CN112648344A - Planet gear single-plate staggered tooth back clearance adjustable planet speed reducer - Google Patents
Planet gear single-plate staggered tooth back clearance adjustable planet speed reducer Download PDFInfo
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- CN112648344A CN112648344A CN202011583172.8A CN202011583172A CN112648344A CN 112648344 A CN112648344 A CN 112648344A CN 202011583172 A CN202011583172 A CN 202011583172A CN 112648344 A CN112648344 A CN 112648344A
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- pin
- back clearance
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- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 33
- 230000005540 biological transmission Effects 0.000 claims abstract description 14
- 230000007704 transition Effects 0.000 claims description 20
- 238000000034 method Methods 0.000 description 8
- 230000008569 process Effects 0.000 description 5
- 238000005299 abrasion Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2863—Arrangements for adjusting or for taking-up backlash
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
Abstract
The invention discloses a planet gear single-plate dislocation tooth back clearance adjustable planet gear reducer in the field of planet gear transmission, which is characterized in that an output end cover, an inner gear ring and an input end cover are coaxially connected to form a closed cavity, a sun gear and at least two planet gears are arranged in the cavity, the sun gear is coaxially connected and fixed on a motor main shaft connecting sleeve, and the motor main shaft connecting sleeve is coaxially and rotatably connected with the input end cover; the planet gear comprises a first gear and a second gear which are connected with the same axis and have the same parameters, the first gear and the second gear are arranged in a staggered mode, and the tooth surfaces of the first gear and the second gear are respectively in contact with the tooth surfaces on two sides of the teeth of the sun gear and the tooth surfaces on two sides of the teeth of the inner gear ring. The invention can adjust the gear radial meshing clearance by adjusting the size of the sun gear to ensure small back clearance, and can adjust the gear radial meshing clearance by replacing the large sun gear to ensure small back clearance, thereby avoiding the scrapping of the speed reducer and saving the cost.
Description
Technical Field
The invention relates to the field of planetary gear transmission, in particular to a planetary reducer with a single-plate staggered tooth back clearance adjustable planet wheel.
Background
The involute planetary transmission reducer is used as a speed reducing, increasing and speed changing transmission device and is widely applied to various machines. The planetary transmission usually adopts a plurality of planetary wheels to transmit load at the same time, and adopts inner gearing to split and reasonable power, so that the planetary transmission has the advantages of compact structure, small volume, light weight, large transmission ratio range, high transmission efficiency, stable operation, low noise, synthesis and decomposition of motion and the like.
For planetary gear reducers with output shafts in two working states, namely anticlockwise working state and clockwise working state, especially for parts to be repeatedly positioned, small-backlash or zero-backlash transmission is always desired, namely, the angle return difference of the two working states is very small, and the planetary gear reducer is mainly applied to servo motors and reducers for stepping motors of CNC (computerized numerical control) machines, engraving machines and the like. Generally, the backlash of each stage of speed reduction of the planetary transmission reducer is not required, and for the speed reduction of each stage of the planetary transmission reducer with the backlash requirement not less than 0.5 degrees, the meshing backlash of gears is usually reduced and verified; however, if the speed reducer with the back clearance below 10' is required, a high-precision gear must be selected, otherwise, the assembly and the normal operation under the condition of the extremely small meshing clearance cannot be ensured; most of gear drive in the design of the existing speed reducer is a straight cylindrical gear. The existing defects are as follows:
1. the speed reducer with the back clearance below 10' is required, and the high-precision gear needs gear grinding, so that the processing period is long, and the cost is greatly increased.
2. The reducer adopting the cylindrical straight gear cannot solve the problem that the back clearance is enlarged due to the increase of the meshing clearance caused by the abrasion of the gear, and only the reducer is scrapped.
Disclosure of Invention
The invention aims to provide a planet gear single-plate staggered tooth back clearance adjustable planet speed reducer to solve the problems in the background technology.
