CN201080991Y - Decelerator for controlling electric motor - Google Patents
Decelerator for controlling electric motor Download PDFInfo
- Publication number
- CN201080991Y CN201080991Y CNU2007201879219U CN200720187921U CN201080991Y CN 201080991 Y CN201080991 Y CN 201080991Y CN U2007201879219 U CNU2007201879219 U CN U2007201879219U CN 200720187921 U CN200720187921 U CN 200720187921U CN 201080991 Y CN201080991 Y CN 201080991Y
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- spring bearing
- planetary pinion
- gear
- gears
- ladder
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- 239000003638 chemical reducing agent Substances 0.000 abstract description 6
- 230000005540 biological transmission Effects 0.000 abstract description 5
- 238000012545 processing Methods 0.000 abstract description 4
- 238000005096 rolling process Methods 0.000 abstract description 2
- 230000020169 heat generation Effects 0.000 abstract 2
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 210000000515 tooth Anatomy 0.000 description 58
- 230000000737 periodic effect Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
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Abstract
The utility model relates to a speed reducer used for controlling a motor, consisting of an input shaft, a ladder planet gear, an internal gear, an output shaft, a right shell, a left shell and a plurality of supporting bearings. The utility model is characterized in that: gears of the speed reducer are provided with high rotating speed engagement, thereby the gears have the advantages of simple processing, low noise and low heat generation, and the characteristic is particularly obvious along with increase of speed reducing ratio; the gears and the bearings are matched with each other by adoption of rolling bearings, thereby efficiency is high, and output and input are coaxial and then assembly is convenient; 4 to 7 gears participate in jogglework when the gears are meshed, thereby load balancing properties of the gears are good; because gear engagement is low-speed engagement motion, the gears have the advantages of low heat generation, low noise and long service life. Four gears can arbitrarily form an arbitrary speed reducer with transmission ratio lower than 100; the speed reducer is suitable for demands of speed reducing ratio of various sequences and convenient for series manufacture. Moreover, high transmission efficiency can be obtained by adoption a reasonable addendum coefficient and a reasonable dentiform engaging angle.
Description
Technical field
The utility model relates to the precision speed reduction device that a kind of suitable control motor is used, and belongs to the mechanical transmissioning technology field.
Background technique
In the prior art, modal control motor reducer, mainly contain PX, PL series planetary reducer, these retarder central gear processed complexs, the number of gears is many, the cost height, particularly the small gear of input shaft need adapt to the rotating speed height, and the operating time is long, participates in joggleword with three planet wheels simultaneously, quick abrasion, planet carrier processing request height.And, this retarder reduction speed ratio in tandem product can not increase reduction speed ratio by Serial No. ordering, can only increase by the multiple of radix as 5,8,12,15,20 etc., increases reduction speed ratio, need to increase the number of gears, also will reduce the efficient of gear simultaneously with the increase of progression.Because this series retarder is by the radial structure planet gear of arranging, under the certain situation of radial dimension, gear and gear shaft are subjected to the restriction of radial dimension, bearing can not be installed, form sliding friction, increase energy consumption, increase with reduction speed ratio, structurally be difficult for the increase modulus yet and improve the strength of gear teeth, in the middle of the reduction speed ratio of same grade, the twisting strength of retarder and the reduction speed ratio of retarder do not match.
The model utility content
At the prior art above shortcomings, it is simple that the purpose of this utility model provides a kind of Gear Processing, and noise is low, heating is few, a kind of control motor retarder that delivery efficiency is high.
The purpose of this utility model is achieved in that a kind of control motor retarder, it is characterized in that being made of input shaft, two ladder planetary pinions, internal gear, output shaft, right shell body, left shell and some spring bearings;
Input shaft is supported on respectively by first spring bearing and second spring bearing in the endoporus of left end of left shell and output shaft, two pairs of eccentric circles that circumferentially differ 180 ° are arranged in the middle of the input shaft, the 3rd spring bearing and the 4th spring bearing are housed on two eccentric circles, and dress has ladder planetary pinion and ladder planetary pinion respectively on the outer ring of the 3rd spring bearing and the 4th spring bearing; Ladder planetary pinion and ladder planetary pinion are formed by an external gear and an internal gear; The planetary inner hole sleeve of ladder is on the cylindrical of the 3rd spring bearing of input shaft left end, and the planetary inner hole sleeve of ladder is on eccentric circle the 4th spring bearing cylindrical of input shaft right-hand member; The external gear of ladder planetary pinion right-hand member and internal gear engagement, the external gear of ladder planetary pinion left end and internal gear engagement; The external tooth of left end engagement on the internal gear of ladder planetary pinion right-hand member and the output shaft; The internal gear folder fixes in the middle of left shell and the right shell body, and output shaft is bearing in the endoporus of right shell body by the 5th spring bearing and the 6th spring bearing.
Compared to existing technology, the utlity model has following advantage:
1, the junction plane of the wheel tooth on the retarder is provided with high rotating speed engagement, thereby Gear Processing is simple, and noise is low, heating is few, and along with the increase of reduction speed ratio, these characteristics are especially obvious.
2, gear and bearing adopt rolling bearing to cooperate, the efficient height, and output, coaxial being convenient to of input are installed.
3, have during gear engagement 4～7 gears to participate in jogglewords, all carrying property of gear are good, and gear engagement is the gear motion of low speed, generate heat little, noise is low, long service life.
4, can form any ratio decelerator below 100 arbitrarily by 4 gears, be fit to the needs of each sequence reduction speed ratio, be convenient to producing in serial form.
5, adopt rational addendum coefficient, modification coefficient and profile of tooth pressure angle can obtain high transmission efficiency.
Description of drawings
Fig. 1 is the first mode of execution structural representation of the present utility model;
Fig. 2 is the second mode of execution structural representation of the present utility model.
Embodiment
Embodiment 1: as shown in Figure 1, a kind of control motor retarder, spring bearing 3,14 by input shaft 1, ladder planetary pinion 4,7 (ladder planetary pinion 4,7 form by an external gear and internal gear), internal gear 6, output shaft 9, right shell body 10, left shell 2, input shaft 1, the spring bearing 5,8 of two ladder planetary pinions 4,7, and the spring bearing 11,12 of output shaft 9 constitutes.Among the figure, 13,15,16 all is ring washers.
Input shaft 1 is supported in the endoporus of left shell 2 and output shaft 9 left ends respectively by first spring bearing 3 and second spring bearing 14, two pairs of eccentric circles that circumferentially differ 180 ° are arranged in the middle of the input shaft 1, the 3rd spring bearing 5, the 4th spring bearing 8 are housed on two eccentric circles, the inner hole sleeve of ladder planetary pinion 4 is on the outer ring of eccentric circle the 3rd spring bearing 5 of input shaft 1 left end, and the inner hole sleeve of ladder planetary pinion 7 is on the outer ring of eccentric circle the 4th spring bearing 8 of input shaft right-hand member.Wherein, the external gear on ladder planetary pinion 4 the right and internal gear 6 engagements, the external gear on ladder planetary pinion 7 left sides and internal gear 6 engagements, the external tooth of left end engagement on the internal gear on ladder planetary pinion 7 the right and the output shaft 9, internal gear 6 folders fix on the centre of left shell 2 and right shell body 10, and output shaft 9 is bearing in right shell body 10 endoporus by the 5th spring bearing 11, the 6th spring bearing 12.
Input shaft 1 passes to the rotation of motor the external tooth of ladder planetary pinion 7 by the eccentric amount e on the 4th spring bearing 8 and the input shaft 1, external tooth z1 on the ladder planetary pinion 7 and the tooth z2 of internal gear 6 engagement, the internal tooth z3 while of ladder planetary pinion 7 and the external tooth z4 engagement on the output shaft 9, the inner ring of second spring bearing 8 is with input shaft 1 high speed rotating, ladder planetary pinion 7 under the reaction of eccentric motion and internal gear 6 tooth z2 with the periodic oppositely rotation of eccentric e, internal gear z3 on the ladder planetary pinion 7 is also with this eccentric motion rotation, and the tooth on it periodically inserts and drives output shaft 9 in the teeth groove of the external tooth z4 on the output shaft 9 and oppositely slow down with input shaft 1 and rotate.
The internal tooth z2 of internal gear 6 and the engagement of the external tooth z1 on the stepped gear 7, there is the eccentric circle of a pair of 180 ° of symmetries in the input shaft stage casing, offset is e, the 3rd spring bearing 5, the 4th spring bearing 8 are housed respectively on two eccentric circles, bearing outer ring matches with stepped gear z1, z3 endoporus, internal tooth z2 engagement on its external tooth z1 and the housing, external tooth z4 engagement on right stepped gear the right internal tooth z3 and the output shaft, input shaft the right bearing puts in output shaft left end endoporus, and output shaft the right bearing is supported on the right shell body.Then
Velocity ratio
Z1, z3 are respectively ladder planet tooth external tooth and internal tooth, and z2 is the internal tooth on the housing, and z4 is the external tooth on the output shaft, and z1, z2 and z3, z4 tooth difference are 1～5.
Present embodiment mainly is applicable to the situation use that velocity ratio is less.
Embodiment 2: with first kind of structure difference be: the tooth on the two ladder planetary pinions 4,7 all is an external tooth, and left end has a circle internal tooth on the output shaft 9, and all the other structures are the same with first kind of structure.
By shown in Figure 2: retarder mainly comprises input shaft 1, the first ladder planetary pinion 4, the second ladder planetary pinion 7, internal gear 6 and output shaft 9, and first spring bearing 3 and second spring bearing 14 that are used to support input shaft 1, be used to support the 3rd spring bearing 5 and the 4th spring bearing 8 of two ladder planetary pinions 4,7, be used to support the 5th spring bearing 11 and the 6th spring bearing 12 of output shaft 9.Among the figure, the 2nd, right shell body, the 10th, left shell, the 13rd, back-up ring.
Input shaft 1 is supported in the endoporus of left shell 2 and output shaft 9 left ends respectively by first spring bearing 3 and second bearing 14, two pairs of eccentric circles that circumferentially differ 180 ° are arranged in the middle of the input shaft 1, be equipped with on two eccentric circles and be used to support two ladder planetary pinions 4,7 the 3rd spring bearing 5 and the 4th spring bearing 8 (ladder planetary pinion 4 and ladder planetary pinion 7 are housed respectively on the outer ring of the 3rd spring bearing 5 and the 4th spring bearing 8), ladder planetary pinion 4 inner hole sleeves are on eccentric circle spring bearing 5 cylindricals of input shaft 1 left end, ladder planetary pinion 7 is enclosed within on eccentric circle spring bearing 8 cylindricals of input shaft 1 right-hand member, ladder planetary pinion 4 is made up of two external gears, as shown in Figure 2, the external gear on ladder planetary pinion 4 the right and internal gear 6 engagements; Ladder planetary pinion 7 also is made up of two external gears, as shown in Figure 2, ladder planetary pinion 7 upper left external tooths also mesh with internal gear 6, the internal tooth of left end engagement on the external tooth on ladder planetary pinion 7 the right and the output shaft 9, internal gear 6 folders fix in the middle of left shell 2 and the right shell body 10, and output shaft 9 is bearing in the right shell body 10 interior shoulder holes by the 5th spring bearing 11 and the 6th spring bearing 12.
Input shaft 1 is the rotation of motor, pass ladder planetary pinion 7 by the eccentric amount e on the 4th spring bearing 8 and the input shaft 1, external tooth z1 on the ladder planetary pinion 7 and the tooth z2 of internal gear 6 engagement, the external tooth z3 while of ladder planetary pinion 7 and the internal tooth z4 engagement on the output shaft 9, the inner ring of the 3rd spring bearing 5 is with input shaft 1 high speed rotating, ladder planetary pinion 7 under the reaction of eccentric motion and tooth z2 and internal gear 6 with the periodic oppositely rotation of eccentric e, external tooth z3 on the ladder planetary pinion 7 is also with this eccentric motion rotation, and the tooth on it periodically inserts and drives the rotation of slowing down in the same way of output shaft 9 and input shaft 1 in the teeth groove of the internal gear on the output shaft 9.
Velocity ratio
Z1, z3 are the external tooth of ladder planetary pinion 7, and z2 is the tooth of internal tooth 6, and z4 is the internal tooth that is fixed on output shaft 9 left ends.
Z1=z3 is during z4-z2=1, then: velocity ratio i=z4
In product percent of pass design if guarantee that two pairs of Gear centers are certain apart from e, external tooth engagement in z1 and the z2, modulus is m1, external tooth engagement in z3 and the z4, modulus is m2, m2-m1=0.25, z1=z3 is under the prerequisite of z4-z2=1, z4=30,31,32 ... 99,100 o'clock, just can obtain corresponding i=30,31,32 ... 99,100 sequence velocity ratio.
Present embodiment mainly is applicable to the situation use that velocity ratio is bigger.
Embodiment 3: omit accompanying drawing, two ladder planetary pinions all are external gears, and the modulus of the first order and second level gear differs 0.25 in the gear engagement inside and outside two-stage, is 1.25 as the first order, the second level is 1.5, guarantees that by adjusting modification coefficient x two pairs of Gear centers are apart from being e.
Velocity ratio
Zi, z3 are the planetary external tooth of ladder, and z2 is the internal tooth of internal gear 6; Z4 is the internal tooth that is fixed on output shaft.
Z1=z3 is during z4-z2=1, then: velocity ratio i=z4
In product percent of pass design if guarantee that two pairs of Gear centers are certain apart from e, external tooth engagement in z1 and the z2, modulus is m1, external tooth engagement in z3 and the z4, modulus is m2, m2-m1=0.25, z1=z3 is under the prerequisite of z4-z2=1, z4=30,31,32 ... 99,100 o'clock, just can obtain corresponding i=30,31,32 ... 99,100 sequence velocity ratio.
Present embodiment mainly be applicable to velocity ratio need by 30,31,32 ... situation when 100 sequence numbers are arranged is used.
Another characteristics of the present utility model are: the translation that forms owing to eccentric motion when planet stepped gear z1, z3 and internal gear z2, output shaft tooth z4 engagement and the compound motion of rotation, in order to reduce the radial component of gear engagement, getting pressure angle is a=9 °～20 °, and addendum coefficient is taken as 0.5 ... 0.3 to improve transmission efficiency, to avoid tooth top to interfere.
The capacity eccentric bearing inner ring is fixed on the eccentric step of input shaft, ladder planetary pinion inner ring is fastened on this bearing outer ring, bearing inner race is with the input shaft high speed rotating, because the effect of eccentric motion drives the stepped gear z1 on the bearing outer ring, z3 revolves round the sun around input shaft, its external tooth z1, z3 inserts in internal tooth z2 and the output shaft z4 teeth groove, because internal tooth z2, the reaction force of output shaft internal tooth z4 makes the reverse rotation of its generation around the capacity eccentric bearing axle center, this rotation is with rotating than the periodic low-speed motion of i, so the gear motion of the flank of tooth is a kind of transmission of low speed, the high-speed motion of motor is born by the high capacity eccentric bearing of precision, finishes retarded motion thus.
Claims (2)
1. a control motor retarder is characterized in that being made of input shaft (1), two groups of ladder planetary pinions (4,7), internal gear (6), output shaft (9), right shell body (10), left shell (2) and spring bearing (3,14,5,8,11,12);
Input shaft (1) is supported on respectively by first spring bearing (3) and second spring bearing (14) in the endoporus of left end of left shell (2) and output shaft (9), two pairs of eccentric circles that circumferentially differ 180 ° are arranged in the middle of the input shaft (1), the 3rd spring bearing (5) and the 4th spring bearing (8) are housed on two eccentric circles, and dress has ladder planetary pinion (4) and ladder planetary pinion (7) respectively on the outer ring of the 3rd spring bearing (5) and the 4th spring bearing (8); Ladder planetary pinion (4) and ladder planetary pinion (7) are formed by an external gear and an internal gear; The inner hole sleeve of ladder planetary pinion (4) is on the cylindrical of the 3rd spring bearing (5) of input shaft (1) left end, and the inner hole sleeve of ladder planetary pinion (7) is on eccentric circle the 4th spring bearing (8) cylindrical of input shaft (1) right-hand member; The external gear of ladder planetary pinion (4) right-hand member and internal gear (6) engagement, the external gear of ladder planetary pinion (7) left end and internal gear (6) engagement; The internal gear of ladder planetary pinion (7) right-hand member and output shaft (9) are gone up the external tooth engagement of left end; Internal gear (6) folder fixes in the middle of left shell (2) and the right shell body (9), and output shaft (9) is bearing in the endoporus of right shell body (10) by the 5th spring bearing (11) and the 6th spring bearing (12).
2. control motor retarder according to claim 1 is characterized in that described two groups of ladder planetary pinions (4,7) all are external gears, and output shaft (9) left end is an internal gear;
Input shaft (1) is supported on respectively by bearing (3,14) in the endoporus of left end of left shell (2) and output shaft (9), two pairs of eccentric circles that circumferentially differ 180 ° are arranged in the middle of the input shaft (1), spring bearing (5,8) is housed on two eccentric circles, ladder planetary pinion (4,7) is housed on its outer ring, ladder planetary pinion (4) inner hole sleeve is on eccentric circle spring bearing (5) cylindrical of input shaft (1) left end, and ladder planetary pinion (7) inner hole sleeve is on eccentric circle spring bearing (8) cylindrical of input shaft (1) right-hand member; The external gear on ladder planetary pinion (4) the right and internal gear (6) engagement, external gear that ladder planetary pinion (7) is upper left and internal gear (6) engagement, the external gear of ladder planetary pinion (7) right-hand member and output shaft (9) are gone up the internal gear engagement of left end, internal gear (6) folder fixes on the centre of left shell (2) and right shell body (10), and output shaft (9) is bearing in the interior shoulder hole of right shell body (10) by spring bearing (11,12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201879219U CN201080991Y (en) | 2007-10-09 | 2007-10-09 | Decelerator for controlling electric motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201879219U CN201080991Y (en) | 2007-10-09 | 2007-10-09 | Decelerator for controlling electric motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201080991Y true CN201080991Y (en) | 2008-07-02 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007201879219U Expired - Lifetime CN201080991Y (en) | 2007-10-09 | 2007-10-09 | Decelerator for controlling electric motor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201080991Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101033727B (en) * | 2007-04-10 | 2010-08-04 | 杭州慧翔机电控制工程有限公司 | Plunger type quantitative hydraulic motor switch variable torque valve control oil distribution component and control method |
| CN101183816B (en) * | 2007-10-09 | 2010-11-17 | 胡菱菱 | Decelerator for control motor |
| CN110848334A (en) * | 2019-11-28 | 2020-02-28 | 黄子帅 | A four gear pair meshing reducer with less tooth difference |
-
2007
- 2007-10-09 CN CNU2007201879219U patent/CN201080991Y/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101033727B (en) * | 2007-04-10 | 2010-08-04 | 杭州慧翔机电控制工程有限公司 | Plunger type quantitative hydraulic motor switch variable torque valve control oil distribution component and control method |
| CN101183816B (en) * | 2007-10-09 | 2010-11-17 | 胡菱菱 | Decelerator for control motor |
| CN110848334A (en) * | 2019-11-28 | 2020-02-28 | 黄子帅 | A four gear pair meshing reducer with less tooth difference |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20080702 Effective date of abandoning: 20071009 |