Coffee grinder clutch variable speed mechanism

Abstract

The present invention relates to the technical field of coffee machines, and in particular to a clutch speed-changing mechanism for a coffee bean grinder, which includes a driving motor, and also includes a speed-reducing component and a gear-shifting component. The speed-reducing component includes an internal gear ring, a planet carrier, a sun gear, and three evenly distributed planet gears. A first outer ridge is connected to the outside of the planet carrier. The gear-shifting component includes an inner ring, an outer ring, a support housing, and a rotating ring. An annular groove is provided on the outside of the inner ring, and an inner ridge is connected to its inner side. An inner ring is provided at the top of the inner side of the support housing, and a second outer ridge is connected to the outside of the inner ring. A common induction motor or a DC brushless motor can be used as the driving motor, which is small in size. By driving the inner ridge to move up and down, the inner ridge can be respectively in abutting cooperation with the first outer ridge and the second outer ridge, so as to realize a large range of speed regulation, and the torque can be synchronously adjusted during speed regulation, thus meeting the product requirements for the interchange of conical knives and flat knives.

Description

Technical Field

[0001] The present invention relates to the technical field of coffee machines, and in particular to a clutch variable speed mechanism for a coffee grinder. Background Art

[0002] Freshly ground coffee has been favored by more and more consumers because it brings a healthy lifestyle and a delicious taste of the drink. Whether it is Italian coffee extracted by high temperature and high pressure, cold brew coffee at low temperature, or hand-brewed coffee, its quality depends to a large extent on the grinding quality of the coffee grinder. However, different types of coffee beans have different requirements for the technical parameters of the grinder, including the type of cutter head, the distance between cutter heads, the motor speed, etc. Therefore, multi-functional and parameter-adjustable grinders have received extensive attention and are loved by consumers.

[0003] However, at present, there are few technological breakthroughs in aspects such as the interchange of different types of cutter heads and speed adjustment. The main technical difficulty after the interchange of cutter heads is to achieve a large range of speed adjustment. For example, the switching between 500 rpm (suitable for conical cutters) and 1500 rpm (suitable for flat cutters), and the problem of torque matching required for the interchange of flat cutters and conical cutters cannot be solved. For example, under the same cutter head size, conical cutters require a larger rotational torque, but a higher starting torque cannot be switched simultaneously after switching to a low speed. Using a high-power DC permanent magnet synchronous motor and vector control (FOC) technology can achieve this speed adjustment function, but this technical solution has problems such as bulky products, high prices, and complex control circuits. Especially when consumers prefer large-sized cutter heads, the products developed based on this technical direction have low cost performance, have many deficiencies, and cannot be commercially applied on a large scale. Summary of the Invention

[0004] In order to overcome the deficiencies of the prior art, the purpose of the present invention is to provide a clutch variable speed mechanism for a coffee grinder that can use a common induction motor or a DC brushless motor as the drive motor, is small in size, and can conveniently achieve a large range of speed adjustment, and can synchronously adjust the torque during speed regulation, thereby meeting the product requirements for the interchange of conical cutters and flat cutters.

[0005] The technical solution adopted by the present invention is as follows:

[0006] A coffee grinder clutch speed change mechanism includes a driving motor, and also includes a reduction component and a shifting component. The reduction component includes an internal gear ring, a planet carrier, a sun gear, and three evenly distributed planet gears. The output end of the driving motor is connected to the sun gear. The planet gears are rotatably installed on the planet carrier and are respectively meshed with the sun gear and the internal gear ring. The top of the planet carrier is connected with an output shaft, and the outer side thereof is connected with a first outer ridge. The shifting component includes an inner ring, an outer ring, a support housing, and a rotating ring. The rotating ring is rotatably connected to the outer side of the support housing, and an annular wave groove is provided on the inner side thereof. A vertical groove is provided on the side surface of the support housing. A pin is connected to the inner side of the outer ring, and a slider is connected to the outer side thereof. The slider passes through the vertical groove and is slidably connected to the annular wave groove and is slidably connected to the vertical groove. An annular groove is provided on the outer side of the inner ring, and an inner ridge is connected to the inner side thereof. The internal gear ring is fixed to the inner side of the inner ring and is arranged below the inner ridge. The pin is slidably connected to the annular groove. An inner ring is provided at the inner top of the support housing, and a second outer ridge is connected to the outer side of the inner ring. The first outer ridge and the second outer ridge are respectively in movable abutment with the inner ridge.

