CN1769740A - Non-clearance double-gear output transmission method and transmission device - Google Patents
Non-clearance double-gear output transmission method and transmission device Download PDFInfo
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- CN1769740A CN1769740A CN 200510032377 CN200510032377A CN1769740A CN 1769740 A CN1769740 A CN 1769740A CN 200510032377 CN200510032377 CN 200510032377 CN 200510032377 A CN200510032377 A CN 200510032377A CN 1769740 A CN1769740 A CN 1769740A
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Abstract
The invention discloses gapless two-gear driving output method and device, which comprises the following steps: setting two helical gears of different rotary directions on the output shaft; transforming the transmission force to two output gears through two driving circuits separately; transmitting torque separately when two output gears are activated by positive and negative direction. The device comprises the following parts: gear box, input-and-output shaft of the same axle, gear I, II shaft on two sides of input shaft, first, second helical gears of different rotary direction on the input shaft, first driven helical gear and first driving gear engaged to the first helical gear on the gear I shaft, second driven helical gear and second driving gear engaged to the second helical gear on the gear II shaft, third driving gear and first output gear engaged to the first driving gear on the output shaft, forth driving gear and second output gear engaged to the second driving gear on output shaft through the bearing case. The invention accomplishes the gapless driving of high precision.
Description
Technical field
The invention belongs to gear transmission, being specifically related to a kind of highi degree of accuracy does not have gear-driven implementation method in gap and transmission device thereof.
Background technique
In gear train assembly, because manufacturing and assembly error unavoidably can be brought backlass.The simple method of making high class gear that adopts is eliminated the gap, makes cost too high.In related domain, normally, under the situation that does not improve the gear accuracy of manufacturing, eliminate the gap as far as possible by adopting particular design, manufacturing and assembly method.Up to the present existing kind more than ten is eliminated the method in gap, and several typical elimination gap structures are as follows:
1, tunable center method: reduce and control gap by regulating centre distance, the advantage of this method is Gear center positioning tolerance and the tolerance of size that allows broad; Shortcoming is because regulation range is less, and is higher to matching requirements, is unfavorable for field maintenance.In addition, this method can only be eliminated normal value gap, and can not eliminate variable gap.
2, spring-loaded scissor gears transmission: be a kind of gap eliminator commonly used, its advantage is not tight to the tolerance in source, normal value gap, as not considering the wearing and tearing of tooth and bearing, can eliminate whole gaps continuously; Shortcoming is: 1) because therefore the spring power of carrying must be only limited to the gear transmission of changeing apart from lower greater than maximum driven loads; 2) improper if the gear loading spring is installed, gear easy break-down then.
3, the equipment gear transmission device in anti-gap: this method is each gear is tightened and to eliminate the gap with an equipment gear Transmitted chains, promptly when engagement, the gear that spring in the output shaft first line of a couplet is loaded, and forms the need that work commentaries on classics distance, reaches the purpose of eliminating the gap.
4, have the toothed no gap of engagement gear drive: at least one element in the component with tooth has several teeth to have the lateral cross section of wavy S shape, and when the arrangement of the gear teeth makes the component with tooth engagement, have tooth of wavy lateral cross section and all have a some contact at least, to prevent to produce the gap with each tooth in two of another element relative and adjacent teeth.This mode need be processed the tooth with wavy S shape lateral cross section, the processing technology complexity, and cost is higher.
Said method mostly relies on spring action to realize eliminating the gap, and is unreliable in the occasion that impact loading is arranged, and the special occasions that also is not suitable for impact uses; Input shaft and output shaft disalignment can't be used under some occasion; And exist structure processing technology or assembling than defectives such as complexity.
Summary of the invention
Technical problem to be solved by this invention is the defective that exists at above-mentioned prior art, provide a kind of compact structure reasonable, it is reliable and stable to turn round, processing technology and assembly technology are simple, easy to maintenance, cost is low, and transmitting torque is big, resistance to shock loads, the non-clearance double-gear output transmission method and the transmission device of realization input shaft and output shaft coaxial line.
