Escapement buffering mechanism of planetary gear train

Abstract

The invention discloses a planetary gear train escapement buffer mechanism, which relates to the technical field of escapement buffer components of precision machinery, and comprises a driving shaft system, a transmission component, a gear ring component and a bolt component, the integrated structural design that the planetary gear train is matched with the cam, the movable pin and the energy storage rebounding assembly is adopted, the conventional mode that a driving shaft is directly locked traditionally is abandoned, power distribution and stable transmission are achieved through the planetary gear train, the impact absorption and buffering energy storage effects are greatly improved in cooperation with an elastic energy storage and rebounding structure of the gear ring assembly, and the service life of the gear ring assembly is prolonged. Rigid impact in the transmission process is effectively relieved, and the service life of core components is prolonged.

Description

Technical Field

[0001] This invention relates to the field of escapement buffer components in precision machinery, and more particularly to a planetary gear escapement buffer mechanism. Background Technology

[0002] As a core component of precision machinery, the escapement mechanism's application prospects are continuously expanding with material innovation, cross-disciplinary technology integration, and emerging market demands, radiating from traditional timing applications to high-end manufacturing, automated industries, and intelligent robots. Conventional escapements mostly lock the drive shaft directly, resulting in limited counter-current energy and insufficient precision in operating frequency control. Furthermore, it is difficult to increase the operating frequency through simple structural superposition, thus limiting their application scenarios.

[0003] Therefore, in response to the above phenomenon, a planetary gear escapement buffer mechanism is proposed to meet the needs of practical use. Summary of the Invention

[0004] This invention provides a planetary gear train escapement buffer mechanism, which solves the technical problems of limited counter-attack energy and insufficient operating frequency control accuracy.

[0005] To solve the above-mentioned technical problems, the present invention provides a planetary gear escapement buffer mechanism, comprising a drive shaft system, a transmission assembly, a gear ring assembly, and a pin assembly; the drive shaft system includes a drive shaft body, a sun gear, and a cam; the sun gear is fixed in the middle of the drive shaft body, and the cam is fixed at the end of the drive shaft body; the transmission assembly includes a planet carrier, planet gears, and a fixed pin; the planet carrier is rotatably connected to the drive shaft body, and the planet carrier is fixedly constrained to an external frame; the planet gears are sleeved on the fixed pin, and the fixed pin is disposed on the planet carrier, with the planet gears meshing with the sun gear; the gear ring assembly includes an external gear ring and a springback unit; the external gear ring is sleeved on the outside of the transmission assembly, and the external gear ring has a clearance fit with the planet carrier and can rotate freely. The outer gear ring has an internal gear structure that meshes with the planetary gears on its inner side. The outer gear ring has a follow-rotation groove and a limiting groove. The springback unit is located at the end of the follow-rotation groove. The springback unit includes a springback pin, a springback push plate, a force-accumulating push plate, and a force-accumulating spring. The lower end of the force-accumulating push plate is located in and adapted to the limiting groove. One side of the force-accumulating push plate is connected to the beginning of the force-accumulating spring, one side of the springback push plate is connected to the springback pin, and the other side of the springback push plate is connected to the end of the force-accumulating spring. The pin assembly includes a ring frame and a movable pin. The ring frame is fixedly connected to the planetary carrier, and the movable pin is movably mounted on the ring frame. When the cam rotates, it can periodically push one end of the movable pin into the follow-rotation groove inside the outer gear ring.

[0006] Preferably, the end of the rotating slot is provided with a spring storage groove for placing the energy storage spring. The spring storage groove is annular, and a mounting post is formed inside the annular spring storage groove. The side of the mounting post is provided with a stepped groove that matches the rebound push plate.

[0007] Preferably, the cam, movable pin, and springback unit can all be stacked and arranged individually along the axial direction of the drive shaft.

[0008] Preferably, multiple rotating slots are evenly arranged along the circumferential direction of the outer gear ring.

[0009] Preferably, the side of the ring frame is provided with a mounting hole, the movable pin is disposed in the mounting hole of the ring frame, the movable pin can slide radially along the mounting hole, the end of the movable pin facing the cam is provided with a smooth rounded corner, and the end of the movable pin facing the rotating groove is a flat engaging end face.

[0010] Preferably, the sun gear is fixedly connected to the drive shaft, and the cam is fixedly connected to the drive shaft.

[0011] Preferably, the energy storage spring is any one of a cylindrical helical compression spring or a wave spring.

[0012] Compared with related technologies, the planetary gear escapement buffer mechanism provided by the present invention has the following beneficial effects:

[0013] This invention adopts an integrated structural design of planetary gear train, cam, movable pin and energy storage and rebound assembly, abandoning the conventional mode of directly locking the drive shaft. It achieves power splitting and smooth transmission through planetary gear train. Combined with the elastic energy storage and rebound structure of the gear ring assembly, it greatly improves the impact absorption and buffer energy storage effect, effectively alleviates rigid impact during transmission and extends the service life of core components.

[0014] This embodiment relies on a planetary transmission layout with a fixed planetary carrier, resulting in a compact and stable overall structure with minimal radial wobble, uniform meshing transmission clearance, and precise and smooth escapement action. It is well-suited to the high-precision transmission and escapement requirements of high-end precision machinery. Through the periodic engagement and disengagement of the movable pin and the follower slot, a stable periodic escapement action is achieved, with clear action logic and high operational reliability.

[0015] This invention allows for the stacking of functional components along the drive shaft axis. For example, by combining a design with a 45° offset arrangement of movable pins, the escapement operating frequency can be doubled without altering the core transmission structure. The frequency control is flexible, and the number of stacked groups can be freely adjusted according to different working conditions. It has strong versatility and expandability, overcoming the drawbacks of fixed frequency and limited application scenarios of traditional escapement mechanisms. Attached Figure Description

[0016] Figure 1This is a schematic diagram of the overall structure of the present invention. Figure 1 ;

[0017] Figure 2 This is a schematic diagram of the overall structure of the present invention. Figure 2 ;

[0018] Figure 3 This is a schematic diagram of the planetary gear train structure of the present invention;

[0019] Figure 4 This is a schematic diagram of the gear ring assembly structure of the present invention;

[0020] Figure 5 This is a schematic diagram of the overall structure of Embodiment 2 of the present invention.

[0021] The diagram is labeled as follows: 1. Drive shaft system; 11. Drive shaft body; 12. Sun gear; 13. Cam; 2. Transmission assembly; 21. Planet carrier; 22. Planet gears; 23. Fixed pin; 3. Gear ring assembly; 31. External gear ring; 311. Follower slot; 312. Limiting slot; 313. Spring storage slot; 314. Mounting column; 32. Spring-return pin; 33. Spring-return push plate; 34. Force-accumulating push plate; 35. Force-accumulating spring; 4. Pin assembly; 41. Ring frame; 42. Movable pin. Detailed Implementation

[0022] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0023] Example 1

[0024] like Figures 1 to 4 As shown, a planetary gear escapement buffer mechanism is proposed, including a drive shaft 1, a transmission assembly 2, a gear ring assembly 3, and a pin assembly 4. The drive shaft 1 serves as the power input component of the overall mechanism, the transmission assembly 2 undertakes the functions of power diversion and transmission, the gear ring assembly 3 cooperates to realize energy storage, springback and escapement, and the pin assembly 4 completes periodic engagement and disengagement actions under the drive of the cam 13. The four components cooperate with each other to achieve a stable escapement buffering effect.

[0025] The drive shaft system 1 includes a drive shaft 11, a sun gear 12, and a cam 13. The drive shaft 11 is an integral power input shaft, with both ends mounted on an external frame via bearings for stable support. The sun gear 12 is fixed in the middle of the drive shaft 11, specifically by a key, and rotates synchronously and coaxially with the drive shaft 11 without relative rotation. The cam 13 is fixed at the end of the drive shaft 11 and is coaxially fixed with the drive shaft 11 by a set screw or a key, maintaining synchronous rotation. The outer contour of the cam 13 adopts a smooth, gradually changing curved surface to match the movement trajectory of the periodically pushing movable pin 42, avoiding impact and jamming during pushing and ensuring stable and smooth pushing action.

[0026] Transmission assembly 2 includes a planetary carrier 21, planetary gears 22, and a fixed pin 23. The planetary carrier 21 is a fixed constraint structure, integrally connected to an external fixed frame by bolts, and does not rotate with the drive shaft 11 or other components. The planetary carrier 21 and the drive shaft 11 are rotatably connected by a deep groove ball bearing, achieving stable support and free rotation of the drive shaft 11 while preventing radial sway of the drive shaft 11. The planetary gears 22 are rotatably sleeved on the fixed pin 23, and the fixed pin 23 is fixedly assembled on the planetary carrier 21. The planetary gear 22 and the fixed pin 23 are rotated by needle roller bearings. The outer ring of the needle roller bearing is interference-fitted with the inner wall of the planetary gear 22, and the inner ring is transition-fitted with the fixed pin 23, which effectively reduces rotational friction. The planetary gear 22 meshes with the sun gear 12. The rotation of the sun gear 12 drives the planetary gear 22 to rotate around the fixed pin 23. At the same time, the planetary gear 22 precisely meshes with the inner teeth of the outer gear ring 31 to form a planetary transmission structure, which smoothly transmits the power of the drive shaft 11 to the gear ring assembly 3, taking into account both deceleration and transmission functions.

[0027] The gear ring assembly 3 includes an outer gear ring 31 and a springback unit; the outer gear ring 31 is sleeved on the outside of the transmission assembly 2 and is a ring gear ring structure. It can rotate freely with the planet carrier 21 through a clearance fit, without rigid locking connection, and can rotate circumferentially with the transmission of the planet gear 22.

[0028] The inner side of the outer gear ring 31 is provided with an internal gear structure that meshes with the planetary gear 22. The module of the internal gear is perfectly matched with that of the planetary gear 22, and the meshing clearance is uniform, ensuring smooth transmission without jamming. The outer gear ring 31 is provided with a follow-up groove 311 and a limiting groove 312 along the circumferential direction. The follow-up groove 311 is provided radially inward along the outer gear ring 31, and the limiting groove 312 is located in the area below the follow-up groove 311, and is interconnected with the follow-up groove 311 and arranged vertically.

[0029] The end of the rotating slot 311 is provided with a spring storage slot 313 for placing the energy storage spring 35. The spring storage slot 313 is annular. An integral mounting post 314 is formed inside the annular part of the spring storage slot 313. The side of the mounting post 314 is provided with a stepped groove that matches the rebound push plate 33. The stepped groove limits the swing stroke of the rebound push plate 33 and ensures that the rebound push plate 33 is accurately positioned and swings without deviation.

[0030] The spring-loaded unit is located in the spring storage groove 313 area at the end of the follow-through groove 311. The spring-loaded unit includes a spring-loaded pin 32, a spring-loaded push plate 33, a force-accumulating push plate 34, and a force-accumulating spring 35, corresponding to the end of the follow-through groove 311 near the outer side of the outer gear ring 31. The head end of the follow-through groove 311 faces the inner side of the gear ring and is adapted to the insertion path of the movable pin 42. Multiple follow-through grooves 311 can be evenly distributed along the circumferential direction on the outer gear ring 31. Each follow-through groove 311 is equipped with a spring-loaded unit at its end, which is adapted to multiple frequency escapement actions.

[0031] The lower end of the power-storing push plate 34 is embedded in and adapted to the limiting slot 312. It can only slide in the circumferential direction along the limiting slot 312 and cannot be disengaged radially. One side of the power-storing push plate 34 is fixedly connected to the first end of the power-storing spring 35. The power-storing spring 35 is a cylindrical helical compression spring, which is elastic, stable and has a long service life. A wave spring can also be selected according to the installation space. The end of the power-storing spring 35 away from the power-storing push plate 34 is sleeved on the outside of the mounting post 314 and stored in the spring storage groove 313.

[0032] One side of the spring-loaded push plate 33 is rotatably connected to the spring-loaded pin 32, which is fixed to the inner wall of the rotating slot 311. It adopts a pin structure with elastic reset function, or a torsion spring pin can be used to achieve elastic reset. One end of the spring-loaded push plate 33 near the mounting post 314 is inserted into the stepped groove and can swing back and forth at a small angle around the spring-loaded pin 32. The other side of the spring-loaded push plate 33 is fixedly connected to the end of the energy storage spring 35. Through the circumferential sliding of the energy storage push plate 34, the energy storage spring 35 is compressed and released to complete the escapement unlocking action.

[0033] The pin assembly 4 includes an annular frame 41 and a movable pin 42. The annular frame 41 is an annular support structure that can be fixedly connected to the planetary carrier 21 via a fixed pin 23, remaining stationary with the planetary carrier 21. It is fitted as a whole onto the outside of the drive shaft 11, in the area between the cam 13 and the external gear ring 31. The movable pin 42 is movably disposed in the radial mounting hole of the annular frame 41, with a clearance fit to the mounting hole, allowing for radial extension and retraction along the mounting hole, with smooth and unobstructed sliding. One end of the movable pin 42 faces the outer contour of the cam 13, and this end is... It has smooth rounded corners to reduce frictional loss with the contour of cam 13. The other end is directly facing the rotating groove 311 on the inner side of the external gear ring 31. This end is a flat engagement end face to ensure stable engagement and prevent slippage. When cam 13 rotates, it relies on the contour curved surface to periodically push the movable pin 42, pushing the end of the movable pin 42 facing the gear ring into the rotating groove 311 to achieve engagement and locking. After cam 13 rotates past the pushing section, the movable pin 42 can retract into the mounting hole under the pushing force of the spring-loaded push plate 33, completing the disengagement and reset, waiting for the next cycle.

[0034] During operation, the drive shaft 11 drives the sun gear 12 and cam 13 to rotate. The cam 13 pushes the movable pin 42 into the follower slot 311. At this time, the external gear ring 31 rotates under the drive of the planet gear 22. The movable pin 42 moves together with the follower slot 311. When it moves to the position of the energy storage push plate 34 of the spring-loaded unit, the movable pin 42 presses the energy storage push plate 34, causing the energy storage push plate 34 to move in the circumferential direction and compress the energy storage spring 35 to store energy. When the energy storage push plate 34 moves to the position of disengaging from the spring-loaded push plate 33, the energy storage spring 35 releases energy and pushes the spring-loaded push plate 33 to rotate around the spring-loaded pin 32. The spring-loaded push plate 33 pushes the movable pin 42 out of the follower slot 311. After the movable pin 42 is out, the elastic force of the spring-loaded pin 32 causes the spring-loaded push plate 33 to reset, thereby driving the entire spring-loaded unit to reset and wait for the next cycle.

[0035] Example 2

[0036] like Figure 5 As shown, this embodiment is an axial superposition frequency enhancement scheme based on embodiment one. On the basis of the original single set of components, another set of functional components is superimposed along the axial direction of the drive shaft 11. The superimposed components also include cam 13, movable pin 42 and spring unit. The two sets of components are arranged parallel to each other along the axial direction of the drive shaft 11, and the upper and lower sets of movable pins 42 are set to be deflected by 45° relative to each other. The corresponding rotation groove 311 on the external gear ring 31 is also doubled and evenly arranged along the circumferential direction.

[0037] In this embodiment, when the drive shaft 11 rotates, the upper and lower sets of cams 13 rotate synchronously, alternately pushing the corresponding movable pins 42 that are deflected by 45°. The two sets of movable pins 42 are alternately engaged in the follow-rotation slots 311, and cooperate with the corresponding spring-back unit to complete the escapement action. Compared with the working frequency of a single set of components in Embodiment 1, the overall escapement frequency of this embodiment is directly doubled, and there is no need to modify the core transmission structure of the transmission component 2 and the gear ring component 3. The frequency can be increased simply by axial superposition and angular deflection. The number of superposition sets and the deflection angle can be flexibly adjusted according to the actual working conditions, further expanding the frequency control range and applicable scenarios of the mechanism, and adapting to the higher frequency precision escapement buffer requirements.

Claims

1. A planetary gear train escapement buffer mechanism, characterized in that: The system includes a drive shaft system, a transmission assembly, a gear ring assembly, and a pin assembly. The drive shaft system includes a drive shaft body, a sun gear, and a cam. The sun gear is fixed in the middle of the drive shaft body, and the cam is fixed at the end of the drive shaft body. The transmission assembly includes a planet carrier, planet gears, and a fixed pin. The planet carrier is rotatably connected to the drive shaft body and is fixedly constrained to an external frame. The planet gears are sleeved on the fixed pin, which is mounted on the planet carrier, and the planet gears mesh with the sun gear. The gear ring assembly includes an external gear ring and a springback unit. The external gear ring is sleeved on the outside of the transmission assembly, and it has a clearance fit with the planet carrier and can rotate freely. The inner side of the external gear ring is provided with a springback unit for contacting the planet gears. The gear ring has an internal gear structure with meshing gears. The external gear ring has a follow-rotation groove and a limiting groove. The springback unit is located at the end of the follow-rotation groove. The springback unit includes a springback pin, a springback push plate, a force-accumulating push plate, and a force-accumulating spring. The lower end of the force-accumulating push plate is located in and adapted to the limiting groove. One side of the force-accumulating push plate is connected to the first end of the force-accumulating spring, one side of the springback push plate is connected to the springback pin, and the other side of the springback push plate is connected to the end of the force-accumulating spring. The pin assembly includes a ring frame and a movable pin. The ring frame is fixedly connected to a planetary carrier, and the movable pin is movably mounted on the ring frame. When the cam rotates, it can periodically push one end of the movable pin into the follow-rotation groove inside the external gear ring.

2. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The end of the rotating slot is provided with a spring storage groove for placing the energy storage spring. The spring storage groove is annular in shape, and a mounting post is formed inside the annular spring storage groove. The side of the mounting post is provided with a stepped groove that matches the rebound push plate.

3. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The cam, movable pin, and springback unit can all be stacked and arranged individually along the axis of the drive shaft.

4. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The rotating slots are evenly arranged in multiple places along the circumference of the outer gear ring.

5. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The ring frame has mounting holes on its side, and the movable pin is set in the mounting holes of the ring frame. The movable pin can slide radially along the mounting holes. The end of the movable pin facing the cam has a smooth rounded corner, and the end of the movable pin facing the rotating groove has a flat engaging end face.

6. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The sun gear is fixedly connected to the drive shaft, and the cam is fixedly connected to the drive shaft.

7. The planetary gear train escapement buffer mechanism according to claim 1, characterized in that, The energy storage spring can be either a cylindrical helical compression spring or a wave spring.

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