CN107035831B - Separated time precision gear transmission mechanism - Google Patents
Separated time precision gear transmission mechanism Download PDFInfo
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- CN107035831B CN107035831B CN201710313911.3A CN201710313911A CN107035831B CN 107035831 B CN107035831 B CN 107035831B CN 201710313911 A CN201710313911 A CN 201710313911A CN 107035831 B CN107035831 B CN 107035831B
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- 230000007246 mechanism Effects 0.000 title claims abstract description 67
- 238000005096 rolling process Methods 0.000 claims abstract description 28
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- WSNMPAVSZJSIMT-UHFFFAOYSA-N COc1c(C)c2COC(=O)c2c(O)c1CC(O)C1(C)CCC(=O)O1 Chemical compound COc1c(C)c2COC(=O)c2c(O)c1CC(O)C1(C)CCC(=O)O1 WSNMPAVSZJSIMT-UHFFFAOYSA-N 0.000 claims 2
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Classifications
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- 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
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
- F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
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- Mechanical Engineering (AREA)
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Abstract
The present invention relates to separated time precision gear transmission mechanisms, belong to precision gear transmission mechanism field, including being set to the intracorporal cylinder wheel of chamber and gear that are made of end cap and shell, cylinder wheel and gear engaged transmission, it is characterized in that: the cylinder wheel includes the roller around the setting of its axle center, the geometric center lines of roller are located on the basic circle of cylinder wheel, are engaged using multiple rollers with gear, realize the transmitting of revolving speed and torque；Roller both ends are equipped with needle roller, realize roller in the pure rolling of the flank of tooth, transmission efficiency is high, and abrasion is small, and drive life is long；The number of teeth for participating in engagement is more, stable drive；Mechanism is anodontia side back gap, high transmission accuracy；Processing and manufacturing is simple.
Description
Technical field
The invention belongs to precision gear transmission mechanism fields, and in particular to separated time precision gear transmission mechanism.
Background technique
The composition such as gear drive major gear, as component part important in gearing, gear drive
Very extensive application is obtained in the industrial production.Large-power High-Speed gear transmission structure is more complex, and the accuracy of manufacture is more demanding；
There is opposite sliding in the flank of tooth, be also easy to produce abrasion；There are flank back clearances, influence transmission accuracy.
Summary of the invention
In order to solve deficiency present in above-mentioned technology, the present invention provides a kind of separated time precision gear transmission mechanism.According to
Gear envelope principle designs tooth, realizes that the rolling of gear is engaged by installing needle roller on gear.By changing gear
Transmission mechanism, can be designed as retarder by the number of upper tooth and speed increaser uses；Gear and cylinder wheel basic circle are tangent, in pitch circle
Place is pure rolling, and transmission ratio is definite value；The flank of tooth is pure rolling, and transmission efficiency is high, and abrasion is small, and drive life is long；Participation is nibbled
The number of teeth of conjunction is more, stable drive；Mechanism is anodontia side back gap, high transmission accuracy；Processing and manufacturing is simple.
Technical solution used by the invention patent is: separated time precision gear transmission mechanism includes gear, cylinder wheel, rolling
Column, key, bearing, shell, baffle, bolt, needle roller, axis；It is characterized in that cylinder wheel is circumferentially uniformly distributed ZgA hole is distributed radius of circle
For r0, roller is mounted in hole by needle roller, and roller number is Zg, roller radius is r, and baffle is mounted on cylinder wheel by screw
End face, gear are circumferentially uniformly machined with ZcA tooth, base radius R, Z1=R/r0, dividing coefficient is k.
At combination cylinder wheel, needle roller eliminates the cunning of roller and cylinder wheel for cylinder wheel, roller, bolt, needle roller, axis, baffle group
Dynamic friction, baffle eliminate roller axial direction displacement freedom, and baffle and idler wheel eliminate the axial freedom of needle roller.
Relationship between roller number and the number of teeth is ZgR=Zcr0, Z1=R/r0, Z1It is the positive reality of finite term for fractional part
Number.
Separated time includes outer separated time and interior separated time, and interior separated time can be according to r0It is divided into interior separated time and inside and outside separated time with the size of R.
Z1When > 1, interior separated time is known as interior separated time；1 > Z1When > 0, interior separated time is known as inside and outside separated time.Divide coefficient for k, k ∈ [1,
0)。
The outer separated time tooth surface equation of i-th of tooth is
H is gear width, Φ in formulaiValue range and i and tooth number ZcIt is related,For normal angle.
The outer practical flank of tooth of separated time is formed after outer separated time flank of tooth pair-wise offset, the gear for being machined with the practical flank of tooth of outer separated time is known as
Outer split gear.Outer split gear practical tooth is the pair-wise offset face of the outer separated time flank of tooth of gear, and offset distance is roller radius.Roller
Geometric center is on cylinder wheel basic circle, roller external cylindrical surface pure rolling in gear practical tooth, realizes engaged transmission.
The interior separated time tooth surface equation of i-th of tooth is
H is gear width, Φ in formulaiValue range and i and tooth number ZcIt is related,For normal angle.
The practical flank of tooth of separated time in being formed after interior separated time flank of tooth pair-wise offset, the gear for being machined with the practical flank of tooth of interior separated time are known as
Interior split gear.Interior split gear practical tooth is the pair-wise offset face of the separated time flank of tooth in gear, and offset distance is roller radius.Roller
Geometric center is on cylinder wheel basic circle, roller external cylindrical surface pure rolling in gear practical tooth, realizes engaged transmission.
The gear fabricated according to outer separated time and interior separated time can form gear train assembly with combination cylinder wheel, and gear passes
Dynamic system includes single gear transmission system, multi-stage gear driving system and planetary transmission system.
The advantages of the invention patent and beneficial effect are: separated time precision gear transmission mechanism can be realized no back clearance transmission,
High transmission accuracy, transmission efficiency is high, and structure is simple, and processing and manufacturing is simple, and abrasion is small, and the service life is long, stable transmission, can be used as deceleration
Device and speed increaser use.
Detailed description of the invention
Fig. 1 is outer separated time precision gear transmission mechanism structure diagram；
Fig. 2 is outer separated time precision gear transmission mechanism engaging portion structure diagram；
Fig. 3 is interior separated time precision gear transmission mechanism structure diagram；
Fig. 4 is interior separated time precision gear transmission mechanism engaging portion structure diagram；
Fig. 5 is inside and outside separated time precision gear transmission mechanism structure diagram；
Fig. 6 is inside and outside separated time precision gear transmission mechanism engaging portion structure diagram；
Fig. 7 is outer interior separated time precision planetary gear transmission mechanism structure diagram；
Fig. 8 is outer interior separated time precision planetary gear transmission mechanism engaging portion structure diagram；
Fig. 9 is outer interior separated time precision two-row planetary gear transmission mechanism structure diagram；
Figure 10 is outer interior separated time precision two-row planetary gear transmission mechanism engaging portion structure diagram；
Figure 11 is outer interior separated time precision planetary gear transmission mechanism structure diagram；
Figure 12 is outer interior separated time precision planetary gear transmission mechanism engaging portion structure diagram；
Figure 13 is to pre-tighten outer separated time precision gear transmission mechanism structure diagram；
Figure 14 is big slide block structure schematic diagram；
Figure 15 is slider I structure diagram；
Figure 16 is II structure diagram of sliding block；
Figure 17 is that combination pre-tightens roller structure schematic diagram；
Figure 18 is VII structure diagram of cylinder wheel；
Figure 19 is supporting structure schematic diagram.
In above-mentioned attached drawing: 1. needle rollers I, 2. big keys I, 3. big axis I, 4. cylinder wheels I, 5. small keys I, 6. small axis I, 7. small axis
Hold I, 8. shells I, 9. rollers I, 10. bolts I, 11. big bearings I, 12. baffles I, 13. gears I, 14. end caps, 15 bolt of cover
I, 16. needle rollers II, 17. cylinder wheels II, 18. small keys II, 19. gears II, 20. big bearings II, 21. big keys II, 22. big axis II,
23. shell II, 24. rollers II, 25. bolts II, 26. small axis II, 27. small bearings II, 28. baffles II, 29. end caps II, 30. ends
Bonnet bolt II, 31. needle rollers III, 32. rollers III, 33. shells III, 34. small keys III, 35. gears III, 36. big keys III, 37. big axis
III, 38. big bearings III, 39 cylinder wheels III, 40. baffles III, 41. end caps III, 42. bolts III, 43. small axis III, 44. small bearings
III, 45. bolt of cover III, 46. needle rollers IV, 47. cylinder wheels IV, 48. bearings I, 49. axis I, 50. big keys IV, 51. big bearings IV,
52. shell IV, 53. retainers I, 54. pinion gears I, 55. rollers IV, 56. end caps IV, 57. retaining rings I, 58. bolts IV, 59. gears
Plate IV, 60. small keys IV, 61. small axis IV, 62. small bearings IV, 63. bolt of cover IV, 64. big axis IV, 65. needle rollers V, 66. rollings
Column V, 67. bearings II, 68. axis II, 69. retainers II, 70. big keys V, 71. big axis V, 72. big bearings V, 73. shells V,
74. roller VI, 75. baffles V, 76. end caps V, 77. retaining rings II, 78. double gears, 79. baffles VI, 80. cylinder wheels V, 81.
Bolt VI, 82. small axis V, 83. small bearings V, 84. small keys V, 85. needle rollers VI, 86. bolts V, 87. bolt of cover V, 88.
Needle roller VI, 89. rollers VI, 90. bearings III, 91. axis III, 92. retainers III, 93. big keys VI, 94. big axis VI, 95. big bearings
VI, 96. shells VI, 97. retaining rings III, 98. double wheels, 99. small front aprons, 100. small bearings VI, 101. small keys VI, 102. small axis
VI, 103. pinion gears II, 104. bolts VII, 105. big baffles, 106. bolt of cover VI, 107. end caps VI, 108. needle rollers VII,
109. big key VII, 110 sliding block baffles, 111. casing bolts, 112. sliding block bolts I, 113. slider Is, 114. small axis VII, 115. is small
Bearing VII, 116 big sliding blocks, 117. sliding block bolts II, 118. sliding blocks II, 119. rollers VII, 120. fixing bolts, 121. big axis
VII, 122. cylinder wheels VI, 123. big bearings VII, 124. axial baffles, 125. gears IV, 126. small keys VII, 127. bolt of cover
VII, 128. end caps VII, 129. shells VII, 130. needle rollers VIII, 131. rollers VIII, 132. positioning bolts, 133. positioning baffles, 134.
End face bolt, 135. brackets, 136. cylinder wheels VII, 137. fixed baffles.
Specific embodiment
With reference to the accompanying drawing and specific embodiment the invention will be further described:
Specific embodiment 1
Fig. 1 is outer separated time precision gear transmission mechanism specific embodiment disclosed by the invention, it is characterised in that I 13 base of gear
Circle is 40mm, facewidth 20mm, and external cylindrical surface is circumferentially uniformly machined with 10 teeth, and I 4 basic circle of cylinder wheel is 80mm, on cylinder wheel I 4
Circumferential to be uniformly equipped with 20 rollers I 9, I 9 diameter of roller is 4mm, and I 9 geometric center lines of roller are on I 4 basic circle of cylinder wheel, rolling
I 9 both ends of column are separately installed with 8 needle rollers I 1, and needle roller I 1 is circumferential to be uniformly distributed, and baffle I 12 is mounted on cylinder wheel by bolt I 10
I 4 end faces, gear I 13 are mounted on small axis I 6, and cylinder wheel I 4 is mounted on big axis I 3, and big axis I 3 and small I 6 centre of gyration of axis are flat
Row, distance are 60mm, and I 13 flank of tooth of gear and roller I 9 are tangent, divide coefficient k=1.
The outer separated time tooth surface equation of i-th of tooth is on gear I 13
Cylinder wheel I 4 and baffle I 12 limit needle roller I 1, roller I 9 moves axially.
When small axis I 6 is as input shaft, outer separated time precision gear transmission mechanism is used as deceleration mechanism, and big axis I 3 rotates
Direction is opposite with small axis I 6.Small I 6 band moving gear I 13 of axis rotates, and tooth pushes roller I 9 on gear I 13, and roller I 9 is in gear I 13
Pure rolling on the flank of tooth, roller I 9 drive I 4 uniform rotation of cylinder wheel by needle roller I 1, and big axis I 3 exports revolving speed, and transmission ratio is definite value
I=2.
When big axis I 3 is as input shaft, outer separated time precision gear transmission mechanism is used as speed increasing mechanism.Big axis I 3 drives
Cylinder wheel I 4 rotates, and cylinder wheel I 4 drives roller I 9 to move by needle roller I 1, roller I 9 and I 13 flank engagement of gear, roller I 9
The pure rolling on I 13 flank of tooth of gear, roller I 9 push I 13 uniform rotation of gear, and small axis I 6 exports revolving speed, and transmission ratio is definite value
0.5。
Specific embodiment 2
Fig. 3 is interior separated time precision gear transmission mechanism specific embodiment disclosed by the invention, it is characterised in that gear II
19 basic circles are 200mm, facewidth 20mm, and inner cylinder face is circumferential to be uniformly machined with 50 teeth, and II 17 basic circle of cylinder wheel is 80mm, cylinder
It takes turns and 20 rollers II 24 is circumferentially uniformly installed on II 17, II 24 diameter of roller is 4mm, and II 24 geometric center lines of roller are in cylinder
It takes turns on II 17 basic circles, II 24 both ends of roller are separately installed with 8 needle rollers II 16, and needle roller II 16 is circumferential to be uniformly distributed, baffle II 28
II 17 end face of cylinder wheel is mounted on by bolt II 25.Gear II 19 is mounted on big axis II 22, and cylinder wheel II 17 is mounted on small
On axis II 26, big axis II 22 is parallel with small II 26 centre of gyration of axis, and distance is 60mm, II 19 flank of tooth of gear and II 24 phase of roller
It cuts.Cylinder wheel II 17 and baffle II 28 limit needle roller II 16, roller II 24 moves axially, and divide coefficient k=1.
The interior separated time tooth surface equation of i-th of tooth is on gear II 19
When big axis II 22 is as input shaft, interior separated time precision gear transmission mechanism is used as speed increasing mechanism, small axis II
26 direction of rotation are identical as big axis II 22.Big II 22 band moving gear II 19 of axis rotates, and the tooth of gear II 19 pushes roller II 24, rolling
Column II 24 drives cylinder wheel II 17 to rotate in II 19 flank of tooth pure rolling of gear, roller II 24 by needle roller II 16, and small axis II 26 is defeated
Constant rotational speed out, transmission ratio are steady state value 0.4.
When small axis II 26 is as input shaft, interior separated time precision gear transmission mechanism is used as deceleration device, big axis II
22 direction of rotation are identical as small axis II 26.Small axis II 26 drives cylinder wheel II 17 to rotate, and cylinder wheel II 17 is pushed away by needle roller II 16
Moving gear II 19 rotates, roller II 16 and II 19 flank engagement of gear, roller II 16 pure rolling, roller on II 19 flank of tooth of gear
II 24 push II 19 uniform rotation of gear, and big axis II 22 exports constant rotational speed, and transmission ratio is definite value 2.5.
Specific embodiment 3
Fig. 5 is inside and outside separated time precision gear transmission mechanism specific embodiment disclosed by the invention, it is characterised in that gear III
35 basic circles are 80mm, facewidth 20mm, and external cylindrical surface is circumferential to be uniformly machined with 20 teeth, and III 39 basic circle of cylinder wheel is 200mm, cylinder
It takes turns and 50 rollers III 32 is circumferentially uniformly installed on III 39, III 32 diameter of roller is 4mm, and III 32 geometric center lines of roller are in cylinder
It takes turns on III 39 basic circles, III 32 both ends of roller are separately installed with 8 needle rollers III 31, and needle roller III 31 is circumferential to be uniformly distributed, baffle III 40
III 39 end face of cylinder wheel is mounted on by bolt III 42.Gear III 35 is mounted on small axis III 43, and cylinder wheel III 39 is mounted on greatly
On axis III 37, big III 37 centre of gyration of axis is parallel with small III 43 centre of gyration of axis, and distance is 60mm, III 35 flank of tooth of gear and roller
III 32 is tangent.Cylinder wheel III 39 and baffle III 40 limit needle roller III 31, roller III 32 moves axially, and divide coefficient k=1.
The inside and outside separated time tooth surface equation of i-th of tooth is on gear III 35
When small axis III 43 is as input shaft, inside and outside separated time precision gear transmission mechanism is used as deceleration mechanism, big axis III
37 direction of rotation are identical as small axis III 43.Small III 43 band moving gear III 35 of axis rotates, and the tooth on gear III 35 pushes roller III 32,
Roller III 32 drives cylinder wheel III 39 to rotate in III 35 flank of tooth pure rolling of gear, roller III 32 by needle roller III 31, big axis III 37
Constant rotational speed is exported, transmission ratio is definite value 2.5.
When big axis III 37 is as input shaft, inside and outside separated time precision gear transmission mechanism is used as speeder, small axis III
43 direction of rotation are identical as big axis III 37.Big axis III 37 drives cylinder wheel III 39 to rotate by big key 36, and cylinder wheel III 39 passes through
Needle roller III 31 drives roller III 32 to move, and roller III 32 pushes gear III 35 to rotate, roller III 32 and III 35 flank engagement of gear,
The pure rolling on III 35 flank of tooth of gear of roller III 32, roller III 32 push III 35 uniform rotation of gear, and small axis III 43 stablizes output
Revolving speed, transmission ratio are definite value 0.4.
Specific embodiment 4
Fig. 7 is outer interior separated time precision planetary gear transmission mechanism specific embodiment disclosed by the invention, it is characterised in that outer
IV 52 inner cylinder face of shell is circumferentially uniformly machined with 50 teeth, and the basic circle of tooth is 200mm, facewidth 20mm, pinion gear I on shell IV 52
54 cylindrical surface peripherals are uniformly machined with 10 teeth, and the basic circle of tooth is 40mm, facewidth 20mm, IV 47 base of cylinder wheel in pinion gear I 54
Circle, which is that 80mm cylinder wheel IV 47 is circumferential, is uniformly equipped with 20 rollers IV 55, and IV 55 diameter of roller is 4mm, in IV 55 geometry of roller
For heart line on IV 47 basic circle of cylinder wheel, IV 55 both ends of roller are separately installed with 8 needle rollers IV 46, and needle roller IV 46 is circumferential uniformly to be divided
Cloth, baffle IV 59 are mounted on IV 47 end face of cylinder wheel by bolt IV 58.
The interior separated time of single tooth on shell IV 52, divides the tooth surface equation of coefficient k=1, i-th tooth to be
Pinion gear I 54 is mounted on small axis IV 61, and retainer I 53 is mounted on big axis IV 64, big IV 64 centre of gyration of axis
It is overlapped with small IV 61 centre of gyration of axis, the flank of tooth of tooth and roller IV 55 are tangent on shell IV 52.Cylinder wheel IV 47 and baffle IV 59
Limit needle roller IV 46, roller IV 55 moves axially.
The outer separated time of single tooth in pinion gear I 54, divides the tooth surface equation of coefficient k=1, i-th tooth to be
Needle roller IV 46, roller IV 55, cylinder wheel IV 47, baffle IV 59, bolt IV 58 form combination cylinder wheel.Combination cylinder
Wheel is connect by bearing I 48 with axis I 49, and 3 combination cylinder wheels are circumferentially distributed in retainer I 53, roller IV on combination cylinder wheel
55 can be tangent with the flank of tooth of tooth on shell IV 52, gear IV 54.
Small axis IV 61 is used as input terminal, and outer interior separated time precision planetary gear transmission mechanism is deceleration device.IV 61 turns of small axis
Speed is constant, and small axis IV 61 drives pinion gear I 54 to rotate by small key IV 60, and pinion gear I 54 pushes roller IV 55 to move, shell IV
Tooth on 52 limits roller IV 55, so that the basic circle pure rolling of IV 47 basic circle of cylinder wheel tooth on shell IV 52, cylinder wheel IV 47
It is moved by I 48 band moving axis I 49 of bearing, axis I 49 pushes retainer I 53 to rotate, and retainer I 53 drives big axis by big key IV 50
IV 64 uniform rotation, big axis IV 64 export constant rotational speed, and big IV 64 direction of rotation of axis is identical as small axis IV 61, and transmission ratio is definite value
6。
Specific embodiment 5
Fig. 9 is outer interior separated time precision two-row planetary gear transmission mechanism specific embodiment disclosed by the invention, and feature exists
It is 200mm in V 73 basic circle of shell, V 73 inner cylinder face of shell is circumferentially uniformly equipped with 50 rollers V 66, V 66 diameter of roller
For 4mm, roller V 66 is connect by 8 needle rollers V 65 with shell V 73, and 8 needle rollers V 65 are uniformly distributed in V 66 outer circle of roller
Cylinder, shell V 73 and baffle V 75 limit needle roller V 65, roller V 66 moves axially.
Double 78 gear wheel basic circle of gear is 80mm, and facewidth 20mm, double 78 pinion gear basic circle of gear is 70mm, the facewidth
For 20mm, double 78 gear wheel basic circle of gear is 80mm, facewidth 20mm.Double gear 78 is mounted on axis by bearing II 67
On II 68, axis II 68 is mounted on retainer II 69.3 axis II 68 are circumferential to be uniformly distributed on retainer II 69, each axis II
A double gear 78 is mounted on 68.Retainer II 69 is connect by big key V 70 with big axis V 71.Big axis V 71 passes through
Big bearing V 72 is installed on shell V 73.
The inside and outside separated time of single tooth on double 78 gear wheel of gear, divides the tooth surface equation of coefficient k=1, i-th tooth to be
The outer separated time of single tooth in double 78 pinion gear of gear, divides the tooth surface equation of coefficient k=1, i-th tooth to be
V 80 inner cylinder face of cylinder wheel is circumferentially uniformly equipped with 15 rollers VI 74, and roller VI 74 passes through 8 needle rollers VI 85
It is connect with cylinder wheel V 80,8 needle rollers VI 85 are uniformly distributed in VI 74 external cylindrical surface of roller, and cylinder wheel V 80 and baffle VI 79 limit
Needle roller VI 85 processed, roller VI 74 move axially.Baffle VI 79 is installed on V 80 end face of cylinder wheel by bolt VI 81.Cylinder wheel V
80 are connect by small key V 84 with small axis 82, and small axis 82 is installed on end cap V 76 by small bearing V 83.
Needle roller V 65, roller V 66, shell V 73, baffle V 75, the composition combination shell of bolt V 86.3 double gears
Gear wheel on 78 is tangent with the roller V 66 combined on shell, the pure rolling of the flank of tooth of the tooth on double gear 78 of roller V 66
It is dynamic.Needle roller VI 85, roller VI 74, cylinder wheel V 80, baffle VI 79, bolt VI 81 form combination cylinder wheel II.3 double gears
Pinion gear on 78 is tangent with the roller VI 74 on cylinder wheel II, the pure rolling of the flank of tooth of the small tooth on double gear 78 of roller VI 74
It is dynamic.
Small axis V 82 is used as input terminal, and outer interior separated time precision two-row planetary gear transmission mechanism is deceleration device.Small axis V
82 invariablenes turning speeds, small axis V 82 drive combination cylinder wheel II to rotate by small key V 84, the roller in the rotation of combination cylinder wheel II
VI 74 push double gear 78 to move, and double gear 78 is limited by roller V 66, and double gear 78 rotates.Double gear 78 is logical
Crossing axis II 68 pushes retainer II 69 to rotate, and retainer II 69 drives big V 71 uniform rotation of axis, big axis V by big key V 70
71 rotation directions are identical as small axis V 82.Transmission ratio is definite value 4.2.
Specific embodiment 6
Figure 11 is outer interior separated time precision planetary gear transmission mechanism specific embodiment disclosed by the invention, it is characterised in that outer
VI 96 basic circle of shell is 200mm, and shell VI 96 inner cylinder face is circumferentially uniformly equipped with 50 rollers VII 89, VII 89 diameter 4mm of roller,
Roller VII 89 is connect by 8 needle rollers VII 88 with shell VI 96, and 8 needle rollers VII 88 are uniformly distributed in VII 89 external cylindrical surface of roller,
Shell VI 96 and big baffle 105 limitation needle roller VII 88, roller VII 89 move axially, and II 103 basic circle of pinion gear is 40mm, and the facewidth is
20mm。
98 rolling circles of double wheel are 80mm, and facewidth 20mm, 98 cylinder wheel basic circles of double wheel are 80mm, and the facewidth is
20mm.Double wheel 98 is mounted on axis III 91 by bearing III 90, and axis III 91 is mounted on retainer III 92.3 axis III 91 weeks
To being uniformly distributed on retainer III 92, a double wheel 98 is mounted on each axis III 91.Retainer III 92 passes through big key
VI 93 connect with big axis VI 94.Big axis VI 94 is installed on shell VI 96 by big bearing VI 95.
The inside and outside separated time of single tooth on 98 gears of double wheel, divides the tooth surface equation of coefficient k=1, i-th tooth to be
The outer separated time of single tooth in pinion gear II 103, divides the tooth surface equation of coefficient k=1, i-th tooth to be
98 upper rollers of double wheel are partially circumferentially uniformly equipped with 20 rollers VII 89, and roller VII 89 passes through 8 needle rollers VII 88
It is connect with pinion gear II 103,8 needle rollers VII 88 are uniformly distributed in VII 89 external cylindrical surface of roller, and double wheel 98 is limited with small front apron 99
Needle roller VII 88 processed, roller VII 89 move axially.Small front apron 99 is installed on 98 end faces of double wheel by bolt VII 104.Pinion gear II
103 are connect by small key VI 101 with small axis VI 102, and small axis VI 102 is installed on end cap VI 107 by small bearing VI 100.
Needle roller VII 88, roller VII 89, shell VI 96, big baffle 105, the composition combination shell of bolt VII 104.3 double wheels
Gear teeth face on 98 is tangent with the roller VII 89 combined on shell, the pure rolling of the flank of tooth of the tooth on double wheel 98 of roller VII 89
It is dynamic.Needle roller VII 88, roller VII 89,98 cylinder wheel parts of double wheel, small front apron 99, bolt VII 104 form combination cylinder wheel.Small tooth
It is tangent with the roller VII 89 on 3 double wheels 98 to take turns II 103 flank of tooth, roller VII 89 is in II 103 flank of tooth pure rolling of pinion gear.
Small axis VI 102 is used as input terminal, and outer interior separated time precision planetary gear transmission mechanism is deceleration device.Small axis VI 102
Invariablenes turning speed, small axis VI 102 drive pinion gear II 103 to rotate by small key VI 101, and pinion gear II 103 pushes 3 double wheels 98
Rotation, the double roller VII 89 taken turns on 98 pure rolling on 98 flank of tooth of double wheel, double wheel 98 push retainer by axis III 91
III 92 rotations, retainer III 92 drive big VI 94 uniform rotation of axis, big VI 94 rotation direction of axis and small axis VI by big key VI 93
102 is identical, and transmission ratio is definite value 6.
Specific embodiment 7
Figure 14 is the outer separated time precision gear transmission mechanism specific embodiment of preload disclosed by the invention, it is characterised in that gear
IV 125 basic circles are 40mm, facewidth 20mm, and external cylindrical surface is circumferential to be uniformly machined with 10 teeth, and VI 122 basic circle of cylinder wheel is 80mm,
Circumferential on cylinder wheel VI 122 to be uniformly equipped with 20 rollers VII 119, VII 119 diameter of roller is 4mm, VII 119 geometric center of roller
For line on VI 122 basic circle of cylinder wheel, VII 119 both ends of roller are separately installed with 8 needle rollers I 108, and needle roller VI 1 is circumferential to be uniformly distributed,
Axial baffle 124 is mounted on VI 122 end face of cylinder wheel by fixing bolt 120, and gear IV 125 is mounted on small axis VII 114, circle
Column wheel VI 122 is mounted on big axis VII 121, and big axis VII 121 is parallel with small VII 114 centre of gyration of axis, and distance is 60mm, gear IV
125 flank of tooth and roller VII 119 are tangent, divide coefficient k=1, and small bearing VII 115 is mounted in big 116 stepped hole of sliding block, big sliding block
116 are mounted on shell VII 129, are equipped with sliding block bolt I 112 between the big conical surface of big sliding block 116 and the big conical surface of shell VII 129,
Sliding block bolt II 117 is installed between VII 129 plane of the big small conical surface of sliding block 116 and shell, sliding block baffle 110 passes through casing bolts
It is mounted on shell VII 129, sliding block bolt I 112 is contacted with slider I 113, and sliding block bolt II 117 is contacted with sliding block II 118.
Cylinder wheel VI 122 and axial baffle 124 limit needle roller I 108, roller VII 119 moves axially.
Tooth pushes roller VII 119, roller VII 119 pure rolling, roller VII 119 on IV 125 flank of tooth of gear on gear IV 125
VI 122 uniform rotation of cylinder wheel is driven by needle roller I 108.
Sliding block bolt II 117 is threadedly coupled with sliding block baffle 110, and sliding block bolt I 112 is threadedly coupled with sliding block baffle 110.
Sliding block bolt I 112 is screwed out, sliding block bolt II 117 is screwed in, sliding block bolt II 117 pushes sliding block II 118, and sliding block II 118 pushes big
Sliding block 116, big sliding block 116 under sliding block baffle 110 and VII 129 restriction effect of shell, big sliding block 116 along sliding block baffle 110 with
Planar movement on shell VII 129, big sliding block 116 push slider I 113 mobile, and big sliding block 116 is driven small by small bearing VII 115
Axis VII 114 is mobile, and small VII 114 band moving gear IV 125 of axis is mobile, realizes that Meshing Pair pre-tightens, screws in sliding block bolt I 112, make big cunning
Block 116 is fixed.II 117 conical surface of sliding block bolt is smaller (1:30-1:20), can be realized reverse self-locking.113 conical surface of slider I is larger
(1:2-1:1), no reverse self-locking.
Specific embodiment 8
Figure 17 is that combination disclosed by the invention pre-tightens idler wheel specific embodiment, and bracket 135 is machined with hole, needle roller VIII 130 with
Roller VIII 131 is mounted in 135 hole of bracket, and cylinder wheel VII 136 is circumferential to be uniformly machined with 10 sliding slots, VII 136 sliding slot of cylinder wheel
Interior mounting bracket 135, bracket 135 and VII 136 contact surface of cylinder wheel exist smaller angle (less than 10 °), and positioning baffle 133 is logical
It crosses positioning bolt 132 to contact with bracket 135, fixed baffle 137 is contacted by end face bolt 134 with bracket 135.
End face bolt 134 screws out, and positioning bolt 132 screws in, and positioning baffle 133 is pushed to move axially, and positioning baffle 133 pushes away
Dynamic bracket 135 moves in VII 136 sliding slot of cylinder wheel, and bracket 135 drives roller VIII 131 to move along bevel direction, roller VIII 131
Cylinder radius surface increases where geometric center, and end face bolt 134 screws in, and bracket 135 is fixed.
Bracket 135 is acted on by radial force, and bracket 135 and the generation of VII 136 contact surface of cylinder wheel are self-locking, and bracket 135 does not move
It is dynamic.
Claims (9)
1. separated time precision gear transmission mechanism, including being set to the intracorporal cylinder wheel of chamber and gear that are made of end cap and shell,
Cylinder wheel and gear engaged transmission, it is characterized in that: the cylinder wheel includes the roller around the setting of its axle center, in the geometry of roller
Heart line is located on the basic circle of cylinder wheel；
Relationship between roller number and the number of teeth of gear is ZgR=Zcr0, Z1=R/r0, Z1It is the positive reality of finite term for fractional part
Number；
Separated time includes outer separated time and interior separated time, and interior separated time can be according to r0It is divided into interior separated time and inside and outside separated time with the size of R；Z1> 1
When, interior separated time is known as interior separated time；1 > Z1When > 0, interior separated time is known as inside and outside separated time；Divide coefficient for k, k ∈ [1,0)；
The outer separated time tooth surface equation of i-th of tooth is
H is gear width in formula,For normal angle；
The outer practical flank of tooth of separated time is formed after outer separated time flank of tooth pair-wise offset, the gear for being machined with the practical flank of tooth of outer separated time is known as outer point
Gear；Outer split gear practical tooth is the pair-wise offset face of the outer separated time flank of tooth of gear, and offset distance is roller radius；Roller geometry
Center is on cylinder wheel basic circle, roller external cylindrical surface pure rolling in gear practical tooth, realizes engaged transmission；
The interior separated time tooth surface equation of i-th of tooth is
H is gear width in formula,For normal angle.
2. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is outer separated time precision gear transmission mechanism, and the cylinder wheel is cylinder wheel I (4), gear is gear I (13), roller is
Roller I (9), end cap are end cap I (14), shell is shell I (8), include needle roller I (1), big key I (2), big axis I in mechanism
(3), cylinder wheel I (4), small key I (5), small axis I (6), small bearing I (7), shell I (8), roller I (9), bolt I (10), big axis
Hold I (11), baffle I (12), gear I (13), end cap (14), bolt of cover I (15)；Gear I (13) external cylindrical surface is circumferentially uniform
It is machined with Zc1A tooth is circumferentially equipped with Z on cylinder wheel I (4)g1A radius is r1Roller I (9), roller I (9) geometric center lines
On cylinder wheel I (4) basic circle, roller I (9) both ends are separately installed with needle roller I (1), and needle roller I (1) is circumferentially uniformly distributed, baffle I
(12) cylinder wheel I (4) end face is mounted on by bolt I (10), gear I (13) is mounted on small axis I (6), cylinder wheel I (4) peace
On big axis I (3), big axis I (3) is parallel with small axis I (6) centre of gyration, and gear I (13) flank of tooth and roller I (9) are tangent, tooth
I (13) base radius of wheel is R1, cylinder wheel I (4) base radius is r01, Z11=R1/r01, dividing coefficient is k1；
The Zg1R1=Zc1r01, Z11Less than 1, k1∈ [1,0), i-th on gear I (13)1The outer separated time tooth surface equation of a tooth is
3. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is interior separated time precision gear transmission mechanism, and the cylinder wheel is cylinder wheel II (17), gear is gear II (19), rolling
Column is roller II (24), end cap is end cap II (29), shell is shell II (23), includes needle roller II (16), cylinder in structure
II (17) of wheel, small key II (18), gear II (19), big bearing II (20), big key II (21), big axis II (22), shell II (23),
Roller II (24), bolt II (25), small axis II (26), small bearing II (27), baffle II (28), end cap II (29), bolt of cover
Ⅱ(30)；The circumferential uniformly processing Z of gear II (19) inner cylinder facec2A tooth, it is circumferential on cylinder wheel II (17) that Z is uniformly installedg2It is a
Radius is r2Roller II (24), roller II (24) geometric center lines are on cylinder wheel II (17) basic circle, roller II (24) both ends point
Needle roller II (16) is not installed, needle roller II (16) is circumferentially uniformly distributed, and baffle II (28) is mounted on cylinder by bolt II (25)
Take turns II (17) end face；Gear II (19) is mounted on big axis II (22), and cylinder wheel II (17) is mounted on small axis II (26), big axis
II (22) are parallel with small axis II (26) centre of gyration, and gear II (19) flank of tooth and roller II (24) are tangent, gear II (19) basic circle
Greater than cylinder wheel II (17) basic circle, gear II (19) base radius is R2, cylinder wheel II (17) base radius is r02, Z12=R2/
r02, dividing coefficient is k2；
The Zg2R2=Zc2r02, Z12Greater than 1, Z is required according to transmission12Desirable decimal and integer, the practical flank of tooth of gear II (19)
For the pair-wise offset line of the flank of tooth, offset distance r2, k2∈ is [1,0) i-th on gear II (19)2The interior separated time flank of tooth side of a tooth
Cheng Wei
4. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is inside and outside separated time precision gear transmission mechanism, and the cylinder wheel is cylinder wheel III (39), gear is gear III (35), rolling
Column is roller III (32), end cap is end cap III (41), shell is shell III (33), includes needle roller III (31), roller in structure
III (32), shell III (33), small key III (34), gear III (35), big key III (36), big axis III (37), big bearing III (38), circle
Column wheel III (39), baffle III (40), end cap III (41), bolt III (42), small axis III (43), small bearing III (44), bolt of cover
Ⅲ(45)；Gear III (35) external cylindrical surface is circumferentially uniformly machined with Zc3A tooth, it is circumferential on cylinder wheel III (39) that Z is uniformly installedg3
A radius is r3Roller III (32), roller III (32) geometric center lines are on cylinder wheel III (39) basic circle, roller III (32) both ends
It is separately installed with needle roller III (31), needle roller III (31) is circumferentially uniformly distributed, and baffle III (40) is mounted on circle by bolt III (42)
Column wheel III (39) end face, gear III (35) are mounted on small axis III (43), and cylinder wheel III (39) is mounted on big axis III (37), greatly
Axis III (37) centre of gyration is parallel with small axis III (43) centre of gyration, and gear III (35) flank of tooth and roller III (32) are tangent, gear
III (35) base radius is R3, cylinder wheel III (39) base radius is r03, Z13=R3/r03, dividing coefficient is k3；
The Zg3R3=Zc3r03, 0 < Z1< 1, the practical flank of tooth of gear III (35) is the pair-wise offset line of the flank of tooth, and offset distance is
r3, k3∈ is [1,0) i-th on gear III (35)3The inside and outside separated time tooth surface equation of tooth is
5. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is outer interior separated time precision planetary gear transmission mechanism, and the cylinder wheel is cylinder wheel IV (47), gear is pinion gear I
(54), roller is roller IV (32), end cap is end cap IV (56), shell is shell IV (52), includes needle roller IV in structure
(46), cylinder wheel IV (47), bearing I (48), axis I (49), big key IV (50), big bearing IV (51), shell IV (52), retainer
I (53), pinion gear I (54), roller IV (55), end cap IV (56), retaining ring I (57), bolt IV (58), baffle IV (59), small key
IV (60), small axis IV (61), small bearing IV (62), bolt of cover IV (63)；The circumferential uniformly processing of shell IV (52) inner cylinder face
Zcd4A tooth, the circumferential uniformly processing Z of pinion gear I (54) external cylindrical surfacecx4A tooth, cylinder wheel IV (47) are circumferentially uniformly equipped with Zg4It is a
Radius is r4Roller IV (55), roller IV (55) geometric center lines are on cylinder wheel IV (47) basic circle, roller IV (55) both ends point
Needle roller IV (46) is not installed, needle roller IV (46) is circumferentially uniformly distributed, and baffle IV (59) is mounted on cylinder by bolt IV (58)
Take turns IV (47) end face, n1(n1>=2) a axis I (49) is axially uniformly mounted on retainer I (53), the gear base on shell IV (52)
Radius of circle is R4, cylinder wheel IV (47) base radius is r04, Z14=R4/r04, pinion gear I (54) basic circle is R14, Z24=R14/
r04, dividing coefficient 1 is k41, dividing coefficient 2 is k42；
The Zg4R4=Zcd4r04, Z14Greater than 1, Z is required according to transmission14Desirable score and integer, gear casing IV (52) are real
The border flank of tooth is the pair-wise offset line of the flank of tooth, offset distance r4, k41∈ [1,0), i-th on shell IV (52)41Interior point of a tooth
Line tooth surface equation is
The Zg4R4=Zcx4r04, 0 < Z24< 1, the practical flank of tooth of pinion gear I (54) is the pair-wise offset line of the flank of tooth, and offset distance is
r4, k42∈ [1,0), i-th in pinion gear I (54)42The outer separated time tooth surface equation of a tooth is
6. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is outer interior separated time precision two-row planetary gear transmission mechanism, and the cylinder wheel is cylinder wheel V (80), gear is double
Gear (78), end cap are end cap V (76), shell is shell V (73), include big axis IV (64) in structure, needle roller V (65),
Roller V (66), bearing II (67), axis II (68), retainer II (69), big key V (70), big axis V (71), big bearing V
(72), shell V (73), roller VI (74), baffle V (75), end cap V (76), retaining ring II (77), double gear (78), baffle
VI (79), cylinder wheel V (80), bolt VI (81), small axis V (82), small bearing V (83), small key V (84), needle roller VI (85),
Bolt V (86), bolt of cover V (87), double gear (78)；Shell IV (73) inner cylinder face is circumferentially uniformly equipped with Zgd5It is a
Radius is r5Roller V (66), roller V (66) are connect by needle roller V (65) with shell IV (73), and needle roller V (65) uniformly divides
It is distributed in roller V (66) external cylindrical surface, double gear (78) is mounted on axis II (68) by bearing II (67), axis II (68) peace
On retainer II (69), n2(n2>=2) a axis II (68) is circumferentially uniformly distributed on retainer II (69), each axis II
(68) a double gear (78) is installed, double gear (78) gear wheel part is machined with Z oncd5A tooth, double gear (78)
Pinion portion is machined with Zcx5A tooth, cylinder wheel V (80) inner cylinder face are circumferentially uniformly equipped with Zgx5A radius is r5Roller VI
(74), cylinder wheel V (80) is circumferentially uniformly equipped with Zgx5A roller VI (74), roller VI (74) pass through needle roller VI (85) and cylinder
V (80) connection is taken turns, needle roller VI (85) is uniformly distributed in roller VI (74) external cylindrical surface, cylinder wheel V (80) and baffle VI (79)
Needle roller VI (85), roller VI (74) axial movement are limited, baffle VI (79) is installed on cylinder wheel V (80) by bolt VI (81)
End face, cylinder wheel V (80) are connect by small key (84) with small axis (82), and small axis (82) is installed on end by small bearing V (83)
Lid V (76), retainer II (69) are connect by big key V (70) with big axis V (71), and big axis V (71) passes through big bearing V
(72) it is installed on shell IV (73), shell IV (73) basic circle is rd5, cylinder wheel V (80) basic circle is rx5, double gear (78)
Gear wheel basic circle is Rd5, double gear (78) pinion gear basic circle is Rx5, Z15=Rd5/rd5, Z25=Rx5/rx5, Rd5Greater than Rx5, or
Person Rd5Equal to Rx5Or Rd5Less than Rx5；Dividing coefficient 1 is k51, dividing coefficient 2 is k52；
The rd5-Rd5=Rx5+rx5, Rd5Greater than rx5Or Rd5Equal to rx5Or Rd5Less than rx5, the Zgd5Rd5=
Zcd5rd5, 0 < Z15< 1, the practical flank of tooth of double gear (78) gear wheel is the pair-wise offset line of the flank of tooth, offset distance r5, k51∈
[1,0), i-th on double gear (78) gear wheel51The inside and outside separated time tooth surface equation of a tooth is
Zgx5Rx5=Zcx5rx5, Z25> 0, the practical flank of tooth of double gear (78) pinion gear is the pair-wise offset line of the flank of tooth, offset distance
For r5, k52∈ [1,0), i-th in double gear (78) pinion gear52The outer separated time tooth surface equation of a tooth is
7. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: the separated time precision gear is driven
Mechanism is outer interior separated time precision two-row planetary gear transmission mechanism, including needle roller VII (88), roller VII (89), bearing III (90),
Axis III (91), retainer III (92), big key VI (93), big axis VI (94), big bearing VI (95), shell VI (96), retaining ring III
(97), double wheel (98), small front apron (99), small bearing VI (100), small key VI (101), small axis VI (102), pinion gear II
(103), bolt VII (104), big baffle (105), bolt of cover VI (106), end cap VI (107)；Shell VI (96) inner cylinder face
It is circumferential that Z is uniformly installedgd6A radius is r6Roller VII (89), roller VII (89) pass through multiple needle rollers VII (88) and shell VI
(96) it connects, needle roller VII (88) is uniformly distributed in roller VII (89) external cylindrical surface, and shell VI (96) and big baffle (105) limitation are rolled
Needle VII (88), roller VII (89) axial movement, double wheel (98) are mounted on axis III (91) by bearing III (90), axis III (91)
It is mounted on retainer III (92), n3(n3>=2) a axis III (91) is circumferentially uniformly distributed on retainer III (92), each axis III
(91) a double wheel (98) is mounted on, retainer III (92) is connect by big key VI (93) with big axis VI (94), big axis
VI (94) are installed on shell VI (96) by big bearing VI (95), and double wheel (98) upper roller is partially circumferentially uniformly equipped with
Zgx6A roller VII (89), roller VII (89) are connect by multiple needle rollers VII (88) with pinion gear II (103), and needle roller VII (88) is equal
Even to be distributed in roller VII (89) external cylindrical surface, small front apron (99) is installed on double wheel (98) end face, small tooth by bolt VII (104)
II (103) of wheel are connect by small key VI (101) with small axis VI (102), and small axis VI (102) is installed on by small bearing VI (100)
End cap VI (107) is machined with Z on double wheel (98)cd6A tooth is machined with Z in pinion gear II (103)cx6A tooth, shell IV (96)
Base radius is rd6, pinion gear II (103) base radius is Rx6, double wheel (98) rolling circle radius is Rd6, double wheel (98)
Cylinder wheel base radius is rx6, Z16=Rd6/rd6, Z26=Rx6/rx6.Dividing coefficient 1 is k61, dividing coefficient 2 is k62；
The rd6-Rd6=Rx6+rx6, Rd6Greater than rx6Or Rd6Equal to rx6Or Rd6Less than rx6；
The Zgd6Rd6=Zcd6rd6, Z16> 1, the double wheel practical flank of tooth of (98) pinion gear is the pair-wise offset line of the flank of tooth, offset
Distance is r6, k61∈ [1,0), i-th on double wheel (98) gear wheel61The inside and outside separated time tooth surface equation of a tooth is
The Zgx6Rx6=Zcx6rx6, 0 < Z26< 1, the practical flank of tooth of pinion gear II (103) pinion gear is the pair-wise offset line of the flank of tooth,
Offset distance is r6, k62∈ [1,0), i-th in pinion gear II (103)62The outer separated time tooth surface equation of a tooth is
8. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: gear IV (125) external cylindrical surface is all
To several teeth are uniformly machined with, roller VII (119), roller VII (119) geometric center are circumferentially installed on cylinder wheel VI (122)
For line on cylinder wheel VI (122) basic circle, roller VII (119) both ends are separately installed with needle roller I (108), and needle roller VI (1) is circumferential uniformly
Distribution, axial baffle (124) are mounted on cylinder wheel VI (122) end face by fixing bolt (120), and gear IV (125) is mounted on
On small axis VII (114), (122 are mounted on big axis VII (121) cylinder wheel VI, in big axis VII (121) and the revolution of small axis VII (114)
The heart is parallel, and gear IV (125) flank of tooth and roller VII (119) are tangent, and small bearing VII 115 is mounted in big sliding block (116) stepped hole,
Big sliding block (116) is mounted on shell VII (129), is equipped between the big conical surface of big sliding block (116) and the big conical surface of shell VII (129)
Sliding block bolt I (112) is equipped with sliding block bolt II (117) between the small conical surface of big sliding block (116) and shell VII (129) plane, sliding
Block baffle (110) is mounted on shell VII (129) by casing bolts, and sliding block bolt I (112) is contacted with slider I (113), sliding
Block bolt II (117) is contacted with sliding block II (118), divides coefficient k7∈[1,0)；
Sliding block bolt II (117) is threadedly coupled with sliding block baffle (110), sliding block bolt I (112) and sliding block baffle (110) screw thread
Connection；It screws out sliding block bolt I (112), screws in sliding block bolt II (117), sliding block bolt II 117 pushes sliding block II (118), sliding block
II (118) push big sliding block (116), and big sliding block (116) is big sliding under sliding block baffle (110) and shell VII (129) restriction effect
Block (116) planar movement along sliding block baffle (110) and shell VII (129), big sliding block (116) push slider I (113) mobile,
Big sliding block (116) drives small axis VII (114) mobile by small bearing VII (115), and small axis VII (114) band moving gear IV (125) is moved
It is dynamic, it realizes that Meshing Pair pre-tightens, screws in sliding block bolt I (112), keep big sliding block (116) fixed；Sliding block bolt II (117) conical surface compared with
It is small, it can be realized reverse self-locking, slider I (113) conical surface is larger, no reverse self-locking.
9. separated time precision gear transmission mechanism according to claim 1, it is characterized in that: bracket (135) is machined with hole, needle roller
VIII (130) and roller VIII (131) are mounted in bracket (135) hole, and cylinder wheel VII (136) is circumferentially uniformly machined with sliding slot, cylinder
Mounting bracket (135) in VII (136) sliding slot is taken turns, bracket (135) and cylinder wheel VII (136) contact surface have smaller angle, fixed
Position baffle (133) contact with bracket (135) by positioning bolt (132), fixed baffle (137) pass through end face bolt (134) and
Bracket (135) contact；
End face bolt (134) screws out, and positioning bolt (132) screws in, and pushes positioning baffle (133) axial movement, positioning baffle
(133) bracket (135) are pushed to move in cylinder wheel VII (136) sliding slot, bracket 135) drive roller VIII (131) along bevel direction
Mobile, cylinder radius surface increases where roller VIII (131) geometric center, and end face bolt (134) screws in, and bracket (135) is fixed, branch
Frame (135) is acted on by radial force, and bracket (135) and the generation of cylinder wheel VII (136) contact surface are self-locking, and bracket (135) does not move.
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| CN107701705A (en) * | 2017-09-19 | 2018-02-16 | 杨荣刚 | The outer/inner engagement of straight-tooth, the outer/inner accurate bevel gear transmission of engagement of helical teeth |
| CN111322354A (en) * | 2018-12-13 | 2020-06-23 | 上海联紫能源科技有限公司 | Planetary roller gear reducer and implementation method thereof |
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| JP2000130560A (en) * | 1998-10-27 | 2000-05-12 | Fuji Kiko Co Ltd | Cycloidal gear with small-numbered teeth |
| CN101182880B (en) * | 2007-12-17 | 2012-05-30 | 宝钢苏冶重工有限公司 | Gear wheel with changed tooth height |
| CN104776179A (en) * | 2015-05-05 | 2015-07-15 | 青岛大学 | Opposite steering ball transmission mechanism |
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Effective date of registration: 20210301 Address after: 210000 No.69 Feitian Avenue, Jiangning Airport Economic Development Zone, Nanjing, Jiangsu Province Patentee after: Nanjing Nanchuan Intelligent Technology Co.,Ltd. Address before: 061000 area C, Huanghe West Road, Cangzhou City, Hebei Province Patentee before: Yang Ronggang |