CN101704134B - Variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain - Google Patents
Variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain Download PDFInfo
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- CN101704134B CN101704134B CN2009102340149A CN200910234014A CN101704134B CN 101704134 B CN101704134 B CN 101704134B CN 2009102340149 A CN2009102340149 A CN 2009102340149A CN 200910234014 A CN200910234014 A CN 200910234014A CN 101704134 B CN101704134 B CN 101704134B
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- 238000010862 gear shaping Methods 0.000 title claims abstract description 36
- 230000005540 biological transmission Effects 0.000 title claims abstract description 27
- 230000009347 mechanical transmission Effects 0.000 abstract description 2
- 238000004519 manufacturing process Methods 0.000 abstract 3
- 238000003754 machining Methods 0.000 abstract 1
- 230000000631 nonopiate Effects 0.000 description 15
- 238000010586 diagram Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
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Abstract
The invention provides a variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain, belonging to the technical field of mechanical transmission. The included angle between the output shaft of the variable-angle reversing mechanism and the gear shaping cutter axis of rotation can be changed between 0 degree to 90 degrees, thus solving the problem of the realization of gear shaping machining under the condition of not changing the reversing mechanism of the orthogonal unbiased face gear and nonorthogonal unbiased face gear with different angles. In the invention, in the premise of not increasing manufacturing cost, not changing the cutter and not increasing the manufacturing difficulty, the problem of the manufacturing of the orthogonal unbiased face gear and nonorthogonal unbiased face gear with different angles by the same reversing mechanism in the processing of the gear shaping, thus having dramatic substantial characteristics and prominent improvement.
Description
Technical field
The present invention is a variable-angle reversing mechanism on the face gear shaping machine dividing tooth transmission chain, is one of crucial transmission mechanism of face gear shaping machine, belongs to mechanical transmission fields.
Background technology
The face gear drive be meant be meshed roller gear intersect the implementation space with bevel gear or alternating axis between transmission.According to the relation of roller gear and face gear two axial lines, the face gear drive can be divided into 4 types of not offset, nonopiate not offset, quadrature biasing of quadrature and nonopiate biasings.
When the axis of rotation of roller gear was crossing and vertical with the axis of rotation of face gear, the face gear drive was referred to as not offset gear drive of quadrature, as shown in Figure 1; When the axis of rotation of the axis of rotation of roller gear and face gear intersects but during out of plumb, the face gear drive is referred to as nonopiate not offset gear drive, as shown in Figure 2; When the axis of rotation of roller gear was staggered and vertical with the axis of rotation of face gear, the face gear drive was referred to as the gear drive of quadrature biasing surface, as shown in Figure 3; During staggered and out of plumb, the face gear drive is referred to as nonopiate biasing surface gear drive, as shown in Figure 4 when the axis of rotation of the axis of rotation of roller gear and face gear.
Compare with Bevel Gear Transmission, the face gear drive has following advantage:
(1) owing to the gear with the face gears engaged is an involute cylindrical gear, it moves axially error to not influence of transmission performance, and the influence of other direction is also minimum, need not the mistake proofing design.And in Bevel Gear Transmission, its axial error will cause serious unbalance loading, and therefore important Bevel Gear Transmission must be carried out the mistake proofing design.
(2) when the gear with the face gears engaged be straight spur gear, then do not have axial force on the roller gear, it supports simple, structure takes up room little.And in the Bevel Gear Transmission, supporting complexity because responsive to axial force makes, structure takes up room greatly.
(3) the gear-driven registration of face big than Bevel Gear Transmission can reach 1.6-1.8 when zero load, and under the load effect, its registration will be bigger.
(4) some contact-making surface gear drive still for fixed than transmission, the gearratio of some contact Bevel Gear Transmission then is to fluctuate within the specific limits, so the gear-driven vibration of face and noise are all less than Bevel Gear Transmission.
The face gear working method is one of main contents of face gear drive research.Gear Shaping then is one of main contents of face gear cutting working research.The Gear Shaping principle of face gear is identical with face meshed transmission gear principle, and the roller gear that is about in the face meshed transmission gear changes the gear shaping cutter into, can realize the Gear Shaping of face gear.Shown in not offset gear drive of Fig. 1 quadrature and nonopiate not offset the gear drive of Fig. 2, during not offset and nonopiate not offset the gear Gear Shaping of quadrature, the crossed axis angle of its axis of rotation and gear shaping cutter axis of rotation is inequality.During nonopiate not offset gear of existing face gear Gear Shaping lathe and different angles not offset at the processing quadrature, must be according to the angle of face gear axis of rotation and gear shaping cutter axis of rotation, change the changement of respective angles, thereby realize the processing of not offset gear of different angles.At present, also be not implemented under the situation of not changing changement, just can carry out the Gear Shaping of not offset gear of different angles.Among the present invention on the face gear shaping machine dividing tooth transmission chain effect of variable-angle reversing mechanism be exactly to be implemented under the situation of not changing changement, carry out the Gear Shaping of not offset gear of different angles.The main difficult point of this variable-angle reversing mechanism is not isolate under the driving-chain situation, realizes that the angle between machined surface gear workpiece axis of rotation and the Gear Shaping axis of rotation changes.
Summary of the invention
The present invention is a variable-angle reversing mechanism on the face gear shaping machine dividing tooth transmission chain, nonopiate not offset the gear that mainly solves not offset gear of quadrature and different angles is on shaping machine, do not needing to change under the disalignment angle of cut changement situation, realizing the problem of Gear Shaping.
The technical scheme of variable-angle reversing mechanism is by the primary input axle on the face gear shaping machine dividing tooth transmission chain, the primary input roller gear, the first shunting power shaft, the first shunting roller gear, the first skimmer cone gear, first reversing shaft, the first commutation conical gear, the first interflow conical gear, the second shunting power shaft, the second shunting roller gear, the second skimmer cone gear, second reversing shaft, the second commutation conical gear, the second interflow conical gear, the interflow output bevel gear, the interflow axle, output bevel gear, output commutation conical gear and output shaft are formed;
Wherein first the shunting power shaft, second the shunting power shaft parallel with the primary input axle respectively, first reversing shaft, second reversing shaft are vertical with the primary input axle respectively, first reversing shaft and the second reversing shaft conllinear, the interflow axle can change between 0 °～90 ° around the axis of first reversing shaft or second reversing shaft, and output shaft is vertical mutually with the interflow axle;
Wherein the first shunting roller gear and the first skimmer cone gear all are installed on the first shunting power shaft, the first commutation conical gear and the first interflow conical gear all are installed on first reversing shaft, the primary input roller gear and the first shunting roller gear engagement, the first skimmer cone gear and the first commutation conical gear engagement;
Wherein the second shunting roller gear and the second skimmer cone gear all are installed on the second shunting power shaft, the second commutation conical gear and the second interflow conical gear all are installed on second reversing shaft, the primary input roller gear and the second shunting roller gear engagement, the second skimmer cone gear and the second commutation conical gear engagement;
Wherein collaborate output bevel gear and output bevel gear and all be installed on the axle of interflow, the interflow output bevel gear collaborates the conical gear and the second interflow conical gear engagement with first simultaneously;
Wherein output commutation conical gear is installed on the output shaft, and output commutation conical gear and output bevel gear engagement realize the rotation of output shaft;
Wherein primary input roller gear and first is shunted the gearratio i of roller gear
24Gearratio i with the primary input roller gear and the second shunting roller gear
210Equate; The gearratio i of the first skimmer cone gear and the first commutation conical gear
56Gearratio i with the second skimmer cone gear and the second commutation conical gear
1112Equate; The gearratio i of the first interflow conical gear and interflow output bevel gear
815Gearratio i with the second interflow conical gear and interflow output bevel gear
1415Equate; The gearratio i of the primary input roller gear and the first shunting roller gear
24Gearratio i with the first skimmer cone gear and the first commutation conical gear
56And first the interflow conical gear and the interflow output bevel gear gearratio i
815Again and the gearratio i of output bevel gear and output commutation conical gear
1718Product be 1.
Utilize variable-angle reversing mechanism on the face gear shaping machine dividing tooth transmission chain, can realize need not to change the Gear Shaping of nonopiate not offset gear of not offset gear of quadrature under the changement situation and different angles, when breaking away from the past not offset gear Gear Shaping of different angles, need to change the problem of corresponding axis angle of cut changement.
Description of drawings
Fig. 1 is not offset gear drive schematic diagram of quadrature.
Fig. 2 is nonopiate not offset gear drive schematic diagram.
Fig. 3 is a quadrature biasing surface gear drive schematic diagram.
Fig. 4 is nonopiate biasing surface gear drive schematic diagram.
Fig. 5 is the schematic diagram of variable-angle reversing mechanism output shaft when vertical with gear shaping cutter axis of rotation.Fig. 5-the 1st wherein, front view during vertical output, Fig. 5-the 2nd, right cutaway view during vertical output.
Schematic diagram when Fig. 6 is γ for variable-angle reversing mechanism output shaft and gear shaping cutter axis of rotation angle.Fig. 6-the 1st, front view when angle is γ, 6-2 are angle right cutaway views when being γ.
Fig. 7 is the schematic diagram of variable-angle reversing mechanism output shaft when parallel with gear shaping cutter axis of rotation.Right cutaway view when Fig. 7-the 1st, front view during parallel output, 7-2 are parallel output.
Label title among the figure: 1. primary input axle, 2. primary input roller gear, 3. first shunt power shaft, 4. first shunt roller gear, 5. the first skimmer cone gear, first the commutation conical gear, 7. first reversing shaft, 8. first collaborates conical gear, 9. second shunt power shaft, 10. second shunt roller gear, 11. the second skimmer cone gear, 12. the second commutation conical gear, 13 second reversing shafts, 14. the second interflow conical gear, 15. interflow output bevel gear, 16. interflow axle, 17. output bevel gear, 18. output commutation conical gear, 19. output shaft, 20. gear shaping tool axis.
The specific embodiment
As Fig. 5-shown in Figure 7, composed as follows by the equipment that variable-angle reversing mechanism on the face gear shaping machine dividing tooth transmission chain constitutes:
Primary input roller gear 2 is assemblied on the primary input axle 1, by rotation drive primary input roller gear 2 rotations of primary input axle 1; The primary input roller gear 2 and the first shunting roller gear 4,10 engagements of the second shunting roller gear are rotated by the primary input roller gear 2 promotions first shunting roller gear 4, the second shunting roller gear 10; The first shunting roller gear 4 and the first skimmer cone gear 5 are installed on the first shunting power shaft 3 simultaneously, the second shunting roller gear 10 and the second skimmer cone gear 11 are installed on the second shunting power shaft 9 simultaneously, rotation by the first shunting roller gear 4 drives 3 rotations of the first shunting power shaft, thereby promote 5 rotations of the first skimmer cone gear, rotation by the second shunting roller gear 10 drives 9 rotations of the second shunting power shaft, thereby promotes 11 rotations of the second skimmer cone gear; The first skimmer cone gear 5 and 6 engagements of the first commutation conical gear promote 6 rotations of the first commutation conical gear by the first skimmer cone gear 5; The second skimmer cone gear 11 and 12 engagements of the second commutation conical gear promote 12 rotations of the second commutation conical gear by the second skimmer cone gear 11; The first commutation conical gear 6 and the first interflow conical gear 8 are installed on first reversing shaft 7 simultaneously, because the rotation of the first commutation conical gear 6 promotes 7 rotations of first reversing shaft, thereby drive 8 rotations of the first interflow conical gear; The second commutation conical gear 12 and the second interflow conical gear 14 are installed on second reversing shaft 13 simultaneously, because the rotation of the second commutation conical gear 12 promotes 13 rotations of second reversing shaft, thereby drive 14 rotations of the second interflow conical gear; The first interflow conical gear 8 and the second interflow conical gear 14 mesh with interflow output bevel gear 15 simultaneously, promote 15 rotations of interflow output bevel gear; Interflow output bevel gear 15 and output bevel gear 17 are installed on the interflow axle 16, by rotation drive interflow axle 16 rotations of interflow output bevel gear 15, rotate thereby promote output bevel gear 17; Output commutation conical gear 18 is installed in on the output shaft 19, and output bevel gear 17 and 18 engagements of output commutation conical gear promote 18 rotations of output commutation conical gear; The final motion output that realizes output shaft 19.
In order to realize this mechanism, must meet the following conditions:
1. primary input roller gear 2 and first is shunted the gearratio i of roller gear 4
24Gearratio i with the primary input roller gear 2 and the second shunting roller gear 10
210Equate;
The first skimmer cone gear 5 and first the commutation conical gear 6 gearratio i
56Gearratio i with the second skimmer cone gear 11 and the second commutation conical gear 12
1112Equate;
3. first reversing shaft 7 and second reversing shaft 13 are wanted conllinear;
4. first collaborates conical gear 8 and the gearratio i that collaborates output bevel gear 15
815Gearratio i with the second interflow conical gear 14 and interflow output bevel gear 15
1415Equate;
5. primary input roller gear 2 and first is shunted the gearratio i of roller gear 4
24Gearratio i with the first skimmer cone gear 5 and the first commutation conical gear 6
56And the gearratio i of first interflow conical gear 8 and interflow output bevel gear 15
815Again and the gearratio i of output bevel gear 17 and output commutation conical gear 18
1718Product be 1, promptly
i
24?i
56?i
815?i
1718＝1
Satisfy gearratio i
24i
56i
815i
1718Under=1 condition, the design procedure of a certain variable-angle reversing mechanism
1. the gearratio of the design primary input roller gear 2 and the first shunting roller gear 4 by the Gear Transmission Design method, is determined parameters such as its modulus, the number of teeth, pressure angle;
2. determine the geometric parameter of the second shunting roller gear 10, it is identical with the first shunting roller gear 4 to get its geometric parameter;
3. the gearratio of the first skimmer cone gear 5 and the first commutation conical gear 6 is taken as the gearratio of the first shunting roller gear 4 and primary input roller gear 2,, determines parameters such as its modulus, the number of teeth, pressure angle by the Gear Transmission Design method;
4. the geometric parameter of getting the second skimmer cone gear 11 is identical with the first skimmer cone gear 5, and the geometric parameter of getting the second commutation conical gear 12 is identical with the first commutation conical gear 6;
5. getting gearratio is 1, by the Gear Transmission Design method, determines the first interflow conical gear 8 and parameters such as the modulus that collaborates output bevel gear 15, the number of teeth, pressure angle;
6. the geometric parameter of getting the second interflow conical gear 14 is identical with the first interflow conical gear 8;
7. getting gearratio is 1, by the Gear Transmission Design method, determines output bevel gear 17 and parameters such as the modulus of exporting commutation conical gear 18, the number of teeth, pressure angle;
8. commutation mechanism axis, bearing etc. are designed and choose;
9. carry out designs such as component structural in the changement, casing, lubricated and sealing.
Embodiment one
The gearratio i of the primary input roller gear 2 and the first shunting roller gear 4
24=1/2, modulus m=4, pressure angle α=20 °, the number of teeth z of primary input roller gear 2
2The number of teeth z of=36, the first shunting roller gear 4
4=18; The geometric parameter of the second shunting roller gear 10 is identical with roller gear 4; The gearratio i of the first skimmer cone gear 5 and the first commutation conical gear 6
56=2, modulus m=2, pressure angle α=20 °, the number of teeth z of the first skimmer cone gear 5
5The number of teeth z of=18, the first commutation conical gear 6
6=36; The geometric parameter of the second skimmer cone gear 11 is identical with the first skimmer cone gear 5, the geometric parameter of the second commutation conical gear 12 and the first commutation conical gear 6; The modulus m=1 of the first interflow conical gear 8, the second interflow conical gear 14 and interflow output bevel gear 15, pressure angle α=20 °, number of teeth z
8=z
14=z
15=16; The modulus m=2 of output bevel gear 17 and output commutation conical gear 18, pressure angle α=20 °, number of teeth z
17=z
18=20.
Embodiment two
The gearratio i of the primary input roller gear 2 and the first shunting roller gear 4
24=1/3, modulus m=6, pressure angle α=25 °, the number of teeth z of primary input roller gear 2
2The number of teeth z of=60, the first shunting roller gear 4
4=20; The geometric parameter of the second shunting roller gear 10 is identical with roller gear 4; The gearratio i of the first skimmer cone gear 5 and the first commutation conical gear 6
56=3, modulus m=3, pressure angle α=25 °, the number of teeth z of the first skimmer cone gear 5
5The number of teeth z of=17, the first commutation conical gear 6
6=51; The geometric parameter of the second skimmer cone gear 11 is identical with the first skimmer cone gear 5, the geometric parameter of the second commutation conical gear 12 and the first commutation conical gear 6; The modulus m=1.5 of the first interflow conical gear 8, the second interflow conical gear 14 and interflow output bevel gear 15, pressure angle α=25 °, number of teeth z
8=z
14=z
15=18; The modulus m=3 of output bevel gear 17 and output commutation conical gear 18, pressure angle α=25 °, number of teeth z
17=z
18=22.
In a word, according to Fig. 5-7 as can be known, because interflow output bevel gear 15 can be around the common axis line rotation of first reversing shaft 7 and second reversing shaft 13, therefore can change the axis of rotation of interflow output bevel gear 15 and the angle between first reversing shaft 7 and second reversing shaft, 13 common axis lines, thereby realize that the angle between output shaft 19 and the gear shaping tool axis 20 changes.When processing nonopiate not offset gear of not offset gear of quadrature or a certain angle, adjust the axis of rotation of interflow output bevel gear 15 and the angle between first reversing shaft 7 and second reversing shaft, 13 common axis lines earlier, make its angle identical with not offset the gear of quadrature or the angle of nonopiate not offset gear of require processing, the position of fixing then interflow output bevel gear 15, thereby the Gear Shaping of nonopiate not offset gear of realization not offset gear of quadrature or respective angles.
Claims (1)
1. variable-angle reversing mechanism on the face gear shaping machine dividing tooth transmission chain is characterized in that:
By primary input axle (1), primary input roller gear (2), the first shunting power shaft (3), the first shunting roller gear (4), the first skimmer cone gear (5), first reversing shaft (7), the first commutation conical gear (6), the first interflow conical gear (8), the second shunting power shaft (9), the second shunting roller gear (10), the second skimmer cone gear (11), second reversing shaft (13), the second commutation conical gear (12), the second interflow conical gear (14), interflow output bevel gear (15), interflow axle (16), output bevel gear (17), output commutation conical gear (18) and output shaft (19) are formed;
Wherein first the shunting power shaft (3), second the shunting power shaft (9) parallel with primary input axle (1) respectively, first reversing shaft (7), second reversing shaft (13) are vertical with primary input axle (1) respectively, first reversing shaft (7) and second reversing shaft (13) conllinear, interflow axle (16) can change between 0 °～90 ° around the axis of first reversing shaft (7) or second reversing shaft (13), and output shaft (19) is vertical mutually with interflow axle (16);
Wherein the first shunting roller gear (4) and the first skimmer cone gear (5) all are installed on the first shunting power shaft (3), the first commutation conical gear (6) and the first interflow conical gear (8) all are installed on (7) on first reversing shaft, the primary input roller gear (2) and first shunting roller gear (4) engagement, the first skimmer cone gear (5) and first commutation conical gear (6) engagement;
Wherein the second shunting roller gear (10) and the second skimmer cone gear (11) all are installed on the second shunting power shaft (9), the second commutation conical gear (12) and the second interflow conical gear (14) all are installed on second reversing shaft (13), the primary input roller gear (2) and second shunting roller gear (10) engagement, the second skimmer cone gear (11) and second commutation conical gear (12) engagement;
Wherein collaborate output bevel gear (15) and all be installed on interflow axle upward (16) with output bevel gear (17), interflow output bevel gear (15) meshes with the first interflow conical gear (8) and the second interflow conical gear (14) simultaneously;
Wherein output commutation conical gear (18) is installed on the output shaft (19), and output commutation conical gear (18) and output bevel gear (17) engagement are realized the rotation of output shaft;
Wherein primary input roller gear (2) and first is shunted the gearratio i of roller gear (4)
24Gearratio i with the primary input roller gear (2) and the second shunting roller gear (10)
210Equate; The gearratio i of the first skimmer cone gear (5) and the first commutation conical gear (6)
56Gearratio i with the second skimmer cone gear (11) and the second commutation conical gear (12)
1112Equate; The gearratio i of the first interflow conical gear (8) and interflow output bevel gear (15)
815Gearratio i with the second interflow conical gear (14) and interflow output bevel gear (15)
1415Equate; The gearratio i of the primary input roller gear (2) and the first shunting roller gear (4)
24Gearratio i with the first skimmer cone gear (5) and the first commutation conical gear (6)
56And the first interflow conical gear (8) and collaborate the gearratio i of output bevel gear (15)
815Again and the gearratio i of output bevel gear (17) and output commutation conical gear (18)
1718Product be 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009102340149A CN101704134B (en) | 2009-11-19 | 2009-11-19 | Variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009102340149A CN101704134B (en) | 2009-11-19 | 2009-11-19 | Variable-angle reversing mechanism on face gear shaping machine dividing tooth transmission chain |
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| Publication Number | Publication Date |
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| CN101704134A CN101704134A (en) | 2010-05-12 |
| CN101704134B true CN101704134B (en) | 2011-02-16 |
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101979202B (en) * | 2010-09-08 | 2012-10-03 | 北京航空航天大学 | Face gear numerical control machining device and machining method |
| CN102601458A (en) * | 2012-03-23 | 2012-07-25 | 河南科技大学 | Gear shaping machining method for gears with inclined tooth surfaces |
| CN104019337B (en) * | 2014-05-23 | 2016-01-13 | 郑州机械研究所 | Two rotary shaft mechanisms that high rigidity gyration center is orthogonal can be realized |
| CN107186622A (en) * | 2017-06-28 | 2017-09-22 | 斯幼云 | A kind of convenient cup device |
| CN107309794A (en) * | 2017-06-28 | 2017-11-03 | 斯幼云 | A kind of cup device |
| CN107322115B (en) * | 2017-08-30 | 2019-04-05 | 佛山科学技术学院 | One kind becoming helical angle gear wheel processing unit (plant) by tooth |
| CN111022601B (en) * | 2019-10-16 | 2021-05-07 | 南京航空航天大学 | Gyroplane tilting mechanism with reverse self-locking capacity |
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