[0007] Preferably, it further includes a mounting seat. The support housing is fixedly connected to the upper side of the mounting seat, the driving motor is fixed to the lower side of the mounting seat, and the planet carrier is rotatably connected to the upper side of the mounting seat.

[0008] Preferably, a first travel switch and a second travel switch are installed on the upper side of the mounting seat. The second travel switch is arranged above the first travel switch. A low-position convex platform and a high-position convex platform are fixedly connected to the outer side of the rotating ring. A plurality of low-position convex platforms are evenly arranged, and each low-position convex platform corresponds to a wave valley of the annular wave groove. A plurality of high-position convex platforms are evenly arranged, and each high-position convex platform corresponds to a wave peak of the annular wave groove. The low-position convex platform is in movable abutment with the first travel switch, and the high-position convex platforms are respectively in movable abutment with the first travel switch and the second travel switch.

[0009] Preferably, an external gear ring is fixedly connected to the outer side of the rotating ring, and the external gear ring is meshed with a toothed transmission member. The toothed transmission member is installed on the upper side of the mounting seat.

[0010] Preferably, the toothed transmission member is a sector gear. A U-shaped frame with an opening facing downward is fixedly connected to the upper side of the mounting seat. A rotating shaft is connected to the top of the U-shaped frame. The middle part of the sector gear is rotatably connected to the rotating shaft, and a lever is connected to the end thereof far from the external gear ring.

[0011] Preferably, a screw head is connected to the top of the rotating shaft, and the bottom thereof passes through the U-shaped frame and is connected with a screw rod. The screw rod is threadedly connected with a nut. The upper side of the nut abuts against the U-shaped frame, the lower side of the screw head abuts against the upper side of the sector gear, and the lower side of the sector gear abuts against the upper side of the U-shaped frame.

[0012] Preferably, the toothed transmission member is a worm, and the worm is connected with a micro motor. The micro motor is fixed to the upper side of the mounting seat.

[0013] Preferably, there are two sliders and two vertical grooves symmetrically arranged. Each slider includes an annular sliding portion and a cylindrical sliding portion. One end of the cylindrical sliding portion is rotatably connected to the outside of the outer ring, and the other end is slidably connected to the annular wavy groove. The annular sliding portion is rotatably connected to the outside of the cylindrical sliding portion and is slidably connected to the vertical groove.

[0014] Preferably, a chute is provided on the inner side of the support housing. The chutes are evenly arranged in an annular array. A rectangular slide rail is connected to the outside of the outer ring. The rectangular slide rails are evenly arranged in an annular array. The plurality of rectangular slide rails are respectively slidably connected to the plurality of chutes.

[0015] Preferably, the top sides of both sides of the first outer ridge are symmetrically provided with first bevels, the bottom sides of both sides of the second outer ridge are symmetrically provided with second bevels, the top sides of both sides of the inner ridge are symmetrically provided with third bevels, and the bottom sides of both sides thereof are symmetrically provided with fourth bevels.

[0016] The beneficial effects of the present invention are as follows:

[0017] The coffee grinder clutch variable speed mechanism can use a common induction motor or a DC brushless motor as the driving motor, which is small in size. By driving the inner ridge to move up and down, the inner ridge can be respectively abutted and cooperated with the first outer ridge and the second outer ridge, thereby realizing a large range of speed adjustment. When adjusting the speed, the torque can be synchronously adjusted, and thus it is applicable to the product requirements of interchangeable conical knives and flat knives. Description of the Drawings

[0018] Figure 1 is a three-dimensional schematic diagram of the coffee grinder clutch variable speed mechanism.

[0019] Figure 2 is a cross-sectional view of the coffee grinder clutch variable speed mechanism.

[0020] Figure 3 is a first exploded schematic diagram of the coffee grinder clutch variable speed mechanism.

[0021] Figure 4 is a second exploded schematic diagram of the coffee grinder clutch variable speed mechanism.

[0022] Figure 5 is Figure 4 an enlarged schematic diagram of part A in

[0023] Figure 6 is an installation schematic diagram of the toothed transmission member and the travel switch.

[0024] Figure 7 is a structural exploded schematic diagram of the sector gear installation structure.

[0025] Figure 8 is a structural schematic diagram of the inner ring.

