hollow pipe portions 214 of the corresponding sun gears 212.
When both ends of the clutch 220 are closed, the clutch 220 connects the hollow tube portion 214 of the corresponding sun gear 212 with the rotation shaft 312, and when both ends of the clutch 220 are separated, the clutch 220 disconnects the hollow tube portion 214 of the corresponding sun gear 212 from the rotation shaft 312.
Preferably, the ring gear 211, the sun gear 212 and the planetary gears 213 are helical gears.
Compared with a straight gear, the helical gear has good transmission meshing performance, stable transmission and small noise, and the larger contact ratio ensures that the load of each group of gear teeth is lower, thereby greatly improving the bearing capacity; in addition, the bevel gear has fewer minimum teeth without undercut than the spur gear. However, on the premise that the circumferential force of the helical gear is constant, the axial thrust can be increased along with the increase of the helical angle, so that the helical angle of the helical gear can only be between 8 and 20 degrees. If the herringbone gear (a special symmetrical helical gear) is adopted, the axial thrust generated by the helical gear can be mutually offset by the symmetrical structure, so that a larger helical angle (25-40 DEG) can be obtained for high-speed and heavy-duty transmission.
Each set of planetary gear assemblies 210 further comprises a gear baffle 215, wherein the gear baffle 215 is sleeved outside the rotating shaft 312 and coaxially arranged with the sun gear 212, and a plurality of gear connecting shafts 216 parallel to the rotating shaft 312 are arranged on the same circumference of one side of the corresponding sun gear 212 and the planet gear 213 at equal intervals; each planetary gear 213 is rotatably sleeved outside the corresponding gear connecting shaft 216.
In this embodiment, the gear baffle 215 is located on the side of the corresponding planetary gear assembly 210 facing away from the opening of the rotating chamber 202.
The gear ratio adjusting mechanism 200 further comprises a rotating sleeve 201, a rotating cavity 202 is arranged in the rotating sleeve 201, and the rotating shaft 312 and each set of planetary gear assemblies 210 are arranged in the rotating cavity 202 of the rotating sleeve 201; annular inner gears 211 of each set of planetary gear assemblies are axially formed on the inner wall of the rotating chamber 202; the end face on one side of the rotating sleeve 201 is fixedly connected with the driving motor 100, and is driven to rotate by the driving motor 100.
When the driving motor 100 drives the rotating sleeve 201 to rotate, the rotating sleeve 201 drives the annular internal gears 211 of the planetary gear assemblies 210 to simultaneously rotate, so as to drive the planetary gear assemblies 210 to simultaneously drive.
In this embodiment, as shown in fig. 2, the opening of the rotating cavity 202 is disposed on the end face of the rotating sleeve 201 facing the side of the rotating mirror mechanism 300, and the bottom of the rotating cavity 202 is disposed on the end face of the rotating sleeve 201 facing the side of the driving motor 100 and is provided with a corresponding wedge-shaped hole 203 fixedly connected with the keyed stepped shaft 101 of the driving motor 100.
By fixed connection in this patent is meant that no relative movement between the two mechanisms or elements connected is possible, but not that the two mechanisms or elements connected are not removable.
Preferably, a motor washer 102 is disposed on an end surface of the driving motor 100 facing the gear ratio adjusting mechanism 200.
In designing the gear ratio adjustment mechanism 200, each set of planetary gear assemblies 210 needs to satisfy the following conditions:
(1) Satisfy the concentric condition
To enable proper operation of each set of planetary gear assemblies 210, the number of teeth of each set of planetary gear assemblies 210 needs to be such that the axes of revolution of their base members are collinear, i.e., concentric.
When standard or indexing gearing is used, each set of planetary gear assemblies 210 should satisfy the following formula:
Z 3 ＝Z 1 +2*Z 2
wherein Z1 is the number of teeth of the annular internal gear 211, Z 2 For the number of teeth, Z, of the planet gears 213 3 Is the number of teeth of the ring gear 211.
