CN2665457Y - Automatic aligning differential device - Google Patents
Automatic aligning differential device Download PDFInfo
- Publication number
- CN2665457Y CN2665457Y CNU2003201129159U CN200320112915U CN2665457Y CN 2665457 Y CN2665457 Y CN 2665457Y CN U2003201129159 U CNU2003201129159 U CN U2003201129159U CN 200320112915 U CN200320112915 U CN 200320112915U CN 2665457 Y CN2665457 Y CN 2665457Y
- Authority
- CN
- China
- Prior art keywords
- planet carrier
- bearing
- input
- output stage
- stage planet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000002131 composite material Substances 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 6
- 125000006850 spacer group Chemical group 0.000 claims description 5
- 210000004907 gland Anatomy 0.000 claims description 2
- 239000003638 chemical reducing agent Substances 0.000 abstract description 3
- 238000005299 abrasion Methods 0.000 abstract 1
- 230000005540 biological transmission Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
An automatic center-regulation differential mechanism belongs to the mechanical drive reducer field, which is an improved Chinese patents 98211242.4 and 01250773.3. An output sun wheel (12) and an input planet carrier (33) are connected by an involute spline. Elastic collars (34) and (35) are used to prevent the output sun wheel (16) from playing axially. An adjusting pad (36) is used to adjust the radial clearance of the output sun wheel (16). Enough clearance along the axial direction and at the side of the spline are left to ensure the output sun wheel (16) to incline slightly and move in the radial direction relative to the input planet carrier (33) and keep floating. When the differential mechanism is in operation three output planet wheels (14) that meshes with the output sun wheel (16) can make the output sun wheel set center automatically. The differential mechanism can automatically eliminate the condition of different centers due to processing errors; the output sun wheel (16) can be easily replaced after abrasion; the carrying capacity of the differential mechanism is strengthened; the utility model which has longer service life can be widely applied in various horizontal helical-conveyer centrifugal.
Description
(1) technical field
The utility model self-aligning differential mechanism belongs to the gear planetary reducer field in the mechanical transmission.It is the improvement of Chinese patent 98211242.4 (oil-film floating all carries planetary reducer) and Chinese patent 01250773.3 differential mechanism.
(2) background technique
In Chinese patent 98211242.4 and 01250773.3, the output sun gear is (16) that are rigidly connected with the input planet carrier.In case output wheel damages, the input planet carrier also will be scrapped thereupon.Because machining error, output sun gear are difficult to be in the central position of three output planetary wheels that are meshed with it, directly influenced its transmission effect and working life.
(3) summary of the invention
The purpose of this utility model provides a kind of more reasonable structure, recoverability is better, and transmission capacity is stronger, the self-aligning differential mechanism of longer service life.
Its end cap (3) and (30) are screwed on housing (1), and with O type ring (2) and (29) sealing, input stage sun gear (24) is by bearing (18) and (20) supporting, and with outside framework oil seal (23) sealing, this oil sealing is located with two elastic scheibes (22); Input stage planet axis (26) cooperates with hole on input stage planet carrier (16) and the cover plate (17) with the axle journal at two ends, and composite material steel-backed bearing (32) adopts interference fit to be pressed in the hole of each input stage planet wheel (27) and each output stage planet wheel (14); The endoporus of steel-backed bearing (32) and input stage planet axis (26) Spielpassung; Axle (26) composite material subtracts pad (31), couples together with pin and input stage planet carrier (16), prevents that it from being driven by planet wheel; The input stage planet carrier assembly is by bearing (15) and bearing (19) supporting, and bearing (15) is located with elastic scheibe (7) and (12); With three bolt, constitute the output stage planet carrier assembly between output stage planet carrier (5) and the gland (6); Output stage planet axis (13) cooperates with hole on planet carrier (5) and the cover plate (6) with the axle journal at two ends, prevent that with blind pin them from rotating relative to planet carrier (5) between output stage planet axis (13) and steel-backed bearing (32) Spielpassung, axle (13), anti-wear gasket (31) and frame (5); The output stage planet carrier assembly supports with bearing (10) and bearing (11), and the spindle nose of output stage planet carrier (5) seals with O type ring (9); Input stage ring gear (28) and output stage ring gear (4) are screwed on housing (1); Be installed in respectively on (16), (24) and (30) in order to spacer (8), (21) (25) of adjusting axial dimension.It is characterized in that exporting sun gear (16) adopts involute splines to connect with input planet carrier (33), be equipped with elastic scheibe (34) and (35) that prevent its axial float on output sun gear (16) is axial, and install additional in order to adjust the finishing pad (36) of exporting sun gear (16) axial clearance and to be used for supporting shaft bearing (15) outer shroud, and can adjust the cover (37) of importing sun gear (24) axial clearance, input planet carrier (33) constitutes the input planet carrier assembly with its cover plate (17) with four bolt together.
