CN203756873U - Planetary difference ring reducer - Google Patents
Planetary difference ring reducer Download PDFInfo
- Publication number
- CN203756873U CN203756873U CN201420046740.4U CN201420046740U CN203756873U CN 203756873 U CN203756873 U CN 203756873U CN 201420046740 U CN201420046740 U CN 201420046740U CN 203756873 U CN203756873 U CN 203756873U
- Authority
- CN
- China
- Prior art keywords
- gear
- ring
- power output
- duplicate
- internal tooth
- 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.)
- Withdrawn - After Issue
Links
Abstract
The utility model discloses a planetary difference ring reducer which comprises a shell and a crankshaft rotatably sleeving the shell. An input end of the crankshaft is connected with a power device, a crank throw of the crankshaft is positioned in the shell, a duplicate gear rotatably sleeves the crank throw of the crankshaft and comprises a first gear and a second gear, the first gear is meshed with internal teeth of an inner gear ring correspondingly and fixedly arranged on the shell, the second gear is meshed with internal teeth of a power output tray, and the power output tray is rotatably arranged on the shell, provided with the internal teeth and connected with an output shaft. The planetary difference ring reducer is small in size, light in weight, stable in transmission, high in transmission efficiency, large in speed ratio, high in bearing capacity, long in service life and particularly applicable to precision equipment such as an industrial robot and numerical control equipment.
Description
Technical field
The utility model relates to retarder field, particularly a kind of planet difference ring retarder.
Background technique
Retarder plays coupling rotating speed and transmitting torque between prime mover and working machine or actuator, retarder is of a great variety at present, conventional has: gear reducer, worm type of reduction gearing, plane table thermoconductivity meter, planetary gear train with a small tooth difference retarder, planet-cycloid reducer, harmonic gear reducer, ball retarder, R-V retarder etc., these retarders respectively have feature, as: the stable drive of gear reducer and worm type of reduction gearing, working life is good, but volume is large, weight is large; The volume of plane table thermoconductivity meter is little, lightweight, stable drive, long service life but its single staged transmission ratio is little; The volume of the capable amount gearing speed-reducer of involute less tooth difference is little, lightweight, and kinematic accuracy is high, and single staged transmission ratio is large, but its speed ratio while exceeding 100:1 transmission efficiency low, working life is short; Planet-cycloid reducer volume is little, lightweight, and single staged transmission ratio is large, but it is high to maintenance technique requirement, price; The single staged transmission ratio of harmonic gear reducer is very large, and kinematic accuracy is high, and volume is little, lightweight, but it easily produces fatigue damage, and working life is not long; The volume of ball retarder is little, lightweight, kinematic accuracy is high, but its bearing capacity is low.And these retarders are except the single-stage scooter 5000:1 of harmonic gear reducer, other retarder single-stage ratio coverage is generally not more than 200:1, but is difficult to drop into practical application because of the easy fatigue damage of harmonic gear reducer; Other retarders need multi-stage serial connection to get up could to realize in the application of large speed ratio and super large speed ratio, at this moment the volume and weight of retarder has all become greatly, and transmission accuracy and bearing capacity will be affected, therefore these retarders are not suitable at some and require will the try one's best little and exigent field of transmission accuracy and bearing capacity of the volume and weight of retarder.
For above-mentioned technological deficiency, be still necessary to invent a kind of volume little, lightweight, stable drive, bearing capacity is high, simultaneously the retarder of the large and long service life of single-stage speed ratio.
Model utility content
The utility model can not meet in order to overcome existing retarder the technological deficiency that single-stage speed ratio is large and body kind is little, lightweight, bearing capacity is high and the life-span is long simultaneously, invent a kind of planet difference ring retarder, it has, and compact structure, volume are little, lightweight, stable drive, and transmission efficiency is high, speed ratio is large, bearing capacity is high and the advantage such as long service life.
For solving the problems of the technologies described above, the utility model adopts following technological scheme:
A kind of planet difference ring retarder, it comprises:
Housing and one is with the bent axle that the mode that can rotate is sheathed on described housing and input end is connected with power plant, and the crank throw of described bent axle is positioned at described housing; On the crank throw of described bent axle, be arranged with duplicate gear in the mode that can rotate, described duplicate gear comprises the first gear and the second gear; Described the first gear is meshed with the corresponding internal tooth that is fixedly installed on the ring gear on described housing; And described the second gear is arranged on described housing and the internal tooth that is provided with the power output disc of internal tooth is meshed with one in the mode that can rotate, and described power output disc is connected with output shaft.
