CN102297257A - Planetary gear reducer with adjustable back lash - Google Patents
Planetary gear reducer with adjustable back lash Download PDFInfo
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- CN102297257A CN102297257A CN2011102500126A CN201110250012A CN102297257A CN 102297257 A CN102297257 A CN 102297257A CN 2011102500126 A CN2011102500126 A CN 2011102500126A CN 201110250012 A CN201110250012 A CN 201110250012A CN 102297257 A CN102297257 A CN 102297257A
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- lock dog
- wheel carrier
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- carrier assembly
- planetary wheel
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- 239000003638 chemical reducing agent Substances 0.000 title abstract description 7
- 238000006073 displacement reaction Methods 0.000 claims description 5
- 230000005540 biological transmission Effects 0.000 abstract description 7
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 230000008030 elimination Effects 0.000 description 2
- 238000003379 elimination reaction Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
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Abstract
The invention discloses a planetary gear reducer with an adjustable back lash; an inner gear ring in the reducer is fixed and cannot rotate; the teeth of the planetary gear are respectively meshed with the outer teeth of a sun gear and the inner teeth of the inner gear ring; the planetary gear reducer with the adjustable back lash is characterized in that: a first planetary gear group and a second planetary gear group are respectively arranged in a transmission level; and end surface teeth which are mutually occluded are respectively arranged on a contact surface between a first planetary gear frame component and a lower lock block and the contact surface between a second planetary gear frame component and an upper lock block. According to the invention, the back lash required by the reducer is obtained through differential gear adjustment by simultaneously eliminating gear side spacing as well as the spacing between a shaft and an inner hole of a planetary gear in a clockwise direction and a counterclockwise direction.
Description
Technical field
The present invention relates to the adjustable plane table thermoconductivity meter of planetary pinion transmission, particularly back clearance in the mechanical transmission.
Background technique
In the planetary type gear transmission unit, usually adopt several planet wheels while transmitted loads, make power dividing and reasonably adopted interior engagement, thereby has a series of advantage: as compact structure, volume is little, in light weight, gear range is big, transmission efficiency height, running are steadily, noise is little, can move synthetic with decompose or the like, thereby be widely used in mechanically multiple, as deceleration, speedup and variable speed drive.
One class Gear Planet Transmission is arranged, require the output revolving shaft of Gear Planet Transmission to have counterclockwise and clockwise two kinds of working staties, require the angle return difference of two kinds of working state conversions very little simultaneously, claim little back clearance, zero back clearance transmission again.Back clearance is defined as: input end is fixed, output terminal clockwise and rotation counterclockwise, when making output terminal produce rated torque ± 2% moment of torsion, the speed reducer output terminal has a small angular displacement, this angular displacement is exactly the backhaul gap. and unit is " branch ", is exactly sixtieth once.As actuating motor, stepper motor retarder, be mainly used in the CNC numerical control machine tool, bag machinery, plastics machinery, printing machinery etc.The back clearance of general each grade of involute planetary gearing speed-reducer deceleration is not done requirement, if the back clearance requirement is arranged and be not less than 0.5 °, then is left intact, and only be to reduce the gear engagement sideshake and verify that its meshing backlass gets final product; But if the retarder of the very little back clearance of high-precision requirement (as 10 ' or 5 '), then the machining accuracy of the machining accuracy of gear and planetary wheel carrier must be very high, otherwise can't guarantee the assembling under minimum back lash and the formedness of running.The deficiency of its existence is:
1, the roll flute of high class gear processing, the Cutter Body Processing with Machining Center of highi degree of accuracy planetary wheel carrier, time process-cycle is long, and cost significantly rises.
2, the meshing backlass that causes of gear wear and the increasing of planet wheel and bearing pin matching gap can't solve back clearance at all and become big problem, only scrap.