[0026] Figure 9 It is a schematic structural diagram of a support housing.

[0027] Figure 10 It is a schematic structural diagram of a limit cover.

[0028] In the figure: 1. Driving motor; 2. Reduction assembly; 201. Internal gear ring; 202. Planet carrier; 203. Sun gear; 204. Planet gear; 205. Output shaft; 206. First outer ridge; 207. First bevel angle; 3. Shifting assembly; 301. Inner ring; 302. Outer ring; 303. Support housing; 304. Rotating ring; 305. Annular wavy groove; 306. Vertical groove; 307. Pin; 308. Slide block; 3081. Annular sliding part; 3082. Cylindrical sliding part; 309. Annular groove; 310. Inner ridge; 311. Inner ring; 312. Second outer ridge; 313. Chute; 314. Rectangular slide rail; 315. Second bevel angle; 316. Third bevel angle; 317. Fourth bevel angle; 4. Mounting seat; 5. First travel switch; 6. Second travel switch; 7. Low-level boss; 8. High-level boss; 9. External gear ring; 10. Sector gear; 11. C-shaped frame; 12. Rotating shaft; 13. Lever; 14. Screw head; 15. Screw; 16. Nut; 17. Worm; 18. Micro motor; 19. Bearing; 20. Limit cover; 21. Elastic clamping block; 22. Card slot. Specific embodiments

[0029] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0030] Please refer to Figures 1-10, the present invention provides a technical solution: a clutch speed change mechanism for a coffee grinder, which includes a driving motor 1, and also includes a speed reduction assembly 2 and a gear shifting assembly 3. The speed reduction assembly 2 includes an internal gear ring 201, a planet carrier 202, a sun gear 203, and three evenly distributed planet gears 204. The output end of the driving motor 1 is connected to the sun gear 203. The planet gears 204 are rotatably installed on the planet carrier 202, and are respectively meshed and connected to the sun gear 203 and the internal gear ring 201. The top of the planet carrier 202 is connected with an output shaft 205, and the outer side thereof is connected with a first outer ridge 206. The gear shifting assembly 3 includes an inner ring 301, an outer ring 302, a support housing 303, and a rotating ring 304. The rotating ring 304 is rotatably connected to the outer side of the support housing 303, and an annular wave groove 305 is provided on the inner side thereof. A vertical groove 306 is provided on the side surface of the support housing 303. A pin 307 is connected to the inner side of the outer ring 302, and a slider 308 is connected to the outer side thereof. The slider 308 passes through the vertical groove 306 and is slidably connected to the annular wave groove 305, and is slidably connected to the vertical groove 306. An annular groove 309 is provided on the outer side of the inner ring 301, and an inner ridge 310 is connected to the inner side thereof. The internal gear ring 201 is fixed to the inner side of the inner ring 301 and is arranged below the inner ridge 310. The pin 307 is slidably connected to the annular groove 309. An inner ring 311 is provided at the inner top of the support housing 303, and a second outer ridge 312 is connected to the outer side of the inner ring 311. The first outer ridge 206 and the second outer ridge 312 are respectively in movable abutment with the inner ridge 310;

[0031] An ordinary induction motor or a DC brushless motor can be used as the driving motor 1, which has a small volume;

[0032] Rotate the rotating ring 304 to make the annular wave groove 305 on the inner side of the rotating ring 304 rotate simultaneously, so that the slider 308 slides relative to the annular wave groove 305. Because the annular wave groove 305 is in an annular closed shape, a 360° rotation gear shifting function can be realized. And because the annular wave groove 305 is in a wave shape, when the slider 308 slides from the trough of the annular wave groove 305 to the peak, the slider 308 slides and rises along the vertical groove 306. And when the slider 308 slides from the peak of the annular wave groove 305 to the trough, the slider 308 slides and descends along the vertical groove 306, realizing the conversion from rotational motion to linear motion;

