CN208474410U - A kind of twin worm point-line meshing transmission mechanism - Google Patents
A kind of twin worm point-line meshing transmission mechanism Download PDFInfo
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- CN208474410U CN208474410U CN201820845408.2U CN201820845408U CN208474410U CN 208474410 U CN208474410 U CN 208474410U CN 201820845408 U CN201820845408 U CN 201820845408U CN 208474410 U CN208474410 U CN 208474410U
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Abstract
The utility model relates to technical field of mechanical transmission, more particularly to a kind of twin worm point-line meshing transmission mechanism, the existing involute of tooth form of the gear tooth profiles such as worm screw, worm gear, helical gear, conical gear in the utility model has circular arc again, i.e. the high half of gear teeth tooth is that involute double wedge is wide, the other half is wide for the concave tooth of easement curve.When transmission system works, different tooth curves, which is meshed, will show different engagement effects.When transition curvilinear tooth profile is meshed with involute profile, point contact is shown as；When involute profile is meshed with involute profile, line contact is shown as.It is in place of the characteristic of the utility model: 1) point-line meshing of gear is generalized to the point-line meshing of worm and wormwheel, further enriches the theoretical system of gear point-line meshing, widen worm geared application range.2) worm screw and helical gear point-line meshing, extend worm geared the connotation and extension.3) point-line meshing worm gear has both the two-fold advantage of involute worm wheel and circular arc worm gear, and intensity is higher.
Description
Technical field
The utility model relates to technical field of mechanical transmission, and in particular to a kind of twin worm point-line meshing transmission mechanism.
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.
Worm geared failure mode often shows as rippling, gluing, tooth surface abrasion and break of gear tooth etc..Due to material
It is always above the intensity of worm gear teeth with the intensity of the reason in structure, worm spiral toothed portion, so failure occurs often in
On worm gear teeth.
Utility model content
In order to which worm gear or the helical gear gear teeth are easy when solving worm gear or helical gear of the existing technology and worm screw cooperation
The problem of failure, the utility model provide a kind of twin worm point-line meshing that worm gear or helical gear teeth bending strength can be improved
Transmission mechanism.
The technical scheme adopted by the utility model to solve the technical problem is as follows:
A kind of twin worm point-line meshing transmission mechanism, including motor, the motor output end are fixedly connected with the first circle
Bevel gear, the first conical gear center are fixed with the first connecting shaft, and the other end of first connecting shaft is fixed with
First helical gear, the first helical gear external toothing have the second helical gear, and the second helical gear center is fixed with second
Connecting shaft, the other end of second connecting shaft are fixed with third helical gear, and the third helical gear external toothing has the 4th
Helical gear, the 4th helical gear external toothing have the 5th helical gear, and the 5th helical gear center is fixed with third connection
Axis, the other end of the third connecting shaft are fixed with the first worm screw, and first worm screw and the first driving wheel are meshed, institute
The first conical gear stated is meshed with the second conical gear, and the second conical gear center is fixed with the fourth connecting shaft,
The other end of the fourth connecting shaft is fixed with the second worm screw, and second worm screw is meshed with the second driving wheel, described
The first driving wheel center be fixed with the 5th connecting shaft, the end of the 5th connecting shaft is fixed with the second driving wheel, described
The first driving wheel be the first worm gear or the 6th helical gear, second driving wheel be the second worm gear or the 7th helical gear, institute
It is necessary to meet following condition for the transmission mechanism stated:
1) the first helical gear and the second helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, end face pressure are taken
Power angle and spiral angle of graduated circle are respectively z3、z4、mn3、mt3、mn4、mt4、αn3、αt3、αn4、αt4、β3、β4, wherein z3、z4Value
It can be made by oneself as needed meeting in the case that root is not cut；β3、β4Often take 8 °~20 °；mn3、mn4、αn3、αn4It can as needed certainly
Calmly or from gear handbook value, it but must satisfy: mt3=mn3/cosβ3=mt4, αt3=arctg (tg αn3/cosβ3)=αt4,β3
=-β4；
2) third helical gear and the 4th helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, end face pressure are taken
Power angle and spiral angle of graduated circle are respectively z5、z6、mn5、mt5、mn6、mt6、αn5、αt5、αn6、αt6、β5、β6, wherein z5、z6Value