Summary of the invention
The present invention is for avoiding above-mentioned existing in prior technology deficiency, provide a kind of back clearance adjustable plane table thermoconductivity meter, by adopting two groups of planetary gear set and planetary wheel carrier assembly, eliminate clockwise and anticlockwise backlash, the axle and the gap of planet wheel endoporus simultaneously, again by the desired back clearance of difference tooth adjustment acquisition retarder.
The technological scheme that technical solution problem of the present invention is adopted is:
The adjustable plane table thermoconductivity meter of back clearance of the present invention, ring gear in the described retarder does not rotate for fixing, planetary gear is meshed with the external tooth of sun gear and the internal tooth of ring gear respectively, its structural feature is: be respectively arranged with first planetary gear set and second planetary gear set in a gear stage, be respectively equipped with the end face tooth of mutual interlock on the surface of contact of the surface of contact of the first planetary wheel carrier assembly and following lock dog and the second planetary wheel carrier assembly and last lock dog, described time lock dog and last lock dog are locked by the lock dog pin; Radial ball bearing is contained in the bearing saddle bore, limits radial ball bearing axial displacement with circlip for hole; Screw is fastened on bearing support the endoporus output terminal of described ring gear; Circlip for shaft limits the position of radial ball bearing on the first planetary wheel carrier assembly is axial; Lock screw tightens together the second planetary wheel carrier assembly, time lock dog, last lock dog and the described first planetary wheel carrier assembly.
The structural feature of the adjustable plane table thermoconductivity meter of back clearance of the present invention also is:
There is the end face tooth number of teeth that is provided with on the first planetary wheel carrier assembly of end face tooth of mutual interlock and the following lock dog to be N at described surface of contact; There is the end face tooth number of teeth that is provided with on the second planetary wheel carrier assembly of end face tooth of mutual interlock and the last lock dog to be N+1 at described surface of contact.
Described retarder is double reduction or multi-stage speed-reducing.
Compared with the prior art, beneficial effect of the present invention is embodied in:
1, retarder of the present invention can use the gear assembling complete machine of conventional grade of accuracy (7 grades); This is because each level has two groups of gears, pass through to adjust two groups of gear trains during assembling, guarantee that one group of gear train is at the pin direction elimination meshing backlass of taking advantage of a situation, another group gear train is eliminated meshing backlass in the counterclockwise direction, gear after installing has like this eliminated whole meshing backlasses, and promptly back clearance is " 0 "; The gear meshing sideshake can not turn round for the retarder of " 0 ", obtains needed back clearance by the adjustment of difference tooth again.
2, retarder of the present invention strengthens in the back lash that gear causes because of wearing and tearing when producing the increase of back clearance, can adjust meshing backlass by the difference tooth, obtains very little back clearance again, promptly can recover to improve even the back clearance precision.
Description of drawings
Fig. 1 analyses and observe total figure for structure of the present invention;
Fig. 2 counterclockwise eliminates the gap schematic representation for the present invention;
Fig. 3 eliminates the gap schematic representation for clockwise direction of the present invention;
Fig. 4 is the second planetary wheel carrier assembly left view among the present invention;
Fig. 5 is the second planetary wheel carrier assembly plan view among the present invention;
Fig. 6 is the second planetary wheel carrier assembly plan view among the present invention;
Fig. 7 is the first planetary wheel carrier assembly plan view among the present invention;
Fig. 8 is the second planetary wheel carrier assembly right elevation among the present invention;
Fig. 9 is for going up lock dog, following lock dog and lock dog pin assembly plan view among the present invention;
Figure 10 is for going up lock dog, following lock dog and lock dog pin assembly right elevation among the present invention;
Figure 11 is for going up lock dog, following lock dog and lock dog pin assembly left view among the present invention.
Figure 12 is the adjustable plane table thermoconductivity meter schematic representation of double reduction back clearance of the present invention.