In order to achieve the purpose, the invention provides the following technical scheme:
a planet gear single-plate dislocation tooth back clearance adjustable planet gear reducer is characterized in that an output end cover, an inner gear ring and an input end cover are coaxially connected to form a closed cavity, a sun gear and at least two planet gears are arranged in the cavity, the sun gear is coaxially connected and fixed on a motor main shaft connecting sleeve, and the motor main shaft connecting sleeve is coaxially and rotatably connected with the input end cover; a transition sleeve is arranged in an inner hole of the planet wheel and is arranged on the pin shaft; one end of the pin shaft is in interference fit with a corresponding shaft hole in the output shaft tray, and the other end of the pin shaft is limited by the planet wheel retainer ring; the two radial side surfaces of the pin shaft, which are matched with the transition sleeve, are of flat square structures, the other two side surfaces of the pin shaft are of round surface structures, the round surface structures are in clearance fit with the inner hole of the transition sleeve, and the axis of the pin shaft is parallel to the axis of the output shaft tray; the planet gear comprises a first gear and a second gear which are coaxially connected and have the same parameters, and the first gear and the second gear are straight cylindrical gears with gear teeth arranged in a staggered manner; the tooth surface of the first gear is in contact with one side tooth surface of the teeth of the sun gear and one side tooth surface of the teeth of the inner gear ring, and the tooth surface of the second gear is in contact with the other side tooth surface of the teeth of the sun gear and the other side tooth surface of the teeth of the inner gear ring.
As an improved scheme of the invention, when the planet wheel modulus is less than or equal to 1, the dislocation angle of the first gear and the second gear is 0.2-0.5 degrees; when the planet wheel modulus is larger than 1, the dislocation angle of the first gear and the second gear is 0.2-1.0 degrees.
As an improved scheme of the invention, the whole pin shaft is of a flat square structure with two radial sides symmetrically cut into planes, the other two sides are of round surface structures, the outer side surface of the transition sleeve is matched with the inner hole of the planet wheel to form a round surface, the inner hole is correspondingly matched with the flat square structure of the pin shaft to form a flat square, and the inner hole is matched with the round surface structure of the pin shaft to form a round.
As an improved scheme of the invention, the pin shaft is step-shaped, two ends of the pin shaft are cylinders and are respectively connected and matched with the output shaft tray and the planet wheel retainer ring, two radial sides of the middle part of the pin shaft are symmetrically cut into flat squares, the outer side surface of the transition sleeve is matched with an inner hole of the planet wheel to form a circular surface, and the inner hole is correspondingly matched with the middle part of the pin shaft.
Has the advantages that: 1. the invention can use the conventional precision grade, namely 7 grades of gears to assemble the speed reducer; the planet wheel in the structure adopts the cylindrical straight gear with single-piece staggered teeth, can move radially along the end face direction of the tray, can adjust the radial meshing gap of the gear by adjusting the size of the sun gear, ensures small back gap, and can reach 3-10 arc minutes of the actual back gap of the loader.
2. The back clearance generated by the increase of the meshing clearance caused by the abrasion of the gear is enlarged, the radial meshing clearance of the gear can still be adjusted by changing a large sun gear, and the small back clearance is ensured, so that the scrapping of the speed reducer is avoided, and the cost is saved.
Drawings
FIG. 1 is a general view of a cross-sectional structure of the present invention;
FIG. 2 is a cross-sectional view of section A-A, B-B of FIG. 1;
FIG. 3 is a schematic view of the axially displaced gears meshing with other gears;
fig. 4 is a schematic view of a planet gear of the present invention;
FIG. 5 is a schematic view of a pin of the present invention;
FIG. 6 is a schematic view of a transition sleeve of the present invention;
in the figure: 1-an output shaft; 2-output shaft flat key; 3-elastic retainer ring for shaft; 4-a first deep groove ball bearing; 5-an output end cover; 6-elastic check ring for first hole; 7-a positioning pin; 8-inner gear ring; 9-a planet wheel; 901-a first gear; 902-a second gear; 10-a transition sleeve; 11-a pin shaft; 12-a sun gear; 13-a planet wheel collar; 14-countersunk head screws; 15-circlip for second hole; 16-axle steel wire retainer ring; 17-a second deep groove ball bearing; 18-O-ring seals; 19-input end cap; 20-motor spindle connecting sleeve; 21-output shaft tray.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1, a planetary reducer with a single planetary gear and a staggered tooth back clearance adjustable is characterized in that an output end cover 5, an inner gear ring 8 and an input end cover 19 are coaxially connected to form a closed cavity, a primary planetary gear transmission gear pair is arranged in the cavity, and the gear pair comprises a sun gear 12 and at least two planetary gears 9.
The peripheral outer side walls of the input end cover 19 and the output end cover 5 are respectively provided with a step structure, the step structures are arranged in the inner gear ring 8, the output end cover 5 is fixed with the inner gear ring 8 by adopting a radially arranged positioning pin 7, and the input end cover 19 is fixed with the inner gear ring 8 by adopting a radially arranged countersunk head screw 14.
The sun gear 12 is coaxially connected and fixed on a motor main shaft connecting sleeve 20, and the motor main shaft connecting sleeve 20 is coaxially and rotatably connected with the input end cover 19. Specifically, the sun gear 12 is press-fitted into the motor spindle connecting sleeve 20 by interference, the motor spindle connecting sleeve 20 is fitted into the input end cover 19 and connected to the input end cover 19 through the second deep groove ball bearing 17, the second deep groove ball bearing 17 is fixed by the second hole circlip 15 and the shaft steel wire retainer ring 16, and the O-ring 18 is provided between the second deep groove ball bearing 17 and the motor spindle connecting sleeve 20.
A transition sleeve 10 is arranged in an inner hole of the planet wheel 9, a pin shaft 11 is arranged in the transition sleeve 10, one end of the pin shaft 11 is in interference fit with a corresponding shaft hole on the output shaft tray 21, and the other end of the pin shaft is limited by a planet wheel retainer ring 13. The output shaft tray 21 is coaxially arranged between the output end cover 5 and the planet wheel 9, the output shaft 1 is fixedly connected with the output shaft tray 21, the first deep groove ball bearing 4 is coaxially arranged between the output shaft 1 and the output end cover 5, and the elastic retainer ring 3 for the shaft and the elastic retainer ring 6 for the first hole are adopted for limiting.
As an embodiment, as shown in fig. 5 to 6, the pin 11 as a whole has a flat square structure in which two radial sides are symmetrically cut into planes, and the other two sides are circular structures, the outer side surface of the transition sleeve 10 is matched with the inner hole of the planet wheel 9 to form a circular surface, the inner hole is correspondingly matched with the flat square structure of the pin 11 to form a flat square, and the inner hole is correspondingly matched with the circular structure of the pin 11 to form a circular shape. When installed, the axis of the pin 11 is parallel to the axis of the output shaft tray 21.
As another embodiment, the pin shaft 11 is step-shaped, two ends of the pin shaft are cylindrical and are respectively connected and matched with the output shaft tray 21 and the planet wheel retainer ring 13, two radial sides of the middle part are symmetrically cut into planes which are flat and square structures, the other two sides are circular structures, the outer side surface of the transition sleeve 10 is matched with the inner hole of the planet wheel 9 to form a circular surface, and the inner side of the transition sleeve is correspondingly matched with the middle part of the pin shaft 11 to prevent the pin shaft 11 from being worn too fast and influencing the back clearance precision of the planetary reducer.
As shown in fig. 2, the number of the planet wheels 9 is 3, which is a conventional design, and theoretically, 2 to several planet wheels can be adopted according to actual requirements.
As shown in fig. 3-4, the sun gear 12 and the inner gear ring 8 both adopt involute cylindrical spur gears, and the planet gear 9 adopts an involute single-piece staggered tooth cylindrical gear. Specifically, the planet gear 9 includes a first gear 901 and a second gear 902 which are coaxially connected and have the same parameters, the first gear 901 and the second gear 902 are arranged in a staggered manner, and the tooth surfaces of the first gear 901 and the second gear 902 are respectively in contact with the tooth surfaces on both sides of the teeth of the sun gear 12 and the tooth surfaces on both sides of the teeth of the ring gear 8. Specifically, the tooth surfaces of the teeth of the first gear 902 contact one side tooth surface of the teeth of the sun gear 12 and one side tooth surface of the teeth of the ring gear 8, and the tooth surfaces of the teeth of the second gear 902 contact the other side tooth surface of the teeth of the sun gear 12 and the other side tooth surface of the teeth of the ring gear 8.
Such as the enlarged view at N1 shown in fig. 3, where the right tooth face of the second gear 902 contacts the left tooth face of the teeth of the ring gear 8 and the left tooth face of the first gear 901 contacts the right tooth face of the teeth. As shown in the enlarged view at N2, the left tooth surface of the second gear 902 contacts the right tooth surface of the tooth of the sun gear 12, and the right tooth surface of the first gear 901 contacts the left tooth surface of the tooth of the sun gear 12.
The design principle of the invention is that on the basis of the meshing of a pair of spur gears, the single face of a first gear 902 is meshed with the tooth surface of one side of a sun gear 12 and an inner gear ring 8, a second gear 902 is meshed with the tooth surface of the other side to form forward and reverse rotation, no gap is generated, or the gap is small, the first gear 901 is only in single-face contact with the second gear 902, and the problem of small-gap jamming is avoided.
The single-piece staggered tooth planet wheel is a gear which is staggered in a segmented mode, the staggered angle of the processed gear cannot be changed, the structure utilizes the staggered gear single-face contact small return stroke principle to adjust the meshing center distance of the gear, so that the meshing gap of a planetary reducer gear is adjusted, the small back gap is ensured, the non-adjustment staggered angle ensures the small back gap, and the planet wheel can slightly move along the radial direction of a planet carrier, so that the round structure of a pin shaft 11 is in clearance fit with the round inner hole of a transition sleeve 10, the meshing center distance of the gear can be adjusted, the size of the meshing gap of the gear is determined by a sun wheel, the staggered gear is adopted to avoid the defects that the gap of a conventional gear is small, double-face friction and easy clamping, and in the use process, the back gap is increased due to abrasion, and the small back gap.
As shown in fig. 4, the planet wheel is in an overall front-rear section staggered tooth shape, the size of a front-rear staggered angle is related to the size of a gear module, and when the module of the planet wheel 9 is less than or equal to 1, the staggered angle between a first gear 901 and a second gear 902 is 0.2-0.5 degrees; when the modulus of the planet wheel 9 is greater than 1, the dislocation angle between the first gear 901 and the second gear 902 is 0.2-1.0 degrees.
The following data are calculated for the reduction ratio in this embodiment.
The parameters of the inner gear ring 8 are as follows: number of teeth: zb 48; modulus: m is 1; pressure angle: a is 20.
The sun gear 12 parameters are: number of teeth: za ═ 16; modulus: m is 1; pressure angle: a is 20.
The parameters of the planet wheel 9 are as follows: number of teeth: zc 15; modulus: m is 1; pressure angle: a is 20.
iab＝Zb/Za+1＝48/16+1＝4
The transmission ratio is therefore 4.
The invention adopts a single-piece staggered tooth cylindrical planet wheel, the planet wheel moves along the end surface of a planet carrier tray in the radial direction, and the meshing clearance of a gear pair is adjusted by adjusting the size of a sun wheel, so that the small back clearance or zero back clearance in operation is ensured, the reducer is prevented from being jammed due to the small back clearance, the back clearance value of the assembled reducer reaches within 5 arc minutes under the precision of a conventional gear (generally 7-grade precision), and the level of a precision reducer is reached. Meanwhile, in the use process of the speed reducer, the back clearance is increased, the sun gear with the increased size is replaced and readjusted, the back clearance precision of a new speed reducer can be achieved, and the service life of the speed reducer is prolonged.
Although the present description is described in terms of embodiments, not every embodiment includes only a single embodiment, and such description is for clarity only, and those skilled in the art should be able to integrate the description as a whole, and the embodiments can be appropriately combined to form other embodiments as will be understood by those skilled in the art.
In the description of the present invention, it should be noted that relational terms such as first and second, and the like, may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
Therefore, the above description is only a preferred embodiment of the present application, and is not intended to limit the scope of the present application; all changes which come within the meaning and range of equivalency of the claims are to be embraced within their scope.
Claims (4)
1. A planet gear single-plate dislocation tooth back clearance adjustable planet reducer is characterized in that an output end cover (5), an inner gear ring (8) and an input end cover (19) are coaxially connected to form a closed cavity, a sun gear (12) and at least two planet gears (9) are arranged in the cavity, the sun gear (12) is coaxially connected and fixed on a motor spindle connecting sleeve (20), and the motor spindle connecting sleeve (20) is coaxially and rotatably connected with the input end cover (19); a transition sleeve (10) is arranged in an inner hole of the planet wheel (9) and is arranged on a pin shaft (11); one end of the pin shaft (11) is in interference fit with a corresponding shaft hole on the output shaft tray (21), and the other end of the pin shaft is limited by a planet wheel retainer ring (13); the transmission mechanism is characterized in that two radial side surfaces of the pin shaft (11) matched with the transition sleeve (10) are of flat square structures, the other two sides of the pin shaft are of round surface structures, the round surface structures are in clearance fit with an inner hole of the transition sleeve (10), and the axis of the pin shaft (11) is parallel to the axis of the output shaft tray (21); the planet gear (9) comprises a first gear (901) and a second gear (902) which are coaxially connected and have the same parameters, and the first gear (901) and the second gear (902) are straight cylindrical gears with gear teeth arranged in a staggered manner; the tooth flanks of the first gear (902) are in contact with one side tooth flanks of the teeth of the sun gear (12) and one side tooth flanks of the teeth of the inner gear ring (8), and the tooth flanks of the second gear (902) are in contact with the other side tooth flanks of the teeth of the sun gear (12) and the other side tooth flanks of the teeth of the inner gear ring (8).
2. The planet gear reducer with the single-plate staggered teeth and the adjustable back clearance of the planet gears as claimed in claim 1, is characterized in that when the module of the planet gears (9) is less than or equal to 1, the staggered angle of the first gear (901) and the second gear (902) is 0.2-0.5 degrees; when the modulus of the planet wheel (9) is larger than 1, the dislocation angle of the first gear (901) and the second gear (902) is 0.2-1.0 degrees.
3. The planet gear single-plate staggered tooth back clearance adjustable planetary reducer according to claim 1 or 2, characterized in that the pin (11) is of a flat square structure with two radial sides symmetrically cut into planes, the other two sides are of circular structures, the outer side surface of the transition sleeve (10) is matched with the inner hole of the planet gear (9) to form a circular surface, the inner hole is correspondingly matched with the flat square structure of the pin (11) to form a flat square, and the outer side surface of the transition sleeve is matched with the circular structure of the pin (11) to form a circular surface.
4. The planet gear single-plate staggered tooth back clearance adjustable planetary reducer according to claim 1 or 2, characterized in that the pin (11) is step-shaped, the two ends of the pin are cylindrical and are respectively connected and matched with the output shaft tray (21) and the planet gear retainer ring (13), the radial two sides of the middle part are symmetrically cut into flat squares, the outer side surface of the transition sleeve (10) is matched with the inner hole of the planet gear (9) to form a circular surface, and the inner side of the transition sleeve is correspondingly matched with the middle part of the pin (11).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011583172.8A CN112648344A (en) | 2020-12-28 | 2020-12-28 | Planet gear single-plate staggered tooth back clearance adjustable planet speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011583172.8A CN112648344A (en) | 2020-12-28 | 2020-12-28 | Planet gear single-plate staggered tooth back clearance adjustable planet speed reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112648344A true CN112648344A (en) | 2021-04-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011583172.8A Pending CN112648344A (en) | 2020-12-28 | 2020-12-28 | Planet gear single-plate staggered tooth back clearance adjustable planet speed reducer |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975248A (en) * | 2010-10-15 | 2011-02-16 | 北京伊贝格机械有限公司 | Backlash planetary retarding mechanism |
| CN202971804U (en) * | 2012-11-28 | 2013-06-05 | 柳州五菱汽车有限责任公司 | Differential mechanism |
| CN104626129A (en) * | 2015-02-10 | 2015-05-20 | 上海巨想机器人科技有限公司 | Five-degree-of-freedom robot tail end transmission mechanism |
| CN108266515A (en) * | 2018-04-05 | 2018-07-10 | 无锡富乐力科技有限公司 | Planetary reduction gear and its assembling structure with motor |
| CN108775383A (en) * | 2018-08-08 | 2018-11-09 | 江苏欧邦电机制造有限公司 | A kind of adjustable precise planet-gear speed reducer |
| WO2018229737A1 (en) * | 2017-06-17 | 2018-12-20 | Genesis Robotics And Motion Technologies Canada, Ulc | Torque amplifier |
| DE102018105604A1 (en) * | 2018-03-12 | 2019-09-12 | Schaeffler Technologies AG & Co. KG | Planet carrier with non-rotating planetary pin; and spur gear differential |
-
2020
- 2020-12-28 CN CN202011583172.8A patent/CN112648344A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975248A (en) * | 2010-10-15 | 2011-02-16 | 北京伊贝格机械有限公司 | Backlash planetary retarding mechanism |
| CN202971804U (en) * | 2012-11-28 | 2013-06-05 | 柳州五菱汽车有限责任公司 | Differential mechanism |
| CN104626129A (en) * | 2015-02-10 | 2015-05-20 | 上海巨想机器人科技有限公司 | Five-degree-of-freedom robot tail end transmission mechanism |
| WO2018229737A1 (en) * | 2017-06-17 | 2018-12-20 | Genesis Robotics And Motion Technologies Canada, Ulc | Torque amplifier |
| DE102018105604A1 (en) * | 2018-03-12 | 2019-09-12 | Schaeffler Technologies AG & Co. KG | Planet carrier with non-rotating planetary pin; and spur gear differential |
| CN108266515A (en) * | 2018-04-05 | 2018-07-10 | 无锡富乐力科技有限公司 | Planetary reduction gear and its assembling structure with motor |
| CN108775383A (en) * | 2018-08-08 | 2018-11-09 | 江苏欧邦电机制造有限公司 | A kind of adjustable precise planet-gear speed reducer |
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