[0033] When the slider 308 slides upward along the vertical groove 306, the slider 308 drives the outer ring 302 to rise. The outer ring 302 drives the inner ring 301 together with the internal gear ring 201 and the inner ridge 310 to rise through the pin 307. When the slider 308 rises to the crest of the annular wave groove 305, the inner ridge 310 rises to one side of the second outer ridge 312. The drive motor 1 drives the sun gear 203 to rotate, the sun gear 203 drives the planet gear 204 to rotate, and the self-rotation of the planet gear 204 drives the rotation of the internal gear ring 201 until the inner ridge 310 comes into contact and cooperation with the second outer ridge 312. At this time, the inner ridge 310 together with the inner ring 301 and the internal gear ring 201 are fixed, and the planet gear 204 rotates self and revolves and drives the planet carrier 202 to rotate. The reduction ratio = 1 + the number of teeth of the internal gear ring 201 / the number of teeth of the sun gear 203. For example, if the number of teeth of the internal gear ring 201 is 32 and the number of teeth of the sun gear 203 is 16, the reduction ratio is 3. When the rotational speed input by the drive motor 1 to the sun gear 203 is 1500 rpm, the rotational speed output by the output shaft 205 is 500 rpm. The calculation formula for the output torque is , where is the output torque, is the input torque, is the reduction ratio, is the efficiency. It can be seen that when the reduction ratio is larger, the output torque is larger;

[0034] When the slider 308 slides downward along the vertical groove 306, the slider 308 drives the outer ring 302 to descend. The outer ring 302 drives the inner ring 301 together with the internal gear ring 201 and the inner ridge 310 to descend through the pin 307. When the slider 308 descends to the trough of the annular wave groove 305, the inner ridge 310 descends to one side of the first outer ridge 206. The drive motor 1 drives the sun gear 203 to rotate, the sun gear 203 drives the planet gear 204 to rotate, the self-rotation of the planet gear 204 drives the rotation of the internal gear ring 201, and the revolution of the planet gear 204 drives the planet carrier 202 to rotate. The rotation directions of the internal gear ring 201 and the planet carrier 202 are opposite until the inner ridge 310 comes into contact and cooperation with the first outer ridge 206. At this time, the sun gear 203, the planet gear 204, the internal gear ring 201 and the planet carrier 202 rotate together as a whole. The output of the internal gear ring 201 and the output of the planet carrier 202 are equal to the input of the sun gear 203, and the reduction ratio is 1. For example, when the rotational speed input by the drive motor 1 to the sun gear 203 is 1500 rpm, the rotational speed output by the output shaft 205 is 1500 rpm;

[0035] Drive the inner ridge 310 to move up and down, so that the inner ridge 310 can be respectively in contact and cooperation with the first outer ridge 206 and the second outer ridge 312, thereby realizing a large range of speed regulation and being able to synchronously adjust the torque during speed regulation, and thus being applicable to the product requirements of the interchange of the taper knife and the flat knife.

[0036] For the convenience of improving the structural stability, in this embodiment, preferably, it further includes a mounting base 4. The support housing 303 is fixedly connected to the upper side of the mounting base 4, the driving motor 1 is fixed to the lower side of the mounting base 4, and the planet carrier 202 is rotatably connected to the upper side of the mounting base 4. The purpose is to improve the structural stability by mounting the driving motor 1, the planet carrier 202, and the support housing 303 on the mounting base 4.

[0037] For the convenience of accurately detecting the in-place states of the high gear and the low gear, in this embodiment, preferably, a first travel switch 5 and a second travel switch 6 are mounted on the upper side of the mounting base 4. The second travel switch 6 is arranged above the first travel switch 5. The outer side of the rotating ring 304 is fixedly connected with a low-position convex platform 7 and a high-position convex platform 8. A plurality of low-position convex platforms 7 are evenly arranged, and each low-position convex platform 7 corresponds to a wave valley of the annular wave groove 305. A plurality of high-position convex platforms 8 are evenly arranged, and each high-position convex platform 8 corresponds to a wave peak of the annular wave groove 305. The low-position convex platform 7 is in movable abutment with the first travel switch 5, and the high-position convex platform 8 is in movable abutment with the first travel switch 5 and the second travel switch 6 respectively;

[0038] The purpose is that when the shifting assembly 3 is in the low gear, the inner ridge 310 collides and cooperates with the second outer ridge 312, the slider 308 is at the wave peak position of the annular wave groove 305, and both the first travel switch 5 and the second travel switch 6 are triggered by the high-position convex platform 8. When the shifting assembly 3 is in the high gear, the inner ridge 310 collides and cooperates with the first outer ridge 206, the slider 308 is at the wave valley position of the annular wave groove 305, the first travel switch 5 is triggered by the low-position convex platform 7 while the second travel switch 6 is not triggered. When the slider 308 is in the middle position, during the shifting period or when there is an abnormal situation of incomplete shifting, neither the first travel switch 5 nor the second travel switch 6 is triggered. Therefore, the automatic monitoring of the gear state is realized by using different travel switch trigger combination logics, and the in-place detection accuracy of the high gear and the low gear is improved.