For solving the problems of the technologies described above, the present invention adopts following technical proposals.
A kind of non-clearance double-gear output transmission method of the present invention, it is characterized in that it is by set two helical gears that rotation direction is opposite on the input shaft, by two drive paths respectively transferring power to the output shaft of input shaft coaxial line on set two output gears, two output gears are passed torque in positive direction actuation and negative sense driving time-division supplementary biography, and guaranteeing does not have the gap when driving commutation.
Realize a kind of non-clearance double-gear output transmission of said method, it is characterized in that it comprises gear housing, input shaft, output shaft, gear I axle and gear II axle, output shaft and input shaft coaxial line, gear I axle and gear II axle are divided into the both sides of input shaft; Described input shaft is provided with the first opposite helical gear of rotation direction and second helical gear, be equiped with the first driven helical gear and first driving gear on the gear I axle, the first driven helical gear and the engagement of first helical gear, gear II axle is equiped with the second driven helical gear and second driving gear, the second driven helical gear and the engagement of second helical gear, be equiped with the 3rd driving gear and first output gear on the described output shaft with the engagement of first driving gear, on output shaft, also be provided with pinion stand by bearing housing, described pinion stand is provided with the 4th driving gear and second output gear, described the 4th driving gear and the engagement of second driving gear.
As a further improvement on the present invention, the input end of described input shaft is provided with locking nut, the described first driven helical gear is anchored on the gear I axle by the first swelling cover, the described second driven helical gear is anchored on the gear II axle by the second swelling cover, and the 3rd driving gear is anchored on the output shaft by the swelling cover.
Further improve as of the present invention, described input shaft is the gear shaft that is made as one with first and second helical gear.
Described output shaft is the gear shaft that is made as one with first output gear.
The 4th driving gear and second output gear that described pinion stand and pinion stand are provided with are made as one, constitute a duplex gear.
Described gear I axle is the gear shaft that is made as one with first driving gear.
Described gear II axle is the gear shaft that is made as one with second driving gear.
Non-clearance double-gear output transmission method of the present invention adopts two drive paths, make two output gears that are positioned on the same axis, the left side of one of them (right side) flank of tooth, another the right side (left side) flank of tooth respectively with the corresponding flank engagement of driven tooth bar or gear ring, article two, drive path is passed torque in positive direction actuation and negative sense driving time-division supplementary biography, has guaranteed when driving commutation very close to each other.Its transmission device, compact structure is reasonable, it is reliable and stable to turn round, and processing technology and assembly technology are simple, and be easy to maintenance, cost is low, can transmit very big moment of torsion, the opposing of impact load is also eliminated the reliable in structure of sideshake than the dependence spring action, and has realized input shaft and output shaft coaxial line, really realized high-precision no gap transmission, be specially adapted to be applied on the machinery of precision machine tool or high-speed overload.
Description of drawings
Fig. 1 is the structural representation of transmission device of the present invention;
Fig. 2 is the partial enlarged drawing at I place among Fig. 1;
Fig. 3 is the partial enlarged drawing at II place among Fig. 1;
Fig. 4 is the profile of tooth schematic representation of driven tooth bar of the present invention or gear ring.
Each label is represented among the figure:
1, gear housing 2, coupling
3, motor 4, input shaft
5, locking nut 6, the first driven helical gear
7, first swelling cover 8, gear I axle
9, first driving gear 10, swelling cover
11, output shaft 12, first output gear
13, second output gear 14, the 4th driving gear
15, the 3rd driving gear 16, second driving gear
17, gear II axle 18, second helical gear
19, second swelling cover, 20, the second driven helical gear
21, first helical gear 22, duplicate gear
23, driven tooth bar or gear ring
Embodiment
Non-clearance double-gear output transmission method of the present invention, it is by set two helical gears that rotation direction is opposite on the input shaft, by two drive paths respectively transferring power to the output shaft of input shaft coaxial line on set two output gears, make two output gears, the left side of one of them output gear (right side) flank of tooth, another output gear right side (left side) flank of tooth respectively with the corresponding flank engagement of driven tooth bar or gear ring, two output gears are passed torque in positive direction actuation and negative sense driving time-division supplementary biography, and guaranteeing does not have the gap when driving commutation.
