CN205101504U - Worm helical drive is vice based on become pressure angle - Google Patents
Worm helical drive is vice based on become pressure angle Download PDFInfo
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- CN205101504U CN205101504U CN201520625175.1U CN201520625175U CN205101504U CN 205101504 U CN205101504 U CN 205101504U CN 201520625175 U CN201520625175 U CN 201520625175U CN 205101504 U CN205101504 U CN 205101504U
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- helical gear
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- worm screw
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Abstract
The utility model discloses a worm helical drive is vice based on become pressure angle. In order to achieve the purposes, the utility model discloses worm helical drive is vice based on become pressure angle contains intermeshing's worm and helical gear, helical gear transverse module (Mt2) worm axial plane modulus (Ma1), helical gear terminal surface reference circle profile angle ( alpha n2) > worm axial plane reference circle profile angle ( alpha n1), oblique gear indexing circle helical angle ( beta 2) worm axial plane lead -angle ( lambda 1), helical gear terminal surface reference circle profile angle ( alpha n2) worm axial plane reference circle profile angle ( alpha n1) is less than 10. The vice transmission of worm helical drive is reliable, durable, and it is easy to make.
Description
Technical field
It is secondary that the utility model relates to a kind of worm helical gear transmission, particularly relates to the transmission that metal worm screw engages with plastic beveled wheel.
Background technique
Worm helical gear transmission is at little to driving contact stress surface (in light level load) and transmission accuracy without the occasion of being strict with, and alternative worm screw worm gear drive, is widely used in the field such as automobile, machine for kitchen use comprehensively.Employ the electric motor of automobile (windscreen wiper shakes window etc.) of worm helical gear transmission, require to have the high and low noise of reliability, long lifetime and characteristic of low cost, this just becomes the operative orientation of enterprise;
Traditional theory is thought: worm screw and helical gear correct engagement condition are: Mt2 (helical gear transverse module)=Ma1 (worm shaft face mould number); α n2 (helical gear end face standard pitch circle tooth-shape angle)=α a1 (worm screw axial plane standard pitch circle tooth-shape angle); β 2 (helical gear spiral angle of graduated circle)=λ 1 (worm screw axial plane lead-angle); Namely need to meet modulus, pressure angle, condition that helix angle is equal respectively.
Thus, owing to will meet the meshing condition of gear traditional theory, worm screw and plastic gear, be generally nonstandard gear, and this considerably increases the difficulty of processing of plastic gear undoubtedly, and usually need open injection mould processing plastic gear, this just creates some problems:
1. gear injection mould, required precision is high, and manufacture difficulty is large, and the cycle is long;
2. gear injection molding machine, required precision is high, and technique is strict;
3. gear material requires high, and need be out of shape little, because gear thickness differs, profile of tooth is yielding, and poor stability.
We have carried out long research for above-mentioned technical problem, the method solved the problems of the technologies described above that we adopt at present is in metal worm screw and plastic beveled wheel transmission, because metal is different with intensity with the material property of plastics, we adopt tangent modification method, thinning worm tooth shape thickness, and the corresponding helical gear profile of tooth thickness that thickens, thus to reach the effect that metal worm tooth and plastics helical teeth can bear onesize power, avoid plastic gear broken teeth, meet motor life requirement; Meanwhile, be ensure less noise, worm screw adopts less off-gauge pressure angle (tooth-shape angle as 10 °, 14.5 ° etc.) usually; For meeting above-mentioned requirements, worm screw and plastic beveled wheel are nonstandard gear (usual pressure angle and transverse tooth thickness nonstandard), and plastic beveled wheel needs injection mould to process; Same, this injection mould required precision is high, and cost is high, and the process-cycle is long, and injection made gear profile of tooth distortion large (profile of tooth became uneven), is unfavorable for new product development and batch production.
Model utility content
Technical problem to be solved in the utility model is for above-mentioned deficiency of the prior art, provides a kind of worm helical gear transmission based on variable pressure angle secondary; The reliable transmission of described worm helical gear transmission pair, durable, easy to manufacture.
In order to achieve the above object, the utility model is achieved by the following technical solutions:
Worm helical gear transmission based on variable pressure angle is secondary, comprises intermeshing worm screw and helical gear; Described worm screw is metal worm screw, and described helical gear is plastic beveled wheel;
Described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1);
Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1);
Helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1);
Described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 10 °.
Feature and further improvement of the above-mentioned mode of execution of the utility model are:
(1) when, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2)=worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L1;
When, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L2;
Centre distance increasing amount (Δ L)=L2-L1;
Helical gear transverse module × 10%≤Δ L≤helical gear transverse module × 30%.
(2) described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 5 degree.
(3) described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1)=0.8;
Described helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1)=7.59389 °;
Described helical gear end face standard pitch circle tooth-shape angle (α n2)=20 °;
Described worm screw axial plane standard pitch circle tooth-shape angle (α n1)=14.5 °.
Further: described centre distance increasing amount (Δ L)=0.15mm.
Further: described helical gear standard pitch diameter is 48.56mm; The pressure angle at described helical gear standard pitch circle place is 14.5 °; Described helical gear root diameter is 48.3mm.
Further: the described helical gear number of teeth, normal profile angle, addendum coefficient, overlap arc, helix direction, spiral angle of graduated circle and spanning measure tooth number are followed successively by: 62,20 °, 1 ,+0.162, right, 7 ° 35 ' 38 " and 6.
Further: the number of threads of described worm screw, normal profile angle, helix direction, overlap arc, mesurement over pins, measuring pin diameter, lead angle, axial pitch, diametral quotient, standard pitch diameter and root diameter are followed successively by: 1,14.5 °, dextrorotation, 0,8.65mm, 1.75mm, 7 ° 35 ' 38 ", 2.535mm, 7.5,6.05mm and 4.5mm.
When above-mentioned worm helical gear transmission pair is used for wiper motor, described wiper motor comprises drive motor, and described drive motor drives the worm screw connecting described worm helical gear transmission pair; The worm drive wiper of described worm helical gear transmission pair swings.
The utility model beneficial effect is:
The utility model is ensureing under the condition that worm screw identical with helical gear modulus (standard module Mn=0.8) is identical with oblique gear spiral angle (7.59389 °) with worm screw angle of lead, adopt different pressures angle (tooth-shape angle) design, worm screw pressure angle (14.5 °), plastic gear is designed to standard pressure angle (20 °).Plastic gear adopts the design of standard (greatly) pressure angle; thus the method for standard hob gear hobbing can be adopted; processing plastic gear; when do not open injection mould or only tooth punching mold; just product research and development of new product and batch production can be carried out; solve in worm helical gear transmission; plastic gear is difficult to processing and profile of tooth holds yielding problem; improve Gear Processing precision; reduce noise; reduce product development cycle, cost and risk, meet product long lifetime, low noise (50dB/30CM) requirement, now produce in batches, supply.
The utility model is concrete:
1. adopt the design of variable pressure angle, design with same pressure angle, the Line of contact (by the line of force) of worm tooth and plastic gear there occurs change, variable quantity and angle variable quantity positive correlation, so angle variable quantity is advisable to be less than 5 °, is usually no more than 10 °;
2., for ensureing different pressures angle worm tooth and plastic gear engagement well, suitably can increase centre distance, advise getting by 10% ~ 30% of modulus, we add 0.2mm in a particular embodiment;
3. adopt the design of variable pressure angle, gears meshing line (standard pitch circle) does not change, and gear ratio does not send out change;
4., because gearing factor is much larger than 1, also reach the requirement of stable drive;
5. be the intensity improving plastic gear further, plastic gear adopts normal shift.
Accompanying drawing explanation
Fig. 1 is the structural representation of the tooth base of injection mould processing;
Fig. 2 is the helical gear structural representation after gear hobbing machine gear hobbing;
Fig. 3 is the structural representation overlooking direction of helical gear a kind of embodiment of the present utility model;
Fig. 4 is that the A-A of Fig. 3 is to sectional structure schematic diagram;
Fig. 5 is the structural representation of a kind of embodiment of worm screw of the present utility model;
Fig. 6 is the perspective view of a kind of embodiment of the rain shaving electrical machine adopting worm helical gear transmission pair of the present invention;
Fig. 7 is the structural representation overlooking direction of Fig. 6.
Description of reference numerals:
1-helical gear, 2-rotating shaft.
Embodiment
Below in conjunction with drawings and Examples, the utility model embodiment is described:
As shown in Fig. 1 ~ 7, it illustrates embodiment of the present utility model, the utility model is secondary based on the worm helical gear transmission of variable pressure angle, comprises intermeshing worm screw and helical gear; Described worm screw is metal worm screw, and described helical gear is plastic beveled wheel; It is characterized in that:
Described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1);
Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1);
Helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1);
Described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 10 °.
In some specific embodiments:
When, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2)=worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L1;
When, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L2;
Centre distance increasing amount (Δ L)=L2-L1;
Helical gear transverse module × 10%≤Δ L≤helical gear transverse module × 30%.
Because pressure angle is different, worm screw and helical gear engagement, need larger gear backlash, worm screw just can be made to be tangential on helical gear at standard pitch circle, and avoid interfering.We increase gear backlash by increasing centre distance; Need the sideshake amount increased, equal the thick value added of helical gear standard pitch circle.Except in the value of gear common normal, consider gap factor, ensure contact ratio condition under, suitably widen centre distance, to increase gear backlash, make worm tooth-surface can near standard pitch circle the plastics flank of tooth tangent, engagement, ensure engagement good.
We are in a kind of specific embodiment, and plastic gear standard pitch circle profile of tooth thickness is increased 0.1mm, and inverse is to center distance change amount Δ a=common normal line variation/2xTan20 °=0.1/2xTan20 °=0.137 (mm); Operating center distance increases 0.15mm (actual processing 28.2-theory calculate 28.05=0.15), is greater than 0.137mm.
Have employed the Another reason of larger gear backlash, is consider in plastic gear loading process, the factor of fever expansion.
In certain embodiments: described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 5 degree.
In a preferred embodiment:
Described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1)=0.8;
Described helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1)=7.59389 °;
Described helical gear end face standard pitch circle tooth-shape angle (α n2)=20 °;
Described worm screw axial plane standard pitch circle tooth-shape angle (α n1)=14.5 °.
Improvement as the further mode of execution of above preferred embodiment: described centre distance increasing amount (Δ L)=0.15mm.
Improvement as the further mode of execution of above preferred embodiment: described helical gear standard pitch diameter is 48.56mm; The pressure angle at described helical gear standard pitch circle place is 14.5 °; Described helical gear root diameter is 48.3mm.
Improvement as the further mode of execution of above preferred embodiment: the described helical gear number of teeth, normal profile angle, addendum coefficient, overlap arc, helix direction, spiral angle of graduated circle and spanning measure tooth number are followed successively by: 62,20 °, 1 ,+0.162, right, 7 ° 35 ' 38 " and 6.
Improvement as the further mode of execution of above preferred embodiment: the number of threads of described worm screw, normal profile angle, helix direction, overlap arc, mesurement over pins, measuring pin diameter, lead angle, axial pitch, diametral quotient, standard pitch diameter and root diameter are followed successively by: 1,14.5 °, dextrorotation, 0,8.65mm, 1.75mm, 7 ° 35 ' 38 ", 2.535mm, 7.5,6.05mm and 4.5mm.
Secondary for worm helical gear transmission above-mentioned disclosed in the utility model, what we were concrete is used for wiper motor by described worm helical gear transmission pair, described wiper motor comprises drive motor, and described drive motor drives the worm screw connecting described worm helical gear transmission pair; The worm drive wiper of described worm helical gear transmission pair swings.
Preferred: the amplitude of fluctuation of described wiper is 90 degree or 160 degree.
In view of creative achievement of the present utility model, we adopt the wiper motor sample of described worm helical gear transmission pair to test, and test result is as following table (life test report):
By reference to the accompanying drawings the utility model preferred implementation is explained in detail above; but the utility model is not limited to above-mentioned mode of execution; in the ken that those of ordinary skill in the art possess; can also make a variety of changes under the prerequisite not departing from the utility model aim; these changes relate to correlation technique well-known to those skilled in the art, and these all fall into the protection domain of the utility model patent.
Do not depart from design of the present utility model and scope can make many other and change and remodeling.Should be appreciated that the utility model is not limited to specific mode of execution, scope of the present utility model is defined by the following claims.
Claims (8)
1. the worm helical gear transmission based on variable pressure angle is secondary, comprises intermeshing worm screw and helical gear; Described worm screw is metal worm screw, and described helical gear is plastic beveled wheel; It is characterized in that:
Described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1);
Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1);
Helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1);
Described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 10 °.
2. the worm helical gear transmission as claimed in claim 1 based on variable pressure angle is secondary, it is characterized in that:
When, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2)=worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L1;
When, described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1); Helical gear end face standard pitch circle tooth-shape angle (α n2) > worm screw axial plane standard pitch circle tooth-shape angle (α n1); During helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1), the centre distance of described helical gear and worm screw is L2;
Centre distance increasing amount (Δ L)=L2-L1;
Helical gear transverse module × 10%≤Δ L≤helical gear transverse module × 30%.
3. the worm helical gear transmission as claimed in claim 1 based on variable pressure angle is secondary, it is characterized in that: described helical gear end face standard pitch circle tooth-shape angle (α n2)-worm screw axial plane standard pitch circle tooth-shape angle (α n1) is less than 5 degree.
4. the worm helical gear transmission based on variable pressure angle as described in as arbitrary in claims 1 to 3 is secondary, it is characterized in that:
Described helical gear transverse module (Mt2)=worm shaft face mould number (Ma1)=0.8;
Described helical gear spiral angle of graduated circle (β 2)=worm screw axial plane lead-angle (λ 1)=7.59389 °;
Described helical gear end face standard pitch circle tooth-shape angle (α n2)=20 °;
Described worm screw axial plane standard pitch circle tooth-shape angle (α n1)=14.5 °.
5. the worm helical gear transmission as claimed in claim 4 based on variable pressure angle is secondary, it is characterized in that: described centre distance increasing amount (Δ L)=0.15mm.
6. the worm helical gear transmission as claimed in claim 4 based on variable pressure angle is secondary, it is characterized in that: described helical gear standard pitch diameter is 48.56mm; The pressure angle at described helical gear standard pitch circle place is 14.5 °; Described helical gear root diameter is 48.3mm.
7. the worm helical gear transmission as claimed in claim 4 based on variable pressure angle is secondary, it is characterized in that: the described helical gear number of teeth, normal profile angle, addendum coefficient, overlap arc, helix direction, spiral angle of graduated circle and spanning measure tooth number are followed successively by: 62,20 °, 1 ,+0.162, right, 7 ° 35 ' 38 " and 6.
8. the worm helical gear transmission as claimed in claim 4 based on variable pressure angle is secondary, it is characterized in that: the number of threads of described worm screw, normal profile angle, helix direction, overlap arc, mesurement over pins, measuring pin diameter, lead angle, axial pitch, diametral quotient, standard pitch diameter and root diameter are followed successively by: 1,14.5 °, dextrorotation, 0,8.65mm, 1.75mm, 7 ° 35 ' 38 ", 2.535mm, 7.5,6.05mm and 4.5mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520625175.1U CN205101504U (en) | 2015-08-19 | 2015-08-19 | Worm helical drive is vice based on become pressure angle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520625175.1U CN205101504U (en) | 2015-08-19 | 2015-08-19 | Worm helical drive is vice based on become pressure angle |
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| CN205101504U true CN205101504U (en) | 2016-03-23 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105179601A (en) * | 2015-08-19 | 2015-12-23 | 深圳市力辉电机有限公司 | Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair |
| CN105840779A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Knurled stepped worm shaft |
| CN105840778A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Stepped worm shaft |
| CN105840777A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Multi-ring locating stepped worm shaft |
| CN108317938A (en) * | 2017-01-16 | 2018-07-24 | 浙江师范大学 | A kind of involute helicoid worm pressure angle special measuring tool |
-
2015
- 2015-08-19 CN CN201520625175.1U patent/CN205101504U/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105179601A (en) * | 2015-08-19 | 2015-12-23 | 深圳市力辉电机有限公司 | Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair |
| CN105840779A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Knurled stepped worm shaft |
| CN105840778A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Stepped worm shaft |
| CN105840777A (en) * | 2016-04-29 | 2016-08-10 | 苏州鼎隆精密机械制造有限公司 | Multi-ring locating stepped worm shaft |
| CN108317938A (en) * | 2017-01-16 | 2018-07-24 | 浙江师范大学 | A kind of involute helicoid worm pressure angle special measuring tool |
| CN108317938B (en) * | 2017-01-16 | 2023-05-12 | 浙江师范大学 | Special measuring tool for involute worm pressure angle |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160323 |