Number in the figure: 1 time lock dog; 2 lock dog pins; Lock dog on 3; 4 second planetary gear set; 5 sun gears; 6 ring gears; 7 first planetary gear set; 8 second planetary wheel carrier assemblies; 9 lock screws; 10 first planetary wheel carrier assemblies; 11 radial ball bearings; 12 circlip for holes; 13 screws; 14 bearing supports; 15 circlips for shaft.
Embodiment
Referring to Fig. 1, present embodiment is a kind of sunlight automatic tracking device retarder.
In concrete the enforcement, the adjustable plane table thermoconductivity meter of back clearance in the present embodiment, ring gear 6 is fixed and is not rotated, planetary gear is meshed with the external tooth of sun gear 5 and the internal tooth of ring gear 6 respectively, in a gear stage, be provided with two groups of planetary gear set, i.e. first planetary gear set 7 and second planetary gear set 4, be respectively equipped with the end face tooth of mutual interlock on the surface of contact of the surface of contact of the first planetary wheel carrier assembly 10 and following lock dog 1 and the second planetary wheel carrier assembly 8 and last lock dog 3, following lock dog 1 is locked by lock dog pin 2 with last lock dog 3; Radial ball bearing 11 is contained in bearing support 14 holes, limits axial displacement with circlip for hole 12; Screw 13 is fastened on ring gear 6 endoporus output terminals with bearing support 14; Circlip for shaft 15 limits radial ball bearings 11 in the position of the first planetary wheel carrier assembly 10 on axially; Lock screw 9 tightens together the second planetary wheel carrier assembly 8, time lock dog 1, last lock dog 3 and the first planetary wheel carrier assembly 10.
The adjustable plane table thermoconductivity meter of back clearance in the present embodiment has the end face tooth of mutual interlock at the first planetary wheel carrier assembly 10 and following lock dog 1 surface of contact, and the identical N that is made as of the number of teeth gets N=80; Then the second planetary wheel carrier assembly 8 and last lock dog 3 surface of contact have the end face tooth of mutual interlock, and the number of teeth is all N+1,80+1=81 mutually;
The design parameter of each part is as follows:
First planetary gear set 7 and second planetary gear set 4 respectively are made up of three gears; The parameter of gear is identical, is:
Modulus m=0.9; Number of teeth z=15; Pressure angle a=25 °;
Modification coefficient x=0.3106;
Public law line length w3=7 (0.04/-0.08);
Sun gear 5 gear parameters:
Modulus m=0.9; Number of teeth z=8; Pressure angle a=25 °;
Modification coefficient x=0.3;
Public law line length w2=4.27 (0.04/-0.08);
Ring gear 6 (one) gear parameter:
Modulus m=0.9; Number of teeth z=40; Pressure angle a=25 °;
Modification coefficient x=-0.0934;
Public law line length w6=15 (0.09/0.04);
Gap between planet wheel endoporus and the bearing pin is 0.04mm (monolateral);
Centre distance 10.85mm;
Back clearance is made up of two-part:
First portion: the meshing backlass between the gear, the sideshake between meshing backlass between sun gear and the planet wheel and planet wheel and the ring gear, through Practical Calculation, it is 0.5385 ° that this two-part sideshake causes back clearance;
Second portion: the back clearance that cause in planet wheel endoporus and bearing pin gap: through being calculated as:
180°*0.04*2/(10.85*π)＝0.2112*2＝0.4224°；
Amount to back clearance=0.4224 °+0.5385 °=0.9610 °;
The adjustment of present embodiment back clearance is finished like this:
Power is from sun gear 5 input: sun gear 5 and ring gear 6 are meshed with first planetary gear set 7 simultaneously, and eliminate 0.41925 ° of the back clearance that clockwise backlash produces; Eliminate axle and 0.2112 ° of the back clearance that the gap produced of planet wheel endoporus simultaneously, as shown in Figure 3.
Power is from sun gear 5 input: sun gear 5 and ring gear 6 are meshed with second planetary gear set 4 simultaneously, and eliminate 0.41925 ° of the back clearance that anticlockwise backlash produces; Eliminate axle and 0.2112 ° of the back clearance that the gap produced of planet wheel endoporus simultaneously, as shown in Figure 2.