[0039] For the convenience of driving the rotation of the rotating ring 304, in this embodiment, preferably, an external gear ring 9 is fixedly connected to the outer side of the rotating ring 304. The external gear ring 9 is meshed with a toothed transmission member, and the toothed transmission member is mounted on the upper side of the mounting base 4. The purpose is to drive the rotation of the rotating ring 304 conveniently through the meshing transmission mode between the toothed transmission member and the external gear ring 9.

[0040] For the convenience of further driving the rotation of the rotating ring 304, in this embodiment, preferably, the toothed transmission member is a sector gear 10. The upper side of the mounting base 4 is fixedly connected with a U-shaped frame 11 with an opening facing downward. The top of the U-shaped frame 11 is connected with a rotating shaft 12. The middle part of the sector gear 10 is rotatably connected to the rotating shaft 12, and a lever 13 is connected to the end of the sector gear 10 far from the external gear ring 9;

[0041] The purpose is to manually turn the lever 13, thereby driving the sector gear 10 to rotate around the rotating shaft 12. While the sector gear 10 rotates, it drives the rotating ring 304 to rotate through the external gear ring 9, improving the convenience of gear position adjustment.

[0042] In order to facilitate the adjustment of the tightness of the sector gear 10, in this embodiment, preferably, a screw head 14 is connected to the top of the rotating shaft 12, and its bottom penetrates through the C-shaped frame 11 and is connected to a screw rod 15. The screw rod 15 is threadedly connected to a nut 16. The upper side of the nut 16 abuts against the C-shaped frame 11, the lower side of the screw head 14 abuts against the upper side of the sector gear 10, and the lower side of the sector gear 10 abuts against the upper side of the C-shaped frame 11.

[0043] The purpose is to turn the screw head 14, thereby driving the screw rod 15 to rotate through the rotating shaft 12, causing the screw rod 15 to move up and down relative to the nut 16, and then driving the screw head 14 to move up and down through the rotating shaft 12. When the screw head 14 rises, the pressing force on the sector gear 10 is reduced, and when the screw head 14 descends, the pressing force on the sector gear 10 is increased, thereby adjusting the tightness of the sector gear 10.

[0044] In order to facilitate automatically driving the rotating ring 304 to rotate and improve the degree of automation, in this embodiment, preferably, the toothed transmission member is a worm 17, and the worm 17 is connected to a micro motor 18, and the micro motor 18 is fixed on the upper side of the mounting seat 4.

[0045] The purpose is to drive the worm 17 to rotate through the micro motor 18. While driving the worm 17 to rotate, it drives the rotating ring 304 to rotate through the external gear ring 9, improving the degree of automation and the convenience of gear position adjustment.

[0046] In order to facilitate improving the smoothness of gear shifting, in this embodiment, preferably, two sliders 308 and two vertical grooves 306 are symmetrically provided. Each slider 308 includes an annular sliding portion 3081 and a cylindrical sliding portion 3082. One end of the cylindrical sliding portion 3082 is rotatably connected to the outer side of the outer ring 302, and the other end thereof is slidably connected to the annular wave groove 305. The annular sliding portion 3081 is rotatably connected to the outside of the cylindrical sliding portion 3082 and is slidably connected to the vertical groove 306.

[0047] The purpose is that when the cylindrical sliding portion 3082 slides along the annular wave groove 305, the cylindrical sliding portion 3082 can rotate relative to the outer ring 302, improving the smoothness and preventing the formation of a stuck state. When the annular sliding portion 3081 slides along the vertical groove 306, the annular sliding portion 3081 can rotate relative to the cylindrical sliding portion 3082, further improving the smoothness and preventing the formation of a stuck state.

[0048] In order to facilitate improving the smoothness and accuracy of the lifting stroke of the outer ring 302, in this embodiment, preferably, a chute 313 is provided on the inner side of the support housing 303. A number of chutes 313 are evenly arranged in a circular array. A rectangular slide rail 314 is connected to the outer side of the outer ring 302. A number of rectangular slide rails 314 are evenly arranged in a circular array. A number of rectangular slide rails 314 are respectively slidably connected to a number of chutes 313;

[0049] The purpose is that while the slider 308 slides up and down along the vertical groove 306, a number of rectangular slide rails 314 respectively slide up and down along a number of chutes 313, thereby improving the smoothness and accuracy of the lifting stroke of the outer ring 302.

[0050] In order to facilitate improving the reliability of gear shifting, in this embodiment, preferably, first bevels 207 are symmetrically provided on both sides of the top of the first outer ridge 206, second bevels 315 are symmetrically provided on both sides of the bottom of the second outer ridge 312, third bevels 316 are symmetrically provided on both sides of the top of the inner ridge 310, and fourth bevels 317 are symmetrically provided on both sides of its bottom;

[0051] The purpose is that during the process of shifting from a low gear to a high gear, the inner ridge 310 moves downward. During the downward movement of the inner ridge 310, it may contact the top of the first outer ridge 206. At this time, the inner ridge 310 and the first outer ridge 206 are staggered from each other by moving along the inclined surfaces of the fourth bevel 317 and the first bevel 207, preventing the first outer ridge 206 from blocking the downward movement of the inner ridge 310 and failing to shift gears properly. During the process of shifting from a high gear to a low gear, the inner ridge 310 moves upward. During the upward movement of the inner ridge 310, it may contact the bottom of the second outer ridge 312. At this time, the inner ridge 310 and the second outer ridge 312 are staggered from each other by moving along the inclined surfaces of the third bevel 316 and the second bevel 315, preventing the second outer ridge 312 from blocking the upward movement of the inner ridge 310 and failing to shift gears properly, and improving the reliability of gear shifting.

[0052] In order to facilitate improving the stability of the output shaft 205 during rotation, in this embodiment, preferably, the outer side of the output shaft 205 is rotatably connected to the support housing 303 through a bearing 19. The purpose is to provide radial support for the output shaft 205 through the bearing 19 to ensure that the output shaft 205 remains stable during rotation.

[0053] In order to facilitate the improvement of shifting reliability, in this embodiment, preferably, the top of the rotating ring 304 is rotatably connected to a limit cover 20. The limit cover 20 is fixedly connected to the upper side of the support housing 303 by screws (not shown in the figure), and a plurality of elastic blocks 21 are connected to the inner side thereof. The central angle formed by the output shaft 205 between two adjacent elastic blocks 21 is equal to the central angle formed by the output shaft 205 between one wave valley and an adjacent wave peak of the annular wave groove 305. A card slot 22 is connected to the outer side of the rotating ring 304. The card slot 22 is arranged above one wave valley of the annular wave groove 305 and is movably clamped with one of the elastic blocks 21.

[0054] The purpose is to achieve indexing positioning through the cooperation of the elastic block 21 and the card slot 22. When rotating the rotating ring 304, it is necessary to first overcome the friction force between the elastic block 21 and the card slot 22, and then rotate the rotating ring 304 relative to the limit cover 20. After rotation, the card slot 22 is clamped with the next elastic block 21 to achieve shifting positioning and in-place prompt, prevent the shifting from being incomplete, and improve the shifting reliability.

[0055] The working principle and usage process of the present invention: Different travel switches are used to trigger the combined logic to control the start and stop of the micro motor 18. When it is necessary to switch from a high gear to a low gear, the control micro motor 18 is controlled to drive the worm 17 to rotate. While driving the worm 17 to rotate, the rotating ring 304 is driven to rotate through the external gear ring 9, so that the annular wave groove 305 inside the rotating ring 304 rotates simultaneously, and then the slider 308 slides from the wave valley of the annular wave groove 305 to the wave peak. The slider 308 slides and rises along the vertical groove 306. The slider 308 drives the outer ring 302 to rise. The outer ring 302 drives the inner ring 301 together with the internal gear ring 201 and the inner ridge 310 to rise through the pin 307. When the slider 308 rises to the wave peak of the annular wave groove 305, the shifting assembly 3 is in the low gear. The first travel switch 5 and the second travel switch 6 are simultaneously triggered by the high-position boss 8, feedback controls the micro motor 18 to stop driving, and feedback controls the display to be in the low-gear state. At this time, the tool connected to the output shaft 205 can be replaced with a taper tool.