According to the design, input planet carrier (33) connects with involute splines with output sun gear (16), radially all leave enough gaps with flank, guarantee radial displacement or inclination that output sun gear (16) can trace with respect to input planet carrier (33) when operation, elastic scheibe (34) and (35) are used for preventing to export sun gear (16) axial float, and finishing pad (36) is used for adjusting the axial clearance of output sun gear (16); Cover (37) is used for the outer shroud of block bearing (15), is used for adjusting the axial clearance of input sun gear (24) simultaneously.Involute splines between output sun gear (16) and input planet carrier (33), radial clearance 0.6-0.9mm, backlash 0.2-0.3mm.
Annotate with an amount of lubricant oil by the oilhole on the housing during work, oilhole is sealed with plug cock.The power of input is made up of two-part, and a power drives planet wheel (27) through sun gear (24), and the latter and ring gear (28) engagement is because of ring gear maintains static, so drive input stage planet carrier and output stage sun gear (16) rotation.This sun gear drives output stage planet wheel (14), and the latter and ring gear (4) engagement because ring gear is fixed, is rotated so drive output stage planet carrier (5).By the outputting power that links to each other with load of the splined hole on this planet carrier.Another power is from output end cap (3), and with the outer drum rigid joint of this end cap and main frame and rotation thereupon, the main frame outer drum is by independent power-actuated during work.Because input stage sun gear (24) is with different rotating speed rotations with shell (1), thereby forms speed discrepancy.Littler speed discrepancy between the velocity ratio of this speed discrepancy through setting, the splined shaft that causes output stage planet carrier (5) and shell (1), planet carrier (5) links by the interior rotary drum of splined hole and main frame, thereby makes the formation speed discrepancy that requires between the interior outer drum of main frame.
The design's differential mechanism is mainly used in the various horizontal centrifuges, is used for forming the speed discrepancy between the outer drum in the horizontal centrifuge.
(4) description of drawings
Fig. 1 is the structural representation of the design's differential mechanism, also is Figure of abstract, among the figure:
1, housing 20, bearing
2, O type ring 21, spacer
3, end cap 22, elastic scheibe (2)
4, output stage internal gear 23, outside framework oil seal
5, output stage planet carrier 24, input stage sun gear
6, output stage planet carrier cover plate 25, spacer
7, elastic scheibe 26, input stage planet wheel shaft (2)
8, spacer 27, input stage planet wheel (2)
9, O type ring 28, input stage internal gear
10, bearing 29, O type ring
11, bearing 30, end cap
12, elastic scheibe 31, composite material anti-wear gasket
13, output stage planet wheel shaft (3) 32, composite material steel-backed bearing
14, output stage planet wheel (3) 33, input planet carrier
15, bearing 34, elastic scheibe
16, output stage sun gear 35, elastic scheibe
17, input stage planet carrier cover plate 36, finishing pad
18, bearing 37, cover
19, bearing
(5) embodiment
A concrete parameter of embodiment of the design's differential mechanism is as follows:
Input stage sun gear modulus m=1.5 number of teeth z=11
Two input stage planet wheel modulus m=1.5 number of teeth z=56
Input stage internal gear modulus m=1.5 number of teeth z=123
Output stage sun gear modulus m=2 number of teeth z=15
Three output stage planet wheel modulus m=2 number of teeth z=39
Output stage internal gear modulus m=2 number of teeth z=93
Input stage planet wheel shaft (26) is 0.10-0.14mm with steel-backed bearing (32) radial clearance.