Preferably, described housing comprises two end caps that relatively distribute;
Described bent axle is two-throw crank shaft, and its two ends are sheathed on described two end caps in the mode that can rotate respectively, and its input end extends outside end cap; Two crank phases of described two-throw crank shaft differ from 180
°, and described two cranks are between described two end caps;
Accordingly, on described two cranks, be arranged with two described duplicate gears in the mode that can rotate respectively, and the second gear of described two duplicate gears lays respectively at the one end away from described two end caps;
Accordingly, described ring gear is two and is fixedly installed on respectively on described two end caps, and the first gear of described two duplicate gears engages with the internal tooth of described two ring gears respectively;
The internal surface of described power output disc middle part is provided with internal tooth to engage with the second gear of described two duplicate gears accordingly, and the internal surface two ends of described power output disc are sheathed on respectively on the outer surface of described two ring gears or described two end caps in the mode that can rotate.
Preferably, described two-throw crank shaft two ends are sheathed on described two end caps in the mode that can rotate by two clutch shaft bearings respectively; Described two duplicate gears are sheathed in the mode that can rotate on described two cranks of described two-throw crank shaft by two the second bearings respectively; Described power output disc internal surface two ends are sheathed on respectively on the outer surface of described two ring gears in the mode that can rotate by two the 3rd bearings.
Preferably, described clutch shaft bearing is deep groove ball bearing; Described the second bearing is needle bearing; Described the 3rd bearing is needle bearing.
Preferably, the external diameter of described second gear of described duplicate gear is greater than the external diameter of described the first gear.
Preferably, the outer surface of described power output disc is provided with flange plate and is connected to realize power output with output shaft to facilitate.
Preferably, described the first gear and described the second gear are involute gear, and the internal tooth of described ring gear and described power output disc is involute gear accordingly.
Preferably, described the first gear and described the second gear are cycloidal gear, and the internal tooth of described ring gear and described power output disc is pinwheel accordingly.
Preferably, the modulus of described the first gear and described the second gear is identical, and the few tooth of the number of teeth of the second gear described in the gear ratio of described the first gear.
Preferably, the few tooth of the internal tooth number of teeth of power output disc described in the internal tooth gear ratio of described ring gear.
The utility model compared with prior art, has following beneficial effect:
1, a kind of planet difference ring of the utility model retarder drives duplicate gear revolution by bent axle, and duplicate gear is carried out rotation and rotates by the second gear driven power output disc under the effect of ring gear by the first gear, thereby realize the object of slowing down, its compact structure, volume is little, lightweight, bearing capacity is high, and transmission efficiency is high, stable drive, kinematic accuracy is high, long service life.
2, the further advantage of the utility model is to select flexibly different dentations to coordinate, available involute gear, also can use cycloidal-pin wheel, can also adopt the gear of other profile of tooth, as long as any tooth-profile of gear of engagement Gear Planet Transmission principle can in meeting, wherein particularly adopt cycloidal-pin wheel can obtain larger ratio coverage, and compact structure also keep higher kinematic accuracy and working life.
3, the utility model further advantage be compared with existing retarder, under identical velocity ratio condition, the volume and weight of planet difference ring retarder is less, particularly its needs single-stage speed reducing just can be realized high transmission ratio, is specially adapted to the precision equipment such as industrial robot and numerical control device.
4, the utility model further advantage be the external diameter of the second gear than the external diameter of the first gear greatly to facilitate it to engage with the internal tooth of power output disc, compact overall structure is reasonable, easy to install.
Brief description of the drawings
Accompanying drawing 1 is a kind of planet difference ring of the utility model reducer structure schematic diagram;
Accompanying drawing 2 is principle schematic of the present utility model;
Wherein:
1, two-throw crank shaft; 11, input end; 12, crank throw;
2, clutch shaft bearing;
3, the second bearing;
4, duplicate gear; 41, the second gear; 42, the first gear;
5, the 3rd bearing;
6, power output disc; 61 flange plate;
7, ring gear;
8, end cap.
Embodiment
Further describe the utility model referring to accompanying drawing and in conjunction with embodiment, to make those skilled in the art can implement according to this with reference to specification word, but be to be understood that protection domain of the present utility model is not subject to the restriction of embodiment.It will be appreciated that, mentioned in following mode of execution of the present utility model " on ", D score, " left side ", " right side " be all taking the direction shown in each figure as benchmark, these words that are used for limiting direction are only used to be convenient to explanation, do not represent the restriction to the concrete technological scheme of the utility model.
Embodiment 1
As shown in Figure 1, a kind of planet difference ring retarder, it comprises: end cap 8, two-throw crank shaft 1, duplicate gear 4, ring gear 7 and power output disc 6, wherein:
The annular mounting platform that end cap 8 one sides are provided with outside projection is for clutch shaft bearing 2 and ring gear 7 are installed, and end cap 8 is that two and left and right distribute relatively, and the mounting platform of left side end cap 8 is to right-hand projection, the projection to the left of the mounting platform of right side end cap 8.
The mounting platform inside circumferential surface of the end cap 8 of the left and right sides is separately installed with two clutch shaft bearings 2, clutch shaft bearing 2 is deep groove ball bearing, two-throw crank shaft 1 two ends, left and right are sheathed on respectively the inner ring of two clutch shaft bearings 2 in left and right rotating with respect to two of left and right end cap 8, the left end of two-throw crank shaft 1 is input end 11, this end stretches out in the left of left side end cap 8, and input end 11 is for being connected with power plant.Two of the left and right crank 12 of two-throw crank shaft 1 is between two end caps 8, and the phase difference 180 of two cranks
°so that two-throw crank shaft 1 keeps balance in rotation process.
On two of the left and right crank 12 of two-throw crank shaft 1, be separately installed with two the second bearings 3, the second bearing 3 is needle bearing, and on the outer ring of two the second bearings 3, be arranged with respectively two duplicate gears 4 so that two duplicate gears 4 can rotate with respect to two cranks 12 respectively, meanwhile, two duplicate gears 4 can rotate together along with two-throw crank shaft 1.Duplicate gear 4 comprises the first gear 42 and the second gear 41, wherein the modulus of the first gear 42 and the second gear 41 can be the same or different, the present embodiment preferably external diameter of the first gear 42 is less than the external diameter of the second gear 41, when both moduluses are designed to when identical, the number of teeth of the second gear 41 is more than the number of teeth of the first gear 42, and now the external diameter of the second gear 41 is just greater than the external diameter of the first gear 42.The duplicate gear 4 of the left and right sides distributes relatively, and wherein the second gear 41 of left side duplicate gear 4 is positioned at right side, and the second gear 41 of right side duplicate gear 4 is positioned at left side.
The internal tooth of ring gear 7 is only arranged at a side of its inner circumferential surface, ring gear 7 is two and is fixedly installed in without a side of profile of tooth on the mounting platform outer circumference surface of left and right sides end cap 8 by its inner circumferential surface respectively, and the inner circumferential surface of left side ring gear 7 is provided with the mounting platform right side projection of a side direction left side end cap 8 of internal tooth to engage with the first gear 42 of left side duplicate gear 4, the inner circumferential surface of right side ring gear 7 is provided with the mounting platform left side projection of a side direction right side end cap 8 of internal tooth to engage with the first gear 42 of right side duplicate gear 4.In the time rotating under the driving of two-throw crank shaft 1 at power plant, two duplicate gears 4 are made revolution motion under the effect of two-throw crank shaft 1, because ring gear 7 is fixed on end cap 8, two duplicate gears 4, in revolution, are made spinning motion around corresponding crank 12 by the first gear 42 respectively with the engagement of ring gear 7.
On the excircle of two ring gears 7 in left and right, being separately installed with two the 3rd bearing 5, the three bearings 5 is needle bearing.Power output disc 6 is cylindric, its inner circumferential surface left and right sides be sheathed on respectively left and right two the 3rd bearings 5 outer ring on so that power output disc 6 can rotate around two ring gears 7, and the middle part of power output disc 6 inner circumferential surfaces is provided with internal tooth, the left and right sides of its internal tooth engages to rotate under the driving at the second gear 41 with the second gear 41 of two duplicate gears 4 in left and right respectively, because the external diameter of the first gear 42 is less than the external diameter of the second gear 41, so not needing to extend internally too much, just can engage with the second gear 41 internal tooth of power output disc 6, compact overall structure is reasonable, easy to install.The first gear 42 of the present utility model and the second gear 41 can be involute gear, the internal tooth of ring gear 7 and power output disc 6 is involute gear accordingly, the first gear 42 and the second gear 41 can be also cycloidal gear, the internal tooth of ring gear 7 and power output disc 6 is pinwheel accordingly, the first gear 42 and the second gear 41 can also be other gears that can meet interior engagement Gear Planet Transmission principle, and the internal tooth of ring gear 7 and power output disc 6 matches with it accordingly.On the external peripheral surface of power output disc 6, being provided with flange plate 61 is connected with outputting power to facilitate by coupling and output shaft (figure depending on) or other output units.
