A slow descent device

Abstract

The application relates to the technical field of slow descent devices, and in particular relates to a slow descent device, which comprises a support base, a transmission mechanism arranged on the support base, and a centrifugal braking mechanism, wherein the centrifugal braking mechanism comprises a support piece which is in transmission connection with a power output end of the transmission mechanism, a conversion piece which is arranged on the support piece and is provided with a curved groove, and a counterweight piece which is accommodated in the curved groove; the support piece is configured to rotate under the action of the transmission mechanism; the counterweight piece is configured to move along the curved groove and generate an axial thrust on a movable part of the conversion piece; and the conversion piece is configured to convert the axial thrust into a driving force for driving the conversion piece to move in the radial direction, so that a braking torque is generated between the conversion piece and the support base. The slow descent device of the application utilizes the variable-curvature characteristic of the curved groove to realize adaptive nonlinear adjustment between the braking torque and the rotating speed, thereby realizing the unification of smooth starting and safe braking in the slow descent process of a heavy load, and improving the applicability and safety of the slow descent device.

Description

Technical Field

[0001] This application relates to the field of descent control technology, and more particularly to a descent control device. Background Technology

[0002] Heavy-duty descent devices are widely used in scenarios such as heavy object descent and high-altitude operation protection, and typically need to support loads ranging from tens to hundreds of kilograms or even heavier (such as construction scaffolding and large equipment hoisting). These devices require providing stable and controllable braking force during the descent of the heavy object to prevent accidents caused by excessive speed.

[0003] In existing technologies, centrifugal descent devices are a widely used type. The working process of a centrifugal descent device is as follows: the falling weight drives the rope pulley to rotate, which in turn drives the rotating component connected to the rope pulley to rotate. The centrifugal element on the rotating component moves along an inclined plane at a fixed angle under the action of centrifugal force, converting the radial centrifugal force into an axial clamping force. This clamping force acts directly on the friction pair, generating a braking torque. Therefore, when the descent device starts at low speed, it is prone to jamming due to excessive braking force; when falling at high speed, it is prone to safety hazards due to insufficient braking force. Summary of the Invention

[0004] The purpose of this application is to provide a descent control device that, through adaptive nonlinear adjustment of the braking torque and rotational speed, can achieve a balance between smooth start and safe braking during heavy load descent, thereby improving the applicability and safety of the descent control device.

[0005] A descent device, comprising: Support base; A transmission mechanism is disposed on the support base, and the transmission mechanism includes a rope pulley for winding a rope; Centrifugal braking mechanism, including: The support component is connected to the power output end of the transmission mechanism. A conversion component is disposed on the support component, and the conversion component has a curved groove with varying curvature; The counterweight is housed within the curved groove; The support member is configured to rotate under the action of the transmission mechanism; The counterweight is configured to move along the curved groove under the centrifugal force of the rotating support and generate an axial thrust on the movable part of the conversion component by interacting with the groove wall. The conversion element is configured to convert the axial thrust into a driving force that drives the movable portion of the conversion element to move radially, thereby generating a braking torque between the conversion element and the support base through the driving force.

[0006] In some embodiments, the curvature of the curved groove changes continuously along the extension path of the groove wall.

[0007] In some embodiments, the extension path of the curved groove is elliptical, or the extension path of the curved groove is formed by connecting multiple arcs with different curvatures.

[0008] In some embodiments, the converter includes: A first component is disposed on the support member, and a first sub-curved groove is formed on the first component; The second component is movably mounted on the support member, and the second component has a second sub-curved groove. The first sub-curved groove and the second sub-curved groove together form the curved groove; The counterweight moves along the curved groove under the action of centrifugal force and generates an axial thrust on the second component to drive the second component to move radially.

[0009] In some embodiments, the opposing surfaces of the first component and the second component are respectively provided with: A first inclined plane and a second inclined plane, both of which are radially inclined; When the second component is subjected to axial thrust, the first inclined surface slides relative to the second inclined surface to convert the axial thrust into a radial driving force.

[0010] In some embodiments, the first component and the second component have: An adjustable gap extends along the extension direction of the curved groove, and the adjustable gap is configured to allow the second component to move radially relative to the first component.

[0011] In some embodiments, the descent device further includes: A friction element and a braking surface, wherein one of the friction element and the braking surface is disposed in the movable portion of the conversion element, and the other of the friction element and the braking surface is disposed in the support base; The friction element is configured such that when the movable part of the conversion element moves radially under the action of the driving force, the friction element presses against the braking surface and generates a frictional torque.

[0012] In some embodiments, the transmission mechanism further includes: The sun gear is coaxially connected to the pulley; Planetary gears are rotatably mounted on the support and mesh with the sun gear; A gear ring is disposed on the support base and meshes with the planetary gear.

[0013] In some embodiments, the support base, the transmission mechanism, and the centrifugal braking mechanism are coaxially arranged.

[0014] In some embodiments, the conversion element is provided in at least two sets, and the descent device further includes: A reinforcing member is disposed on the support member, and the reinforcing member is located between the at least two sets of conversion members.