Keep to descend under the gap elimination state lock dog 1 and three lock dog pins of last lock dog 3 usefulness, 2 pins dead, as Fig. 9, Figure 10 and shown in Figure 11.
At the first planetary wheel carrier assembly 10 and following lock dog 1 surface of contact the end face tooth of mutual interlock is arranged, as shown in Figure 7 and Figure 8, among Fig. 7 " A " the reference level number of teeth is N=80, the number of teeth of " C " reference level among Fig. 9 is N=80; And the second planetary wheel carrier assembly 8 and last lock dog 3 surface of contact have the end face tooth of mutual interlock equally, and as Fig. 4, Fig. 5 and shown in Figure 6, " B " reference level end face tooth number of teeth among Fig. 4 is N+1=81, and the end face tooth number of teeth of " D " reference level among Fig. 9 is N+1=81; Be that the two number of teeth differs a tooth.Because the first planetary wheel carrier assembly 10 and following lock dog 1 number of teeth of interlock mutually equate to be 80, the second planetary wheel carrier assembly 8 and last lock dog 3 number of teeth of interlock mutually are 81, work as the second planetary wheel carrier assembly 8 so and turning over a transverse pitch clockwise, with respect to lock dog assembly parts up and down, the corner that promptly descends lock dog 1, lock dog pin 2 and last lock dog 3 is 360 °/81; Lock dog assembly parts about the first planetary wheel carrier assembly 10 is equally also turning over a transverse pitch clockwise, and it is relative, the corner that promptly descends lock dog 1, lock dog pin 2 and last lock dog 3 is 360 °/80; The difference of the two corner in the clockwise direction be 360 °/(81*80); This angle is exactly the minimum regulation unit of micro-adjusting mechanism: 360 °/(80*81)=0.0555556 °=3.3 '.
Eliminate all clockwise and counterclockwise behind the gap, carry out mark at the cylindrical of the first planetary wheel carrier assembly 10 and the second planetary wheel carrier assembly 8; Each part is installed in the ring gear 6, the first planetary wheel carrier assembly 10 is adjusted a transverse pitch with respect to last lock dog 3 and following lock dog 1 assembly parts clockwise direction; Simultaneously the second planetary wheel carrier assembly 8 is adjusted a transverse pitch with respect to last lock dog 3 and the same clockwise direction of following lock dog 1 assembly parts, like this, the two has certain relative rotation with respect to before not adjusting a transverse pitch for the first planetary wheel carrier assembly 10 and the second planetary wheel carrier assembly 8.At this moment, first planetary gear set 7 and second planetary gear set 4 can in ring gear 6, go slick and guarantee minimum back clearance about 3.33 ', also can adjust two end face teeth simultaneously, so back clearance will become 2*3.33 '=6.66 '; Last locked lock screw 9.
When the tooth thickness wear that gear occurs and planet wheel cooperate wearing and tearing and when causing back clearance to become can not to satisfy usage requirement greatly with bearing pin, lock screw 9 can be unclamped, the first planetary wheel carrier assembly 10 and the second planetary wheel carrier assembly 8 are eliminated a certain amount of back clearance with the certain relative rotation of rotation direction adjustment again, it is turned round under the back clearance that is fit to, prolong the working life of retarder and the workmanship of raising retarder.
Figure 12 shows that the adjustable plane table thermoconductivity meter schematic representation of double reduction back clearance; Same principle also can be designed to the multi-stage speed-reducing retarder.