As shown in Figure 2, it is principle schematic of the present utility model, establishes: the standard pitch diameter of the first gear 42 of duplicate gear 4 is d
1, modulus is m
1, the number of teeth is z
1, the standard pitch diameter of the second gear 41 is d
2, modulus is m
2, the number of teeth is z
2, and z
2be greater than z
1; The standard pitch diameter of ring gear 7 is d
3, the internal tooth number of teeth of ring gear 7 is z
3, because it engages with the first gear 42 of duplicate gear 4, for meeting meshing condition, the modulus of ring gear 7 is identical with the modulus of the first gear 42, therefore the modulus of ring gear 7 is m
1; The standard pitch diameter of the internal tooth of power output disc 6 is d
4, the number of teeth is z
4, for meeting second gear 41 meshing conditions of internal tooth and duplicate gear 4 of power output disc 6, therefore the modulus of its internal tooth is the m identical with the second gear 41 moduluses
2.
So have:
d
1=m
1z
1
d
2=m
2z
2
d
3=m
1z
3
d
4=m
2z
4
When two-throw crank shaft 1 revolves while turning around, duplicate gear 4 is along with two-throw crank shaft 1 public affairs turn around, and carries out spinning motion under the engagement of the first gear 42 and ring gear 7 simultaneously, and the number of turns of its rotation is:
So, the circular arc length that the standard pitch circle of the second gear 41 of duplicate gear 4 rolls because of the resultant motion of revolution and rotation is:
L'
2=nπd
2=πnm
1z
2
And the internal tooth standard pitch circle girth of the power output disc 6 engaging with the second gear 41 in duplicate gear 4 is:
L
4=πd
4=πm
2z
4
The circumferential distance of supposing the standard pitch circle rotation of power output disc 6 is s, and during according to the internal tooth of power output disc 6 and the second gear 41 normal gear motion, the principle of the tangent pure rolling of two standard pitch circles can obtain:
L'
2=L
4+s
So when two-throw crank shaft 1 revolves while turning around, the circumferential distance of the standard pitch circle rotation of power output disc 6 is s, namely when revolving power output disc 6 while turning around, rotates two-throw crank shaft 1
circle.The velocity ratio that therefore can obtain planet difference ring retarder is:
Obtained by formula above:
s=L'
2－L
4
Substitution velocity ratio formula obtains
In formula, "-" number expression output turns to contrary with input redirect.When the each parameter of design meets the following conditions: m
1z
2z
3-m
2z
1z
4≠ 0, and i is greater than at 1 o'clock, just can reach the effect of deceleration.
When by canonical parameter design gear, can obtain velocity ratio is that 20:1 is to more than 30000:1, if while pressing nonstandard parameter designing gear, can obtain in theory almost infinitely-great velocity ratio.
As: the first gear 42 and second gear 41 of duplicate gear adopt involute gear, work as m
1=m
2, z
1=13, z
2=14, z
3=39, z
4=40 o'clock, substitution velocity ratio formula can obtain: i=20.
The first gear 42 and second gear 41 of duplicate gear adopt cycloidal gear, work as m
1=m
2, z
1=173, z
2=174, z
3=174, z
4=175 o'clock, substitution velocity ratio formula can obtain: i=30275.
It should be noted that in the time that the first gear 42 of duplicate gear and the second gear 41 adopt involute gear z
2with z
3should not equate or differ should be not very little, if equate, pressure angle is not 20 ° of standard, but exceed 50 °, the radial pressure of planet duplicate gear becomes very large in this case, bearing easily damages, compact structure when the first gear 42 of duplicate gear and the second gear 41 adopt involute gear and be applicable to the occasion that speed ratio is relatively lower.In the time that the first gear 42 of duplicate gear and the second gear 41 adopt cycloidal gear, can obtain larger ratio coverage, and compact structure can keep higher kinematic accuracy and working life, but z
2with z
3should equate as far as possible or differ can not be too large, otherwise structure is compact not, and the utility model is z preferably
2with z
3equate.
In addition, preferably the first gear 42 modulus m of duplicate gear of the utility model
1modulus m with the second gear 41
2identical, the number of teeth z of the first gear 42
1than the number of teeth z of the second gear 41
2a few tooth, simultaneously the internal tooth number of teeth z of ring gear 7
3than the internal tooth number of teeth z of power output disc
4the few tooth of the internal tooth number of teeth, its manufacturing process is relatively simple like this, overall structure is very compact, is specially adapted to the equipment such as industrial robot and accurate digital control.
Embodiment 2
In order to verify the correctness of planet difference ring retarder deceleration principle of the present utility model, specially make a model machine and done the test of being correlated with.While manufacturing and designing, profile of tooth manufactures and designs by standard involute profile, and its parameter is taken as:
m
1=m
2=1.5
z
1=30
z
2=31
z
3=45
z
4=46
The speed ratio of parameter substitution above formula is obtained
Prototype test: pass through the shaft joint drive model machine running of 1:1 as power with the threephase asynchronous of 0.75KW, the data that then record with light electric tachometer are:
Input end revolution is: 1456 revs/min;
Output terminal revolution is: 15.8 revs/min;
Calculate speed ratio:
This result conforms to calculated value, and the error of generation is because the reading of tachometer not accurately causes.Hence one can see that, and deceleration principle of the present utility model is feasible.
In addition, by model machine being tested to discovery, model machine smooth running, vibrates very littlely, and the planet-cycloid reducer on vibratory output and market is suitable, and no-load running does not almost have temperature rise for eight hours.The design output torque of this model machine is 485Nm, if the gear of this retarder adopts cycloidal-pin wheel, can obtain larger bearing capacity.
The utility model both can have been realized less single-stage driving speed ratio, can realize again very large single-stage driving speed ratio, and ensure compact structure simultaneously, volume is little, lightweight, stable drive, transmission efficiency is high, speed ratio is large, and the high long service life of bearing capacity, is particularly useful for the precision equipment such as industrial robot and numerical control device.
Disclosed is above only specific embodiment of the utility model; but; the utility model is not limited thereto; the changes that any person skilled in the art can think of as: crank and duplicate gear etc. that the different or number of teeth of the first gear of the modulus of the first gear and the second gear and the number of teeth of the second gear differ several or other quantity are set are set, all should fall into protection domain of the present utility model.
Claims (10)
1. a planet difference ring retarder, is characterized in that: it comprises:
Housing and one is with the bent axle that the mode that can rotate is sheathed on described housing and input end is connected with power plant, and the crank throw of described bent axle is positioned at described housing; On the crank throw of described bent axle, be arranged with duplicate gear in the mode that can rotate, described duplicate gear comprises the first gear and the second gear; Described the first gear is meshed with the corresponding internal tooth that is fixedly installed on the ring gear on described housing; And described the second gear is arranged on described housing and the internal tooth that is provided with the power output disc of internal tooth is meshed with one in the mode that can rotate, and described power output disc is connected with output shaft.
2. planet difference ring retarder according to claim 1, is characterized in that: described housing comprises two end caps that relatively distribute;
Described bent axle is two-throw crank shaft, and its two ends are sheathed on described two end caps in the mode that can rotate respectively, and its input end extends outside end cap; Two crank phases of described two-throw crank shaft differ from 180
°, and described two cranks are between described two end caps;
Accordingly, on described two cranks, be arranged with two described duplicate gears in the mode that can rotate respectively, and the second gear of described two duplicate gears lays respectively at the one end away from described two end caps;
Accordingly, described ring gear is two and is fixedly installed on respectively on described two end caps, and the first gear of described two duplicate gears engages with the internal tooth of described two ring gears respectively;
The internal surface of described power output disc middle part is provided with internal tooth to engage with the second gear of described two duplicate gears accordingly, and the internal surface two ends of described power output disc are sheathed on respectively on the outer surface of described two ring gears or described two end caps in the mode that can rotate.
3. planet difference ring retarder according to claim 2, is characterized in that: described two-throw crank shaft two ends are sheathed on described two end caps in the mode that can rotate by two clutch shaft bearings respectively; Described two duplicate gears are sheathed in the mode that can rotate on described two cranks of described two-throw crank shaft by two the second bearings respectively; Described power output disc internal surface two ends are sheathed on respectively on the outer surface of described two ring gears in the mode that can rotate by two the 3rd bearings.