[0015] The technical solution provided in this application can achieve at least the following beneficial effects: The slow-descent device provided in this application embodiment houses a counterweight within a curved groove on a conversion component. The counterweight moves along the groove under the centrifugal force of the rotating support component, generating an axial thrust on the moving part of the conversion component. This axial thrust is converted by the conversion component into a radial driving force that moves the moving part of the conversion component, thereby generating a braking torque between the conversion component and the support base. Thus, through the variable curvature guidance of the curved groove and the synergistic effect of the conversion between axial thrust and radial driving force, adaptive nonlinear adjustment of the braking torque with rotational speed can be achieved.

[0016] Specifically, during the low-speed start-up phase, the counterweight is located in the section of the curved groove with a larger curvature. The normal direction of the groove wall in this section is close to the radial direction, resulting in a smaller axial thrust exerted by the counterweight on the moving part of the conversion component. Simultaneously, the support component rotates at a lower speed, resulting in a smaller centrifugal force. Therefore, the radial driving force is small during the low-speed start-up phase, the braking torque increases gradually, and the load can start smoothly, avoiding jamming. During the high-speed descent phase, the counterweight moves to the section of the curved groove with a smaller curvature under the influence of centrifugal force. The normal direction of the groove wall in this section is closer to the axial direction, increasing the axial thrust. At the same time, the support component rotates at a higher speed, resulting in a larger centrifugal force. Therefore, the radial driving force increases sharply during the high-speed descent phase, and the braking torque increases sharply accordingly, ensuring the safe deceleration of the load.

[0017] Thus, by adaptive nonlinear adjustment between braking torque and rotational speed, it is possible to achieve a balance between smooth start and safe braking during heavy load descent, thereby improving the applicability and safety of the descent device. Attached Figure Description

[0018] Figure 1 A schematic diagram of the external structure of the descent device provided in an exemplary embodiment of this application is shown; Figure 2 A schematic diagram of the internal structure of a descent device provided in an exemplary embodiment of this application is shown; Figure 3 for Figure 2 Enlarged view of part A in the image; Figure 4A schematic diagram of the transmission mechanism provided in an exemplary embodiment of this application is shown; Figure 5 A schematic diagram of the centrifugal braking mechanism provided in an exemplary embodiment of this application is shown; Figure 6 for Figure 5 Enlarged view of part B in the image; Figure 7 A cross-sectional schematic diagram of a descent device provided in an exemplary embodiment of this application is shown.

[0019] Explanation of reference numerals in the attached figures: 01. Rope; 1. Support base; 11. Fixed shaft; 2. Transmission mechanism; 21. Sheave; 22. Sun gear; 23. Planet gears; 24. Gear ring; 3. Centrifugal braking mechanism; 31. Support component; 32. Conversion component; 321. Curved groove; 322. First part Component; 3221, First inclined plane; 323, Second component; 3231, Second inclined plane; 324, Movement clearance; 33, Counterweight; 4. Friction components; 5. Partitions; 6. Guide components; 7. Reinforcing components. Detailed Implementation

[0020] To enable those skilled in the art to better understand the technical solutions of this application, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort should fall within the scope of protection of this application.

[0021] It should be noted that many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0022] In the description of this application, it should be understood that the terms "upper," "lower," "horizontal," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this application. In this application, unless otherwise expressly specified and limited, the first feature being "upper" or "lower" than the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium.

[0023] In this application, unless otherwise expressly specified and limited, the terms "connected," "linked," and "fixed," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral unit; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. However, specifying a direct connection indicates that the two connected entities do not establish a connection relationship through a transitional structure, but are connected solely by a connecting structure to form a whole. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0024] In this application, the use of terms such as "first," "second," etc., is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features.

[0025] Heavy-duty descent devices are widely used in scenarios such as heavy object descent and high-altitude operation protection, and typically need to support loads ranging from tens to hundreds of kilograms or even heavier (such as construction scaffolding and large equipment hoisting). These devices require providing stable and controllable braking force during the descent of the heavy object to prevent accidents caused by excessive speed.

[0026] In existing technologies, centrifugal descent devices are a widely used type. The working process of a centrifugal descent device is as follows: the falling weight drives the rope pulley to rotate, which in turn drives the rotating component connected to the rope pulley to rotate. The centrifugal element on the rotating component moves along an inclined plane at a fixed angle under the action of centrifugal force, converting the radial centrifugal force into an axial clamping force. This clamping force acts directly on the friction pair, generating a braking torque. Therefore, when the descent device starts at low speed, it is prone to jamming due to excessive braking force; when falling at high speed, it is prone to safety hazards due to insufficient braking force.

[0027] To address the technical problems of existing centrifugal descent devices, such as easy jamming during low-speed start-up and insufficient braking force during high-speed descent, referring to... Figures 1 to 3As shown in the figure, this application embodiment provides a descent control device. This descent control device guides the movement of the counterweight 33 through a variable-curvature groove 321, converting centrifugal force into axial thrust. The axial thrust is then converted into radial driving force by a conversion element 32, thereby generating a braking torque between the conversion element 32 and the support base 1 that is non-linearly related to the rotational speed. Ultimately, the braking torque increases gradually in the low-speed region to ensure smooth starting, and increases sharply in the high-speed region to ensure braking safety.

