CN105864362B

CN105864362B - Planetary gearing train structure

Info

Publication number: CN105864362B
Application number: CN201510025282.5A
Authority: CN
Inventors: 刘家铭; 陈任垣
Original assignee: Hiwin Technologies Corp
Current assignee: Hiwin Technologies Corp
Priority date: 2015-01-19
Filing date: 2015-01-19
Publication date: 2018-04-17
Anticipated expiration: 2035-01-19
Also published as: CN105864362A

Abstract

The present invention provides a kind of planetary gearing train structure, through the planetary outer flank of tooth and inner peripheral surface in epicyclic train, outer shroud grooving and inner ring grooving are set respectively, planetary intensity is reduced accordingly, planetary gear is set to produce a little deformability or elasticity, as long as axial force is applied vertically to the planetary both ends, the planetary gear just can deflection that is axially compressed and producing radial direction with and meanwhile eliminate and back clearance between central gear, rim gear wheel, improve transmission efficiency；And the present invention is the effect for providing deformation in itself by planetary gear and eliminating gap, is not required to assemble extra component, therefore has the advantages that structure is simplified again, reduce volume, improve applicability.

Description

Planetary gearing train structure

Technical field

The present invention relates to a kind of planetary gearing train structure, it is related with transmission device.

Background technology

Planetary gear has the advantages that large carrying capacity, small, transmission efficiency and stable working, therefore is a kind of quilt The transmission device being widely used in various maneuvering systems, and planetary basic framework is engaged in by an at least planetary gear Formed between one central gear and a rim gear wheel, during due to transmission by each gear drive for being meshed, thus each gear is nibbled It is right to be directly related to transmission efficiency, and general processing level can not simultaneously avoid producing back clearance between each gear, once Back clearance is produced between each gear will also influence transmission efficiency.

Therefore be as shown in Figure 1, 2 a kind of planetary gear set 10 with backlash eliminator, it mainly includes a gear ring 11st, a central gear 12, four planetary gear modules 13 and two backlash eliminators 14, wherein, each planetary gear module 13 One first planetary gear 131 and one second planetary gear 132, first planetary gear 131 and second row are included respectively Star gear 132, which overlaps, to be set, and respectively second planetary gear 132 engages the gear ring 11, and the central gear 12 is engaged in respectively Between first planetary gear 131；And two backlash eliminators 14 are coupled pulling department 141 and one comprising one respectively and are coupled Pushing part 142, each the first planetary gear 131 and the second row for being coupled pulling department 141 and being disposed therein two planetary gear modules 13 Between star gear 132, and respectively the connection pushing part 142 is then arranged at the first planetary gear of other two planetary gears module 13 131 and second between planetary gear 132；Connection pulling department 141 is produced prefastening force, and be coupled pushing part 142 and produce Pretension thrust, and the effect for eliminating back clearance can be produced in the rotating of planetary gear set 10.

However, the planetary gear module 13 of the planetary gear set 10 must be by the first planetary gear 131 and the second planet tooth Wheel 132 is formed, therefore the thickness of planetary gear module 13 is general planetary double, and can dramatically increase overall body Product, and influence the applicability of overall planetary gear set 10；Moreover the planetary gear set 10 must be included at least to coordinate to be coupled and pulled Portion 141 and the two planetary gear modules 13 for being coupled pushing part 142, so must just include at least four planetary gears, equally Ground is also to have increase volume, the situation of weight, and influences applicability.

The content of the invention

The present invention provides a kind of planetary gearing train structure, it is to improve common planetary gear group to have structure composition component More, the problem of volume is big, applicability is bad.

