CN217401520U - Jacking type planetary clutch transmission structure, steering transmission structure and mini-tiller - Google Patents
Jacking type planetary clutch transmission structure, steering transmission structure and mini-tiller Download PDFInfo
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- CN217401520U CN217401520U CN202221450746.9U CN202221450746U CN217401520U CN 217401520 U CN217401520 U CN 217401520U CN 202221450746 U CN202221450746 U CN 202221450746U CN 217401520 U CN217401520 U CN 217401520U
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Abstract
The utility model relates to a plough the machine field a little, specifically disclose jacking formula planet separation and reunion transmission structure, turn to transmission structure and plough the machine a little, wherein jacking formula planet separation and reunion transmission structure, including the clutch box, the power input shaft, transmission shaft and planetary gear train, planetary gear train is located the clutch box, and planetary gear train connects power input shaft and transmission shaft simultaneously, still is provided with the retaining member that is used for locking planetary gear train's ring gear in the clutch box, the retaining member is located one side that power input shaft was kept away from to planetary gear train's ring gear, the retaining member includes the friction disk and is used for the jacking friction disk so that the ring gear can be by friction disk and clutch box inner top surface extrusion's jacking drive assembly relatively. The utility model discloses a set up the friction disk, thereby the jacking through the friction disk makes the ring gear can be realized the braking of ring gear by friction disk and casing relative extrusion, adopts under the mode prerequisite of extrudeing downwards or the tight ring gear of radial clamp at current ring gear braking, has increased a new mode and structure of ring gear braking.
Description
Technical Field
The utility model belongs to the technical field of plough the machine a little, concretely relates to jacking formula planet separation and reunion transmission structure, turn to transmission structure and plough the machine a little.
Background
The existing clutch system of the mini-tiller adopts a gear ring of a planetary gear speed reducing system as a clutch object, and power is transmitted from a sun gear to a planet carrier through braking the gear ring.
The braking mode of ring gear usually adopts and sets up a clamp plate at the ring gear top, through pressing down to the clamp plate to realize the braking of ring gear, for example the utility model patent "a plough quick-witted planet speed reduction clutch a little" (patent number ZL 202122852372.5). Or a braking mechanism is arranged on the circumferential direction of the outer edge of the gear ring, and the gear ring is radially clamped from the gear ring, so that the braking of the gear ring is realized, for example, the utility model discloses a mini-tiller clutch gearbox system for realizing safe operation through a handle (patent number ZL 202210029031.4).
In the prior art, the gear ring is braked in a mode of pressing downwards or clamping the gear ring in a radial direction, and the applicant is dedicated to searching a new mode for braking the gear ring in a clutch system of the mini-tiller.
SUMMERY OF THE UTILITY MODEL
To the not enough of above-mentioned prior art, the utility model aims to solve the technical problem that: how to provide a new way of braking the ring gear, different from what is currently available.
In order to solve the technical problem, the utility model discloses a following technical scheme:
the jacking type planetary clutch transmission structure comprises a clutch box, a power input shaft, a transmission shaft and a planetary gear train, wherein the planetary gear train is located in the clutch box and is simultaneously connected with the power input shaft and the transmission shaft, a locking piece used for locking a gear ring of the planetary gear train is further arranged in the clutch box, the locking piece is located on one side, away from the power input shaft, of the gear ring of the planetary gear train, and the locking piece comprises a friction disc and a jacking driving assembly used for jacking the friction disc so that the gear ring can be relatively extruded by the friction disc and the inner top surface of the clutch box.
The beneficial effects of the utility model reside in that:
the utility model discloses a set up the friction disk, thereby the jacking through the friction disk makes the ring gear can be realized the braking of ring gear by friction disk and casing relative extrusion, adopts under the mode prerequisite of extrudeing downwards or the tight ring gear of radial clamp at current ring gear braking, has increased a new mode and structure of ring gear braking.