[0056] In the low gear state, the inner ridge 310 rises to one side of the second outer ridge 312. The drive motor 1 drives the sun gear 203 to rotate. The sun gear 203 drives the planet gear 204 to rotate. The self-rotation of the planet gear 204 drives the rotation of the internal gear ring 201 until the inner ridge 310 comes into contact and cooperation with the second outer ridge 312. At this time, the inner ridge 310, together with the inner ring 301 and the internal gear ring 201, remains stationary. The planet gear 204 rotates and revolves and drives the planet carrier 202 to rotate. The reduction ratio = 1 + the number of teeth of the internal gear ring 201 / the number of teeth of the sun gear 203. For example, if the number of teeth of the internal gear ring 201 is 32 and the number of teeth of the sun gear 203 is 16, the reduction ratio is 3. When the rotational speed input by the drive motor 1 to the sun gear 203 is 1500 rpm, the rotational speed output by the output shaft 205 is 500 rpm. The calculation formula for the output torque is , where is the output torque, is the input torque, is the reduction ratio, is the efficiency. It can be seen that when the reduction ratio is larger, the output torque is larger, that is, the torque is increased after deceleration, which is suitable for the taper cutter and solves the problem that the taper cutter requires a larger rotational torque under the same cutter head size;

[0057] When it is necessary to switch from the low gear to the high gear, the control micro motor 18 drives the worm 17 to rotate. While driving the worm 17 to rotate, the outer gear ring 9 drives the rotating ring 304 to rotate, so that the annular wave groove 305 inside the rotating ring 304 rotates at the same time. Then, the slider 308 slides from the wave crest of the annular wave groove 305 to the wave trough. The slider 308 slides and descends along the vertical groove 306. The slider 308 drives the outer ring 302 to descend. The outer ring 302 drives the inner ring 301, together with the internal gear ring 201 and the inner ridge 310, to descend through the pin 307. When the slider 308 descends to the wave trough of the annular wave groove 305, when the shifting component 3 is in the high gear, the first travel switch 5 is triggered by the low-position boss 7 and the second travel switch 6 is not triggered. The feedback controls the micro motor 18 to stop driving, and the feedback controls the display to be in the high gear state. At this time, the cutter connected to the output shaft 205 can be replaced with a flat cutter;

[0058] In the high gear state, the inner ridge 310 descends to one side of the first outer ridge 206. The drive motor 1 drives the sun gear 203 to rotate. The sun gear 203 drives the planet gears 204 to rotate. The self-rotation of the planet gears 204 drives the internal gear ring 201 to rotate. The revolution of the planet gears 204 drives the planet carrier 202 to rotate. The rotation directions of the internal gear ring 201 and the planet carrier 202 are opposite. Until the inner ridge 310 comes into contact and cooperation with the first outer ridge 206. At this time, the sun gear 203, the planet gears 204, the internal gear ring 201, and the planet carrier 202 rotate together as a whole. The output of the internal gear ring 201 and the output of the planet carrier 202 are equal to the input of the sun gear 203, and the reduction ratio is 1. For example, when the rotational speed input by the drive motor 1 to the sun gear 203 is 1500 rpm, the rotational speed output by the output shaft 205 is 1500 rpm, which is applicable to the flat knife that requires a relatively high rotational speed.