It can be made by oneself as needed meeting in the case that root is not cut；β5、β6Often take 8 °~20 °；mn5、mn6、αn5、αn6It can as needed certainly
Calmly or from gear handbook value, it but must satisfy: mt5=mn5/cosβ5=mt6, αt5=arctg (tg αn5/cosβ5)=αt6, β5
=-β6；
3) the 5th helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, transverse pressure angle and reference circle are taken
Helical angle is respectively z7、mn7、mt7、αn7、αt7、β7, wherein z7Value meet root is not cut in the case where can make by oneself as needed；
β7Often take 8 °~20 °；mn7、αn7It can make by oneself or from gear handbook value, but must satisfy as needed: mt7=mn7/cosβ7=
mt6, αt7=arctg (tg αn7/cosβ7)=αt6, and meet β7=-β6；
4) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the first worm screw are respectively z8、q8、mx8、αx8,
Middle z8Usually take 1,2,4,6；q8Value can refer to design of gears handbook；mx8、αx8It can make by oneself as needed or from gear handbook
Value, but specific value is related with the transverse module of the first driving wheel and transverse pressure angle；The lead-angle of first worm screw
γ8=arctanz8/q8Degree；
5) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the first driving wheel are taken9、β9、mt9、
αt9.When the first driving wheel is the first worm gear, z9Value range often between 28~80；When the first driving wheel is the 6th helical teeth
When wheel, z9Value meet root is not cut in the case where can make by oneself as needed；β9It can make by oneself as needed；mt9、αt9It can basis
It needs to make by oneself or from gear handbook value, but must satisfy: mx8=mt9, αx8=αt9.In the first worm screw and two axis of the first driving wheel
In the case that angle is 90 degree, also meet β9=γ8；
6) taking the number of teeth of the first conical gear and the second conical gear, big end modulus, big end pressure angle is respectively z2、z10、
m2、m10、α2、α10, wherein z2、z10Value meet root is not cut in the case where can make by oneself as needed；m2、m10、α2、α10It can root
It according to needing to make by oneself or from gear handbook value, but must satisfy: m2=m10, α2=α10；
7) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the second worm screw are respectively z11、q11、mx11、αx11,
Wherein z11Usually take 1,2,4,6；q11Value can refer to design of gears handbook；mx11、αx11It can make by oneself as needed or from gear
Handbook value, but specific value is related with the transverse module of the second driving wheel and transverse pressure angle；The reference circle of second worm screw is led
Journey angle γ11=arctanz11/q11Degree；
8) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the second driving wheel are taken12、β12、mt12、
αt12.When the second driving wheel is the second worm gear, z12Value range often between 28~80；When the second driving wheel is the 7th oblique
When gear, z12Value meet root is not cut in the case where can make by oneself as needed；β12It can make by oneself as needed；mt12、αt12It can
It makes by oneself or from gear handbook value, but must satisfy as needed: mx11=mt12, αx11=αt12.It is passed in the second worm screw with second
In the case that two axle clamp angle of driving wheel is 90 degree, also meet β12=γ11。
Further, first conical gear, the first helical gear, the second helical gear, third helical gear, the 4th helical teeth
The gear tooth profiles such as wheel, the 5th helical gear, the first worm screw, the first driving wheel, the second conical gear, the second worm screw and the second driving wheel
The existing involute of tooth form have circular arc again, i.e., the high half of gear teeth tooth is that the double wedge of involute profile is wide, the other half is bent for transition
The concave tooth of line tooth form is wide.
The utility model has the advantages that
1) point-line meshing of gear is generalized to the point-line meshing of worm and wormwheel by the utility model, further enriches gear
The theoretical system of point-line meshing has widened worm geared application range.2) worm screw and helical gear point-line meshing, extend snail
The connotation and extension of bar transmission.3) point-line meshing worm gear has both the two-fold advantage of involute worm wheel and circular arc worm gear, and intensity is higher.
Therefore, compared with conventional worm gearing, the utility model has large carrying capacity, service life length, high reliablity, not easily broken
The advantages that tooth.
Detailed description of the invention
Utility model will be further described in detail below with reference to the attached drawings and specific embodiments.
Fig. 1 is the structural schematic diagram of the utility model twin worm point-line meshing transmission mechanism；
Fig. 2 is the point-line meshing form of the utility model twin worm point-line meshing transmission mechanism.
Wherein, 1, motor, the 2, first conical gear, the 3, first helical gear, the 4, second helical gear, 5, third helical gear, 6,
4th helical gear, the 7, the 5th helical gear, the 8, first worm screw, the 9, first driving wheel, the 10, second conical gear, the 11, second worm screw,
12, the second driving wheel.