Adopt the mode of extrusion downwards among the prior art to realize the ring gear braking for the extruded article of extrusion ring gear need install in the top of ring gear, needs great assembly space, and the thickness that consequently the clutch box need set up is great, the utility model discloses a braking of ring gear is realized to the mode of friction disk jacking, and the friction disk is located the outside of ring gear, does not need additionally to set up the assembly space of friction disk above the ring gear, consequently the whole thickness of clutch box can reduce.
When adopting radial extruded mode to realize the ring gear braking among the prior art, radial cohesion ring gear is great to the ring gear damage, and the ring gear is out of shape easily, and planetary gear train transmission is inefficacy, and life reduces, the utility model discloses a jacking mode of friction disk realizes the braking of ring gear, and the ring gear is difficult to warp, prolongs its life.
Drawings
Fig. 1 is a schematic view of the overall structure of the present invention.
Fig. 2 is an exploded view of a first embodiment of the present invention.
Fig. 3 is a schematic structural view of the first embodiment of the present invention with the flange removed.
Fig. 4 is a structural diagram of fig. 3 with the planetary gear train, the friction disc and the toggle ring removed.
Fig. 5 is a longitudinal sectional view of a first embodiment of the present invention.
Fig. 6 is an enlarged view of a portion a in fig. 5.
Fig. 7 is another longitudinal sectional view of the first embodiment of the present invention, and the section line is along the axis of the output shaft.
Fig. 8 is a schematic structural view of the transmission shaft in fig. 7.
Fig. 9 is a schematic structural diagram of a friction disc according to a first embodiment of the present invention.
Fig. 10 is a bottom view of fig. 9.
Fig. 11 is a schematic structural view of a first toggle ring according to an embodiment of the present invention.
Fig. 12 is a schematic structural view of the manual toggle mechanism in fig. 2 and 3.
Fig. 13 is an exploded view of the second embodiment of the present invention.
Fig. 14 is a structural diagram of the second embodiment of the present invention without the flange, the planetary gear train, the friction disc, and the toggle ring.
Fig. 15 is a longitudinal sectional view of the second embodiment of the present invention.
Fig. 16 is an enlarged view at B in fig. 15.
Fig. 17 is a schematic structural view of a friction disc according to a second embodiment of the present invention.
Fig. 18 is a bottom view of the structure of fig. 17.
Fig. 19 is a schematic structural view of a dial ring in the second embodiment of the present invention.
Fig. 20 is a bottom view of the structure of fig. 19.
Wherein the reference numerals include:
the power input shaft 100, the clutch box 101, the flange 1011, the transitional connection box 102, the traveling box 103, the planetary gear train 2, the sun gear 201, the planet gear 202, the gear ring 203, the friction ring 2030, the friction plate 2031, the planet carrier 204, the friction disc 3, the folded part 301, the jacking ball 3010, the support ring 302, the gear ring support ball I3020, the toggle ring 4, the spiral groove 401, the lug plate 402, the rectangular hole 4021, the friction disc support ball 403, the jacking inclined plane 404, the manual toggle mechanism 5, the clutch fork shaft 501, the clutch arm 502, the connecting arm 503, the fork 504, the transmission shaft 6, the external rectangular spline 601, the bevel gear 602, the output shaft 701, the traveling bevel gear 702, the toggle ring support ball 8, the guide column 9, the cylinder 10 and the gear ring support ball II 11.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings.
In the specific implementation: as shown in the figures 1-20 of the drawings,
the steering transmission structure of the mini-tiller comprises a box body, wherein the box body comprises an integrally formed clutch box 101, a transitional connection box 102 and a walking box 103, a flange 1011 is arranged at the top of the clutch box 101, and the flange 1011 is arranged at the top of the clutch box 101 through a bolt cover.
The clutch box 101 is internally provided with a planetary gear train 2, and the planetary gear train 2 is simultaneously connected with the power input shaft 100 and the transmission shaft 6. The power input shaft 100 passes through the flange 1011 and then penetrates into the clutch box 101. A vertical mounting hole is formed in the transitional connection box 102, and the transmission shaft 6 is arranged in the vertical mounting hole.