Claims (3)
1. adjustable plane table thermoconductivity meter of back clearance, ring gear in the described retarder (6) does not rotate for fixing, planetary gear is meshed with the external tooth of sun gear (5) and the internal tooth of ring gear (6) respectively, it is characterized in that: in a gear stage, be respectively arranged with first planetary gear set (7) and second planetary gear set (4), be respectively equipped with the end face tooth of mutual interlock on the surface of contact of the surface of contact of the first planetary wheel carrier assembly (10) and following lock dog (1) and the second planetary wheel carrier assembly (8) and last lock dog (3), described lock dog (1) down and last lock dog (3) are locked by lock dog pin (2); Radial ball bearing (11) is contained in the bearing saddle bore, limits radial ball bearing (11) axial displacement with circlip for hole (12); Screw (13) is fastened on bearing support (14) the endoporus output terminal of described ring gear (6); Circlip for shaft (15) limits the position of radial ball bearing (11) on the first planetary wheel carrier assembly (10) is axial; Lock screw (9) tightens together the second planetary wheel carrier assembly (8), time lock dog (1), last lock dog (3) with the described first planetary wheel carrier assembly (10).
2. the adjustable plane table thermoconductivity meter of back clearance according to claim 1 is characterized in that: have the first planetary wheel carrier assembly (10) and the last end face tooth number of teeth that is provided with of following lock dog (1) of the end face tooth of mutual interlock to be N at described surface of contact; There are the second planetary wheel carrier assembly (8) and the last end face tooth number of teeth that is provided with of last lock dog (3) of the end face tooth of mutual interlock to be N+1 at described surface of contact.
3. the adjustable plane table thermoconductivity meter of back clearance according to claim 1 and 2 is characterized in that described retarder is double reduction or multi-stage speed-reducing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110250012 CN102297257B (en) | 2011-08-26 | 2011-08-26 | Planetary gear reducer with adjustable back lash |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110250012 CN102297257B (en) | 2011-08-26 | 2011-08-26 | Planetary gear reducer with adjustable back lash |
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| CN102297257A true CN102297257A (en) | 2011-12-28 |
| CN102297257B CN102297257B (en) | 2013-06-12 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927207A (en) * | 2012-11-05 | 2013-02-13 | 合肥波林新材料有限公司 | Zero back clearance planetary transmission speed reducing device |
| CN103277500A (en) * | 2013-04-11 | 2013-09-04 | 宁波海天精工股份有限公司 | Gap eliminating method of gear transmission device |
| TWI452218B (en) * | 2012-02-07 | 2014-09-11 | Nat Univ Chung Cheng | No backlash gear structure |
| CN105351449A (en) * | 2015-12-16 | 2016-02-24 | 湖南机油泵股份有限公司 | Planetary transmission structure |
| CN105508585A (en) * | 2016-01-20 | 2016-04-20 | 湖北科峰传动设备有限公司 | Gap-eliminating planetary speed reducer |
| CN108061146A (en) * | 2016-11-09 | 2018-05-22 | 何汉权 | A kind of small size big retarding ratio is without back clearance retarder |
| CN111520456A (en) * | 2020-04-29 | 2020-08-11 | 浙江大学昆山创新中心 | Intelligent speed reducer |
| CN113404820A (en) * | 2021-06-29 | 2021-09-17 | 重庆大学 | Adjustable-gap multi-crank variable-tooth-thickness precision transmission device |
| CN115370441A (en) * | 2021-05-18 | 2022-11-22 | 博格华纳公司 | Electrically actuated camshaft phaser with reduced backlash |
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| CN202170990U (en) * | 2011-08-26 | 2012-03-21 | 合肥波林新材料有限公司 | Adjustable-back-gap planetary gear decelerator |
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2011
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| JPH02283939A (en) * | 1989-04-25 | 1990-11-21 | Harmonic Drive Syst Ind Co Ltd | Planetary gear device with backlash adjusting mechanism |
| JP3550583B2 (en) * | 1994-11-04 | 2004-08-04 | 株式会社ニコン | Microscope coarse and fine focusing device |
| EP1171341B1 (en) * | 1998-06-25 | 2004-06-23 | Aimbridge Pty. Ltd. | A motor for driving a propeller including a phase adjuster for altering the pitch of the propeller blades |
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| DE102008035114A1 (en) * | 2008-07-28 | 2010-02-04 | Magna Powertrain Ag & Co Kg | Low-backlash planetary gear has ring gear with conical toothing and another ring gear with another conical toothing, where former ring gear is arranged adjacent to latter ring gear |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI452218B (en) * | 2012-02-07 | 2014-09-11 | Nat Univ Chung Cheng | No backlash gear structure |
| CN102927207A (en) * | 2012-11-05 | 2013-02-13 | 合肥波林新材料有限公司 | Zero back clearance planetary transmission speed reducing device |
| CN102927207B (en) * | 2012-11-05 | 2015-08-05 | 合肥波林新材料有限公司 | A kind of zero back clearance planetary transmission speed reducer |
| CN103277500A (en) * | 2013-04-11 | 2013-09-04 | 宁波海天精工股份有限公司 | Gap eliminating method of gear transmission device |
| CN103277500B (en) * | 2013-04-11 | 2015-12-09 | 宁波海天精工股份有限公司 | A kind of gap adjusting method that disappears of gear drive |
| CN105351449A (en) * | 2015-12-16 | 2016-02-24 | 湖南机油泵股份有限公司 | Planetary transmission structure |
| CN105508585A (en) * | 2016-01-20 | 2016-04-20 | 湖北科峰传动设备有限公司 | Gap-eliminating planetary speed reducer |
| CN108061146A (en) * | 2016-11-09 | 2018-05-22 | 何汉权 | A kind of small size big retarding ratio is without back clearance retarder |
| CN111520456A (en) * | 2020-04-29 | 2020-08-11 | 浙江大学昆山创新中心 | Intelligent speed reducer |
| CN115370441A (en) * | 2021-05-18 | 2022-11-22 | 博格华纳公司 | Electrically actuated camshaft phaser with reduced backlash |
| US11852053B2 (en) | 2021-05-18 | 2023-12-26 | Borgwarner Inc. | Electrically-actuated camshaft phaser with backlash reduction |
| CN113404820A (en) * | 2021-06-29 | 2021-09-17 | 重庆大学 | Adjustable-gap multi-crank variable-tooth-thickness precision transmission device |
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| CN102297257B (en) | 2013-06-12 |
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Denomination of invention: Planetary gear reducer with adjustable back lash Effective date of registration: 20141021 Granted publication date: 20130612 Pledgee: Huizhou Merchants Bank, Hefei Shuguang Road subbranch Pledgor: Hefei Bolin Advanced Materials Co., Ltd. Registration number: 2014990000875 |
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Date of cancellation: 20151020 Granted publication date: 20130612 Pledgee: Huizhou Merchants Bank, Hefei Shuguang Road subbranch Pledgor: Hefei Bolin Advanced Materials Co., Ltd. Registration number: 2014990000875 |
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Denomination of invention: Planetary gear reducer with adjustable back lash Effective date of registration: 20151022 Granted publication date: 20130612 Pledgee: Huizhou Merchants Bank, Hefei Shuguang Road subbranch Pledgor: Hefei Bolin Advanced Materials Co., Ltd. Registration number: 2015990000900 |
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Address after: 16 No. 230088 Anhui province high tech Zone of Hefei science and Technology Park Bo weir Magnolia Avenue Patentee after: HEFEI BOLIN ADVANCE MATERIALS CO., LTD. Address before: 16 No. 230088 Anhui province high tech Zone of Hefei science and Technology Park Bo weir Magnolia Avenue Patentee before: Hefei Bolin Advanced Materials Co., Ltd. |
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Denomination of invention: Planetary gear reducer with adjustable back lash Effective date of registration: 20161014 Granted publication date: 20130612 Pledgee: Huizhou Merchants Bank, Hefei Shuguang Road subbranch Pledgor: HEFEI BOLIN ADVANCE MATERIALS CO., LTD. Registration number: 2016340000057 |
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