Two-dimensional adjustment system with electrically powered locking and method of use thereof

Abstract

The present application relates to the technical field of optical mirror, and discloses a two-dimensional adjustment system with electric locking and a use method thereof, comprising an adjustment unit for optical mirror pose adjustment, an electric control unit for providing a first driving input and a manual control unit for providing a second driving input are arranged on one side of the adjustment unit, and a switching unit is arranged in a support frame; the present application takes a telescopic rod as a control hub, linear motion of the telescopic rod is converted into synchronous rotation of a driving gear and axial movement of a limiting gear ring through a rigidly connected connecting plate and a connecting rod. The driving gear controls clamping and separation of a brake disc by a brake clamp plate, and the limiting gear ring controls engagement and disengagement of a limiting gear block, the two actions are forced to be synchronous, opposite in direction, completely overlapped in time and continuously and gradually changed in force, so that smooth and seamless handover of power between electric and manual inputs of a planetary gear differential is ensured.

Description

Technical Field

[0001] This invention relates to the field of optical mirror technology, and more specifically to a two-dimensional adjustment system with electric locking and its method of use. Background Technology

[0002] In the field of two-dimensional precision adjustment involving large-aperture, high-precision optical mirrors, existing technologies generally adopt a dual-mode electric and manual drive system equipped with an independent locking mechanism. The typical implementation is as follows: the mirror is driven to move via a first drive source, such as a servo motor, through a first transmission chain to achieve electric adjustment; and manual fine-tuning is achieved via a second drive interface, such as a handwheel, through a second transmission chain. Two independent control elements are configured, such as electromagnetic brakes or clutches acting on the motor shaft and handwheel shaft respectively, to switch and lock the working mode.

[0003] However, this architecture reveals a significant and difficult-to-overcome drawback in practical applications: the unavoidable mechanical shock and optical axis disturbance during mode switching. This problem is mainly caused by the following mechanisms:

[0004] First, even if the two independent locking and releasing elements receive synchronized electronic control signals, their starting and ending times cannot achieve true microscopic synchronization due to differences in their respective mechanical inertia, electromagnetic response delays, and inherent gaps in the transmission links.

[0005] Secondly, the essence of switching is the transfer of power between two drive chains. Ideally, when attempting to switch from electric to manual mode, the brake on the motor shaft should be fully engaged to provide damping, while the clutch on the handwheel shaft should be fully disengaged. However, due to the asynchrony of these actions, in reality, there are often brief power interruptions where neither drive chain effectively takes over, or power conflicts where both drive chains simultaneously attempt to take over. Both of these states can cause a sudden change or oscillation in the effective torque on the final output shaft of the drive mirror. This transient torque change is amplified by the transmission system, ultimately manifesting as a small but not negligible angular acceleration on the mirror surface, thus causing a sudden jump in the optical axis direction or low-frequency vibration. For precision optical systems, this switching disturbance has a significant impact on the optical mirror, forcing operators to perform time-consuming and complex optical path calibration after each mode switch, severely restricting assembly, adjustment, and testing efficiency. Furthermore, repeated impact loads can accelerate the wear of transmission components, affecting the long-term accuracy retention of the system.

[0006] Therefore, how to ensure the absolute smoothness and continuity of power transmission during mode switching from the mechanical structure level, and completely eliminate the impact of switching shock on the stability of the optical axis, has become a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0007] In view of the above-mentioned shortcomings of the prior art, the present invention provides a two-dimensional adjustment system with electric locking and its usage method, which can effectively solve the problems existing in the prior art.

[0008] To achieve the above objectives, the present invention provides the following technical solution:

[0009] The present invention provides a two-dimensional adjustment system with electric locking, including a support frame, an optical reflector disposed in the support frame, an adjustment unit for adjusting the position of the optical reflector disposed on the support frame, an electric control unit for providing a first drive input and a manual control unit for providing a second drive input disposed on one side of the adjustment unit, and a switching unit disposed in the support frame, the switching unit being used to selectively transmit the first drive input or the second drive input to the output end of the adjustment unit based on an operation command through differential coordination.

[0010] Furthermore, the adjustment unit includes a planetary gear differential, which has a first port, a second port, and a third port. The first port is connected to the electric control unit to receive a first drive input, the second port is connected to the manual control unit to receive a second drive input, and the third port constitutes the output terminal of the adjustment unit.

[0011] Furthermore, the first port includes a central gear and a first connecting shaft. The central gear serves as the sun gear of the planetary gear differential. The first connecting shaft is coaxially and fixedly connected to the central gear and extends outward. The second port includes a planet carrier and a second connecting shaft. A planetary gear shaft is mounted on the planet carrier. The second connecting shaft is coaxially and fixedly connected to the planet carrier and extends outward, forming the input interface of the manual control unit. The second connecting shaft is sleeved on the first connecting shaft. The third port includes an external gear ring and an output flange. The internal teeth of the external gear ring mesh with the planetary gears of the planetary gear differential. The output flange is coaxially and fixedly connected to the external gear ring, forming the output end of the adjustment unit.

[0012] Furthermore, the electric control unit includes a drive device disposed on one side of the support frame, and the output end of the drive device is connected to the first connecting shaft for transmission.

[0013] Furthermore, the switching unit includes a brake disc mounted on the first connecting shaft, brake plates for applying braking damping are mounted on both sides of the brake disc, a drive rack is mounted at the bottom of the brake plates, a drive gear meshing with the drive rack is mounted inside the support frame, a connecting plate is connected to one side of the drive gear, a telescopic rod is connected to the end of the connecting plate away from the drive gear, a connecting rod is mounted on one side of the telescopic rod, a limit gear ring is mounted on the top of the connecting rod, and a limit tooth block that cooperates with the limit gear ring is mounted on the outer wall of the second connecting shaft.

[0014] Furthermore, the manual control unit includes a rotating rod disposed on one side of the drive device, a handwheel disposed at one end of the rotating rod, and a transmission gear disposed at the end of the rotating rod away from the handwheel, the transmission gear being connected to the limit gear block in a transmission connection.

[0015] Furthermore, when the telescopic rod is in the extended position, the connecting plate drives the drive gear to rotate, causing the brake plates on both sides to separate from the brake disc. At the same time, the connecting rod drives the limiting gear ring to mesh with the limiting gear block.

[0016] Furthermore, when the telescopic rod is in the retracted position, the connecting plate drives the drive gear to rotate in the opposite direction, causing the brake plates on both sides to clamp the brake disc. At the same time, the connecting rod drives the limit gear ring to disengage from the limit gear block.

[0017] A method for using the two-dimensional adjustment system with electric locking is also provided, including the following steps:

[0018] Step 1: Receive the mode switching command and control the telescopic rod to move between the extended and retracted positions;

[0019] Step 2: During the movement of the telescopic rod, the connecting plate connected to the telescopic rod pulls the drive gear to rotate, which in turn causes the two drive racks meshing with the drive gear to move the brake plates closer or further apart, so as to gradually apply or release the clamping of the brake disc.

[0020] Step 3: During the same process of the telescopic rod's movement, the connecting rod connected to the telescopic rod drives the limiting gear ring to move synchronously, so that the limiting gear ring and the limiting gear block gradually disengage or engage, so as to release or lock the second port synchronously.

[0021] Step 4: By overlapping the actions of the brake clamp and the limiting gear ring in time and gradually changing the force in Steps 2 and 3, the power transition between the first drive input and the second drive input is achieved.

[0022] Furthermore, in step two, the connecting plate converts the linear motion of the telescopic rod into the rotational motion of the drive gear;

[0023] In step three, the connecting rod converts the linear motion of the telescopic rod into the axial movement of the limiting gear ring;

[0024] Both the connecting plate and the connecting rod are driven by the telescopic rod, so that the rotation of the drive gear and the axial movement of the limiting gear ring are executed synchronously in a single continuous stroke of the telescopic rod.

[0025] The technical solution provided by this invention has the following advantages compared with the prior art:

[0026] 1. This invention, by setting up a mechanism driven by a telescopic rod and connected to a locking control element via a connecting plate, ensures that the braking action on the first port and the locking action on the second port are driven by the same power source and completed in the same continuous stroke. This fundamentally guarantees the absolute synchronization of the two actions and the reverse coordination of their directions of motion from the mechanical structure itself. It fundamentally eliminates the power interruption or power conflict caused by the response delay and action sequence difference of the two independent elements, thereby ensuring that the driving torque transmitted to the third port is continuous and without sudden changes throughout the entire process of mode switching, and completely avoids the optical axis disturbance caused by switching shock.

[0027] 2. This invention, through a linkage structure, transforms the complex power transfer control during mode switching into linear control of the displacement of a single telescopic rod. This allows the process of establishing the clamping force of the brake disc on the brake caliper and the process of releasing the meshing force of the limiting gear ring and the limiting gear block to naturally exist on the same time axis and have complementary force change curves. This achieves a seamless and smooth transition of power between the first drive input and the second drive input, eliminating the need for recalibrating the optical path of the optical reflector before and after switching. This significantly improves the efficiency of precision assembly and testing and the long-term reliability of the system. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0029] Figure 1 This is a schematic diagram of the structure of an embodiment of the present invention;

[0030] Figure 2 This is a schematic diagram of the structure of the adjustment unit in an embodiment of the present invention;

[0031] Figure 3 This is a cross-sectional view of the adjustment unit in an embodiment of the present invention;

[0032] Figure 4 This is a cross-sectional view of the external gear ring in an embodiment of the present invention;

[0033] Figure 5 This is a schematic diagram of the planetary carrier structure in an embodiment of the present invention;

[0034] Figure 6 This is a schematic diagram of the planetary gear differential in an embodiment of the present invention;

[0035] Figure 7 This is a schematic diagram of the electric control unit and the manual control unit in an embodiment of the present invention;

[0036] Figure 8 This is a schematic diagram of the electric control unit in an embodiment of the present invention;

[0037] Figure 9 This is a schematic diagram of the manual control unit in an embodiment of the present invention;

[0038] Figure 10 This is a schematic diagram of the switching unit in an embodiment of the present invention;

[0039] Figure 11 This is a schematic diagram of the brake clamp and the limiting gear ring in an embodiment of the present invention;

[0040] Figure 12 This is a flowchart illustrating the usage method of the two-dimensional adjustment system with electric locking in an embodiment of the present invention.

[0041] Explanation of icon numbers:

[0042] 1. Support frame; 11. Optical reflector;

[0043] 2. Adjustment unit; 21. Planetary gear differential; 211. First port; 2111. Center gear; 2112. First connecting shaft; 212. Second port; 2121. Planetary carrier; 2122. Second connecting shaft; 213. Third port; 2131. External gear ring; 2132. Output flange;

[0044] 3. Electric control unit; 31. Drive unit;

[0045] 4. Manual control unit; 41. Rotating lever; 42. Handwheel; 43. Transmission gear;

[0046] 5. Switching unit; 51. Brake disc; 52. Brake clamp; 53. Drive rack; 54. Drive gear; 55. Connecting plate; 56. Telescopic rod; 57. Connecting rod; 58. Limiting gear ring; 59. Limiting gear block. Detailed Implementation

[0047] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0048] The present invention will be further described below with reference to embodiments.

[0049] Example 1

[0050] Reference Figure 1 - Figure 11 This first embodiment of the invention provides a two-dimensional adjustment system with electric locking, including a support frame 1, in which an optical mirror 11 is disposed. This optical mirror 11 is typically a large-sized plane mirror with extremely high surface accuracy. Its core function is to serve as an indispensable reference element during the construction, debugging, image quality testing, and optical axis calibration of a precision optical system. To ensure the performance of the optical system, the pitch and azimuth angles of the optical mirror 11 need to be able to be adjusted with extreme precision and remain stable for a long time after adjustment.

[0051] In existing technical solutions, to achieve both electric rapid positioning and manual fine-tuning, a parallel architecture with two independent transmission chains is typically used. One chain, driven by a motor, is responsible for electric adjustment, while the other, driven by a handwheel 42, is responsible for manual operation. Each chain is equipped with an independent electromagnetic brake or clutch to achieve mode switching and locking. The two locking elements rely on their respective independent electronic signals for triggering, making it difficult to achieve precise mechanical synchronization down to the millisecond or even microsecond level during actual operation.

[0052] This minute timing difference can cause a brief power vacuum or power overlap in the drive chain of the optical reflector 11 at the moment of switching, resulting in a sudden change or oscillation in the output torque. After being amplified by the transmission system, this torque disturbance will directly cause the optical reflector 11 to produce a small, unexpected angular acceleration, which manifests as an instantaneous jump in the optical axis or a slight jitter lasting for several seconds. This disturbance introduced by mode switching is a fatal flaw, which forces the operator to re-execute the tedious and time-consuming optical path alignment procedure after each switch of working mode, which seriously restricts work efficiency and system reliability.

[0053] An adjustment unit 2 for performing the aforementioned angle adjustment function is installed on the support frame 1. One side of the adjustment unit 2 is connected to an electric control unit 3 that provides the first drive input, and the other side is connected to a manual control unit 4 that provides the second drive input. The support frame 1 also integrates a switching unit 5. The function of the switching unit 5 is to intelligently select, according to the external operation command, to transmit the rotational power of the first drive input or the second drive input to the output end of the adjustment unit 2 that ultimately drives the optical reflector 11 to rotate through the internal differential coordination mechanism.

[0054] The adjustment unit 2 includes a planetary gear differential 21, which has three functional ports: a first port 211, a second port 212, and a third port 213. The first port 211 is used to connect to and receive a first drive input from the electric control unit 3, the second port 212 is used to connect to and receive a second drive input from the manual control unit 4, and the third port 213 serves as the power output terminal of the entire adjustment unit 2, whose rotational motion is directly converted into the attitude change of the optical reflector 11.

[0055] Specifically, the first port 211 includes a central gear 2111 that serves as a sun gear, and a first connecting shaft 2112 that is coaxially fixed to the central gear 2111 and extends outward. The power output from the motor will be input through the first connecting shaft 2112 to drive the central gear 2111 to rotate.

[0056] The second port 212 includes a planet carrier 2121 and a second connecting shaft 2122 that is coaxially fixed to the planet carrier 2121 and extends outward. It is worth noting that the second connecting shaft 2122 is mounted outside the first connecting shaft 2112 in a sleeve manner. The two can rotate independently around the same axis. During manual operation, power is input through the second connecting shaft 2122 to drive the planet carrier 2121 to rotate. Multiple planetary gears are evenly distributed on the planet carrier 2121. These planetary gears mesh with the central gear 2111 at the center and an external gear ring 2131 on the periphery.

[0057] The third port 213 consists of the external gear ring 2131 and the output flange 2132, which is coaxially fixed with it. According to the kinematic principle of the classic planetary gear mechanism, once the motion state of any two of the three components—the central gear 2111, the planet carrier 2121, and the external gear ring 2131—is determined, the motion state of the third component is also uniquely determined. Therefore, by selectively controlling the states of the first port 211 and the second port 212, even if they are in different states such as free rotation, being driven, or being locked, the power flow can be precisely guided, so that the output flange 2132 that ultimately drives the optical reflector 11 is driven only by the motor or only by the handwheel 42.

[0058] The electric control unit 3 mainly includes a drive device 31 fixedly installed on the side of the support frame 1. Its output shaft is connected to the first connecting shaft 2112 mentioned above through a coupling or similar transmission component. The drive device 31 can be selected from high-precision servo motors or stepper motors according to the needs of specific application scenarios. Its core function is to provide controllable and high-precision rotational motion for the system in electric working mode, so as to realize the rapid positioning or low-speed precision scanning of the optical reflector 11.

[0059] The switching unit 5 includes a brake disc 51 fixedly mounted on the first connecting shaft 2112. The brake disc 51 rotates synchronously with the first connecting shaft 2112. A pair of brake clamps 52 are symmetrically arranged on two sides of the brake disc 51. The two brake clamps 52 are mounted on precision linear guides provided by the support frame 1 to ensure that they can only slide in a direction perpendicular to the plane of the brake disc 51. A drive rack 53 is rigidly connected to the bottom of each brake clamp 52. A drive gear 54 is installed on the inner frame of the support frame 1. The drive gear 54 maintains a meshing relationship with the drive racks 53 at the bottom of the left and right brake clamps 52.

[0060] One side of the drive gear 54 is driven by a connecting plate 55, the other end of which is hinged to the end of a telescopic rod 56. When the telescopic rod 56 reciprocates linearly, it pushes or pulls the drive gear 54 through the connecting plate 55, forcing the drive gear 54 to produce precise rotational motion. The rotation of the drive gear 54 synchronously drives the two drive racks 53 meshing with it to move in opposite directions linearly, thereby precisely controlling the two brake plates 52 to move synchronously towards each other to clamp the brake disc 51, or to move synchronously away from each other to release the brake disc 51. The clamping of the brake disc 51 provides an adjustable frictional damping force to the first connecting shaft 2112, i.e., the sun gear shaft, while in the released state, the sun gear shaft is in a free rotation state.

[0061] As the sole power source for the entire switching unit 5, the telescopic rod 56 can be driven by various linear actuation methods, such as electric push rods, pneumatic cylinders, or hydraulic cylinders. These are all mature existing technology components, and their internal structures will not be described in detail here.

[0062] A connecting rod 57 is rigidly connected to one side of the cylinder or piston rod of the telescopic rod 56. A semi-annular or circular limiting gear ring 58 is installed at the top of the connecting rod 57. Correspondingly, a limiting gear block 59 is machined on the outer circumferential surface of the second connecting shaft 2122, which is fitted outside the first connecting shaft 2112. When the telescopic rod 56 performs telescopic movement, it will synchronously drive the limiting gear ring 58 to move axially through the connecting rod 57. When the limiting gear ring 58 moves to a specific position and fully engages with the limiting gear block 59 on the second connecting shaft 2122, it will mechanically lock the second connecting shaft 2122 and prevent it from rotating. When the limiting gear ring 58 moves to another position and completely disengages from the limiting gear block 59, it will completely release the second connecting shaft 2122 and allow it to rotate freely.

[0063] The manual control unit 4 is independent of the drive unit 31. It includes a rotating rod 41 rotatably supported on the support frame 1. One end of the rotating rod 41 is equipped with a handwheel 42 for direct operation by the operator, and the other end is equipped with a transmission gear 43. The transmission gear 43 can mesh with a limiting tooth block 59 reserved on the outer wall of the second connecting shaft 2122 through an intermediate gear set or directly, so as to seamlessly transmit the rotation operation on the handwheel 42 to the second connecting shaft 2122, thereby driving the planetary carrier 2121 to rotate.