The planetary gear train 2 comprises a gear ring 203, a sun gear 201, a planet carrier 204 and a plurality of planetary gears 202, a friction ring 2030 is arranged on the outer edge of the gear ring 203, the friction ring 2030 and the gear ring 203 are integrally formed or fixedly connected, friction plates 2031 are fixed on the upper end face and the lower end face of the friction ring 2030, the sun gear 201 and the power input shaft 100 are coaxially arranged and integrally formed, the planet carrier 204 is mounted at the bottom of the clutch box 101 through a rolling bearing, each planetary gear 202 is rotatably arranged on the planet carrier 204, the top of the transmission shaft 6 penetrates into a central hole of the planet carrier 204, an external rectangular spline 601 at the top of the transmission shaft 6 is matched with an internal rectangular spline of the central hole of the planet carrier 204, when the planet carrier 204 rotates, the transmission shaft 6 can be driven to rotate simultaneously, and a bevel gear 602 is arranged at the bottom of the transmission shaft 6.
The traveling mechanism is arranged in the traveling box 103, and as shown in fig. 7, the traveling mechanism comprises an output shaft 701 and a traveling bevel gear 702 sleeved on the output shaft 701, the traveling bevel gear 702 is engaged with a bevel gear 602 at the bottom of the transmission shaft 6, the output shaft 701 is rotatably connected in the traveling box 103 and penetrates through the traveling box 103, and when the transmission shaft 6 rotates, the traveling bevel gear 702 and the output shaft 701 can be driven to rotate by engagement of the bevel gear 602 at the bottom of the transmission shaft 6 and the traveling bevel gear 702 in the traveling box 103.
A locking member for locking the gear ring 203 is further arranged in the clutch box 101, and the locking member comprises a friction disc 3 and a lifting driving assembly for lifting the friction disc 3 so that the gear ring 203 can be pressed by the friction disc 3 and a flange 1011 of the clutch box 101 to realize locking of the gear ring 203.
Example one
The friction disc 3 is structurally shown in fig. 9 and 10, a central hole of the friction disc 3 extends downwards to form a cylindrical folded part 301, the gear ring 203 is located inside the cylindrical folded part 301, a support ring 302 is fixed on the inner wall of the cylindrical folded part 301, three support circular holes are formed in the support ring 302, gear ring support balls i 3020 are embedded in the support circular holes, an annular groove is formed below the support ring 302 on the inner bottom surface of the clutch case 101, and the bottom end of the gear ring support ball i 3020 is clamped into the annular groove, so that the friction disc 3 is supported in the clutch case 101 through the gear ring support ball i 3020. The bottom of the ring gear 203 is in contact with the top ends of ring gear support balls i 3020, so that the ring gear 203 is supported on the support ring 302 by three ring gear support balls i 3020 to enable the ring gear 203 to rotate on the support ring 302.
In order to enable the friction disc 3 to vertically lift in the clutch box 101 (along the axial motion of the gear ring 203), four guide posts 9 distributed in an annular shape are fixed in the clutch box 101, guide round holes in sliding fit with the guide posts 9 are formed in the friction disc 3, springs (not shown in the figure) are wound on the guide posts 9, the springs are located above the friction disc 3, the top end of each spring is connected with the inner side surface of the top of the clutch box 101, the bottom end of each spring is connected with the top surface of the friction disc 3, and the springs on the four guide posts 9 can ensure that the friction disc 3 can stably lift along the four guide posts 9.
The jacking driving assembly comprises a toggle ring 4 sleeved outside the turnover part 301, the toggle ring 4 is structured as shown in fig. 11, a plurality of spiral grooves 401 are formed in the inner wall of the toggle ring 4, a plurality of jacking balls 3010 are embedded on the outer side wall of the turnover part 301 of the friction disc 3 along the circumferential direction, and the plurality of jacking balls 3010 are respectively clamped in the plurality of spiral grooves 401. An annular groove is formed in the clutch box 101 below the toggle ring 4, a plurality of toggle ring supporting balls 8 are arranged in the annular groove, and the toggle ring 4 is supported in the clutch box 101 through the plurality of toggle ring supporting balls 8, so that the toggle ring 4 can rotate in the clutch box 101. When stirring ring 4 and rotate, through the cooperation of helicla flute 401 with jacking ball 3010, can drive friction disk 3 along the vertical lift of guide post 9, during the vertical lift of friction disk 3, can drive ring gear 203 and go up and down in step.
In order to facilitate driving the dial ring 4 to rotate, the manual dial mechanism 5 is further provided in this embodiment, as shown in fig. 12, the manual dial mechanism 5 includes a clutch shift shaft 501 and a clutch arm 502, the clutch arm 502 is fixed to a portion of the clutch shift shaft 501 located outside the flange 1011, a connecting arm 503 is fixedly sleeved on a portion of the clutch shift shaft 501 located inside the clutch box 101, and a shift fork 504 is fixed to an outer end of the connecting arm 503. An ear plate 402 is integrally formed at the outer edge of the toggle ring 4, a rectangular hole 4021 extending along the radial direction of the toggle ring 4 is formed in the ear plate 402, and the shifting fork 504 is embedded in the rectangular hole 4021. The clutch shift shaft 501 is rotated by pulling the clutch arm 502, and the shift ring 4 is rotated by the shift fork 504.
When the ring gear 203 is in an unlocked state, a gap is formed between the friction plate 2031 on the upper end surface of the friction ring 2030 on the ring gear 203 and the flange 1011, the friction plate 2031 on the lower end surface of the friction ring 2030 is in contact with the top surface of the friction disc 3, and power is transmitted from the power input shaft 100 to the ring gear 203 under the support of the support ring 302 on the friction disc 3 by the ring gear 203 so that the ring gear 203 rotates.
When the gear ring 203 needs to be locked, the clutch arm 502 is pulled off to drive the stirring ring 4 to rotate, when the stirring ring 4 rotates, the spiral groove 401 on the stirring ring 4 is matched with the jacking balls 3010 on the friction disc 3 to drive the friction disc 3 to vertically ascend along the guide post 9, the friction disc 3 drives the gear ring 203 to synchronously ascend when ascending, the friction disc 2031 on the upper end surface of the friction ring 2030 on the gear ring 203 is contacted with the flange 1011 to generate friction, and the friction ring 2030 on the gear ring 203 simultaneously receives the friction force between the flange 1011 and the friction disc 2031, so that the gear ring 203 is locked.
Example two
The difference between this embodiment and the first embodiment is:
as shown in fig. 17 and 18, the friction disc 3 has a plate-like structure, the ring gear 203 is located inside a central hole of the friction disc 3, and similarly, in order to allow the friction disc 3 to vertically move up and down in the clutch case 101, a guide post 9 is provided in the clutch case 101, and a spring is wound around the guide post 9.
The jacking driving assembly comprises a toggle ring 4, the toggle ring 4 is positioned on one side of the friction disc 3 far away from the friction ring 2030, when the gear ring 203 is in an unlocked state, the friction plate 2031 on the top surface of the friction ring 2030 on the gear ring 203 is in contact with the top of the inner cavity of the clutch box 101, a gap is reserved between the toggle ring 4 and the friction disc 3, as shown in fig. 14, a plurality of annularly distributed gear ring supporting balls II 11 are embedded on the inner bottom surface of the clutch box 101, and the bottom of the gear ring 203 is in contact with each gear ring supporting ball II 11, so that the gear ring 203 is supported in the clutch box 101, and the gear ring 203 can rotate in the clutch box 101.
The structure of the toggle ring 4 is as shown in fig. 19 and 20, a plurality of friction disc support balls 403 distributed in an annular shape are embedded in the top surface of the toggle ring 4, an annular groove is formed in the bottom surface of the friction disc 3, each friction disc support ball 403 is embedded in the annular groove, the friction disc 3 is supported on the toggle ring 4 by the matching of each friction disc support ball 403 and the annular groove, and the toggle ring 4 and the friction disc 3 can rotate relatively.
The end surface of the toggle ring 4 far from the friction disc 3 is provided with a plurality of jacking inclined planes 404 protruding out of the bottom surface of the friction disc 3, as shown in fig. 20, the intersection line of the jacking inclined planes 404 and the bottom surface of the toggle ring 4 extends along the radial direction of the toggle ring 4, rolling bodies respectively contacting with the jacking inclined planes 404 are embedded in the inner bottom surface of the clutch box 101, and the toggle ring 4 is vertically supported by the rolling bodies. This rolling element can select spheroid or cylinder 10, preferably cylinder 10, the outer fringe of cylinder 10 and the contact of the jacking inclined plane 404 of stirring circle 4 bottom, be line contact during both contacts, it is corresponding, the bottom surface has the semi-cylindrical groove with cylinder 10 complex in the clutch box 101, cylinder 10 inlays and locates this semi-cylindrical inslot, make cylinder 10 can follow cylinder 10 self axis rotation in the semi-cylindrical inslot, carry out the roll support to stirring circle 4 through each cylinder 10, can make stirring circle 4 rotatory in each cylinder 10 top.
Similarly, in order to drive the dial ring 4 to rotate, the present embodiment is also provided with a manual dial mechanism 5 having the same structure as that of the first embodiment, which is not described herein again.
When the ring gear 203 is in an unlocked state, a gap is formed between the friction plate 2031 on the lower end face of the friction ring 2030 of the ring gear 203 and the friction plate 3, and power is transmitted from the power input shaft 100 to the ring gear 203 by the ring gear 203 being supported by the respective ring gear support balls ii 11 on the inner bottom portion of the clutch case 101, so that the ring gear 203 rotates.
When the gear ring 203 needs to be locked, the clutch arm 502 is pulled off to drive the toggle ring 4 to rotate, when the toggle ring 4 rotates, through the matching between the jacking inclined plane 404 at the bottom of the toggle ring 4 and the cylinder 10 at the inner bottom surface of the clutch box 101, the toggle ring 4 is jacked up gradually while rotating, the friction disc 3 supported on the top surface of the toggle ring 4 is jacked up gradually along the guide column 9, friction force is generated by the contact of the top surface of the friction disc 3 and the friction plate 2031 at the bottom of the friction ring 2030 on the gear ring 203, the friction ring 2030 on the gear ring 203 is simultaneously subjected to the friction force of the flange 1011 and the friction plate 2031, and therefore the gear ring 203 is locked.
The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various changes and modifications can be made without departing from the technical scope of the present invention, and the technical scope of the present invention is also considered to fall into the scope of the claims.
Claims (10)
1. The jacking type planetary clutch transmission structure comprises a clutch box, a power input shaft, a transmission shaft and a planetary gear train, wherein the planetary gear train is positioned in the clutch box and is simultaneously connected with the power input shaft and the transmission shaft, a locking piece for locking a gear ring of the planetary gear train is also arranged in the clutch box,
the locking piece is positioned on one side, far away from the power input shaft, of the gear ring of the planetary gear train and comprises a friction disc and a jacking driving assembly used for jacking the friction disc so that the gear ring can be relatively extruded by the friction disc and the inner top surface of the clutch box.
2. The lift-up planetary clutch transmission according to claim 1, wherein the top of the ring gear is fixed with a friction ring protruding from the outer edge of the ring gear, the top surface of the friction ring has a gap with the top surface of the clutch case, the bottom surface of the friction ring contacts with the top surface of the friction disk, and the bottom of the ring gear is supported on the friction disk in a rolling manner.
3. The lift-type planetary clutch transmission according to claim 1, wherein the top of the ring gear is fixed with a friction ring protruding from the outer edge of the ring gear, the top surface of the friction ring is in contact with the top surface of the inside of the clutch case, the bottom surface of the friction ring is spaced from the top surface of the friction disc, and the bottom of the ring gear is supported on the bottom surface of the inside of the clutch case in a rolling manner.
4. The lift-type planetary clutch transmission structure according to claim 2 or 3, wherein the lift-type driving assembly comprises a toggle ring, the toggle ring is located on one side of the friction disc away from the gear ring, the friction disc is turned downwards at a central hole of the friction disc to form a cylindrical turning part, the toggle ring is located on the outer side of the turning part, a plurality of spiral grooves are formed in the inner side wall of the toggle ring, and a plurality of rolling bodies which are matched with the spiral grooves in a one-to-one correspondence mode are arranged on the outer side wall of the turning part of the friction disc.
5. The lift-type planetary clutch transmission structure according to claim 4, wherein an annular groove is formed in the inner bottom surface of the clutch case, a plurality of rolling bodies are embedded in the annular groove, and the stirring ring is supported on each rolling body.
6. The lift-type planetary clutch transmission structure according to claim 2 or 3, wherein the lift-type driving assembly comprises a shift ring, the shift ring is located on one side of the friction disc away from the gear ring, the end surface of the friction disc is rotationally connected with the end surface of the shift ring through a plurality of balls, the end surface of the shift ring away from the friction disc is provided with a plurality of lift-up inclined surfaces, and a plurality of rolling bodies in one-to-one contact with the plurality of lift-up inclined surfaces are arranged in the clutch box.
7. The lift-type planetary clutch transmission structure according to claim 6, wherein the rolling element in the clutch box contacting the lift-up inclined surface is a cylinder, and a semi-cylindrical groove matching with the cylinder is formed at the bottom of the clutch box, and the cylinder can rotate in the semi-cylindrical groove.
8. The lift-type planetary clutch transmission structure as claimed in claim 1, wherein a plurality of guide posts extending axially along the gear ring are fixed in the clutch case, the friction plates are provided with guide circular holes slidably engaged with the guide posts, the guide posts are wound with springs, the springs are located above the friction plates, and the top ends of the springs are connected with the inner top surface of the clutch case and the bottom ends of the springs are connected with the top surfaces of the friction plates.
9. The steering transmission structure is characterized by comprising the jacking type planetary clutch transmission structure as claimed in claim 1, and further comprising a transitional connection box and a walking box, wherein a vertical mounting hole is formed in the transitional connection box, the transmission shaft is arranged in the vertical mounting hole, one end of the transmission shaft is in transmission connection with a planetary carrier of the planetary gear train, the other end of the transmission shaft is provided with a bevel gear, a walking mechanism is arranged in the walking box and comprises an output shaft and a walking bevel gear sleeved on the output shaft, the walking bevel gear is meshed with the bevel gear, and the output shaft is rotatably connected in the walking box and penetrates through the walking box.
10. A micro-cultivator comprising the steering transmission structure as claimed in claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221450746.9U CN217401520U (en) | 2022-06-10 | 2022-06-10 | Jacking type planetary clutch transmission structure, steering transmission structure and mini-tiller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202221450746.9U CN217401520U (en) | 2022-06-10 | 2022-06-10 | Jacking type planetary clutch transmission structure, steering transmission structure and mini-tiller |
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| Publication Number | Publication Date |
|---|---|
| CN217401520U true CN217401520U (en) | 2022-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202221450746.9U Active CN217401520U (en) | 2022-06-10 | 2022-06-10 | Jacking type planetary clutch transmission structure, steering transmission structure and mini-tiller |
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| Country | Link |
|---|---|
| CN (1) | CN217401520U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114569923A (en) * | 2022-03-29 | 2022-06-03 | 江苏经贸职业技术学院 | Laboratory fire safety emergency treatment equipment |
-
2022
- 2022-06-10 CN CN202221450746.9U patent/CN217401520U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114569923A (en) * | 2022-03-29 | 2022-06-03 | 江苏经贸职业技术学院 | Laboratory fire safety emergency treatment equipment |
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