CN208831621U - A point-line meshing worm drive mechanism - Google Patents
A point-line meshing worm drive mechanism Download PDFInfo
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- CN208831621U CN208831621U CN201820845029.3U CN201820845029U CN208831621U CN 208831621 U CN208831621 U CN 208831621U CN 201820845029 U CN201820845029 U CN 201820845029U CN 208831621 U CN208831621 U CN 208831621U
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Abstract
本实用新型公开了一种点线啮合蜗杆传动机构，属于蜗杆传动设计技术领域。一种点线啮合蜗杆传动机构，包括蜗杆、与蜗杆啮合的传动轮和与传动轮啮合的斜齿条，所述蜗杆、传动轮和斜齿条均采用渐开线与圆弧综合的齿形，其齿高的一半为渐开线凸齿廓，另一半为过渡曲线凹齿廓，所述传动轮为蜗轮或斜齿轮。有益效果：本实用新型的点线啮合蜗杆传动机构进一步丰富了点线啮合齿轮的理论体系，扩大了点线啮合齿轮的应用范围，拓宽了蜗杆传动的内涵和外延。相对于常规蜗杆传动机构，点线啮合蜗杆传动机构具有承载能力大、寿命长、可靠性高等等优点。
The utility model discloses a point-line meshing worm drive mechanism, which belongs to the technical field of worm drive design. A point-line meshing worm drive mechanism includes a worm, a drive wheel meshed with the worm, and a helical rack meshed with the drive wheel, wherein the worm, the drive wheel and the helical rack all adopt a tooth shape integrated with an involute and a circular arc. , half of the tooth height is an involute convex tooth profile, the other half is a transition curve concave tooth profile, and the transmission gear is a worm gear or a helical gear. Beneficial effects: The point-line meshing worm drive mechanism of the utility model further enriches the theoretical system of the point-line meshing gear, expands the application range of the point-line meshing gear, and broadens the connotation and extension of the worm drive. Compared with the conventional worm drive mechanism, the point-line meshing worm drive mechanism has the advantages of large bearing capacity, long service life, high reliability and so on.
Description
Technical field
The utility model belongs to Worm Gear Drive Design technical field more particularly to a kind of point-line meshing worm gearing.
Background technique
Worm-drive is widely used because of big, stable drive, with small vibration, low noise advantages with transmission ratio.Worm screw
The superiority and inferiority of transmission performance and its quality finally will affect the quality height of engineening goods, therefore, increasingly increase to meet people
The needs of long material progress, it is desirable that the transmission performance of worm screw is continued to optimize.
Worm geared failure mode often shows as rippling, gluing, abrasion and break of gear tooth etc..The gear teeth once occur
It fractures, will affect the normal operation of endless screw transmission agent, serious person results even in the generation of equipment breakdown and casualties.By
In the reason on material and structure, the intensity of worm spiral toothed portion is always above the intensity for the worm gear teeth being engaged with, institute
It is occurred often on worm gear teeth with failure.
Point-line meshing gear is a kind of novel gear, i.e., intermeshing a pair of of gear pair, the high half of tooth is gradually
Burst at the seams double wedge exterior feature, the other half is wide for the concave tooth of easement curve.When gear pair engaged transmission, when the involute teeth of one of gear
Exterior feature forms point contact when being meshed with the easement curve flank profil of coupling gear；Involute profile and pairing when one of gear
Line contact is formed when the involute profile of gear is meshed.Point-line meshing gear combines pair of involute gear and wildhaber-novikov gear
Weight advantage, has many advantages, such as that large carrying capacity, service life are long.
In order to improve the resistance to fracture of worm gear teeth, the utility model proposes a kind of point-line meshing worm gearings
Design concept.The related report in terms of worm and wheel or helical gear point-line meshing is not yet retrieved at present.
Utility model content
To solve the problems, such as that worm gear teeth is vulnerable in worm gearing of the existing technology, the utility model is provided
A kind of point-line meshing worm gearing.
In order to solve the above technical problems, technical solution used by the utility model is as follows, a kind of point-line meshing worm screw biography
Motivation structure, including worm screw, the driving wheel engaged with worm screw and the helical rack engaged with driving wheel, the worm screw, driving wheel with
And helical rack is all made of the tooth form of involute and circular arc synthesis, the high half of tooth is that involute double wedge is wide, the other half is transition
The concave tooth of curve is wide, and the driving wheel is worm gear or helical gear；
The point-line meshing worm gearing meets the following conditions:
When worm and wheel is meshed, the lead-angle, axial plane modulus, axial plane pressure angle of worm screw is taken to be respectively
γ3、mx3、αx3；The spiral angle of graduated circle, transverse module, transverse pressure angle for taking worm gear are respectively β4、mt4、αt4, then it must satisfy:
mt4=mx3、αt4=αx3, in the case where two axle clamp angle of worm and wheel is 90 degree, also meet β4=γ3；
When worm gear is meshed with helical rack, take the helical angle of helical rack, transverse module, transverse pressure angle, normal module,
Normal pitch pressure angle is respectively β5、mt5、αt5、mn5、αn5, then must satisfy: mt5=mn5/ cos β=mt4、αt5=arctg (tg αn5/
Cos β)=αt4、β5=-β4；
When worm screw is meshed with helical gear, the lead-angle, axial plane modulus, axial plane pressure angle of worm screw is taken to be respectively
γ3、mx3、αx3；Take helical gear spiral angle of graduated circle, transverse module, transverse pressure angle, normal module, normal pitch pressure angle difference
For β4、mt4、αt4、mn4、αn4, then must satisfy: mx3=mt4、αx3=αt4、mt4=mn4/cosβ4、In snail
In the case that bar and two axle clamp angle of helical gear are 90 degree, also meet β4=γ3；
When helical gear is meshed with helical rack, the helical angle of helical rack, normal module, the normal pitch pressure angle is taken to be respectively
β5、mn5、αn5, then must satisfy: mn5=mn4、αn5=αn4、β5=-β4。
Preferably, forming two point contact when the easement curve flank profil of worm screw is meshed with the involute profile of worm gear；
When the easement curve flank profil of worm gear is meshed with the involute profile of helical rack, two point contact is formed；When the involute teeth of worm screw
When exterior feature is meshed with the involute profile of worm gear, line contact is formed；The involute profile of worm gear and the involute profile of helical rack
When being meshed, line contact is formed.
Preferably, forming two point when the easement curve flank profil of worm screw is meshed with helical gear involute profile and connecing
Touching；When helical gear easement curve flank profil is meshed with the involute profile of helical rack, two point contact is formed；When gradually opening for worm screw
When line flank profil is meshed with helical gear involute profile, line contact is formed；Helical gear involute profile and helical rack are gradually
When the flank profil that bursts at the seams is meshed, line contact is formed.
The utility model has the advantages that the point-line meshing worm gearing of the utility model further enriches the reason of point-line meshing gear
By system, the application range of point-line meshing gear is expanded, has widened worm geared the connotation and extension.Relative to conventional worm screw
Transmission mechanism, point-line meshing worm gearing have many advantages, such as large carrying capacity, service life length, high reliablity etc.；Helical gear replaces
For worm gear and worm screw engaged transmission, the difficulty of spiral case making can be substantially reduced, having reduces production cost, improves production efficiency etc.
Effect.
Detailed description of the invention
Fig. 1 is the engaged transmission schematic diagram of the utility model point-line meshing worm gearing；
Fig. 2 is the point-line meshing form schematic diagram of the gear teeth of the utility model point-line meshing worm gearing；
1, motor in figure, 2, shaft coupling, 3, worm screw, 4, driving wheel, 5, helical rack.
Specific embodiment
As shown in Figure 1, a kind of point-line meshing worm gearing, including worm screw 3, the driving wheel engaged with worm screw 34 and
The helical rack 5 engaged with driving wheel 4, worm screw 3 is fixedly connected by shaft coupling 2 with the output end of motor 1, in the drive of motor 1
Under, the rotary motion of worm screw 3 is converted into the straight reciprocating of helical rack 5.As shown in Fig. 2, the worm screw 3, driving wheel 4 and
Helical rack 5 is all made of the tooth form of involute and circular arc synthesis, and the high half of tooth is that involute double wedge is wide, the other half is bent for transition
The concave tooth of line is wide, and the driving wheel 4 is worm gear or helical gear.When the easement curve flank profil of worm screw 3 and the involute profile of worm gear
When being meshed, two point contact is formed；When the easement curve flank profil of worm gear is meshed with the involute profile of helical rack 5, formed double
Point contact.When the involute profile of worm screw 3 is meshed with the involute profile of worm gear, line contact is formed；The involute of worm gear
When flank profil is meshed with the involute profile of helical rack 5, line contact is formed.When worm screw 3 easement curve flank profil with it is helical gear
When involute profile is meshed, two point contact is formed；Helical gear easement curve flank profil and the involute profile of helical rack 5 are mutually nibbled
When conjunction, two point contact is formed.When the involute profile of worm screw 3 is meshed with helical gear involute profile, line contact is formed；
When helical gear involute profile is meshed with the involute profile of helical rack 5, line contact is formed.Such as Fig. 2, two are defined here
Pitch wheel is gear 1 and gear 2, and in Fig. 2, two pitch circle points of tangency P at, O1O2 is center line, and N1N2 is nibbles
Zygonema section, J are meshing point；
The point-line meshing worm gearing meets the following conditions:
When worm screw 3 is meshed with worm gear, the lead-angle, axial plane modulus, axial plane pressure angle of worm screw 3 is taken to be respectively
γ3、mx3、αx3；The spiral angle of graduated circle, transverse module, transverse pressure angle for taking worm gear are respectively β4、mt4、αt4, then it must satisfy:
mt4=mx3、αt4=αx3, in the case where worm screw 3 and two axle clamp angle of worm gear are 90 degree, also meet β4=γ3；
When worm gear is meshed with helical rack 5, helical angle, the transverse module, transverse pressure angle, method face mould of helical rack 5 are taken
Number, normal pitch pressure angle are respectively β5、mt5、αt5、mn5、αn5, then must satisfy: mt5=mn5/ cos β=mt4、αt5=arctg (tg
αn5/ cos β)=αt4、β5=-β4。
When worm screw 3 is meshed with helical gear, the lead-angle, axial plane modulus, axial plane pressure angle of worm screw 3 is taken to distinguish
For γ3、mx3、αx3；Take helical gear spiral angle of graduated circle, transverse module, transverse pressure angle, normal module, normal pitch pressure angle point
It Wei not β4、mt4、αt4、mn4、αn4, then must satisfy: mx3=mt4、αx3=αt4、mt4=mn4/cosβ4、?
In the case that worm screw 3 and two axle clamp angle of helical gear are 90 degree, also meet β4=γ3；
When helical gear is meshed with helical rack 5, the helical angle of helical rack 5, normal module, the normal pitch pressure angle is taken to be respectively
β5、mn5、αn5, then must satisfy: mn5=mn4、αn5=αn4、β5=-β4。
Embodiment one:
It 1), is easy analysis, it is assumed that the gear teeth hand of spiral of worm screw 3 is left-handed.Since worm gear is meshed with worm screw 3, then
The gear teeth hand of spiral of worm gear be also it is left-handed, worm-gear driven helical rack 5 is mobile, then the gear teeth hand of spiral of helical rack 5 is dextrorotation；
2), as shown in Figure 1, when motor 1 is rotated according to upward solid arrow direction, by shaft coupling 2, worm screw is driven
3 rotations, the rotation direction of worm screw 3 are identical as 1 rotation direction of motor；
3) head number, diameter quotient, axial plane modulus, the axial plane pressure angle for, taking worm screw 3 are respectively z3、q3、mx3、αx3, wherein
z3、q3Value can refer to design of gears handbook；mx3、αx3It can make by oneself as needed or from gear handbook value, but specific value
It is related with the transverse module of worm gear and transverse pressure angle；The lead-angle γ of worm screw 33=arctanz3/q3Degree；
4) the reference diameter d of worm screw 3, is taken3=mx3q3Millimeter, the base circle diameter (BCD) of worm screw 3Millimeter, worm screw
3 tip diameterMillimeter, whereinFor addendum coefficient, 1 is often taken；
5), worm screw 3 drives worm gear to rotate counterclockwise；
6), taking the number of teeth of worm gear, spiral angle of graduated circle, transverse module, transverse pressure angle is respectively z4、β4、mt4、αt4,
Middle z4Value range is often 28~80.mt4、αt4It can make by oneself or from gear handbook value, but must satisfy as needed: mt4=
mx3、αt4=αx3.In the case where worm screw 3 and two axle clamp angle of worm gear are 90 degree, also meet β4=γ3；
7) the end face modification coefficient for, taking worm gear is xt4, value selects according to design requirement；
8), worm gear is meshed with helical rack 5, and helical rack 5 is driven to move right, as shown in figure 1 shown in solid arrow direction；
9), taking the helical angle of helical rack 5, transverse module, transverse pressure angle, normal module, normal pitch pressure angle is respectively β5、
mt5、αt5、mn5、αn5, wherein β5、mn5、αn5It can make by oneself or from gear handbook value, but must satisfy as needed: mt5=mn5/
Cos β=mt4、αt5=arctg (tg αn5/ cos β)=αt4、β5=-β4；
10), similarly, as shown in Figure 1, passing through shaft coupling 2, band when motor 1 is rotated according to downward dotted arrow direction
Dynamic worm screw 3 rotates；Worm screw 3 and worm gear engaged transmission, drive worm gear to rotate clockwise；5 engaged transmission of worm gear and helical rack, is realized
Helical rack 5 is moved to the left, as shown in figure 1 shown in dotted arrow direction.
Embodiment two:
1), assume the hand of helix of worm screw 3 be it is left-handed, the characteristics of according to worm screw 3 and helical gear engaged transmission, then helical teeth
The gear teeth hand of spiral of wheel be also it is left-handed, the characteristics of according to helical gear and the engaged transmission of helical rack 5, then the gear teeth spiral shell of helical rack 5
Rotation direction is dextrorotation；
2), as shown in Figure 1, when motor 1 is rotated according to upward solid arrow direction, by shaft coupling 2, worm screw is driven
3 rotations, the rotation direction of worm screw 3 are identical as 1 rotation direction of motor；
3) head number, diameter quotient, axial plane modulus, the axial plane pressure angle for, taking worm screw 3 are respectively z3、q3、mx3、αx3, wherein
z3、q3Value can refer to design of gears handbook, mx3、αx3Value can refer to design of gears handbook, but specific value and helical teeth
The transverse module of wheel is related with transverse pressure angle；The lead-angle γ of worm screw 33=arctanz3/q3Degree；
4) the reference diameter d of worm screw 3, is taken3=mx3q3Millimeter, the base circle diameter (BCD) of worm screw 3Millimeter, worm screw
3 tip diameterMillimeter, whereinFor addendum coefficient, 1 is often taken；
5), worm screw 3 drives helical gear to rotate counterclockwise；
6) the helical gear number of teeth, spiral angle of graduated circle, transverse module, transverse pressure angle, normal module, method surface pressure, are taken
Angle is respectively z4、β4、mt4、αt4、mn4、αn4, wherein z4The value as needed in the case where guaranteeing that root is not cut.mn4、αn4It can basis
It needs to make by oneself or from gear handbook value, mt4=mn4/cosβ4、But it must satisfy: mx3=mt4、αx3=
αt4.In the case where worm screw 3 and two axle clamp angle of helical gear are 90 degree, also meet β4=γ3；
7), taking helical gear end face modification coefficient is xt4, value selects according to design requirement；
8), helical gear and the engaged transmission of helical rack 5, and helical rack 5 is driven to move right, as shown in figure 1 solid arrow direction
It is shown；
9), taking the helical angle of helical rack 5, normal module, normal pitch pressure angle is respectively β5、mn5、αn5, wherein β5、mn5、αn5
It can make by oneself or from gear handbook value, but must satisfy as needed: mn5=mn4、αn5=αn4、β5=-β4；
10), similarly, as shown in Figure 1, passing through shaft coupling 2, band when motor 1 is rotated according to downward dotted arrow direction
Dynamic worm screw 3 rotates；Worm screw 3 and helical gear engaged transmission, drive helical gear to rotate clockwise；Helical gear engages biography with helical rack 5
It is dynamic, realize that helical rack 5 is moved to the left, as shown in figure 1 shown in dotted arrow direction.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201820845029.3U CN208831621U (en) | 2018-06-01 | 2018-06-01 | A point-line meshing worm drive mechanism |
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| CN201820845029.3U CN208831621U (en) | 2018-06-01 | 2018-06-01 | A point-line meshing worm drive mechanism |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110792754A (en) * | 2019-10-12 | 2020-02-14 | 西华大学 | Method for calculating indexing circular-arc tooth thickness of straight gear according to meshing parameters of worm and straight gear |
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2018
- 2018-06-01 CN CN201820845029.3U patent/CN208831621U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110792754A (en) * | 2019-10-12 | 2020-02-14 | 西华大学 | Method for calculating indexing circular-arc tooth thickness of straight gear according to meshing parameters of worm and straight gear |
| CN110792754B (en) * | 2019-10-12 | 2021-01-15 | 西华大学 | Calculation Method of Meshing Parameters of Worm and Spur Gear |
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