Specific embodiment
Such as Fig. 1, a kind of twin worm point-line meshing transmission mechanism, including motor 1,1 output end of motor are fixedly connected with first
Conical gear 2,2 center of the first conical gear are fixed with the first connecting shaft, and the other end of the first connecting shaft is fixed with the first helical teeth
Wheel 3,3 external toothing of the first helical gear has the second helical gear 4, and 4 center of the second helical gear is fixed with the second connecting shaft, the second connecting shaft
The other end be fixed with third helical gear 5,5 external toothing of third helical gear has the 4th helical gear 6, and 6 external toothing of the 4th helical gear has
5th helical gear 7,7 center of the 5th helical gear are fixed with third connecting shaft, and the other end of third connecting shaft is fixed with the first worm screw
8, the first worm screw 8 and the first driving wheel 9 are meshed, and the first conical gear 2 is meshed with the second conical gear 10, the second circular cone tooth
It takes turns 10 centers and is fixed with the fourth connecting shaft, the other end of the fourth connecting shaft is fixed with the second worm screw 11, the second worm screw 11 and second
Driving wheel 12 is meshed, and 9 center of the first driving wheel is fixed with the 5th connecting shaft, and the end of the 5th connecting shaft is fixed with the second transmission
Wheel 12, the first driving wheel 9 are the first worm gear or the 6th helical gear, and the second driving wheel 12 is the second worm gear or the 7th helical gear, are passed
It is necessary to meet following condition for motivation structure:
1) the first helical gear and the second helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, end face pressure are taken
Power angle and spiral angle of graduated circle are respectively z3、z4、mn3、mt3、mn4、mt4、αn3、αt3、αn4、αt4、β3、β4, wherein z3、z4Value
It can be made by oneself as needed meeting in the case that root is not cut；β3、β4Often take 8 °~20 °；mn3、mn4、αn3、αn4It can as needed certainly
Calmly or from gear handbook value, it but must satisfy: mt3=mn3/cosβ3=mt4, αt3=arctg (tg αn3/cosβ3)=αt4,β3
=-β4；
2) third helical gear and the 4th helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, end face pressure are taken
Power angle and spiral angle of graduated circle are respectively z5、z6、mn5、mt5、mn6、mt6、αn5、αt5、αn6、αt6、β5、β6, wherein z5、z6Value
It can be made by oneself as needed meeting in the case that root is not cut；β5、β6Often take 8 °~20 °；mn5、mn6、αn5、αn6It can as needed certainly
Calmly or from gear handbook value, it but must satisfy: mt5=mn5/cosβ5=mt6, αt5=arctg (tg αn5/cosβ5)=αt6, β5
=-β6；
3) the 5th helical gear number of teeth, normal module, transverse module, normal pitch pressure angle, transverse pressure angle and reference circle are taken
Helical angle is respectively z7、mn7、mt7、αn7、αt7、β7, wherein z7Value meet root is not cut in the case where can make by oneself as needed；
β7Often take 8 °~20 °；mn7、αn7It can make by oneself or from gear handbook value, but must satisfy as needed: mt7=mn7/cosβ7=
mt6, αt7=arctg (tg αn7/cosβ7)=αt6, and meet β7=-β6；
4) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the first worm screw are respectively z8、q8、mx8、αx8,
Middle z8Usually take 1,2,4,6；q8Value can refer to design of gears handbook；mx8、αx8It can make by oneself as needed or from gear handbook
Value, but specific value is related with the transverse module of the first driving wheel and transverse pressure angle；The lead-angle of first worm screw
γ8=arctanz8/q8Degree；
5) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the first driving wheel are taken9、β9、mt9、
αt9.When the first driving wheel is the first worm gear, z9Value range often between 28~80；When the first driving wheel is the 6th helical teeth
When wheel, z9Value meet root is not cut in the case where can make by oneself as needed；β9It can make by oneself as needed；mt9、αt9It can basis
It needs to make by oneself or from gear handbook value, but must satisfy: mx8=mt9, αx8=αt9.In the first worm screw and two axis of the first driving wheel
In the case that angle is 90 degree, also meet β9=γ8；
6) taking the number of teeth of the first conical gear and the second conical gear, big end modulus, big end pressure angle is respectively z2、z10、
m2、m10、α2、α10, wherein z2、z10Value meet root is not cut in the case where can make by oneself as needed；m2、m10、α2、α10It can root
It according to needing to make by oneself or from gear handbook value, but must satisfy: m2=m10, α2=α10；
7) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the second worm screw are respectively z11、q11、mx11、αx11,
Wherein z11Usually take 1,2,4,6；q11Value can refer to design of gears handbook；mx11、αx11It can make by oneself as needed or from gear
Handbook value, but specific value is related with the transverse module of the second driving wheel and transverse pressure angle；The reference circle of second worm screw is led
Journey angle γ11=arctanz11/q11Degree；
8) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the second driving wheel are taken12、β12、mt12、
αt12.When the second driving wheel is the second worm gear, z12Value range often between 28~80；When the second driving wheel is the 7th oblique
When gear, z12Value meet root is not cut in the case where can make by oneself as needed；β12It can make by oneself as needed；mt12、αt12It can
It makes by oneself or from gear handbook value, but must satisfy as needed: mx11=mt12, αx11=αt12.It is passed in the second worm screw with second
In the case that two axle clamp angle of driving wheel is 90 degree, also meet β12=γ11。
First conical gear 2, the first helical gear 3, the second helical gear 4, third helical gear 5, the 4th helical gear the 6, the 5th are tiltedly
The gear tooth profiles such as gear 7, the first worm screw 8, the first driving wheel 9, the second conical gear 10, the second worm screw 11 and the second driving wheel 12
The existing involute of tooth form have circular arc again, i.e., the high half of gear teeth tooth is that involute double wedge is wide, the other half is recessed for easement curve
Flank profil.When work, different tooth curves, which is meshed, will show different engagement effects.When transition curvilinear tooth profile and involute
When flank profil is meshed, point contact is shown as；When involute profile is meshed with involute profile, line contact is shown as.Such as figure
2, defining two pitch wheels here is gear 1 and gear 2, in figure, at two pitch circle points of tangency P, and O1O2Centered on
Line, N1N2 are engagement line segment, and J is meshing point.
It should be appreciated that specific embodiment described above is only used for explaining the utility model, it is not used to limit this reality
With novel.By the utility model the obvious changes or variations extended out of spirit still in the utility model protection
Among range.
Claims (2)
1. a kind of twin worm point-line meshing transmission mechanism, it is characterised in that: including motor (1), the motor (1) output end is solid
Surely it being connected with the first conical gear (2), described the first conical gear (2) center is fixed with the first connecting shaft, and described first
The other end of connecting shaft is fixed with the first helical gear (3), and described the first helical gear (3) external toothing has the second helical gear (4), institute
The second helical gear (4) center stated is fixed with the second connecting shaft, and the other end of second connecting shaft is fixed with third helical teeth
It takes turns (5), described third helical gear (5) external toothing has the 4th helical gear (6), and the 4th described helical gear (6) external toothing has the
Five helical gears (7), the 5th described helical gear (7) center are fixed with third connecting shaft, the other end of the third connecting shaft
It is fixed with the first worm screw (8), first worm screw (8) and the first driving wheel (9) are meshed, first conical gear
(2) it is meshed with the second conical gear (10), described the second conical gear (10) center is fixed with the fourth connecting shaft, described
The other end of the fourth connecting shaft is fixed with the second worm screw (11), and second worm screw (11) mutually nibbles with the second driving wheel (12)
It closes, described the first driving wheel (9) center is fixed with the 5th connecting shaft, and the end of the 5th connecting shaft is fixed with the second biography
Driving wheel (12), first driving wheel (9) are the first worm gear or the 6th helical gear, and second driving wheel (12) is second
Worm gear or the 7th helical gear, it is necessary to meet following condition for the transmission mechanism:
1) number of teeth, the normal module, transverse module, normal pitch pressure angle, end face of the first helical gear (3) and the second helical gear (4) are taken
Pressure angle and spiral angle of graduated circle are respectively z3、z4、mn3、mt3、mn4、mt4、αn3、αt3、αn4、αt4、β3、β4, wherein z3、z4Take
Value can be made by oneself in the case that root is not cut as needed in satisfaction；β3、β4Often take 8 °~20 °；mn3、mn4、αn3、αn4It can be as needed
It makes by oneself or from gear handbook value, but must satisfy: mt3=mn3/cosβ3=mt4, αt3=arctg (tg αn3/cosβ3)=αt4,
β3=-β4；
2) number of teeth, the normal module, transverse module, normal pitch pressure angle, end face of third helical gear (5) and the 4th helical gear (6) are taken
Pressure angle and spiral angle of graduated circle are respectively z5、z6、mn5、mt5、mn6、mt6、αn5、αt5、αn6、αt6、β5、β6, wherein z5、z6Take
Value can be made by oneself in the case that root is not cut as needed in satisfaction；β5、β6Often take 8 °~20 °；mn5、mn6、αn5、αn6It can be as needed
It makes by oneself or from gear handbook value, but must satisfy: mt5=mn5/cosβ5=mt6, αt5=arctg (tg αn5/cosβ5)=αt6,
β5=-β6；
3) number of teeth, normal module, transverse module, normal pitch pressure angle, transverse pressure angle and the reference circle spiral shell of the 5th helical gear (7) are taken
Swing angle is respectively z7、mn7、mt7、αn7、αt7、β7, wherein z7Value meet root is not cut in the case where can make by oneself as needed；β7
Often take 8 °~20 °；mn7、αn7It can make by oneself or from gear handbook value, but must satisfy as needed: mt7=mn7/cosβ7=mt6,
αt7=arctg (tg αn7/cosβ7)=αt6, and meet β7=-β6:
4) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the first worm screw (8) are respectively z8、q8、mx8、αx8, wherein
z8Usually take 1,2,4,6；q8Value can refer to design of gears handbook；mx8、αx8It can make by oneself or be taken from gear handbook as needed
Value, but specific value is related with the transverse module of the first driving wheel and transverse pressure angle；The lead-angle of first worm screw (8)
γ8=arctanz8/q8Degree；
5) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the first driving wheel (9) are taken9、β9、mt9、αt9,
When the first driving wheel (9) are the first worm gear, z9Value range often between 28~80；When the first driving wheel (9) are the 6th
When helical gear, z9Value meet root is not cut in the case where can make by oneself as needed；β9It can make by oneself as needed；mt9、αt9It can
It makes by oneself or from gear handbook value, but must satisfy as needed: mx8=mt9, αx8=αt9, passed in the first worm screw (8) with first
In the case that (9) two axle clamp angle of driving wheel is 90 degree, also meet β9=γ8；
6) taking the number of teeth of the first conical gear (2) and the second conical gear (10), big end modulus, big end pressure angle is respectively z2、
z10、m2、m10、α2、α10, wherein z2、z10Value meet root is not cut in the case where can make by oneself as needed；m2、m10、α2、α10
It can make by oneself or from gear handbook value, but must satisfy as needed: m2=m10, α2=α10；
7) head number, diameter quotient, axial plane modulus and the axial plane pressure angle for taking the second worm screw (11) are respectively z11、q11、mx11、αx11,
Wherein z11Usually take 1,2,4,6；q11Value can refer to design of gears handbook；mx11、αx11It can make by oneself as needed or from gear
Handbook value, but specific value is related with the transverse module of the second driving wheel 12 and transverse pressure angle；The indexing of second worm screw 11
Circle lead angle γ11=arctanz11/q11Degree；
8) number of teeth, spiral angle of graduated circle, transverse module and the transverse pressure angle difference z of the second driving wheel (12) are taken12、β12、mt12、
αt12, when the second driving wheel (12) are the second worm gear, z12Value range often between 28~80；When the second driving wheel (12)
When for seven helical gears, z12Value meet root is not cut in the case where can make by oneself as needed；β12It can make by oneself as needed；
mt12、αt12It can make by oneself or from gear handbook value, but must satisfy as needed: mx11=mt12, αx11=αt12, in the second worm screw
(11) in the case where being 90 degree with (12) two axle clamp angle of the second driving wheel, also meet β12=γ11。
2. a kind of twin worm point-line meshing transmission mechanism according to claim 1, it is characterised in that: first circular cone
Gear (2), the first helical gear (3), the second helical gear (4), third helical gear (5), the 4th helical gear (6), the 5th helical gear
(7), the first worm screw (8), the first driving wheel (9), the second conical gear (10), the second worm screw (11) and second driving wheel (12) etc.
The existing involute of the tooth form of gear tooth profile has circular arc again, i.e. the high half of gear teeth tooth is that the double wedge of involute profile is wide, the other half
It is wide for the concave tooth of easement curve tooth form.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820845408.2U CN208474410U (en) | 2018-06-01 | 2018-06-01 | A kind of twin worm point-line meshing transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820845408.2U CN208474410U (en) | 2018-06-01 | 2018-06-01 | A kind of twin worm point-line meshing transmission mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN208474410U true CN208474410U (en) | 2019-02-05 |
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ID=65215963
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| CN201820845408.2U Expired - Fee Related CN208474410U (en) | 2018-06-01 | 2018-06-01 | A kind of twin worm point-line meshing transmission mechanism |
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2018
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Granted publication date: 20190205 Termination date: 20210601 |