[0028] It should be noted that this descent device achieves adaptive nonlinear adjustment of braking torque with rotational speed through the synergistic effect of variable curvature guidance and the conversion of axial thrust and radial driving force. This descent device can be used for precision descent of light equipment, as well as for the safe lowering of heavy loads (tens to hundreds of kilograms) such as building scaffolds and large equipment components, covering multiple fields such as industry, construction, and rescue.

[0029] Reference Figures 1 to 3 As shown, in some embodiments, the descent device includes a support base 1. The support base 1 forms the mounting base for the descent device. The support base 1 can be fixed to an external bracket, wall, or ground anchor point to provide stable reaction force support during the descent process.

[0030] Reference Figures 1 to 3 As shown, in some examples, the support base 1 can be a hollow cylindrical structure. This hollow structure facilitates the accommodation of other components of the descent device, improving the overall structural compactness of the descent device, while the cylindrical shape is advantageous for installation in confined spaces.

[0031] Reference Figure 1 , Figure 2 and Figure 4 As shown, in some embodiments, the descent device further includes a transmission mechanism 2. The transmission mechanism 2 is disposed on the support base 1. The transmission mechanism 2 includes a pulley 21 for winding the rope 01.

[0032] It should be noted that a rope 01 connected to the weight is wound around the pulley 21. Thus, the pulley 21 can receive the tension generated by the falling weight through the rope 01, thereby converting the linear motion of the weight into the rotational motion of the pulley 21. The rotational speed of the pulley 21 is directly related to the descent speed of the weight; therefore, the descent speed of the weight can be controlled by controlling the rotational speed of the pulley 21.

[0033] It should also be noted that the aforementioned axial direction refers to the direction parallel to the rotation axis of the rope pulley 21, see [link / reference]. Figure 1 As indicated by the middle arrow a. The radial direction mentioned above refers to the direction perpendicular to the rotation axis of the rope pulley 21, see [link / reference]. Figure 1 As indicated by the middle arrow b.

[0034] Reference Figure 2 As shown, in some examples, the surface of the pulley 21 may be provided with anti-slip texture or covered with friction material to prevent the rope 01 from slipping on the pulley 21 and ensure transmission efficiency.

[0035] Reference Figure 2 and Figure 3 As shown, in some embodiments, the transmission mechanism 2 may further include a spacer 5. The spacer 5 is disposed on the support base 1 and located between the two sides of the rope 01 hanging from the pulley 21.

[0036] Thus, the partition 5 can separate the drooping rope 01 from the rotating components (such as the rope pulley 21 and the support 31), preventing the rope 01 from getting tangled on the rotating components when it sways or slackens, ensuring the continuity and safety of the descent process. At the same time, the partition 5 can limit the swing amplitude of the rope 01, preventing the rope 01 from undergoing excessive lateral deviation when it is lowered at high speed, thereby improving the stability of the descent.

[0037] Reference Figure 2 and Figure 3 As shown, in some embodiments, the transmission mechanism 2 may further include at least one guide member 6. The guide member 6 is disposed on the support base 1 and located to the side of the falling path of the rope 01, for guiding the falling direction of the rope 01.

[0038] Thus, the guide member 6 enables the rope 01 to enter the pulley groove at a predetermined angle and position, preventing the rope 01 from wearing or jumping out of the groove due to deviation, thereby improving the smoothness and reliability of the transmission. At the same time, the guide member 6 can reduce the direct friction between the rope 01 and the support base 1, extending the service life of the rope 01.

[0039] It should be noted that the number of guide members 6 can be one, two, or three, and this application does not impose a strict limitation on this. The number of guide members 6 is determined according to the width of the rope 01, the size of the pulley 21, and the installation space of the descent device, to ensure that the rope 01 can be stably guided.

[0040] Reference Figure 2 and Figure 3 As shown, in some examples, the number of guide members 6 can be set to two. The two guide members 6 are located on opposite sides of the descent path of the rope 01, that is, the two guide members 6 are respectively set on both sides of the partition member 5. In this way, the two guide members 6 limit and guide the rope 01 from both sides, forming a double guide rail constraint structure, thereby suppressing the lateral vibration of the rope 01 and keeping the rope 01 always in the center position of the rope pulley 21, further improving the stability of the transmission and the smoothness of the descent.

[0041] Reference Figure 2 and Figure 3As shown, in some examples, the guide 6 can be a rotatable guide roller or a fixed guide block. When the guide 6 is a guide roller, there is rolling friction between the rope 01 and the guide roller, which can further reduce frictional resistance and improve transmission efficiency.

[0042] Reference Figures 4 to 6 As shown, in some embodiments, the descent device further includes a centrifugal braking mechanism 3.

[0043] It should be noted that the centrifugal braking mechanism 3 is used to receive the rotational motion transmitted by the transmission mechanism 2, and based on the centrifugal force generated by the rotational motion, generates a braking torque that can be automatically adjusted with the rotational speed to achieve adaptive descent.

[0044] Reference Figures 4 to 7 As shown, in some embodiments, the support base 1, the transmission mechanism 2, and the centrifugal braking mechanism 3 are arranged coaxially.

[0045] It is understandable that the support base 1, transmission mechanism 2 and centrifugal braking mechanism 3 are arranged coaxially. On the one hand, this can make full use of the space of the support base 1, reduce unnecessary radial dimensions, and thus improve the structural compactness of the descent device. On the other hand, it helps to ensure the concentricity of the movement of each rotating component, thereby improving the transmission smoothness and overall reliability.

[0046] Reference Figures 4 to 7 As shown, in some embodiments, the centrifugal braking mechanism 3 may include a support member 31. The support member 31 is drive-connected to the power output end of the transmission mechanism 2 and is used to receive rotational power. The support member 31 is configured to rotate under the action of the transmission mechanism 2 to provide a high-speed motion environment required to generate centrifugal force to the components located on the support member 31.

[0047] Reference Figures 4 to 7 As shown, in some examples, the support 31 may include a turntable and a fixed shaft 11. The fixed shaft 11 is fixedly connected to the turntable. The turntable is movably connected to the support base 1 via the fixed shaft 11 (e.g., via a bearing). The power output end of the transmission mechanism 2 can be fixedly mounted on the fixed shaft 11 to directly transmit rotational force to the fixed shaft 11, and then to the turntable. In this way, the support 31 rotates smoothly as a whole, which is beneficial to the stable generation of centrifugal force.

[0048] Reference Figure 4 and Figure 5 As shown, in some embodiments, the centrifugal braking mechanism 3 further includes a conversion member 32. The conversion member 32 is disposed on the support member 31 and rotates synchronously with the support member 31. A curved groove 321 is formed on the conversion member 32. The curved groove 321 has a varying curvature.

[0049] It is understandable that the curved groove 321 has a varying curvature, meaning it is configured to have a variable curvature characteristic. Variable curvature refers to the difference in the rate of directional change (i.e., curvature) per unit arc length between different sections of the curved groove 321. Thus, the counterweight 33 generates normal forces of varying magnitudes on the groove wall at different stages of its movement along the curved groove 321; the axial component of this normal force is the axial thrust. Since the normal force changes non-linearly with the position of the counterweight 33, the resulting axial thrust also exhibits non-linear characteristics, providing a basis for subsequent non-linear adjustment of the braking torque.

[0050] It should be noted that the curved groove 321 refers to a groove or through-slot extending along the surface of the conversion element 32 to guide the movement of the counterweight 33. The extension path of the curved groove 321 (i.e., its projection on a plane perpendicular to the axis of rotation, i.e., the trajectory of the counterweight 33) determines the trajectory of the counterweight 33, and thus determines the variation of the axial thrust with the position of the counterweight 33. The extension path of the curved groove 321 has varying curvature to achieve the required nonlinear braking characteristics. For example, the extension path of the curved groove 321 can be a curved path with a continuously varying single curvature (such as an ellipse, parabola, or spline curve), or it can be a curved path smoothly connected by multiple arcs with different curvatures (e.g., multiple tangent circular arcs), as long as the overall curvature of the extension path of the curved groove 321 changes with position.

[0051] It should also be noted that the cross-sectional shape of the curved groove 321 along the depth direction (i.e., the cross-sectional shape along the axis of rotation) can be set independently according to actual needs and matched with the curvature variation characteristics of the curved groove 321.

[0052] In some examples, the cross-section of the curved groove 321 along the depth direction can be an incomplete rectangle, that is, the rectangle is missing one side to form the opening of the curved groove 321. The counterweight 33 is inserted into the curved groove 321 through the opening. In this way, the curved groove 321 is easy to process and provides stable guidance.

[0053] In other embodiments, the cross-section of the curved groove 321 along the depth direction may be an incomplete trapezoid, that is, the trapezoid lacks an upper or lower base to form an opening in the curved groove 321. The width of the trapezoidal opening is greater than the width of the groove bottom, so that the counterweight 33 can be inserted into the curved groove 321 from the opening. In this way, a guide structure with inclined sidewalls is formed, which is beneficial for limiting the movement of the counterweight 33.

[0054] Of course, the cross-sectional shape of the curved groove 321 along the depth direction can also be U-shaped, V-shaped, or other shapes, and this application does not impose strict limitations on this. As long as the extension path of the curved groove 321 has a varying curvature, it is acceptable.

[0055] Reference Figure 4 and Figure 5As shown, in some examples, the curved groove 321 may be formed on the end face of the conversion element 32.

[0056] Reference Figure 4 and Figure 5 As shown, in some embodiments, the centrifugal braking mechanism 3 further includes a counterweight 33. The counterweight 33 is housed within a curved groove 321. The counterweight 33 is configured to move along the curved groove 321 under the centrifugal force generated by the rotation of the support member 31.

[0057] It is understandable that during the movement of the counterweight 33 along the curved groove 321, the counterweight 33 exerts an axial thrust on the moving part of the conversion member 32 through its interaction with the groove wall of the curved groove 321. The magnitude and direction of this axial thrust depend on the instantaneous position of the counterweight 33 within the curved groove 321 and the normal direction of the groove wall at that location.

[0058] Reference Figure 4 and Figure 5 As shown, in some examples, the counterweight 33 can be spherical (such as a steel ball) or cylindrical roller. This reduces sliding friction, facilitates the rolling of the counterweight 33 within the curved groove 321, and improves the transmission sensitivity and service life of the descent device.

[0059] Reference Figure 4 and Figure 5 As shown, in some embodiments, the converter 32 is configured to convert axial thrust into a driving force that drives its movable portion to move radially, thereby generating a braking torque between the converter 32 and the support base 1.

[0060] Understandably, the movable part of the conversion element 32 tends to move under the action of axial thrust. This tendency is guided to move radially by the conversion element 32, thereby transforming the original axial thrust along the axis into a radial driving force along the radial direction.

[0061] Reference Figure 4 and Figure 5 As shown, in some embodiments, the curvature of the curved groove 321 changes continuously along the extension path of the groove wall.

[0062] Understandably, a continuous change in curvature means that the curvature of the curved groove 321 transitions smoothly at any position, without any abrupt changes. For example, the extension path of the curved groove 321 along the groove wall can be an ellipse, a spline curve, or a curve with a monotonically changing radius of curvature (such as a parabola). Thus, the counterweight 33 will not experience impact or sudden speed changes when moving along the curved groove 321, and its movement will be smooth and stable, which helps improve the transmission stability and service life of the descent device.

[0063] It is also understandable that by setting the curvature variation law with the position of the counterweight 33, the axial thrust generated by the counterweight 33 at different motion positions can be precisely controlled. In some examples, in the low-speed section near the center of the counterweight 33, a gentle path with a larger radius of curvature (i.e., smaller curvature) is used to moderate the increase in axial thrust; in the high-speed section far from the center of the counterweight 33, a steep path with a smaller radius of curvature (i.e., larger curvature) is used to cause a sharp increase in axial thrust. For example, the extension path of the curved groove 321 along the groove wall can be an ellipse. In this way, nonlinear adjustment of braking torque with rotational speed can be achieved.

[0064] It should be noted that the specific shape of the curved groove 321 that achieves continuous curvature variation can be various, and this application does not impose strict restrictions on it, as long as the curvature changes continuously along the extension path.

[0065] Reference Figure 4 and Figure 5 As shown, in some embodiments, the extension path of the curved groove 321 is elliptical.

[0066] Understandably, the curvature of the ellipse changes continuously at different positions, and the ratio of the major and minor axes is adjustable, which can provide a smooth transition from gentle to steep. This allows the axial thrust to change continuously and steplessly with the position of the counterweight 33, improving the braking stability and reliability of the descent device.

[0067] It should be noted that the ratio of the major and minor axes of the ellipse can be adjusted according to the required degree of nonlinearity. The larger the ratio, the greater the difference between low-speed braking force and high-speed braking force.

[0068] In some embodiments, the extension path of the curved groove 321 can be elliptical, and the ratio of the major axis to the minor axis of the ellipse can be selected in the range of 1.5:1 to 3:1. For example, the ratio of the major axis to the minor axis of the ellipse can be 1.5:1, 2:1, or 3:1. By adjusting the ratio of the major and minor axes of the ellipse, the gradient of curvature along the groove wall can be changed. Specifically, when the counterweight 33 is close to the center of rotation (low-speed zone), the radius of curvature at its location is larger, and the normal direction of the groove wall is closer to the radial direction, resulting in a smaller and more gradual increase in the axial thrust generated by the counterweight 33; when the counterweight 33 is far from the center of rotation (high-speed zone), the radius of curvature at its location is smaller, and the normal direction of the groove wall is closer to the axial direction, resulting in a significant increase in the axial thrust. Those skilled in the art can determine the appropriate ratio of the major and minor axes and other specific dimensions based on the target load and the required braking characteristic curve (such as the desired start-up smoothness and high-speed braking force) through conventional curve fitting or simulation calculations.

[0069] In other embodiments, the extension path of the curved groove 321 is formed by connecting multiple arcs with different curvatures.

[0070] In this way, by selecting combinations of arcs with different radii, the required variable curvature curve can be flexibly customized, making the descent device suitable for different load ranges or different braking requirements, thus improving the applicability of the device.

[0071] In some examples, the extension path of the curved groove 321 can be formed by connecting two or three arc segments end to end. For example, the middle arc segment has the largest radius, while the arc segments at both ends have smaller radii, and the three arc segments form an overall S-shape, with each adjacent arc segment being tangent at the connection point. The counterweight 33 is guided more gently in the low-speed region (large radius arc segment) and more steeply in the high-speed region (small radius arc segment), achieving nonlinear braking force while ensuring smooth motion, thereby meeting the needs of different load conditions.

[0072] Reference Figure 4 and Figure 5 As shown, in some embodiments, the conversion member 32 may include a first component 322 and a second component 323. The first component 322 is fixedly disposed on the support member 31. A first sub-curved groove is formed on the first component 322. The second component 323 is movably disposed on the support member 31 and can move radially. A second sub-curved groove is formed on the second component 323. The first sub-curved groove and the second sub-curved groove are disposed opposite to each other, together forming a curved groove 321.

[0073] It is understandable that the curved groove 321 is formed by the first sub-curved groove and the second sub-curved groove, creating a split structure. Correspondingly, when the counterweight 33 moves along the curved groove 321 under centrifugal force, it generates an axial thrust on the second component 323 that forms the groove wall, thereby driving the second component 323 to move radially. This approach not only ensures the machining accuracy of the curved groove 321 but also facilitates the radial movement of the movable part of the second component 323.

[0074] Reference Figure 4 and Figure 5 As shown, in some examples, the first component 322 and the support 31 can be integrally formed to improve the motion accuracy of the counterweight 33 and the connection strength between the first component 322 and the support 31.

[0075] Reference Figure 4 and Figure 5 As shown, in some embodiments, a first inclined surface 3221 and a second inclined surface 3231 are respectively formed on the opposing surfaces of the first component 322 and the second component 323. Both the first inclined surface 3221 and the second inclined surface 3231 are radially inclined.

[0076] Understandably, when the second component 323 is subjected to axial thrust, the second inclined plane 3231 slides along the first inclined plane 3221. According to the principle of inclined planes, during the sliding process of the second inclined plane 3231 along the first inclined plane 3221, the axial thrust on the second component 323 is decomposed and converted into a radial driving force that drives the second component 323 to move radially. Thus, through the synergistic effect of the first inclined plane 3221 and the second inclined plane 3231, on the one hand, the direction of the force can be changed, thereby generating a braking torque between the second component 323 and the support base 1; on the other hand, by selecting an appropriate inclined plane angle, force amplification (wedge-shaped force amplification effect) can be achieved, thereby obtaining a larger radial driving force with a smaller centrifugal force, and thus improving the braking efficiency and sensitivity of the descent device.

[0077] It should be noted that the inclination angle between the first inclined plane 3221 and the second inclined plane 3231 (i.e., the angle between the inclined plane and the radial plane) is a key parameter affecting the efficiency of converting axial thrust into radial driving force. Optionally, this inclination angle can be set between 15° and 30°. For example, the inclination angle can be 15°, 20°, or 30°. When the inclination angle is 20°, according to the principle of inclined plane mechanics, the axial thrust can be amplified by approximately 2.92 times and converted into radial driving force. If the inclination angle is too small, it may result in an excessively long radial travel and a non-compact structure; if the inclination angle is too large, the force amplification effect will be weakened. Those skilled in the art can determine a suitable inclination angle through conventional calculations based on the required braking torque response speed, structural space constraints, and the friction coefficient of the friction pair.

[0078] Reference Figure 4 and Figure 5 As shown, in some examples, the tilt angles of the first inclined plane 3221 and the second inclined plane 3231 can be set according to the required force amplification factor. The smaller the tilt angle (the gentler the slope), the greater the force amplification factor, and the greater the radial travel of the second component 323; the larger the tilt angle (the steeper the slope), the smaller the force amplification factor, and the faster the response. The tilt angles of the first inclined plane 3221 and the second inclined plane 3231 can be set according to the actual load and space constraints.

[0079] Reference Figure 4 and Figure 5 As shown, in some embodiments, there is an active gap 324 between the first component 322 and the second component 323 along the extension direction of the curved groove 321.

[0080] Understandably, by setting the movable gap 324, the second component 323 can move freely radially relative to the first component 322, avoiding motion interference caused by machining errors or assembly deviations, and ensuring the sensitivity of braking force response.

[0081] It should be noted that the size of the movable clearance 324 can be set according to the machining accuracy and required sensitivity. In some examples, the size of the movable clearance 324 can range from 0.05mm to 0.5mm.

[0082] Reference Figure 4 and Figure 5 As shown, in some embodiments, the descent control device further includes a friction element 4 and a braking surface. The friction element 4 and the braking surface together form a friction pair that generates braking torque. One of the friction element 4 and the braking surface is disposed in the movable portion of the conversion element 32 (i.e., the second component 323). The other of the friction element 4 and the braking surface is disposed in the support base 1.

[0083] Understandably, when the second component 323 moves under the action of radial driving force, the friction component 4 presses against the braking surface, thereby generating a braking torque that hinders the rotation of the moving part of the conversion component 32, thus realizing real-time, adaptive nonlinear adjustment of the descent speed of the heavy object, ensuring smooth low-speed start and reliable high-speed braking.

[0084] Reference Figure 4 and Figure 5 As shown, in some examples, the friction element 4 can be disposed on the outer periphery of the second component 323, and the braking surface can be fixed to the inner wall of the support base 1.