(2) Meets the uniform distribution condition
In order to uniformly assemble the planetary gears 213 of each set of planetary gear assemblies 210, the following formula should be satisfied between the number of planetary gears 213 of each set of planetary gear assemblies 210 and the number of teeth of the ring gear 211 and the sun gear 212:
(Z 1 +Z 3 )/k＝N
z1 is the number of teeth of the annular internal gear 211, Z 3 K is the number of the planetary gears 213, and N is a positive integer, which is the number of teeth of the ring gear 211.
I.e. the sum of the number of teeth of ring gear 211 and sun gear 212 in the same set of planetary gear assemblies 210 should be divisible by the number k of planetary gears 213.
(3) Meeting the adjacency condition
In order to avoid collision between the adjacent two planetary gears 213, the center-to-center distances of the adjacent two planetary gears 213 should satisfy the following formula:
(Z 1 +Z 2 )sin(180°/k)＞Z 2 +2*ha
wherein Z1 is the number of teeth of the annular internal gear 211, Z 2 K is the number of the planetary gears 213, ha is the center-to-center distance between two adjacent planetary gears 213.
(4) Helical angle condition
Since the planetary gear assemblies 210 are helical gears, the helical gear engagement of the planetary gear assemblies 210 should satisfy the following conditions:
external engagement β1= - β2
Internally engaged β1=β2
Wherein, β1 and β2 are the helical angles of two helical gears which are meshed respectively, namely, when external meshing is performed, the helical angles of the two helical gears are consistent, but the helical directions are opposite, and when internal meshing is performed, the helical angles of the two helical gears are the same, and the helical directions are the same.
Example two
As an optimization scheme of the first embodiment, in this embodiment, as shown in fig. 4, the rotating mirror mechanism 300 further includes two support assemblies 310 that are connected to support the rotating mirror 301, where one support assembly 310 is located on one axial end of the rotating mirror 301, and the other support assembly 310 is located on the other axial end of the rotating mirror 301.
Each supporting component 310 comprises a supporting seat 311 and a plurality of friction wheels 313, wherein a plurality of wheel cavities 314 are formed on the end surface of the supporting seat 311 facing to one side of the rotary mirror 301, and each wheel cavity 314 is distributed around the center of the supporting seat 311 at equal intervals; the center of each wheel cavity 314 is provided with a positioning pin shaft 314, and each friction wheel 313 is rotatably sleeved outside the corresponding positioning pin shaft 314 to be accommodated in the corresponding wheel cavity 314 and is in friction and propped against the outer wall of the rotating mirror shaft 302 on the end surface of the rotating mirror 301; the rotation shaft 312 is formed by extending the center of the support seat 311 of the support member 310 toward the gear ratio adjusting mechanism 200 into the gear ratio adjusting mechanism 200.
When the rotating shaft 312 rotates, the supporting component 310 facing to one side of the transmission ratio adjusting mechanism 200 is driven to rotate together, and then each friction wheel 313 on the side is driven to revolve around the rotating mirror shaft 302 by the supporting seat 311 on the side, and then the rotating mirror 301 is driven to rotate around the rotating mirror shaft 302 by the friction force of each friction wheel 313.
The support component 310 of the present patent adopts a plurality of friction wheels 313 to support the rotary mirror 301, has the advantages of high speed and large bearing capacity, can bear vibration load, and compared with the air film, oil film and magnetic force support in the prior art, no external equipment is needed, so that the support structure of the rotary mirror mechanism 300 is stable and reliable, and is convenient to control.
Wherein, the supporting component 310 facing the gear ratio adjusting mechanism 200 plays a role of driving the rotary mirror 301 to rotate through the rotating shaft 312 in addition to the role of supporting the rotary mirror 301.
In fact, the supporting component 310 in this embodiment is also a component for increasing the rotation speed, and the rotation speed is increased by means of the transmission structure among the supporting seat 311, the friction wheel 313 and the rotating mirror shaft 302, so that the low-frequency output of the driving motor 100 can be increased together with the transmission ratio adjusting mechanism 200.
The total gear ratio i of the gear ratio adjustment mechanism 200 and the support assembly 310 of this patent satisfies the following formula:
i＝i 1 *i 2
wherein i is 1 I is the gear ratio of the gear ratio adjustment mechanism 200 2 Is the gear ratio of the support assembly 310.
As shown in fig. 5, the gear ratio i of the support assembly 310 2 The following formula is satisfied:
wherein D is an equivalent diameter (mm) of the support seat 311, D is a diameter (mm) of the rotating mirror shaft 302, and D0 is an outer diameter (mm) of the friction wheel 313.
While the gear ratio i of the support assembly 310 2 In the case of a variable diameter of the shaft of the rotary mirror shaft 302 and of the outer diameter of the friction wheels 313, there is a maximum value, i.e. in the case of an exactly tangential outer diameter of the three friction wheels 313, the maximum transmission ratio can be achieved. This is the case:
substituting d into the previous gear ratio i 2 Can be obtained in the formula (I) 2 I is the maximum value of (i) 2 max is as followsThe following steps:
the turning mirror 301 is a critical component in the ultra-high speed turning mirror device, and the component having the highest rotational speed in the device should have sufficient strength and rigidity to ensure that the turning mirror can be prevented from being deformed or broken by centrifugal force during the high speed rotation, and in addition, the turning mirror 301 should have high reflectivity, high smoothness and high flatness in order to ensure the imaging quality and the brightness of the reflection target. The material of the rotary mirror 301 is determined according to the maximum rotation speed of the rotary mirror, when the maximum rotation speed is not higher than 15 ten thousand rpm, high-quality spring steel (60 Si2 CrA) is usually adopted, when the rotation speed is 30-60 ten thousand rpm, beryllium material is required, and when the rotation speed exceeds 60 ten thousand rpm, special tool steel is required. Common turning mirrors 301 include a single-sided turning mirror 301, a double-sided turning mirror 301, a triangular turning mirror 301, a quadrangular turning mirror 301, and the like. The triangular rotating mirror 301 is adopted in the embodiment, and has the characteristics of small deformation and low driving power. Moreover, it has been shown that comparing triangular-section and rectangular-section turning mirrors 301, the triangular-section turning mirror 301 allows higher rotational speeds, i.e., the limit rotational speed of the triangular-section turning mirror 301 is about 1.4 times that of the rectangular-section turning mirror 301, with the same material and mirror widths.
In this embodiment, the friction wheel 313 is a bearing, and a friction material such as rubber, silica gel or cloth is sleeved on the outer wall of the friction wheel.
In this embodiment, the outer ring of the bearing supports the rotating mirror shaft 302, while the inner ring is not stressed, and the positioning pin 314 fixes the bearing on the supporting seat 311, so that the concentricity of the rotating mirror 301 to the supporting seat 311 can be adjusted, and the pressure between the bearing and the rotating mirror shaft 302 can be changed. The experiment shows that: the radial ball bearing type C26 is most suitable for use in this construction. When the brass wave-shaped retainer is adopted, the bearing can reach 6 ten thousand revolutions per minute; the stainless steel wave-shaped retainer can reach 9-10 ten thousand rpm; for the ultra-high speed rotating mirror 301, a specially designed bearing C306026KJ may be used, and the outer ring rotation speed may exceed 15 ten thousand rpm, so that the rotating mirror 301 may theoretically reach a high speed of millions of revolutions according to the calculated maximum transmission ratio. In addition, this structure has an advantage that the rotation speed of the bearing is different from that of the rotary mirror shaft 302, and when the rotary mirror 301 rotates at a high speed of up to several hundred thousand rpm, the rotation speed of the bearing is only several tens of thousands rpm due to the transmission ratio therebetween, thus greatly improving the life of the bearing.
The turning mirror mechanism 300 further comprises a turning mirror chamber 320, the turning mirror 301 is disposed in the turning mirror chamber 320, and two support assemblies 310 are respectively disposed on two axial ends of the turning mirror chamber 320 to seal the turning mirror chamber 320; the turning mirror chamber 320 has a light-transmitting cover 321, and the range of the light-transmitting cover 321 is adapted to the range of the light-emitting and light-entering of the turning mirror 301.
If the rotating mirror 301 rotates at a high speed in the air, a large air resistance is received, so that energy consumption and heat generation are greatly consumed, and thus the rotation speed of the rotating mirror 301 is improved, and even the imaging quality is reduced. The operating environment of the turning mirror 301 is thus of great importance for its normal operation. The experiment was carried out by not treating, introducing helium gas and evacuating the same parameters in the rotating mirror chamber 320, and comparing the rotation speeds during operation, and finding that the rotation speed of the rotating mirror 301 is the fastest under vacuum, and then, the slowest under helium gas is the air environment which is not treated. It is known that the change of the medium environment has a significant effect on the rotational speed increase of the rotary mirror 301, and in addition, the vacuum degree has a great effect on the speed of the rotary mirror 301, and when the vacuum degree is 100-300 mmHg, the change of the vacuum degree causes a large speed change of the rotary mirror 301. Therefore, in the design, the rotary mirror chamber 320 may be kept in a vacuum state by the design of the glass shield, the sealing ring, the air-pumping hole, etc., so that the rotary mirror 301 may be operated in vacuum, and if a high vacuum degree cannot be achieved due to the cost effect, the air resistance of the rotary mirror 301 may be reduced by introducing helium gas into the rotary mirror chamber 320 through the air-pumping hole and exhausting air.
Example III
As an optimization scheme of the first embodiment or the second embodiment, in this embodiment, as shown in fig. 1, the ultra-high speed rotating mirror device further includes a speed measuring mechanism, where the speed measuring mechanism is disposed on an end surface of the rotating mirror mechanism 300 facing away from the side of the transmission ratio adjusting mechanism 200.
The ultra-high speed rotating mirror device can detect the rotating speed of the rotating mirror 301 through the speed measuring mechanism, so that the rotating speed of the rotating mirror 301 is fed back to the controller, and the controller controls the closing or the separation of each clutch 220 in the transmission ratio adjusting mechanism 200 according to a preset control program.
The ultra-high speed rotating mirror device further comprises a protective shell, wherein the protective shell is approximately cylindrical in shape, is similar to the driving motor 100 in shape, and is connected to one end face of one side of the driving motor 100; the transmission ratio adjusting mechanism 200, the rotating mirror mechanism 300 and the speed measuring mechanism 400 are all arranged in the protective shell, a window is arranged on the protective shell, and a light-transmitting cover of the rotating mirror mechanism 300 is exposed out of the window of the protective shell.
Finally, it should be noted that the foregoing embodiments are merely for illustrating the technical solution of the embodiments of the present utility model and are not intended to limit the embodiments of the present utility model, and although the embodiments of the present utility model have been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that the technical solution of the embodiments of the present utility model may be modified or replaced with the same, and the modified or replaced technical solution may not deviate from the scope of the technical solution of the embodiments of the present utility model.
Claims (10)
1. The ultra-high-speed rotating mirror device based on the planetary gear assembly comprises a driving motor and a rotating mirror mechanism, wherein the rotating mirror mechanism comprises a rotating mirror and a rotating shaft, and is characterized by further comprising a transmission ratio adjusting mechanism, wherein the transmission ratio adjusting mechanism is positioned between the driving motor and the rotating mirror mechanism and comprises a plurality of sets of planetary gear assemblies and corresponding clutches thereof, and each set of planetary gear assembly is respectively connected between the driving motor and the rotating shaft in a transmission way; each set of planetary gear assembly has different transmission ratios, is axially and sequentially arranged on the rotating shaft, and is connected or disconnected with the rotating shaft through a corresponding clutch, and is simultaneously in transmission connection with the driving motor.
2. The ultra-high-speed rotating mirror device based on planetary gear assemblies according to claim 1, wherein each set of planetary gear assemblies comprises an annular internal gear, a sun gear and a plurality of planetary gears, the sun gear is sleeved outside the rotating shaft and is connected with or disconnected from the rotating shaft through a corresponding clutch, each planetary gear is arranged on the periphery of the sun gear at equal intervals and is meshed with the sun gear, and the annular internal gear is sleeved outside each planetary gear and is meshed with each planetary gear; the driving motor is connected with and drives the annular internal gears of the planetary gear assemblies to rotate simultaneously.