As shown in Figure 1, 2, 3, non-clearance double-gear output transmission of the present invention, comprise gear housing 1, be installed in input shaft 4, output shaft 11, gear I axle 8 and gear II axle 17 on the gear housing 1, input shaft 4 links to each other with the output shaft of motor 3 by coupling 2, its input end is provided with locking nut 5, can axially strain input shaft 4.Output shaft 11 and input shaft 4 coaxial lines, gear I axle 8 and gear II axle 17 are divided into the both sides of input shaft 4.Input shaft 4 is provided with the first opposite helical gear 21 of rotation direction and second helical gear 18, and as shown in the figure, input shaft 4 is a gear shaft that is provided with first and second helical gear 21,18 in the present embodiment; Be equiped with the first driven helical gear 6 and first driving gear 9 on the gear I axle 8, it is the gear shaft that one and first driving gear 9 are made as one, the first driven helical gear 6 is anchored on the gear I axle 8 and with first helical gear 21 by first swelling cover 7 and meshes, gear II axle 17 is equiped with the second driven helical gear 20 and second driving gear 16, it is the gear shaft that one and second driving gear 16 are made as one, the second driven helical gear 20 is anchored on the gear II axle 17 by second swelling cover 19, and meshes with second helical gear 18.On output shaft 11, be equiped with the 3rd driving gear 15 and first output gear 12, output shaft 11 also is a rooted tooth wheel shaft, be connected as a single entity with first output gear 12,15 of the 3rd driving gears overlap 10 by swelling and are anchored on the output shaft 11, and mesh with first driving gear 9; On output shaft 11, also be provided with pinion stand by bearing housing, pinion stand is provided with the 4th driving gear 14 and second output gear 13, present embodiment middle gear seat and the 4th driving gear 14 and second output gear 13 are connected as a single entity, constitute a duplex gear 22, this duplicate gear 22 is between the 3rd driving gear 15 and first output gear 12, second output gear 13 is near first output gear 12, and both tooth-shape structure parameters are in full accord, the 4th driving gear 14 and 16 engagements of second driving gear.Because duplicate gear 22 is placed on the output shaft 11 by bearing, thereby first and second output gear 12,13 can relatively rotate.
The present invention on input shaft 4, be provided with two rotation directions opposite first, two helical gears 21,18, make first, two output gears 12,13 are meshed with the two adjacent teeth face A and the flank of tooth B (as shown in Figure 4) of driven tooth bar or gear ring 23 respectively, in transmission system just, during backward rotation, divide two drive paths, article one, drive path passes through the first driven helical gear 6 by first helical gear 21, first driving gear 9, the 3rd driving gear 15 drives first output gear 12 to being driven tooth bar or gear ring 23 runnings, another drive path is by the second driven helical gear 20 by second helical gear 18, second driving gear 16, the 4th driving gear 14 drives second output gear 13 to being driven tooth bar or gear ring 23 antiports, reaches the purpose of eliminating the gap.