To solve the above problems, the present invention provides a kind of planetary gearing train structure, it is located at a ring tooth comprising a central gear In wheel, at least a planetary gear is engaged between the central gear and the rim gear wheel, and the planetary gear is a ring gear and has There are an inner peripheral surface and an outer flank of tooth, and respectively the planetary both ends closure is defined as axial direction, vertical axial is defined as footpath To；

The planetary outer flank of tooth is disposed radially an outer shroud grooving and has an outer shroud grooving bottom, and the planet tooth The inner peripheral surface of wheel is disposed radially an inner ring grooving and has an inner ring grooving bottom, and the outer shroud grooving is with the inner ring grooving in axis Upward minimum spacing is a wheelbase, which is 0.6~1.5 times of the planetary modulus.

The present invention sets outer shroud grooving and interior respectively through the planetary outer flank of tooth and inner peripheral surface in epicyclic train Ring cutting groove, provides the planetary gear and produces a little deformability or elasticity accordingly, as long as to the planetary both ends along axis To apply axial force, the planetary gear just can deflection that is axially compressed and producing radial direction with the same time eliminate and central gear, Back clearance between rim gear wheel, improves transmission efficiency；And the present invention is the effect for providing deformation in itself by planetary gear and eliminating gap, It is not required to assemble extra component, therefore has the advantages that structure is simplified again, reduce volume, improve applicability.

Brief description of the drawings

Fig. 1 is the stereochemical structure exploded view of common planetary gear group.

Fig. 2 is the assembled sectional view of common planetary gear group.

Fig. 3 is the stereochemical structure combination diagram of planetary gearing train structure of the present invention.

Fig. 4 is the stereochemical structure decomposing schematic representation of planetary gearing train structure of the present invention.

Fig. 5 is the planetary stereo appearance figure of planetary gearing train structure of the present invention.

Fig. 6 is the planetary sectional view of planetary gearing train structure of the present invention.

Fig. 7 is the planetary appearance plan of planetary gearing train structure of the present invention.

Description of reference numerals

10 gear ring 11 of planetary gear set

12 planetary gear module 13 of central gear

First planetary gear, 131 second planetary gear 132

Backlash eliminator 14 is coupled pulling department 141

It is coupled pushing part 142

20 rim gear wheel 30 of central gear

40 inner peripheral surface 41 of planetary gear

411 inner ring grooving bottom 412 of inner ring grooving

The outer flank of tooth 42 of bearing tank 413

421 outer shroud grooving bottom 422 of outer shroud grooving

The axial direction of planet carrier 50 X

Radial direction Y moduluses M

Wheelbase Xd1 outer shroud well widths Xd2

Inner ring well width Xd3 bearing tank width Xd4

The first most short most short radial distance Yd2 of radial distance Yd1 second

Radius of corner r1 radiuss of corner r2

Embodiment

The preferred embodiment of planetary gearing train structure of the present invention is located at a ring as shown in FIG. 3 to 7, comprising a central gear 20 In gear 30, at least a planetary gear 40 is engaged between the central gear 20 and the rim gear wheel 30, and a planet carrier 50 divides The central gear 20 and the planetary gear 40 are not incorporated into, and the quantity of the planetary gear 40 of the present embodiment is three, and the planet Gear 40 is a ring gear and has an inner peripheral surface 41 and an outer flank of tooth 42, and the respectively both ends closure of the planetary gear 40 Axial X is defined as, vertical axial X is defined as radial direction Y.

Radially Y sets an outer shroud grooving 421 and has an outer shroud grooving bottom the outer flank of tooth 42 of the planetary gear 40 422, and radially Y sets an inner ring grooving 411 and has an inner ring grooving bottom 412 inner peripheral surface 41 of the planetary gear 40, The outer shroud grooving 421 is parallel with the inner ring grooving 411, and more depression sets a bearing tank 413 on the inner peripheral surface 41.

The outer shroud grooving 421 and the inner ring grooving 411 are a wheelbase Xd1, wheelbase Xd1 in the minimum spacing on axial X For 0.6~1.5 times (i.e. Xd1=(0.6~1.5) the * M) of the modulus M of the planetary gear 40, most preferably 0.75~1 times of (i.e. Xd1 =(0.75~1) * M).

The outer shroud grooving bottom 422 to the most short radial distance between the bearing tank 413 for one first most minor axis to away from From Yd1, the inner ring grooving bottom 412 to the most short radial distance between the tooth root of the planetary gear 40 for one second most minor axis to away from From the modulus M that Yd2, the first most short radial distance Yd1 and the second most short radial distance Yd2 are respectively the planetary gear 40 0.6~1.5 times (i.e. Yd1, Yd2=(0.6~1.5) * M)), most preferably 0.75~1 times (i.e. Yd1, Yd2=(0.75~1) * M).

In having an outer shroud well width Xd2 on axial X, which has the outer shroud grooving 421 on axial X The 1~2.2 of one inner ring well width Xd3, outer shroud well width Xd2, the modulus M that inner ring well width Xd3 is the planetary gear 40 Times (i.e. Xd2, Xd3=(1~2.2) * M), most preferably 1.2~2 times (i.e. Xd2, Xd3=(1.2~2) * M), and the outer shroud groove width Degree Xd2, inner ring well width Xd3 are more than 1mm.

The outer shroud grooving bottom 422 of the outer shroud grooving 421 is circular, the inner ring grooving bottom 412 of the inner ring grooving 411 For circle, the radius of corner r1 of the outer shroud grooving bottom 422 is 0.5 times (i.e. the r1=0.5*Xd2) of outer shroud well width Xd2； The radius of corner r2 of the inner ring grooving bottom 412 is 0.5 times (i.e. r2=0.5*Xd3) of inner ring well width Xd3；And

For the bearing tank 413 in having a bearing tank width Xd4 on axial X, bearing tank width Xd4 is the outer shroud Summation (the i.e. Xd4=Xd2+Xd3+3* of the modulus M of well width Xd2, the inner ring well width Xd3 and 3 times of planetary gears 40 M)。

It is the structural configuration and feature of planetary gearing train structure of the present invention above, the present invention only needs a planetary gear 40 With regard to that can form epicyclic train, and the planetary gear 40 mainly passes through and sets edge respectively in the outer flank of tooth 42 and the inner peripheral surface 41 Outer shroud grooving 421 and the inner ring grooving 411 of radial direction Y extensions, reduce the planetary gear 40 and set the outer shroud grooving 421 accordingly And the part of the inner ring grooving 411 structural strength and the planetary gear 40 can be made to produce a little deformability or elasticity, then will After the planetary gear 40 assembling forms the epicyclic train of the present invention, if the planetary gear 40 and the central gear 20 or should When there is back clearance between rim gear wheel 30, as long as the both ends X applications vertically axial force to the planetary gear 40, the planetary gear 40 Just X compresses and produces the deflection of radial direction Y vertically, just can be more tight when the planetary gear 40 produces the deflection of radial direction Y Thickly close to the central gear 20 or the rim gear wheel 30, and then eliminate back clearance, improve the purpose of transmission efficiency.

And the planetary gear 40 is from above-listed each relational expression, as long as the outer flank of tooth 42 of the present invention in the planetary gear 40 And the inner peripheral surface 41 is set under the basis of the outer shroud grooving 421 and the inner ring grooving 411 respectively, through the mould of the planetary gear 40 Number M can calculate the outer shroud grooving 421 and every numerical value of the inner ring grooving 411, thus can be suitably used for various sizes of row Star gear 40.

In addition, the present invention sets outer shroud grooving 421 and inner ring grooving 411 by planetary gear 40 itself, make the planetary gear 40 itself produce elastic deformation forces, are not required to set extra elastic component just can be through the planetary gear 40 elastic deformation of itself Eliminate back clearance；And the planetary gear 40 of the present invention is again to be engaged in the central gear 20 and the rim gear wheel 30 at the same time, therefore it is not required to The planetary gear 40 of paired quantity can just eliminate the back clearance between central gear 20 and between the rim gear wheel 30, simplify overall structure Composition, and integrated member quantity is substantially reduced, reduce overall volume and weight, improve applicability.

Claims

1. a kind of planetary gearing train structure, is located in a rim gear wheel, at least a planetary gear is engaged in this comprising a central gear Between central gear and the rim gear wheel, the planetary gear is a ring gear and has an inner peripheral surface and an outer flank of tooth, and respectively should Planetary both ends closure is defined as axial direction, and vertical axial is defined as radially, it is characterised in that：

The planetary outer flank of tooth is disposed radially an outer shroud grooving and has an outer shroud grooving bottom, and this is planetary Inner peripheral surface is disposed radially an inner ring grooving and has an inner ring grooving bottom, and the outer shroud grooving is with the inner ring grooving in axial direction Minimum spacing be a wheelbase (Xd1), which is 0.6~1.5 times of (i.e. Xd1 of the planetary modulus (M) =(0.6~1.5) * M).

2. planetary gearing train structure as claimed in claim 1, it is characterised in that：The wheelbase（Xd1）It is planetary for this 0.75~1 times (i.e. Xd1=(0.75~1) * M) of modulus (M).

3. planetary gearing train structure as claimed in claim 1, it is characterised in that：Also it is recessed on the planetary inner peripheral surface Let puts a bearing tank, the outer shroud grooving bottom to the most short radial distance between the bearing tank for one first most minor axis to Distance (Yd1), the inner ring grooving bottom to the most short radial distance between the planetary tooth root for one second most minor axis to away from From (Yd2), the first most short radial distance (Yd1) and the second most short radial distance (Yd2) are respectively that this is planetary 0.6~1.6 times (i.e. Yd1, Yd2=(0.6~1.6) * M) of modulus (M).

4. planetary gearing train structure as claimed in claim 3, it is characterised in that：Described first most short radial distance (Yd1) and The second most short radial distance (Yd2) be respectively the planetary modulus (M) 0.75~1 times (i.e. Yd1, Yd2= (0.75~1) * M).

5. planetary gearing train structure as claimed in claim 1, it is characterised in that：The outer shroud grooving is outside in axial direction with one Annular groove width (Xd2), in having an inner ring well width (Xd3) in axial direction, the outer shroud well width (Xd2), be somebody's turn to do the inner ring grooving Inner ring well width (Xd3) is 1~2.2 times (i.e. Xd2, Xd3=(1~2.2) * M) of the planetary modulus (M), and should Outer shroud well width (Xd2), the inner ring well width (Xd3) are more than 1mm.

6. planetary gearing train structure as claimed in claim 5, it is characterised in that：The outer shroud well width (Xd2), the inner ring Well width (Xd3) is 1.2~2 times (i.e. Xd2, Xd3=(1.2~2) * M) of the planetary modulus (M).

7. planetary gearing train structure as claimed in claim 5, it is characterised in that：The outer shroud grooving bottom of the outer shroud grooving is Circle, the inner ring grooving bottom of the inner ring grooving is circle, and the radius of corner (r1) of the outer shroud grooving bottom is the outer groove 0.5 times (i.e. r1=0.5*Xd2) of width (Xd2), the radius of corner (r2) of the inner ring grooving bottom are the inner ring well width (Xd3) 0.5 times (i.e. r2=0.5*Xd3).

8. planetary gearing train structure as claimed in claim 5, it is characterised in that：It is recessed on described planetary inner peripheral surface Fall into and a bearing tank is set, the bearing tank is in having a bearing tank width (Xd4), the bearing tank width (X in axial direction D4) for the outer shroud well width (Xd2), the inner ring well width (Xd3) and 3 times of planetary moduluses (M) summation (i.e. Xd4=Xd2+Xd3+3*M).

9. planetary gearing train structure as claimed in claim 1, it is characterised in that：The planetary quantity is three.

10. planetary gearing train structure as claimed in claim 1, it is characterised in that：The outer shroud grooving is put down with the inner ring grooving OK.