[0059] Finally, it should be noted that the above are only preferred examples of the present invention and are not used to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements for some of the technical features. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A coffee grinder clutch speed change mechanism, comprising a drive motor (1), characterized in that: It also includes a speed reduction component (2) and a gear shifting component (3). The speed reduction component (2) includes an internal gear ring (201), a planet carrier (202), a sun gear (203), and three evenly distributed planet gears (204). The output end of the drive motor (1) is connected to the sun gear (203). The planet gears (204) are rotatably mounted on the planet carrier (202) and are respectively meshed with the sun gear (203) and the internal gear ring (201). The top of the planet carrier (202) is connected with an output shaft (205), and its outer side is connected with a first outer ridge (206). The gear shifting component (3) includes an inner ring (301), an outer ring (302), a support housing (303), and a rotating ring (304). The rotating ring (304) is rotatably connected to the outer side of the support housing (303), and its inner side is provided with an annular wave groove (305). The side surface of the support housing (303) is provided with a vertical groove (306). The inner side of the outer ring (302) is connected with a pin (307), and its outer side is connected with a slider (308). The slider (308) passes through the vertical groove (306) and is slidably connected to the annular wave groove (305), and it is slidably connected with the vertical groove (306). The outer side of the inner ring (301) is provided with an annular groove (309), and its inner side is connected with an inner ridge (310). The internal gear ring (201) is fixed to the inner side of the inner ring (301) and is arranged below the inner ridge (310). The pin (307) is slidably connected to the annular groove (309). The inner top of the support housing (303) is provided with an inner ring (311), and the outer side of the inner ring (311) is connected with a second outer ridge (312). The first outer ridge (206) and the second outer ridge (312) are respectively in movable abutment with the inner ridge (310). It also includes a mounting seat (4). The support housing (303) is fixedly connected to the upper side of the mounting seat (4). The drive motor (1) is fixed to the lower side of the mounting seat (4). The planet carrier (202) is rotatably connected to the upper side of the mounting seat (4). The upper side of the mounting seat (4) is provided with a first travel switch (5) and a second travel switch (6). The second travel switch (6) is arranged above the first travel switch (5). The outer side of the rotating ring (304) is fixedly connected with a low-position convex platform (7) and a high-position convex platform (8). A plurality of low-position convex platforms (7) are evenly arranged, and each low-position convex platform (7) corresponds to a trough of the annular wave groove (305). A plurality of high-position convex platforms (8) are evenly arranged, and each high-position convex platform (8) corresponds to a crest of the annular wave groove (305). The low-position convex platform (7) is in movable abutment with the first travel switch (5). The high-position convex platforms (8) are respectively in movable abutment with the first travel switch (5) and the second travel switch (6). The outer side of the rotating ring (304) is fixedly connected with an external gear ring (9). The external gear ring (9) is meshed with a toothed transmission member. The toothed transmission member is mounted on the upper side of the mounting seat (4).The toothed transmission member is a sector gear (10), and a C-shaped frame (11) with an opening facing downward is fixedly connected to the upper side of the mounting seat (4). A rotating shaft (12) is connected to the top of the C-shaped frame (11). The middle part of the sector gear (10) is rotatably connected to the rotating shaft (12), and a lever (13) is connected to the end of the sector gear (10) away from the outer gear ring (9).

2. The coffee grinder clutch speed change mechanism according to claim 1, characterized in that: The top of the rotating shaft (12) is connected to a screw head (14), and its bottom penetrates through the U-shaped frame (11) and is connected to a screw rod (15). The screw rod (15) is threadedly connected to a nut (16). The upper side of the nut (16) abuts against the U-shaped frame (11). The lower side of the screw head (14) abuts against the upper side of the sector gear (10). The lower side of the sector gear (10) abuts against the upper side of the U-shaped frame (11).

3. The clutch variable speed mechanism of the coffee grinder according to claim 1, wherein: The toothed transmission member is a worm (17). The worm (17) is connected to a micro motor (18). The micro motor (18) is fixed to the upper side of the mounting seat (4).

4. The coffee grinder clutch and variable speed mechanism according to claim 1, wherein: The slider (308) and the vertical groove (306) are both symmetrically provided with two. Each slider (308) includes an annular sliding portion (3081) and a cylindrical sliding portion (3082). One end of the cylindrical sliding portion (3082) is rotatably connected to the outside of the outer ring (302), and the other end thereof is slidably connected to the annular wave groove (305). The annular sliding portion (3081) is rotatably connected to the outside of the cylindrical sliding portion (3082) and is slidably connected to the vertical groove (306).

5. The clutch variable speed mechanism of the coffee grinder according to claim 1, wherein: The inner side of the support housing (303) is provided with a chute (313). The chutes (313) are evenly arranged in an annular array. The outside of the outer ring (302) is connected with a rectangular slide rail (314). The rectangular slide rails (314) are evenly arranged in an annular array. A plurality of the rectangular slide rails (314) are respectively slidably connected to a plurality of the chutes (313).

6. The clutch speed change mechanism of the coffee grinder according to claim 1, wherein: On both sides of the top of the first outer ridge (206), first bevels (207) are symmetrically provided. On both sides of the bottom of the second outer ridge (312), second bevels (315) are symmetrically provided. On both sides of the top of the inner ridge (310), third bevels (316) are symmetrically provided, and on both sides of its bottom, fourth bevels (317) are symmetrically provided.

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