3. The ultra-high-speed rotating mirror device based on planetary gear assembly according to claim 2, wherein at least one of a transmission ratio between the ring gear and the planetary gear, and a transmission ratio between the planetary gear and the sun gear is different between each set of planetary gear assemblies.
4. The ultra-high-speed rotating mirror device based on the planetary gear assembly according to claim 2, wherein a central through hole is formed in the sun gear of each set of planetary gear assembly, and the central through hole extends out of the hollow pipe part towards one side end surface of the central through hole; the rotating shafts sequentially penetrate through the central through holes of the sun gears, the clutches are sleeved outside the rotating shafts and the hollow pipe parts of the corresponding sun gears, one clutch ends of the clutches are fixedly connected with the rotating shafts, and the other clutch ends of the clutches are fixedly connected with the hollow pipe parts of the corresponding sun gears.
5. The ultra-high-speed rotating mirror device based on a planetary gear assembly according to claim 2, wherein the annular internal gear, the sun gear and the planetary gear are helical gears.
6. The ultra-high-speed rotating mirror device based on planetary gear assemblies according to claim 2, wherein each set of planetary gear assemblies further comprises a gear baffle plate, the gear baffle plate is sleeved outside the rotating shaft and coaxially arranged with the sun gear, and a plurality of gear connecting shafts parallel to the rotating shaft are arranged at equal intervals on the same circumference on one side of the corresponding sun gear and the side face of the planet gear and outside one side of the corresponding sun gear and the side face of the planet gear; each planet wheel is rotatably sleeved outside the corresponding gear connecting shaft.
7. The ultra-high-speed rotating mirror device based on the planetary gear assembly according to claim 2, wherein the transmission ratio adjusting mechanism further comprises a rotating sleeve, a rotating cavity is arranged in the rotating sleeve, and the rotating shaft and each set of planetary gear assembly are arranged in the rotating cavity of the rotating sleeve; the annular internal gears of the planetary gear assemblies are axially formed on the inner wall of the rotating cavity; the end face of one side of the rotary sleeve is fixedly connected with the driving motor, and is driven to rotate by the driving motor.
8. The ultra-high speed rotating mirror device based on a planetary gear assembly according to claim 1, wherein the rotating mirror mechanism further comprises two support assemblies connected to support the rotating mirror, one support assembly being located on one axial end of the rotating mirror and the other support assembly being located on the other axial end of the rotating mirror.
9. The ultra-high-speed rotating mirror device based on the planetary gear assembly according to claim 8, wherein each supporting assembly comprises a supporting seat and a plurality of friction wheels, a plurality of wheel cavities are formed in the end face of the supporting seat facing one side of the rotating mirror, and the wheel cavities are distributed around the center of the supporting seat at equal intervals; the center of each friction containing cavity is provided with a positioning pin shaft, and each friction wheel is rotatably sleeved outside the corresponding positioning pin shaft so as to be contained in the corresponding wheel cavity and in friction and propping against the outer wall of the rotating mirror shaft on the end face of the rotating mirror; the rotating shaft is formed by extending the center of a supporting seat of a supporting component facing one side of the transmission ratio adjusting mechanism into the transmission ratio adjusting structure.
10. The ultra-high-speed rotating mirror device based on the planetary gear assembly according to claim 1, further comprising a speed measuring mechanism, wherein the speed measuring mechanism is arranged on an end surface of the rotating mirror mechanism, which is opposite to one side of the transmission ratio adjusting mechanism.
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| CN202320997231.9U CN219737969U (en) | 2023-04-24 | 2023-04-24 | Ultra-high-speed rotating mirror device based on planetary speed change |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202320997231.9U CN219737969U (en) | 2023-04-24 | 2023-04-24 | Ultra-high-speed rotating mirror device based on planetary speed change |
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| CN202320997231.9U Active CN219737969U (en) | 2023-04-24 | 2023-04-24 | Ultra-high-speed rotating mirror device based on planetary speed change |
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