4. planet difference ring retarder according to claim 3, is characterized in that: described clutch shaft bearing is deep groove ball bearing; Described the second bearing is needle bearing; Described the 3rd bearing is needle bearing.
5. planet difference ring retarder according to claim 1 and 2, is characterized in that: the external diameter of described second gear of described duplicate gear is greater than the external diameter of described the first gear.
6. planet difference ring retarder according to claim 1 and 2, is characterized in that: the outer surface of described power output disc is provided with flange plate and is connected to realize power output with output shaft to facilitate.
7. planet difference ring retarder according to claim 1 and 2, is characterized in that: described the first gear and described the second gear are involute gear, and the internal tooth of described ring gear and described power output disc is involute gear accordingly.
8. planet difference ring retarder according to claim 1 and 2, is characterized in that: described the first gear and described the second gear are cycloidal gear, and the internal tooth of described ring gear and described power output disc is pinwheel accordingly.
9. planet difference ring retarder according to claim 1 and 2, is characterized in that: the modulus of described the first gear and described the second gear is identical, and the few tooth of the number of teeth of the second gear described in the gear ratio of described the first gear.
10. planet difference ring retarder according to claim 9, is characterized in that: the few tooth of the internal tooth number of teeth of power output disc described in the internal tooth gear ratio of described ring gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420046740.4U CN203756873U (en) | 2014-01-24 | 2014-01-24 | Planetary difference ring reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420046740.4U CN203756873U (en) | 2014-01-24 | 2014-01-24 | Planetary difference ring reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203756873U true CN203756873U (en) | 2014-08-06 |
Family
ID=51252153
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420046740.4U Withdrawn - After Issue CN203756873U (en) | 2014-01-24 | 2014-01-24 | Planetary difference ring reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203756873U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836121A (en) * | 2014-01-24 | 2014-06-04 | 玉林市中创机械有限公司 | Planetary differential ring speed reducer |
-
2014
- 2014-01-24 CN CN201420046740.4U patent/CN203756873U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836121A (en) * | 2014-01-24 | 2014-06-04 | 玉林市中创机械有限公司 | Planetary differential ring speed reducer |
| CN103836121B (en) * | 2014-01-24 | 2016-08-17 | 玉林市中创机械有限公司 | A kind of planet difference ring decelerator |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2119940A4 (en) | Speed reducer and tracking-type solar photovoltaic power generation device | |
| CN103836121A (en) | Planetary differential ring speed reducer | |
| CN203686041U (en) | Precision 2K-V-type speed reducer | |
| CN104482130A (en) | RV reducer comprising constant-depth tooth spiral bevel gear | |
| CN203130928U (en) | RV double-cycloidal-pin-wheel speed reducer | |
| CN107345555A (en) | A kind of RV reductors | |
| CN104121335A (en) | Planetary speed reducer with two planetary gears | |
| US20110092331A1 (en) | Harmonic gear device | |
| CN107355524A (en) | A kind of differential differential speed reducer | |
| CN104534031B (en) | A kind of transmission device for joint of robot | |
| CN207715681U (en) | A kind of harmonic speed reducer | |
| CN203756873U (en) | Planetary difference ring reducer | |
| CN203421121U (en) | High-speed-ratio tooth difference transmission | |
| CN104633062A (en) | Double-cycloidal speed reducer | |
| CN106015501A (en) | Differential gear reducer | |
| CN207569150U (en) | A kind of precision speed reduction device | |
| CN206600418U (en) | New-type wind turbine gearbox mechanical pump transmission connecting structure | |
| CN201925420U (en) | Two-stage planet-gear speed reducer | |
| CN204253749U (en) | The speed reducer of a kind of involute gear and cycloidal gear combination transmission | |
| CN206458785U (en) | A kind of variable paddle speed reducer | |
| CN208951231U (en) | Herringbone curved tooth planetary transmission system | |
| CN200993196Y (en) | Planetary reducer | |
| WO2012088752A1 (en) | High-precision and high-efficiency speed reducer | |
| CN203809637U (en) | Speed reduction device with torsion induction differential planetary gear trains | |
| CN202301771U (en) | Rotary speed reducer of crane |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140806 Effective date of abandoning: 20160817 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |