CN203892473U - Novel planetary gear box - Google Patents
Novel planetary gear box Download PDFInfo
- Publication number
- CN203892473U CN203892473U CN201420256930.9U CN201420256930U CN203892473U CN 203892473 U CN203892473 U CN 203892473U CN 201420256930 U CN201420256930 U CN 201420256930U CN 203892473 U CN203892473 U CN 203892473U
- Authority
- CN
- China
- Prior art keywords
- gear
- driving
- driving mechanism
- planet
- gears
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Abstract
The utility model discloses a novel planetary gear box comprising a box body. A transmission device is arranged in the box body and comprises a planetary reducer, the planetary reducer comprises a first transmission mechanism, a third transmission mechanism and a second transmission mechanism, the second transmission mechanism is connected with the first transmission mechanism and the third transmission mechanism, a motor gear shaft is arranged on one side, away from the second transmission mechanism, of the first transmission mechanism, and an output shaft is arranged on one side, away from the second transmission mechanism, of the third transmission mechanism. By the novel planetary gear box, load uniformity between planetary gears can be ensured, the problem of misalignment or offcenter caused by torsional deflection of planetary carriers is eliminated, transmission ratio of mechanical transmission is increased, and mounting space is saved as duty volume is small.
Description
Technical field
The utility model relates to mechanical transmission fields, relates in particular to a kind of epicyclic gearbox.
Background technique
Epicyclic gearbox is that planetary reduction box is again gear-box, gearbox, and its structure is the mechanism that multiple planetary pinions rotate around a sun gear, is also that transmission speed ratio is reduced, simultaneously again by the mechanism of the proportional increase of motor torsion, apply very extensively, coordinate with motor at first, except for Miniature speed reducing motor, also for sunshade industry office automation, Smart Home, the production automation, medical apparatus, finance machinery, machine tool feeding mechanism, the fields such as gaming machine.Along with the appearance of hand riveter, the application of epicyclic gearbox in hand riveter is also more and more extensive.
A kind of Novel gearbox is disclosed in the invention that is 201210181923.2 in the patent No., comprise: gear-box, main shaft, tapered roller bearing, the first Planetary Gear Transmission level, the second Planetary Gear Transmission level, compliant pin and integrated form compliant pin bearing, described tapered roller bearing is sleeved on the input end of gear-box, described main shaft support is at the gear-box input end of tapered roller bearing, by the power distribution of main shaft, in the first Planetary Gear Transmission level and the second Planetary Gear Transmission level, described compliant pin is sleeved in integrated form compliant pin bearing.By the way, gear-box of the present invention can reduce the contact load of gear, improves transmission stability and the reliability of gear-box.
It is even that above-mentioned epicyclic gearbox has between the planetary pinion of guaranteeing load, and eliminated dual-gripper planet carrier due to misaligning or eccentricity issues that the distortion that twists causes.But the flexibility of the gear teeth is inadequate in the process of transmission, noise and dynamic load are still larger, and velocity ratio can not meet the demand of hand riveter, due to the particularity of hand riveter structure, this epicyclic gearbox degree of matching is not high, should use or exist some problems.Epicyclic gearboxes more of the prior art, person simple in structure often velocity ratio is very low, for example single-stage driving; The high person of velocity ratio but complex structure, volume is comparatively huge, for example three grades of transmissions, level Four transmission.Therefore, between its volume and velocity ratio, be difficult to be optimized simultaneously.
Model utility content
Technical problem to be solved in the utility model is to provide one to be applicable to hand riveter for the above-mentioned state of the art, and compact structure, volume are little, can realize the novel planetary gear-box of more excellent velocity ratio.
For achieving the above object, the utility model provides following technological scheme: a kind of novel planetary gear-box, comprise casing, in described casing, be provided with transmission device, described transmission device comprises the motor gear axle, planetary reduction gear and the output shaft that connect successively, described planetary reduction gear comprises the first driving mechanism, the 3rd driving mechanism and connects the second driving mechanism of the first driving mechanism and the 3rd driving mechanism
Described the first driving mechanism comprises the first planet carrier, the first sun gear and three the first driving gears, described the first planet carrier is along being circumferentially evenly equipped with three the first planet axis and being connected with described the first driving gear by the first planet axis, described the first sun gear is installed on the center of described three the first driving gears and is meshed with three the first driving gears
Described the second driving mechanism comprises the second planet carrier, the second sun gear and three the second driving gears, described the second planet carrier is along being circumferentially evenly equipped with three the second planet axis and being connected with described the second driving gear by the second planet axis, described the second sun gear is installed on the center of described three the second driving gears and is meshed with three the second driving gears
Described the 3rd driving mechanism comprises third planet frame, the 3rd sun gear and three the 3rd driving gears, described third planet frame is along being circumferentially evenly equipped with three third planet axles and being connected with described the 3rd driving gear by third planet axle, described the 3rd sun gear is installed on the center of described three the 3rd driving gears and is meshed with three the 3rd driving gears
Between described the first driving gear, the second driving gear and the 3rd driving gear, be linked, described the first driving mechanism is connected with motor gear axle in the side away from the second driving mechanism, and described the 3rd driving mechanism is connected with output shaft in the side away from the second driving mechanism.
By adopting technique scheme, epicyclic gearboxes more of the prior art, person simple in structure often velocity ratio is very low, for example single-stage driving; The high person of velocity ratio but complex structure, volume is comparatively huge, for example three grades of transmissions, level Four transmission.Therefore, between its volume and velocity ratio, be difficult to be optimized simultaneously.The utility model adopts the mode of three grades of interlocks to carry out transmission, and every grade of driving mechanism all comprises three driving gears, guarantees that between planetary pinion, load is even, and has eliminated planet carrier due to misaligning or eccentricity issues that the distortion that twists causes.Optimized mechanically operated velocity ratio, but to occupy volume little simultaneously, saved space.
As concrete technological scheme of the present utility model, the gear teeth of described the first driving gear, the second driving gear and the 3rd driving gear are crowned teeth.
By adopting technique scheme, bearing and gear can cause certain displacement and rock due to powerful impact force in the process of hand riveter running, cause asymmetric configuration, and in the time that bearing does asymmetric configuration with respect to gear before stand under load, axle is without bending deflection, gear teeth meshing is normal, two pitch cylinders are just tangent, but after stand under load, axle can produce bending deflection, also deflection thereupon just of gear on axle, this just makes to act on load on the flank of tooth along Line of contact skewness, and being arranged to crowned teeth, the gear teeth can improve the degree of load along Line of contact skewness.
The utility model is further set to: the number of teeth of described the second driving gear is 18.
By adopting technique scheme, if ensure, gear-driven centre distance is constant, increases the number of teeth, can increase contact ratio, improve the stationarity of transmission, the utility model is arranged to 18 according to the practical structures of hand riveter and large young pathbreaker's number of teeth, and this number of teeth makes stationary performance access effective guarantee.
The utility model is further set to: the wheel tooth pressure angle of described the second driving gear is 16 °.
By adopting technique scheme, China is 20 ° to general purpose gear transmission specified standard pressure angle, can increase pressure angle in some occasions for strengthening gear-driven flexural strength and contact strength, but increasing pressure angle might not be all favourable to transmission, for the gear of some high speed rotating, pressure angle can strengthen the flexibility of the gear teeth the scope of 16 ° to 18 °, reduce noise and dynamic load, and the utility model is preferably 16 °.
The utility model is further set to: described the first driving gear, the second driving gear and the 3rd driving gear are forged steel gear.
By adopting technique scheme, the dimension precision requirement of the utility model gear mesh transmission is higher, does not allow in the time of processing or heat treatment, to occur very large dimensional changes, and adopts the characteristic of forged steel can just meet the requirement that adds man-hour taking forged steel as material.
Compared with prior art, the utility model has the advantage of: guarantee that between planetary pinion, load is even, and eliminated planet carrier due to misaligning or eccentricity issues that the distortion that twists causes.Improved mechanically operated velocity ratio, but duty volume is little simultaneously, has saved space, the flexible reinforced of the gear teeth, noise and dynamic load are smaller.
Brief description of the drawings
Fig. 1 is the structural representation of transmission device in the utility model embodiment;
Fig. 2 is transmission device explosive view in the utility model embodiment;
Fig. 3 is novel planetary gear box structure schematic diagram in the utility model embodiment.
Reference character: 1, casing; 2, transmission device; 3, motor gear axle; 4, planetary reduction gear; 5, output shaft; 6, the first driving mechanism; 7, the second driving mechanism; 8, the 3rd driving mechanism; 61, the first planet carrier; 62, the first sun gear; 63, the first planet axis; 64, the first driving gear; 71, the second planet carrier; 72, the second sun gear; 73, the second planet axis; 74, the second driving gear; 81, third planet frame; 82, the 3rd sun gear; 83, third planet axle; 84, the 3rd driving gear.
Embodiment
Below in conjunction with accompanying drawing embodiment, novel planetary gear-box of the present utility model is described in further detail.
As shown in Figure 1, Figure 2, Figure 3 shows, a kind of novel planetary gear-box, comprise casing 1, in described casing 1, be provided with transmission device 2, described transmission device 2 comprises the motor gear axle 3, planetary reduction gear 4 and the output shaft 5 that connect successively, due to epicyclic gearboxes more of the prior art, person simple in structure often velocity ratio is very low, for example single-stage driving; The high person of velocity ratio but complex structure, volume is comparatively huge, for example three grades of transmissions, level Four transmission.Therefore, between its volume and velocity ratio, be difficult to be optimized simultaneously.Described planetary reduction gear 4 comprises the first driving mechanism 6, the second driving mechanism 7 of the 3rd driving mechanism 8 and connection the first driving mechanism 6 and the 3rd driving mechanism 8, described the first driving mechanism 6 comprises the first planet carrier 61, the first sun gear 62 and three the first driving gears 64, described the first planet carrier 61 is along being circumferentially evenly equipped with three the first planet axis 63 and being connected with described the first driving gear 64 by the first planet axis 63, described the first sun gear is installed on described three the first driving gear 64 centers and is meshed with three the first driving gears 64, described the second driving mechanism 7 comprises the second planet carrier 71, the second sun gear 72 and three the second driving gears 74, described the second planet carrier 71 is along being circumferentially evenly equipped with three the second planet axis 73 and being connected with described the second driving gear 74 by the second planet axis 73, described the second sun gear 72 is installed on described three the second driving gear 74 centers and is meshed with three the second driving gears 74, described the 3rd driving mechanism 8 comprises third planet frame 81, the 3rd sun gear 82 and three the 3rd driving gears 84, described third planet frame 81 is along being circumferentially evenly equipped with three third planet axles 83 and being connected with described the 3rd driving gear 84 by third planet axle 83, described the 3rd sun gear 82 is installed on described three the 3rd driving gear 84 centers and is meshed with three the 3rd driving gears 84, described the first driving gear 64, between the second driving gear 74 and the 3rd driving gear 84, be linked, described the first driving mechanism 6 is connected with motor gear axle 3 in the side away from the second driving mechanism 7, described the 3rd driving mechanism 8 is connected with output shaft 5 in the side away from the second driving mechanism 7.The utility model adopts the mode of three grades of interlocks to carry out transmission, and every grade of driving mechanism all comprises three driving gears, guarantees that between planetary pinion, load is even, and has eliminated planet carrier due to misaligning or eccentricity issues that the distortion that twists causes.Improved mechanically operated velocity ratio, but to occupy volume little simultaneously, saved space.
As shown in Figure 1, the gear teeth of described the first driving gear 64, the second driving gear 74 and the 3rd driving gear 84 are crowned teeth.Bearing and gear can cause certain displacement and rock due to powerful impact force in the process of hand riveter running, cause asymmetric configuration, and in the time that bearing does asymmetric configuration with respect to gear before stand under load, axle is without bending deflection, gear teeth meshing is normal, two pitch cylinders are just tangent, but after stand under load, axle can produce bending deflection, also deflection thereupon just of gear on axle, this just makes to act on load on the flank of tooth along Line of contact skewness, can improve the degree of load along Line of contact skewness and the gear teeth are arranged to crowned teeth.The number of teeth of described the second driving gear 74 is 18.If ensure, gear-driven centre distance is constant, increases the number of teeth, can increase contact ratio, improve the stationarity of transmission, so the utility model is arranged to 18 according to the practical structures of hand riveter and large young pathbreaker's number of teeth, this number of teeth makes stationary performance access effective guarantee.The wheel tooth pressure angle of described the second driving gear 74 is 16 °.China is 20 ° to general purpose gear transmission specified standard pressure angle, can increase pressure angle in some occasions for strengthening gear-driven flexural strength and contact strength, but increasing pressure angle might not be all favourable to transmission, for the gear of some high speed rotating, pressure angle can strengthen the flexibility of the gear teeth the scope of 16 ° to 18 °, reduce noise and dynamic load, the utility model is preferably 16 °.Because the dimension precision requirement of the utility model gear mesh transmission is higher, do not allow in the time of processing or heat treatment, to occur very large dimensional changes, and adopt the characteristic of forged steel can just meet the requirement that adds man-hour taking forged steel as material.Described the first driving gear 64, the second driving gear 74 and the 3rd driving gear 84 are forged steel gear.
When work, moment is come from 3 transmissions of motor gear axle, by the cooperation of planetary pinion and sun gear, from the first driving mechanism 6, the second driving mechanism 7, successively decrease step by step successively power is delivered to the 3rd driving mechanism 8, and output shaft 5 is connected with third planet frame 81, can from joint obtain slow down moment, realize deceleration object.
The above is only preferred implementation of the present utility model, and protection domain of the present utility model is also not only confined to above-described embodiment, and all technological schemes belonging under the utility model thinking all belong to protection domain of the present utility model.It should be pointed out that for those skilled in the art, in the some improvements and modifications that do not depart under the utility model principle prerequisite, these improvements and modifications also should be considered as protection domain of the present utility model.
Claims (5)
1. a novel planetary gear-box, comprise casing, in described casing, be provided with transmission device, described transmission device comprises the motor gear axle, planetary reduction gear and the output shaft that connect successively, it is characterized in that: described planetary reduction gear comprises the first driving mechanism, the 3rd driving mechanism and connects the second driving mechanism of the first driving mechanism and the 3rd driving mechanism
Described the first driving mechanism comprises the first planet carrier, the first sun gear and three the first driving gears, described the first planet carrier is along being circumferentially evenly equipped with three the first planet axis and being connected with described the first driving gear by the first planet axis, described the first sun gear is installed on the center of described three the first driving gears and is meshed with three the first driving gears
Described the second driving mechanism comprises the second planet carrier, the second sun gear and three the second driving gears, described the second planet carrier is along being circumferentially evenly equipped with three the second planet axis and being connected with described the second driving gear by the second planet axis, described the second sun gear is installed on the center of described three the second driving gears and is meshed with three the second driving gears
Described the 3rd driving mechanism comprises third planet frame, the 3rd sun gear and three the 3rd driving gears, described third planet frame is along being circumferentially evenly equipped with three third planet axles and being connected with described the 3rd driving gear by third planet axle, described the 3rd sun gear is installed on the center of described three the 3rd driving gears and is meshed with three the 3rd driving gears
Between described the first driving gear, the second driving gear and the 3rd driving gear, be linked, described the first driving mechanism is connected with motor gear axle in the side away from the second driving mechanism, and described the 3rd driving mechanism is connected with output shaft in the side away from the second driving mechanism.
2. novel planetary gear-box according to claim 1, is characterized in that: the gear teeth of described the first driving gear, the second driving gear and the 3rd driving gear are crowned teeth.
3. novel planetary gear-box according to claim 2, is characterized in that: the number of teeth of described the second driving gear is 18.
4. novel planetary gear-box according to claim 3, is characterized in that: the wheel tooth pressure angle of described the second driving gear is 16 °.
5. according to the novel planetary gear-box described in arbitrary claim in claim 1 to 4, it is characterized in that: described the first driving gear, the second driving gear and the 3rd driving gear are forged steel gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420256930.9U CN203892473U (en) | 2014-05-20 | 2014-05-20 | Novel planetary gear box |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420256930.9U CN203892473U (en) | 2014-05-20 | 2014-05-20 | Novel planetary gear box |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203892473U true CN203892473U (en) | 2014-10-22 |
Family
ID=51718881
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420256930.9U Expired - Fee Related CN203892473U (en) | 2014-05-20 | 2014-05-20 | Novel planetary gear box |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203892473U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105023503A (en) * | 2015-08-03 | 2015-11-04 | 南京康尼机电股份有限公司 | High precision economic cycloidal pin-wheel reducer for teaching |
| CN105114556A (en) * | 2015-09-10 | 2015-12-02 | 韦兆利 | Planet gear multi-group transmission self-force-increasing device |
| CN105757182A (en) * | 2014-12-16 | 2016-07-13 | 财团法人精密机械研究发展中心 | Hollow planetary reducer |
| CN107152499A (en) * | 2016-03-04 | 2017-09-12 | 德昌电机(深圳)有限公司 | drive device |
| CN107448558A (en) * | 2017-09-18 | 2017-12-08 | 温州赫驰科技有限公司 | A kind of novel variable speed mechanism |
| CN110173556A (en) * | 2019-05-05 | 2019-08-27 | 沙雅钵施然智能农机有限公司 | A kind of power distribution gearbox and cotton picker |
-
2014
- 2014-05-20 CN CN201420256930.9U patent/CN203892473U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105757182A (en) * | 2014-12-16 | 2016-07-13 | 财团法人精密机械研究发展中心 | Hollow planetary reducer |
| CN105023503A (en) * | 2015-08-03 | 2015-11-04 | 南京康尼机电股份有限公司 | High precision economic cycloidal pin-wheel reducer for teaching |
| CN105114556A (en) * | 2015-09-10 | 2015-12-02 | 韦兆利 | Planet gear multi-group transmission self-force-increasing device |
| CN105114556B (en) * | 2015-09-10 | 2017-09-22 | 江苏锡沂高新区科技发展有限公司 | The multigroup transmission self energizing effort device of planetary gear |
| CN107152499A (en) * | 2016-03-04 | 2017-09-12 | 德昌电机(深圳)有限公司 | drive device |
| CN107448558A (en) * | 2017-09-18 | 2017-12-08 | 温州赫驰科技有限公司 | A kind of novel variable speed mechanism |
| CN110173556A (en) * | 2019-05-05 | 2019-08-27 | 沙雅钵施然智能农机有限公司 | A kind of power distribution gearbox and cotton picker |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN203892473U (en) | Novel planetary gear box | |
| CN201125999Y (en) | Gear | |
| CN202251737U (en) | Speed reducer in double-planet structure | |
| CN203560366U (en) | Multistage gear drive device | |
| CN201858308U (en) | Double-helical-teeth planetary speed reducer | |
| CN202628954U (en) | Planetary reducer for large plate bending machine | |
| CN204729551U (en) | A kind of novel bevel gear speed reducer | |
| CN202612486U (en) | Fracturing pump driving device for planetary reduction box | |
| CN208858867U (en) | A kind of straightener overlength double helical tooth distributor box | |
| CN204677695U (en) | A kind of mechanical synchronization speed reducer | |
| CN204755751U (en) | Bevel gear speed reducer with jump ring | |
| CN103267105A (en) | Effort-saving, distance-saving and labor-saving machine | |
| CN208966972U (en) | A kind of built-in planetary speed reducer dipper crowding gear | |
| CN106402351A (en) | Buffer mounting structure of input end of planet gear speed reducer | |
| CN202194997U (en) | Speed reducer for wood working machine | |
| CN206816758U (en) | Two level cycloidal pin teeth planetary reduction gear | |
| CN203656068U (en) | Reduction gearbox structure | |
| CN204512320U (en) | The multistage Involutes Gears Transmission that the multiple kind of drive is formed | |
| CN216045327U (en) | Synchronous gearbox of large high-pressure ball press | |
| CN203962871U (en) | A kind of speed reducer of input output coaxial state band speed ratio | |
| CN209233657U (en) | A kind of transmission mechanism of capstan winch motor | |
| CN203223519U (en) | Double-crank cycloidal pin gear speed reducer | |
| CN203272621U (en) | Gear case for high strength steel plate leveling machine | |
| CN205479159U (en) | Floating planet gear for cylinder | |
| CN203272639U (en) | Gear box for dynamic balancing machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141022 Termination date: 20160520 |