[0064] The clear working logic of the entire system is as follows: When the telescopic rod 56 is in the fully extended mechanical position, the drive gear 54 is rotated to a specific angle through the transmission of the connecting plate 55, causing the brake plates 52 on both sides to be in the maximum separation state, the brake disc 51 to be fully released, and the sun gear shaft to be free. At the same time, through the transmission of the connecting rod 57, the limiting gear ring 58 is lifted to a specific height, so that it enters a fully meshed state with the limiting gear block 59 on the second connecting shaft 2122, thereby firmly locking the second port 212. This state is defined as the electric drive mode. In this mode, the electric motor can drive the first connecting shaft 2112 to rotate without obstruction, while the locked planetary carrier 2121 forces the planetary gear mechanism to transmit the motor power to the external gear ring 2131 at a fixed transmission ratio, thereby driving the optical reflector 11. The handwheel 42 cannot rotate because the second port 212 is mechanically locked. When the telescopic rod 56 is in the fully retracted mechanical position, the drive gear 54 rotates in the opposite direction under the action of the connecting plate 55, driving the brake clamps 52 on both sides to move towards each other until the brake disc 51 is clamped, thereby forming a preset braking damping on the first connecting shaft 2112.

[0065] It should be noted that, according to the kinematic principle of planetary gear systems, when the planet carrier 2121 is driven, if the central gear 2111 is completely free, the system will be in a state of motion uncertainty. The output speed of the external gear ring 2131 and the input speed of the planet carrier 2121 cannot maintain a definite transmission ratio, and the operator will lack force feedback, resulting in a vague feel and difficulty in precise control.

[0066] Therefore, in this scheme, the sun gear shaft is not completely locked in manual mode. Instead, a moderate and adjustable frictional damping is applied through the brake clamp 52. This damping force is sufficient to constrain the inertial motion of the sun gear shaft, so that it remains approximately stationary during manual operation. This establishes an approximately fixed reduction ratio between the input of the planetary carrier 2121 and the output of the external gear ring 2131, which is approximately the ratio of the number of teeth of the external gear ring 2131 to the number of teeth of the central gear 2111. This ensures a linear and predictable relationship between the rotation angle of the handwheel 42 and the rotation angle of the optical reflector 11.

[0067] At the same time, this damping force also provides the operator with clear operating feedback, enabling stable and fine-tuning of the optical mirror 11. Under the damping action, the first connecting shaft 2112 may only produce extremely small follow-up motion, but its main motion is effectively suppressed, avoiding the transmission gap and instability introduced by completely free rotation.

[0068] The damping force applied by the brake clamp 52 can be adjusted according to actual needs in actual use. For example, the damping force during clamping can be controlled by adjusting the initial position of the brake clamp 52 or by adjusting the material of the brake clamp 52. The specific methods will not be elaborated here.

[0069] In this way, the solution applies damping to the first connecting shaft 2112 in manual mode instead of absolutely locking it. While ensuring transmission certainty and operating feel, it reduces the stringent requirements on the braking mechanism, eliminates the need for extremely large locking force, and further reduces the impact and wear that may be caused by complete locking, thus achieving the best balance between reliability, operability and performance.

[0070] The mechanism by which this design fundamentally eliminates the impact of mode switching lies in the fact that the clamping and releasing action of the brake plate 52 on the brake disc 51, and the engagement, locking, and disengagement action of the limiting gear ring 58 on the second connecting shaft 2122, are driven synchronously by the single continuous linear stroke of the same telescopic rod 56, through a rigid mechanical structure connecting the connecting plate 55 and the connecting rod 57. This means that the two key actions are absolutely synchronized in time and are kinematically designed to be strictly opposite and complementary.

[0071] Specifically, during the continuous process of the telescopic rod 56 moving from the extended position to the retracted position, i.e., the system switching from electric mode to manual mode, the process of the limit gear ring 58 disengaging to release the handwheel shaft, and the process of the brake clamp 52 starting to contact and clamp the brake disc 51 to brake the motor shaft, there is an overlapping interval on the time axis, and the force is continuously and gradually changing rather than abruptly changing.

[0072] This ensures a smooth and continuous transition of power from the motor shaft to the handwheel shaft, eliminating the non-ideal state of instantaneous complete interruption or simultaneous connection of two paths in the power transmission link. This guarantees that the final output torque driving the optical reflector 11 to rotate will not change abruptly. It is this characteristic that, from a physical principle perspective, eliminates the possibility of angular acceleration impact and optical axis disturbance caused by switching operations on the mirror surface.

[0073] In summary, the solution provided in this embodiment, by employing a planetary gear differential 21 as the core power distribution and synthesis mechanism, and innovatively designing a linkage switching unit 5 driven by a single telescopic rod 56, controlling the brake clamp 52 through a connecting plate 55, drive gear 54, and drive rack 53, and simultaneously controlling the limiting gear ring 58 through a rigid connecting rod 57, transforms the complex dynamic control problem of dual-mode switching into a simple linear drive problem where the mechanical structure itself ensures absolute synchronization of actions and complementary reverse motion. This effectively achieves a seamless, smooth, and shock-free transition of power between electric and manual input.

[0074] Example 2

[0075] Reference Figure 12 This is a second embodiment of the present invention, providing a method for using a two-dimensional adjustment system with electric locking based on the system described in Embodiment 1 above. The method includes the following detailed steps:

[0076] Step 1: System initialization and waiting for instructions. In actual use, when the operator issues a mode switching instruction through the control panel or host computer software, the system controller receives and parses the instruction. According to the instruction requirements, the controller sends a corresponding control signal to the telescopic rod 56 of the drive switching unit 5, commanding its piston rod to begin continuous linear movement from the currently represented mode position, such as the fully extended position corresponding to the electric drive mode, to the target mode position, such as the fully retracted position corresponding to the manual adjustment mode, and vice versa.

[0077] Step 2: During the linear motion of the telescopic rod 56, the connecting plate 55, which is hinged to the end of its piston rod, is directly pushed or pulled. The linear displacement of the connecting plate 55 is converted into the angular displacement of the shaft of the drive gear 54 connected to it, thereby driving the drive gear 54 to rotate. Since the drive gear 54 simultaneously meshes with the drive racks 53 at the bottom of the brake plates 52 on both sides, its rotational motion is synchronously converted into linear motion of the two drive racks 53 in opposite directions.

[0078] The linear motion of the drive rack 53 is further transmitted to the brake plates 52 fixed thereon, forcing the two brake plates 52 to smoothly move closer or further apart along the guide rail on the support frame 1. This process is continuous and controlled, thereby realizing the gradual and smooth application or release of the clamping force on the brake disc 51 fixed on the first connecting shaft 2112 from zero to a preset value, or from a preset value to zero.

[0079] Step 3: Within the same travel and time interval as in Step 2, the connecting rod 57, which is rigidly connected to the telescopic rod 56, also moves in a synchronous linear motion. The limiting tooth ring 58 at the top of the connecting rod 57 then undergoes axial displacement, causing its tooth structure to gradually enter a fully engaged state with the limiting tooth block 59 structure on the outer wall of the second connecting shaft 2122, or gradually disengage from the engaged state. This action is also continuous and gradual, thereby establishing or releasing the mechanical locking state of the second port 212.

[0080] Step 4: Since the actions of the brake clamp 52 described in Step 2 and the actions of the limiting gear ring 58 described in Step 3 both originate from the single drive source of the same telescopic rod 56, and are forcibly synchronized through the two sets of rigid mechanical linkage components, the clamping force generated by the brake clamp 52 on the brake disc 51 and the engagement locking or disengagement release process generated by the limiting gear ring 58 on the second connecting shaft 2122 are completely overlapped in time.

[0081] The change curves of these two forces are predefined by mechanical design to be interconnected and complementary. This temporal overlap and the complementary nature of the force change curves ensure that, during the dynamic process of the entire mode switching, the final power source driving the rotation of the optical reflector 11, whether it is the motor from the first drive input or the handwheel 42 from the second drive input, can continuously and smoothly provide torque to the output end through the planetary gear differential 21 without any interruption or sudden change. Thus, at the functional level, a perfect transition of power between the two sets of drive inputs is achieved without shock or disturbance.

[0082] Furthermore, in step two, the core function of the connecting plate 55 is to convert the linear mechanical motion output by the telescopic rod 56 into the rotational motion of the drive gear 54. In step three, the core function of the connecting rod 57 is to convert the same linear mechanical motion output by the telescopic rod 56 into the axial linear movement of the limiting gear ring 58.

[0083] Since the connecting plate 55 and the connecting rod 57 are physically fixed directly or indirectly to the moving parts of the telescopic rod 56, the two key actions they drive respectively, namely the rotation of the drive gear 54 and the axial movement of the limiting gear ring 58, are mechanically constrained to be executed synchronously within the same continuous stroke of the telescopic rod 56.

[0084] In summary, this invention simplifies the traditionally complex dual-power switching problem, which requires complex coordinated control, into direct control of the telescopic rod 56 through the detailed operating method defined above. At the same time, by utilizing a rigid mechanical linkage mechanism to ensure the absolute synchronous execution of the two key actions of braking and locking, as well as the gradual complementary change of force, it provides an extremely simple, reliable, and efficient means at the operational level. This ensures that no disturbance of any kind is introduced when the optical mirror 11 switches between electric adjustment mode and manual fine-tuning mode, meeting the highest standard of optical system application requirements.

[0085] As can be seen from Embodiments 1 and 2, the technical solution of the present invention uses the telescopic rod 56 as a unified control and execution hub. The single linear movement of the telescopic rod 56 is synchronously converted into the rotation of the drive gear 54 and the axial movement of the limiting gear ring 58 through the connecting plate 55 and the connecting rod 57 rigidly connected to it. The rotation of the drive gear 54 controls the clamping or disengagement of the brake clamp 52 on the brake disc 51, while the axial movement of the limiting gear ring 58 controls its engagement or disengagement with the upper limit gear block 59 of the second connecting shaft 2122. These two actions, which are forced to be synchronized and have opposite directions of movement, completely overlap in time and change continuously and gradually in force, thereby ensuring a smooth and seamless transfer of power between the electric input and manual input of the planetary gear differential 21.

[0086] The significant advantages of this invention are:

[0087] First, by driving a single telescopic rod 56 and synchronously controlling the braking and locking actions through a rigid linkage component, the absolute synchronization and reverse coordination of the actions are forcibly guaranteed from the mechanical structure itself, completely eliminating the interruption or conflict of power transmission caused by the response delay of the dual actuators.

[0088] Second, by utilizing the aforementioned rigid linkage, the process of establishing the clamping force of the brake plate 52 on the brake disc 51 and the process of releasing the engagement lock of the limiting gear ring 58 on the second connecting shaft 2122 are constrained on the same time axis and designed as complementary force change curves, thereby realizing the continuous gradual change of driving torque during the switching process, thus eliminating the sudden torque change and optical axis disturbance during mode switching.

[0089] Third, the complex dual-path power switching control is simplified to the control of the telescopic rod 56, and the state is maintained through pure mechanical linkage. The system structure is simple, eliminating the need for complex synchronous electronic control logic, thus reducing control complexity and failure risk. Fourth, the entire switching process is based on a defined mechanical motion relationship, ensuring reliable state switching, strong anti-interference capability, and high safety as it can maintain its current position through mechanical self-locking in the event of power failure.

[0090] The working principle of this invention is as follows: When the system is in electric drive mode, the telescopic rod 56 of the switching unit 5 is in the extended position. At this time, the connecting plate 55 drives the drive gear 54 to rotate to the position where the brake clamp 52 is completely separated, and the brake disc 51 on the first connecting shaft 2112 is completely released. At the same time, the connecting rod 57 drives the limiting gear ring 58 to move to the position where it is fully engaged with the limiting gear block 59 on the second connecting shaft 2122, thereby locking the manual input shaft. In this state, the drive device 31 of the electric control unit 3 can freely drive the first connecting shaft 2112 to rotate. Since the planetary carrier 2121 is locked, the power of the motor is transmitted to the outer gear ring 2131 through the central gear 2111 and planetary gears, driving the output flange 2132 and the optical reflector 11 connected thereto to perform precise angle positioning.

[0091] When manual fine-tuning is required, the system receives a switching command and controls the telescopic rod 56 to begin continuous movement from the extended position to the retracted position. During this single continuous stroke, two forced synchronous mechanical actions with opposite directions occur:

[0092] On the one hand, the connecting plate 55 pulls the drive gear 54 to rotate in the opposite direction, driving the brake clamps 52 on both sides to gradually and smoothly approach each other along the guide rail, and the clamping force on the brake disc 51 increases continuously from zero, thereby applying an adjustable and gradual damping torque to the first connecting shaft 2112.

[0093] On the other hand, the connecting rod 57, which is rigidly connected to the same telescopic rod 56, synchronously drives the limiting gear ring 58 to move axially, so that the meshing force between it and the upper limit gear block 59 of the second connecting shaft 2122 gradually decreases until it is completely disengaged, thereby smoothly releasing the manual input shaft.

[0094] These two actions overlap in time and complement each other mechanically, ensuring that the drive torque transmitted to the output end via the planetary gear differential 21 does not change abruptly during the switching process. After the switching is completed, the system enters the manual adjustment mode. The operator turns the handwheel 42, and the power is input to the planetary carrier 2121 through the released second connecting shaft 2122, driving the optical reflector 11 to move. At this time, the first connecting shaft 2112 moves with controllable damping.

[0095] When it is necessary to switch back from manual mode to electric mode, the telescopic rod 56 moves from the retracted position to the extended position, driving the brake clamp 52 to gradually release its grip on the brake disc 51. At the same time, the limit gear ring 58 is driven to re-engage and lock the second connecting shaft 2122, and the power smoothly transitions back to the electric drive chain.

[0096] In summary, the present invention, through a switching unit 5 driven by a single telescopic rod 56 and mechanically forced to link the mechanical linkage between the rigid connecting plate 55 and the connecting rod 57, integrates the damping application and release action of the brake clamp 52 on the first port 211 and the locking and release action of the limiting gear ring 58 on the second port 212 into a continuous linear stroke without intermediate states. This achieves seamless, smooth, and shock-free switching of power between electric and manual input chains, fundamentally eliminating optical axis disturbances caused by mode switching.

[0097] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions will not cause the essence of the corresponding technical solutions to deviate from the protection scope of the technical solutions of the embodiments of the present invention.

Claims

1. A two-dimensional adjustment system with electric locking, comprising a support frame (1), wherein an optical reflector (11) is disposed in the support frame (1), characterized in that: The support frame (1) is provided with an adjustment unit (2) for adjusting the position of the optical reflector (11). On one side of the adjustment unit (2) are an electric control unit (3) for providing a first drive input and a manual control unit (4) for providing a second drive input. A switching unit (5) is provided in the support frame (1). The switching unit (5) is used to selectively transmit either the first drive input or the second drive input to the output of the adjustment unit (2) based on an operation command and differential coordination. The adjustment unit (2) includes a planetary gear differential (21), which has a first port (211), a second port (212), and a third port (213). The first port... The first port (211) is connected to the electric control unit (3) to receive the first drive input, the second port (212) is connected to the manual control unit (4) to receive the second drive input, and the third port (213) constitutes the output end of the adjustment unit (2). The first port (211) includes a central gear (2111) and a first connecting shaft (2112). The central gear (2111) serves as the sun gear of the planetary gear differential (21). The first connecting shaft (2112) is coaxially fixedly connected to the central gear (2111) and extends outward. The second port (212) includes a planet carrier (2121) and a second connecting shaft (2122). The planet carrier (2121) is provided with a planetary gear shaft. The second connecting shaft (2122) is coaxially fixedly connected to the planetary carrier (2121) and extends outward to form the input interface of the manual control unit (4). The second connecting shaft (2122) is sleeved on the first connecting shaft (2112). The third port (213) includes an external gear ring (2131) and an output flange (2132). The internal teeth of the external gear ring (2131) mesh with the planetary gears of the planetary gear differential (21). The output flange (2132) is coaxially fixedly connected to the external gear ring (2131) to form the output end of the adjustment unit (2). The electric control unit (3) includes a drive device (31) disposed on one side of the support frame (1). The output end of the drive device (31) The switching unit (5) is connected to the first connecting shaft (2112) for transmission. It includes a brake disc (51) on the first connecting shaft (2112). Brake plates (52) for applying braking damping are provided on both sides of the brake disc (51). A drive rack (53) is provided at the bottom of the brake plate (52). A drive gear (54) meshing with the drive rack (53) is provided inside the support frame (1). A connecting plate (55) is connected to one side of the drive gear (54). A telescopic rod (56) is connected to one end of the connecting plate (55) away from the drive gear (54). A connecting rod (57) is provided on one side of the telescopic rod (56). A limit gear ring (58) is provided at the top of the connecting rod (57).The outer wall of the second connecting shaft (2122) is provided with a limiting tooth block (59) that cooperates with the limiting tooth ring (58). The manual control unit (4) includes a rotating rod (41) disposed on one side of the driving device (31). One end of the rotating rod (41) is provided with a handwheel (42), and the end of the rotating rod (41) away from the handwheel (42) is provided with a transmission gear (43). The transmission gear (43) is connected to the limiting tooth block (59) in a transmission manner.

2. The two-dimensional adjustment system with electric locking according to claim 1, characterized in that: When the telescopic rod (56) is in the extended position, the connecting plate (55) drives the drive gear (54) to rotate, causing the brake clamps (52) on both sides to separate from the brake disc (51). At the same time, the connecting rod (57) drives the limiting gear ring (58) to mesh with the limiting gear block (59).

3. The two-dimensional adjustment system with electric locking according to claim 2, characterized in that: When the telescopic rod (56) is in the retracted position, the connecting plate (55) drives the drive gear (54) to rotate in the opposite direction, so that the brake clamps (52) on both sides clamp the brake disc (51). At the same time, the connecting rod (57) drives the limiting tooth ring (58) to disengage from the limiting tooth block (59).

4. A method of using a two-dimensional adjustment system with electric locking, implemented based on the two-dimensional adjustment system with electric locking as described in any one of claims 1 to 3, characterized in that: Includes the following steps: Step 1: Receive the mode switching command and control the telescopic rod (56) to move between the extended position and the retracted position; Step 2: During the movement of the telescopic rod (56), the connecting plate (55) connected to the telescopic rod (56) pulls the drive gear (54) to rotate, thereby causing the two drive racks (53) meshing with the drive gear (54) to drive the brake plates (52) to move closer or further apart, so as to gradually apply or release the clamping of the brake disc (51). Step 3: During the same process of the telescopic rod (56) moving, the limiting tooth ring (58) is driven to move synchronously through the connecting rod (57) connected to the telescopic rod (56), so that the limiting tooth ring (58) and the limiting tooth block (59) gradually disengage or engage, so as to release or lock the second port (212) synchronously. Step 4: Through the overlap of time and the continuous gradual change of force between the action of the brake clamp (52) and the action of the limiting tooth ring (58) described in Step 2 and Step 3, the power transition between the first drive input and the second drive input is realized.

5. The method of using the two-dimensional adjustment system with electric locking according to claim 4, characterized in that: In step two, the connecting plate (55) converts the linear motion of the telescopic rod (56) into the rotational motion of the drive gear (54); In step three, the connecting rod (57) converts the linear motion of the telescopic rod (56) into the axial movement of the limiting gear ring (58); Both the connecting plate (55) and the connecting rod (57) are driven by the telescopic rod (56), so that the rotation of the driving gear (54) and the axial movement of the limiting gear ring (58) are performed synchronously in a single continuous stroke of the telescopic rod (56).

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