Output stage planet wheel shaft (13) is 0.34-0.42mm with steel-backed bearing (32) radial clearance.
The axial clearance of both sides sum is 0.20-0.40mm between the end face of input stage planet wheel (27) and the anti-wear gasket (31).
The axial clearance of both sides sum is 0.20-0.40mm between the end face of output stage planet wheel (14) and the anti-wear gasket (31).
Involute splines between output sun gear (16) and input planet carrier (33), radial clearance 0.6-0.9mm, backlash 0.2-0.3mm.
Claims (3)
1, a kind of self-aligning differential mechanism, its end cap (3) and (30) are screwed on housing (1), and with O type ring (2) and (29) sealing, input stage sun gear (24) is by bearing (18) and (20) supporting, with outside framework oil seal (23) sealing, this oil sealing is located with two elastic scheibes (22); Input stage planet axis (26) cooperates with hole on input stage planet carrier (16) and the cover plate (17) with the axle journal at two ends, and composite material steel-backed bearing (32) adopts interference fit to be pressed in the hole of each input stage planet wheel (27) and each output stage planet wheel (14); The endoporus of steel-backed bearing (32) and input stage planet axis (26) Spielpassung; Axle (26), composite material subtract pad (31), couple together with pin and input stage planet carrier (16), prevent that it from being driven by planet wheel; The input stage planet carrier assembly is by bearing (15) and bearing (19) supporting, and bearing (15) is located with elastic scheibe (7) and (12); With three bolt, constitute the output stage planet carrier assembly between output stage planet carrier (5) and the gland (6); Output stage planet axis (13) cooperates with hole on planet carrier (5) and the cover plate (6) with the axle journal at two ends, prevent that with blind pin them from rotating relative to planet carrier (5) between output stage planet axis (13) and steel-backed bearing (32) Spielpassung, axle (13), anti-wear gasket (31) and frame (5); The output stage planet carrier assembly supports with bearing (10) and bearing (11), and the spindle nose of output stage planet carrier (5) seals with O type ring (9); Input stage ring gear (28) and output stage ring gear (4) are screwed on housing (1); In order to adjust the spacer (8) of axial dimension, (21) (25) are installed in (16) respectively, (24) and on (30), it is characterized in that exporting sun gear (16) adopts involute splines to connect with input planet carrier (33), be equipped with elastic scheibe (34) and (35) that prevent its axial float on output sun gear (16) is axial, and install additional in order to adjust the finishing pad (36) of exporting sun gear (16) axial clearance and to be used for supporting shaft bearing (20) outer shroud, and can adjust the cover (37) of importing sun gear (24) axial clearance, input planet carrier (33) constitutes the input planet carrier assembly with its cover plate (17) with four bolt together.
2,, it is characterized in that its one group concrete parameter is as follows according to the self-aligning differential mechanism of claim 1:
Input stage sun gear modulus m=1.5 number of teeth z=11
Two input stage planet wheel modulus m=1.5 number of teeth z=56
Input stage internal gear modulus m=1.5 number of teeth z=123
Output stage sun gear modulus m=2 number of teeth z=15
Three output stage planet wheel modulus m=2 number of teeth z=39
Output stage internal gear modulus m=2 number of teeth z=93
Radial clearance between input stage planet axis (26) and the steel-backed bearing (32) is 0.10-0.14mm;
Radial clearance between output stage planet axis (13) and the steel-backed bearing (32) is 0.34-0.42mm;
The axial clearance of both sides sum is 0.20-0.40mm between input stage planet wheel (27) and the anti-wear gasket (31);
The axial clearance of both sides sum is 0.20-0.40mm between output stage planet wheel (14) and the anti-wear gasket (31).