[0085] Understandably, when the second component 323 moves radially outward, the friction element 4 presses against the inner wall of the support base 1, generating a braking torque. Thus, on the one hand, the braking arm is large, enabling the generation of a large braking torque with a relatively small radial driving force, improving braking efficiency; on the other hand, it helps to improve the structural compactness of the descent control device.

[0086] In some examples, the braking surface can be disposed on the second component 323, and the friction element 4 can be fixed to the support base 1. In this way, the second component 323 only needs to drive the braking surface to move, which helps to simplify the structural design of the second component 323, reduce the moment of inertia of the second component 323, and improve the response speed.

[0087] It should be noted that the friction element 4 can be a friction pad made of wear-resistant materials (such as copper-based powder metallurgy or carbon fiber composite materials), and the braking surface can be a metal surface that matches the friction element 4 or another friction pad to provide a stable and durable coefficient of friction.

[0088] Reference Figure 4 and Figure 7 As shown, in some embodiments, the transmission mechanism 2 may further include a sun gear 22, planet gears 23, and a gear ring 24. The sun gear 22 is coaxially connected to the pulley 21. The planet gears 23 are rotatably mounted on the support member 31 and mesh with the sun gear 22. The gear ring 24 is fixed to the support base 1 and meshes with the planet gears 23.

[0089] Understandably, the sun gear 22, planet gears 23, and ring gear 24 together constitute a planetary gear speed-increasing mechanism. The input speed of the rope pulley 21 is amplified by this planetary gear speed-increasing mechanism, driving the support member 31 to rotate at a higher speed. In this way, it can be ensured that even when the initial speed of the falling object is low, the support member 31 can quickly obtain a high speed, thereby quickly generating sufficient centrifugal force and improving the response speed and low-speed braking effect of the descent device.

[0090] It should be noted that the speed increase ratio of this planetary gear speed-increasing mechanism can be set by adjusting the ratio of the number of teeth between the sun gear 22 and the ring gear 24. In some examples, the speed increase ratio of this planetary gear speed-increasing mechanism can be set between 2:1 and 5:1 to adapt to different load and speed requirements.

[0091] Reference Figure 4 and Figure 5 As shown, in some embodiments, the conversion element 32 is provided in at least two sets and is arranged symmetrically along the circumference of the support element 31.

[0092] It is understandable that by setting multiple sets of conversion elements 32 arranged symmetrically along the circumference of the support 31, on the one hand, a greater overall braking force can be provided; on the other hand, it is beneficial to balance the centrifugal force when the support 31 rotates, thereby improving the smoothness of the operation of the descent device.

[0093] It should be noted that the number of conversion components 32 can be set to two, three, or four sets, etc., and this application does not impose a strict limitation on this. Each set of conversion components 32 includes an independent first component 322, a second component 323, and a curved groove 321. Each set of conversion components 32 corresponds to one curved groove 321.

[0094] Reference Figure 4 and Figure 5 As shown, in some embodiments, the descent device further includes a reinforcing member 7. The reinforcing member 7 is disposed on the support member 31 and located between at least two sets of conversion members 32.

[0095] Understandably, the reinforcing member 7 can enhance the rigidity of the support member 31 in the stress area of ​​the multiple sets of conversion members 32, prevent the support member 31 from deforming under long-term high load, and thus ensure the long-term stability of transmission accuracy and braking performance.

[0096] It should be noted that the reinforcing member 7 can be a reinforcing rib, a spoke plate, or a ring-shaped connector, etc., and this application does not impose strict limitations on it.

[0097] The descent control device provided in this application operates as follows: First, the support base 1 of the descent device is fixed to an external anchor point. One end of the rope 01 is connected to the weight, and the other end of the rope 01 is wrapped around the pulley 21. When the weight falls under gravity, the rope 01 pulls the pulley 21 to rotate. The pulley 21 drives the sun gear 22, which is coaxially connected to it, to rotate. The sun gear 22 drives the planet gears 23 to rotate. Since the gear ring 24 is fixed to the support base 1 and meshes with the planet gears 23, the planet gears 23 revolve around the gear ring 24 while rotating, thereby driving the support member 31 to revolve around the sun gear 22, so that the support member 31 obtains a rotational speed higher than that of the pulley 21. The support member 31 drives the conversion member 32 (first component 322 and second component 323) fixed thereon and the counterweight 33 housed in the curved groove 321 to rotate synchronously at high speed.

[0098] The centrifugal force generated by the rotation drives each counterweight 33 to move outward along the curved groove 321. Since the curved groove 321 is designed with variable curvature (e.g., elliptical or multiple arcs with different curvatures), the counterweights 33 exert varying axial thrusts on the movable part (second component 323) of the conversion component 32 at different positions. This axial thrust is converted into a radial driving force through the engagement between the first inclined surface 3221 of the first component 322 and the second inclined surface 3231 on the second component 323, propelling the second component 323 to move radially outward.

[0099] The radial movement of the second component 323 causes the friction element 4 (or braking surface) on it to press against the corresponding braking surface (or friction element 4) on the support base 1, generating a frictional torque. This frictional torque is transmitted in the reverse direction through the transmission mechanism 2 (rope wheel 21, sun gear 22, planet gear 23, gear ring 24, support component 31), and finally acts on the rope wheel 21 to balance part of the weight of the object, so that the object descends slowly and uniformly at a basically constant speed.

[0100] Throughout the process, if the descent speed of the load increases, the rotational speed of the support component 31 increases, the centrifugal force increases, the counterweight 33 moves to a section of the curved groove 321 with a smaller curvature, the axial thrust increases, and the radial driving force after the inclined plane conversion increases significantly nonlinearly. The clamping force of the friction component 4 increases sharply, and the braking torque rises rapidly, thus effectively suppressing excessive speed increase. Conversely, if the descent speed of the load decreases, the braking torque decreases accordingly. In this way, the device achieves adaptive, nonlinear feedback control of the descent speed, ensuring that the load is not stuck during low-speed start-up and is safely braked during high-speed descent.

[0101] The above detailed embodiments further illustrate the purpose, technical solution, and beneficial effects of the embodiments of this application. It should be understood that the above are merely specific embodiments of the embodiments of this application and are not intended to limit the scope of protection of the embodiments of this application. Any modifications, equivalent substitutions, improvements, etc., made based on the technical solutions of the embodiments of this application should be included within the scope of protection of the embodiments of this application.

Claims

1. A descent device, characterized in that, include: Support base (1); The transmission mechanism (2) is disposed on the support base (1), and the transmission mechanism (2) includes a rope wheel (21) for winding the rope (01). Centrifugal braking mechanism (3) includes: The support member (31) is connected to the power output end of the transmission mechanism (2); A conversion component (32) is disposed on the support component (31), and a curved groove (321) is provided on the conversion component (32), the curved groove (321) having a varying curvature; The counterweight (33) is housed within the curved groove (321); The support member (31) is configured to be able to rotate under the action of the transmission mechanism (2); The counterweight (33) is configured to move along the curved groove (321) under the centrifugal force of the rotation of the support (31), and generate an axial thrust on the movable part of the conversion member (32) by interacting with the groove wall of the curved groove (321); The conversion element (32) is configured to convert the axial thrust into a driving force that drives the movable part of the conversion element (32) to move radially, thereby generating a braking torque between the conversion element (32) and the support base (1) through the driving force.

2. The descent device according to claim 1, characterized in that, The curvature of the curved groove (321) changes continuously along the extension path of the groove wall.

3. The descent device according to claim 1, characterized in that, The extension path of the curved groove (321) is elliptical, or the extension path of the curved groove (321) is formed by connecting multiple arcs with different curvatures.

4. The descent device according to claim 1, characterized in that, The conversion element (32) includes: The first component (322) is disposed on the support member (31), and the first component (322) has a first sub-curved groove. The second component (323) is movably mounted on the support member (31), and the second component (323) has a second sub-curved groove. The first sub-curved groove and the second sub-curved groove are arranged opposite to each other and together form the curved groove (321). The counterweight (33) moves along the curved groove (321) under the action of centrifugal force and generates an axial thrust on the second component (323) to drive the second component (323) to move radially.

5. The descent device according to claim 4, characterized in that, The opposing surfaces of the first component (322) and the second component (323) are respectively provided with: The first inclined plane (3221) and the second inclined plane (3231) are both radially inclined. When the second component (323) is subjected to axial thrust, the first inclined surface (3221) slides relative to the second inclined surface (3231) to convert the axial thrust into a radial driving force.

6. The descent device according to claim 4, characterized in that, The first component (322) and the second component (323) have the following characteristics: An active gap (324) extends along the extension direction of the curved groove (321) and is configured to allow the second component (323) to move radially relative to the first component (322).

7. The descent device according to claim 1, characterized in that, The descent control device also includes: Friction element (4) and braking surface, one of the friction element (4) and the braking surface is disposed in the movable part of the conversion element (32), and the other of the friction element (4) and the braking surface is disposed in the support base (1). The friction element (4) is configured such that when the movable part of the conversion element (32) moves radially under the action of the driving force, the friction element (4) presses against the braking surface and generates a friction torque.

8. The descent device according to claim 1, characterized in that, The transmission mechanism (2) further includes: The sun gear (22) is coaxially connected to the rope pulley (21); Planetary gears (23) are rotatably mounted on the support (31) and mesh with the sun gear (22); A gear ring (24) is disposed on the support base (1) and meshes with the planetary gear (23).

9. The descent device according to claim 1, characterized in that, The support base (1), the transmission mechanism (2) and the centrifugal braking mechanism (3) are coaxially arranged.

10. The descent device according to claim 1, characterized in that, The conversion element (32) is provided in at least two sets, and the descent device further includes: A reinforcing member (7) is disposed on the support member (31), and the reinforcing member (7) is located between the at least two sets of conversion members (32).

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