Installation and Debugging process of the present invention is: make first and second output gear 12,13 respectively with the two adjacent flank of tooth A and flank of tooth B (as shown in Figure 4) tight engagement of driven tooth bar or gear ring 23, the axial adjustment by input shaft 4 can realize above-mentioned requirements.But when the gap in the Transmitted chains is very big, require the width dimensions of first and second helical gear 21,18 very big.Since be subjected to the restriction of spatial structure, obviously inadvisable.First swelling overlaps 7, locking nut 5 carries out coarse adjustment and accurate adjustment realizes by being provided with in the present invention.At first adopt first swelling cover 7, carry out coarse adjustment.Unscrew first swelling cover 7 earlier, make the first driven helical gear 6 can do relative rotation with gear I axle 8, make first and second output gear 12,13 do rightabout rotation respectively, the flank of tooth of this two gear contacts with flank of tooth B with two adjacent flank of tooth A of driven tooth bar or gear ring 23 respectively, lock first swelling cover 7 then, finish coarse adjustment.The concrete practice is, clamp gear I axle 8 with spanner, the crawl actuating motor 3 then, actuating motor 3 is by second helical gear, 18, the second driven helical gear 20, second driving gear 16, the 4th driving gear 14, second output gear 13 drives outside tooth bar or gear ring, because first swelling cover 7 has unclamped, and gear I axle 8 is clamped by spanner, the outside is driven gear or tooth bar will be by first output gear 12, the 3rd driving gear 15 reverse actuation gear I axles 8, when actuating motor 3 electric currents obviously increase, actuating motor 3 stops, and locks first swelling cover 7.At this moment, the left and right sides flank of tooth of first and second output gear 12,13 is driven the corresponding flank engagement of gear or gear ring respectively with the outside, and coarse adjustment is finished.
Adjusting lock nut 5 carries out accurate adjustment then: accurate adjustment is by tightening locking nut 5, and the axial displacement of input shaft 4 realizes thereby backlass is converted to.Because two helical gears on the input shaft 4 are that the rotation direction of first and second helical gear 21,18 is opposite, when tightening locking nut 5, the axial displacement of input shaft 4, the backward rotation of first helical gear 21 and second helical gear 18 will be converted into, drive first output gear 12 and second output gear 13 also with backward rotation, the left and right sides flank of tooth of such first output gear 12 and second output gear 13 will be tightr with the corresponding flank engagement that is driven outside gear ring or tooth bar, and backlass is further eliminated.As shown in Figure 1, make the locking nut 5 that screws up with a wrench, then input shaft 4 will be outside gear-box play, this moment first helical gear 21 will drive the first driven helical gear 6 to just (instead) to rotation, and reach gear I axle 8, reach the 3rd driving gear 15 again by first driving gear 9, reach first output gear 12 at last, with driven tooth bar or gear ring 23 engagements; Simultaneously second helical gear 18 will drive the second driven helical gear 20 to instead (just) to rotation, and reach gear II axle 17, reach the 4th driving gear 14 by second driving gear 16 again, at last by second output gear 13 and driven tooth bar or gear ring 23 engagements.The flank of tooth of first and second output gear 12,13 of such two coaxial lines is tighter with flank of tooth A and flank of tooth B engagement respectively, reaches the purpose of eliminating the gap.Because the helix angle of two first and second helical gears 21,18 on the input shaft 4 is generally very little, first and second output gear 12,13 relative rotations of two coaxial lines that axial adjustment causes are very little, so only play the accurate adjustment effect.After backlass was eliminated, input shaft 4 all was tightened up at axial both direction, can not produce axial float when transmission.
Non-clearance double-gear output transmission method of the present invention adopts two drive paths, the left and right sides flank of tooth that makes two output gears by structural design and adjusting method cleverly respectively with the corresponding flank engagement that is driven tooth bar or gear ring, article two, drive path is passed torque in positive direction actuation and negative sense driving time-division supplementary biography, has guaranteed when driving commutation very close to each other.The gear of this structure has effectively been eliminated backlass, can transmit very big moment of torsion, and the opposing of impact load also than relying on spring action to eliminate the reliable in structure of sideshake, is specially adapted on the machinery of precision machine tool or high-speed overload.
Claims (8)
1, a kind of non-clearance double-gear output transmission method, it is characterized in that it is by set two helical gears that rotation direction is opposite on the input shaft, by two drive paths respectively transferring power to the output shaft of input shaft coaxial line on set two output gears, two output gears are passed torque in positive direction actuation and negative sense driving time-division supplementary biography, and guaranteeing does not have the gap when driving commutation.
2, a kind of non-clearance double-gear output transmission of method according to claim 1, it is characterized in that it comprises gear housing (1), input shaft (4), output shaft (11), gear I axle (8) and gear II axle (17), output shaft (11) and input shaft (4) coaxial line, gear I axle (8) and gear II axle (17) are divided into the both sides of input shaft (4); Described input shaft (4) is provided with opposite first helical gear (21) of rotation direction and second helical gear (18), be equiped with the first driven helical gear (6) and first driving gear (9) on the gear I axle (8), the first driven helical gear (6) and first helical gear (21) engagement, be equiped with the second driven helical gear (20) and second driving gear (16) on the gear II axle (17), the second driven helical gear (20) and second helical gear (18) engagement, be equiped with the 3rd driving gear (15) and first output gear (12) on the described output shaft (11) with first driving gear (9) engagement, on output shaft (11), also be provided with pinion stand by bearing housing, described pinion stand is provided with the 4th driving gear (14) and second output gear (13), described the 4th driving gear (14) and second driving gear (16) engagement.
3, non-clearance double-gear output transmission according to claim 2, the input end that it is characterized in that described input shaft (4) is provided with locking nut (5), the described first driven helical gear (6) is anchored on the gear I axle (8) by the first swelling cover (7), the described second driven helical gear (20) is anchored on the gear II axle (17) by the second swelling cover (19), and the 3rd driving gear (15) is anchored on the output shaft (11) by swelling cover (10).
4,, it is characterized in that described input shaft (4) is the gear shaft that is made as one with first and second helical gear (21,18) according to claim 2 or 3 described non-clearance double-gear output transmissions.
5, non-clearance double-gear output transmission according to claim 4 is characterized in that described output shaft (11) is the gear shaft that is made as one with first output gear (12).
6, non-clearance double-gear output transmission according to claim 5 is characterized in that the 4th driving gear (14) and second output gear (13) that described pinion stand and pinion stand are provided with are made as one, constitute a duplex gear (22).
7, non-clearance double-gear output transmission according to claim 6 is characterized in that described gear I axle (8) is the gear shaft that is made as one with first driving gear (9).
8, non-clearance double-gear output transmission according to claim 7 is characterized in that described gear II axle (17) is the gear shaft that is made as one with second driving gear (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323776A CN100343552C (en) | 2005-11-15 | 2005-11-15 | Non-clearance double-gear output transmission method and transmission device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100323776A CN100343552C (en) | 2005-11-15 | 2005-11-15 | Non-clearance double-gear output transmission method and transmission device |
Publications (2)
| Publication Number | Publication Date |
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| CN1769740A true CN1769740A (en) | 2006-05-10 |
| CN100343552C CN100343552C (en) | 2007-10-17 |
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| CNB2005100323776A Expired - Fee Related CN100343552C (en) | 2005-11-15 | 2005-11-15 | Non-clearance double-gear output transmission method and transmission device |
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| CN (1) | CN100343552C (en) |
Cited By (11)
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| CN101758416A (en) * | 2009-12-04 | 2010-06-30 | 威海华东数控股份有限公司 | Device for eliminating back clearance of X-shaft drive gear box of machine tool |
| CN102537302A (en) * | 2011-12-30 | 2012-07-04 | 大连益利亚工程机械有限公司 | Gapless gear transmission multifunctional limiter |
| CN102597351A (en) * | 2009-09-09 | 2012-07-18 | 恒天(奥地利)控股有限公司 | Device for needling a fibrous web |
| CN102672516A (en) * | 2011-03-14 | 2012-09-19 | 发得科技工业股份有限公司 | Workbench driving device |
| CN102996715A (en) * | 2011-09-19 | 2013-03-27 | 无锡市阳通机械设备有限公司 | Power transmission mechanism |
| CN103573926A (en) * | 2012-07-19 | 2014-02-12 | 伦克股份有限公司 | Power distribution transmission mechanism |
| US8893572B2 (en) | 2011-12-08 | 2014-11-25 | Industrial Technology Research Institute | Backlash eliminating device for helical gears |
| CN106704547A (en) * | 2016-12-08 | 2017-05-24 | 济南二机床集团有限公司 | Double-gear automatic compensation gap elimination transmission structure for swing angle head rotating shaft |
| CN108818009A (en) * | 2018-07-18 | 2018-11-16 | 四川理工学院 | A kind of Multi-axis Machining machine tool high speed high precision turntable |
| CN112178152A (en) * | 2020-10-16 | 2021-01-05 | 魏家斌 | Bevel gear differential mechanism |
| CN113090738A (en) * | 2021-03-26 | 2021-07-09 | 陕西东弘机电设备有限公司 | Cylindrical gear coaxial commutator |
Families Citing this family (2)
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| CN100545487C (en) * | 2008-04-22 | 2009-09-30 | 南京数控机床有限公司 | Clearance eliminating mechanism during a kind of mechanical transmission |
| CN101936365A (en) * | 2010-08-31 | 2011-01-05 | 北京伊贝格机械有限公司 | Multi-output backlash retarding mechanism |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4554842A (en) * | 1983-04-25 | 1985-11-26 | Cincinnati Milacron Inc. | Anti-backlash mechanism for machine drive |
| GB8610756D0 (en) * | 1986-05-02 | 1986-06-11 | Pengilly E A | Power transmission |
| US5240462A (en) * | 1991-03-19 | 1993-08-31 | Isel Co., Ltd. | Planetary reduction gear |
| JPH08303558A (en) * | 1995-04-28 | 1996-11-19 | Isuzu Motors Ltd | Backlash eliminating device |
-
2005
- 2005-11-15 CN CNB2005100323776A patent/CN100343552C/en not_active Expired - Fee Related
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| CN102597351A (en) * | 2009-09-09 | 2012-07-18 | 恒天(奥地利)控股有限公司 | Device for needling a fibrous web |
| CN101758416A (en) * | 2009-12-04 | 2010-06-30 | 威海华东数控股份有限公司 | Device for eliminating back clearance of X-shaft drive gear box of machine tool |
| CN102672516B (en) * | 2011-03-14 | 2014-11-12 | 发得科技工业股份有限公司 | Workbench driving device |
| CN102672516A (en) * | 2011-03-14 | 2012-09-19 | 发得科技工业股份有限公司 | Workbench driving device |
| CN102996715A (en) * | 2011-09-19 | 2013-03-27 | 无锡市阳通机械设备有限公司 | Power transmission mechanism |
| US8893572B2 (en) | 2011-12-08 | 2014-11-25 | Industrial Technology Research Institute | Backlash eliminating device for helical gears |
| CN102537302A (en) * | 2011-12-30 | 2012-07-04 | 大连益利亚工程机械有限公司 | Gapless gear transmission multifunctional limiter |
| CN102537302B (en) * | 2011-12-30 | 2014-12-31 | 大连益利亚工程机械有限公司 | Gapless gear transmission multifunctional limiter |
| CN103573926A (en) * | 2012-07-19 | 2014-02-12 | 伦克股份有限公司 | Power distribution transmission mechanism |
| CN106704547A (en) * | 2016-12-08 | 2017-05-24 | 济南二机床集团有限公司 | Double-gear automatic compensation gap elimination transmission structure for swing angle head rotating shaft |
| CN106704547B (en) * | 2016-12-08 | 2023-06-13 | 济南二机床集团有限公司 | Double-gear automatic compensation anti-backlash transmission structure for swing angle head rotating shaft |
| CN108818009A (en) * | 2018-07-18 | 2018-11-16 | 四川理工学院 | A kind of Multi-axis Machining machine tool high speed high precision turntable |
| CN112178152A (en) * | 2020-10-16 | 2021-01-05 | 魏家斌 | Bevel gear differential mechanism |
| CN112178152B (en) * | 2020-10-16 | 2023-02-21 | 魏家斌 | Bevel gear differential mechanism |
| CN113090738A (en) * | 2021-03-26 | 2021-07-09 | 陕西东弘机电设备有限公司 | Cylindrical gear coaxial commutator |
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| CN100343552C (en) | 2007-10-17 |
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Granted publication date: 20071017 Termination date: 20111115 |