3,, it is characterized in that exporting the involute splines between sun gear (16) and input planet carrier (33), radial clearance 0.6-0.9mm, backlash 0.2-0.3mm according to the differential mechanism of claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2003201129159U CN2665457Y (en) | 2003-12-05 | 2003-12-05 | Automatic aligning differential device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2003201129159U CN2665457Y (en) | 2003-12-05 | 2003-12-05 | Automatic aligning differential device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2665457Y true CN2665457Y (en) | 2004-12-22 |
Family
ID=34344777
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2003201129159U Expired - Fee Related CN2665457Y (en) | 2003-12-05 | 2003-12-05 | Automatic aligning differential device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2665457Y (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101832375A (en) * | 2009-03-11 | 2010-09-15 | 孟凡英 | Spline direct-connected planetary conical disc type stepless reducer |
| CN101929528A (en) * | 2010-08-06 | 2010-12-29 | 江苏省金象减速机有限公司 | Dual-input power dividing differential planetary reducer |
| CN102042369A (en) * | 2010-12-28 | 2011-05-04 | 上海合纵重工机械有限公司 | Improved planetary reducer |
| WO2011072601A1 (en) * | 2009-12-14 | 2011-06-23 | Smart Manufacturing Technology (Shanghai) Ltd. | Geared drive system with load sharing |
| CN102121522A (en) * | 2011-03-11 | 2011-07-13 | 许晓华 | Improved structure of minitype planet gear speed changing box |
| CN102128251A (en) * | 2011-03-11 | 2011-07-20 | 许晓华 | Improved planetary gear locating structure of miniature planetary gear box |
| CN104797850A (en) * | 2012-11-05 | 2015-07-22 | 住友重机械工业株式会社 | Simple planetary reduction gear |
| CN106949195A (en) * | 2017-05-09 | 2017-07-14 | 华东交通大学 | It is self-regulated to carry based on planet row and the uni-drive gear box carried coexists being linked between level |
| CN109681594A (en) * | 2018-12-03 | 2019-04-26 | 中国北方车辆研究所 | A kind of design method improving the planet row service life |
-
2003
- 2003-12-05 CN CNU2003201129159U patent/CN2665457Y/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101832375A (en) * | 2009-03-11 | 2010-09-15 | 孟凡英 | Spline direct-connected planetary conical disc type stepless reducer |
| WO2011072601A1 (en) * | 2009-12-14 | 2011-06-23 | Smart Manufacturing Technology (Shanghai) Ltd. | Geared drive system with load sharing |
| CN101929528A (en) * | 2010-08-06 | 2010-12-29 | 江苏省金象减速机有限公司 | Dual-input power dividing differential planetary reducer |
| CN101929528B (en) * | 2010-08-06 | 2012-12-05 | 江苏省金象减速机有限公司 | Dual-input power dividing differential planetary reducer |
| CN102042369A (en) * | 2010-12-28 | 2011-05-04 | 上海合纵重工机械有限公司 | Improved planetary reducer |
| CN102042369B (en) * | 2010-12-28 | 2013-07-31 | 上海合纵重工机械有限公司 | Improved planetary reducer |
| CN102121522A (en) * | 2011-03-11 | 2011-07-13 | 许晓华 | Improved structure of minitype planet gear speed changing box |
| CN102128251A (en) * | 2011-03-11 | 2011-07-20 | 许晓华 | Improved planetary gear locating structure of miniature planetary gear box |
| CN102121522B (en) * | 2011-03-11 | 2013-06-05 | 许晓华 | Improved structure of minitype planet gear speed changing box |
| CN104797850A (en) * | 2012-11-05 | 2015-07-22 | 住友重机械工业株式会社 | Simple planetary reduction gear |
| CN106949195A (en) * | 2017-05-09 | 2017-07-14 | 华东交通大学 | It is self-regulated to carry based on planet row and the uni-drive gear box carried coexists being linked between level |
| CN109681594A (en) * | 2018-12-03 | 2019-04-26 | 中国北方车辆研究所 | A kind of design method improving the planet row service life |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: ZHANG XIANYING Free format text: FORMER OWNER: CHANGCHUN YINGGUANG ELECTROMECHANICAL TECHNOLOGIES CO., LTD. Effective date: 20050225 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20050225 Address after: Nanhu road 130021 in Jilin province Changchun City Tianjiao building room 1202 No. 2030 Patentee after: Zhang Xianying Address before: 130022 No. 2030 nanhu road, Jilin City, Changchun Province Patentee before: Changchun Yingguang Electromechanical Technologies Co., Ltd. |
|
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |