CN105179601A - Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair - Google Patents
Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair Download PDFInfo
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- CN105179601A CN105179601A CN201510509308.3A CN201510509308A CN105179601A CN 105179601 A CN105179601 A CN 105179601A CN 201510509308 A CN201510509308 A CN 201510509308A CN 105179601 A CN105179601 A CN 105179601A
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 43
- 229920003023 plastic Polymers 0.000 claims description 22
- 239000004033 plastic Substances 0.000 claims description 22
- 239000002184 metal Substances 0.000 claims description 5
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000002347 injection Methods 0.000 description 7
- 239000007924 injection Substances 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 238000012545 processing Methods 0.000 description 7
- 238000013461 design Methods 0.000 description 5
- 238000012360 testing method Methods 0.000 description 3
- 238000012356 Product development Methods 0.000 description 2
- 238000010923 batch production Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 241000202814 Cochliomyia hominivorax Species 0.000 description 1
- 206010037660 Pyrexia Diseases 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000002715 modification method Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000007634 remodeling Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
- F16H1/18—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes the members having helical, herringbone, or like teeth
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60S—SERVICING, CLEANING, REPAIRING, SUPPORTING, LIFTING, OR MANOEUVRING OF VEHICLES, NOT OTHERWISE PROVIDED FOR
- B60S1/00—Cleaning of vehicles
- B60S1/02—Cleaning windscreens, windows or optical devices
- B60S1/04—Wipers or the like, e.g. scrapers
- B60S1/06—Wipers or the like, e.g. scrapers characterised by the drive
- B60S1/16—Means for transmitting drive
- B60S1/18—Means for transmitting drive mechanically
- B60S1/26—Means for transmitting drive mechanically by toothed gearing
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gears, Cams (AREA)
- Gear Transmission (AREA)
Abstract
The invention discloses a worm and helical gear transmission pair based on a variable pressure angle and application of the worm and helical gear transmission pair. The worm and helical gear transmission pair is reliable in transmission, durable and easy to manufacture. In order to achieve the purposes, the worm and helical gear transmission pair based on the variable pressure angle comprises a worm and a helical gear which are engaged with each other, wherein the transverse module (Mt2) of the helical gear is equal to the shaft surface module (Ma1) of the worm; the tooth profile angle alpha n2 of the end face reference circle of the helical gear is larger than the tooth profile angle alpha n1 of the shaft surface reference circle of the worm; the swing angle beta 2 of the reference circle of the helical gear is equal to the lead angle lambda 1 of the shaft surface reference circle of the worm; the difference between the tooth profile angle alpha n2 of the end face reference circle of the helical gear and the tooth profile angle alpha n1 of the shaft surface reference circle of the worm is smaller than 10 degrees.
Description
Technical field
The present invention relates to a kind of worm helical gear transmission secondary, particularly relate 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 t2 (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.
Summary of the invention
Technical problem to be solved by this invention is for above-mentioned deficiency of the prior art, provides a kind of worm helical gear transmission based on variable pressure angle secondary and uses thereof; The reliable transmission of described worm helical gear transmission pair, durable, easy to manufacture.
In order to achieve the above object, the present invention 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 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 present invention 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 at described helical gear standard pitch circle place comparatively 14.5 °; Described helical gear root diameter is 48.3mm.
Further: the described helical gear number of teeth, normal pitch profile angle, addendum coefficient, overlap arc, helix direction, helix angle at reference cylinder 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.
The invention also discloses a kind of purposes of above-mentioned worm helical gear transmission pair, it is characterized in that, described worm helical gear transmission pair is used for wiper motor, and 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.
Further: the amplitude of fluctuation of described wiper is 90 degree or 160 degree.
Beneficial effect of the present invention is:
The present invention 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 present invention 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., due to gearing factor >>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 invention;
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 invention;
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 specific embodiment of the invention is described:
As shown in Fig. 1 ~ 7, it illustrates the specific embodiment of the present invention, the worm helical gear transmission that the present invention is based on variable pressure angle is secondary, comprises intermeshing worm screw and helical gear; 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 Δ L/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 at described helical gear standard pitch circle place comparatively 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 pitch profile angle, addendum coefficient, overlap arc, helix direction, helix angle at reference cylinder 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.
For the embodiment of the purposes of above-mentioned worm helical gear transmission pair disclosed by the invention, 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 invention, 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 preferred embodiment for the present invention is explained in detail above; but the invention is not restricted 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 present inventive concept; these changes relate to correlation technique well-known to those skilled in the art, and these all fall into the protection domain of patent of the present invention.
Do not depart from the spirit and scope of the present invention and can make other changes many and remodeling.Should be appreciated that and the invention is not restricted to specific mode of execution, scope of the present invention is defined by the following claims.
Claims (10)
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 at described helical gear standard pitch circle place comparatively 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 pitch profile angle, addendum coefficient, overlap arc, helix direction, helix angle at reference cylinder 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.
9. the purposes of the worm helical gear transmission pair described in claim 1 ~ 8, it is characterized in that, described worm helical gear transmission pair is used for wiper motor, and 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.
10. the purposes of worm helical gear transmission pair as claimed in claim 9, is characterized in that: the amplitude of fluctuation of described wiper is 90 degree or 160 degree.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510509308.3A CN105179601A (en) | 2015-08-19 | 2015-08-19 | Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201510509308.3A CN105179601A (en) | 2015-08-19 | 2015-08-19 | Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair |
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| CN105179601A true CN105179601A (en) | 2015-12-23 |
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| CN201510509308.3A Pending CN105179601A (en) | 2015-08-19 | 2015-08-19 | Worm and helical gear transmission pair based on variable pressure angle and application of worm and helical gear transmission pair |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443689A (en) * | 2016-01-11 | 2016-03-30 | 珠海格力电器股份有限公司 | Transmission mechanism of windshield wiper |
| CN108561519A (en) * | 2018-06-01 | 2018-09-21 | 江苏理工学院 | A kind of large pressure angle worm gearing |
| CN108775378A (en) * | 2018-06-01 | 2018-11-09 | 江苏理工学院 | A kind of large pressure angle worm screw hoisting mechanism |
| CN108775379A (en) * | 2018-06-01 | 2018-11-09 | 江苏理工学院 | A kind of large pressure angle double worm mechanism |
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| CN103410917A (en) * | 2013-07-01 | 2013-11-27 | 江苏理工学院 | Asymmetric involute worm and bevel gear pair |
| CN205101504U (en) * | 2015-08-19 | 2016-03-23 | 深圳市力辉电机有限公司 | Worm helical drive is vice based on become pressure angle |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443689A (en) * | 2016-01-11 | 2016-03-30 | 珠海格力电器股份有限公司 | Transmission mechanism of windshield wiper |
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| CN108775378A (en) * | 2018-06-01 | 2018-11-09 | 江苏理工学院 | A kind of large pressure angle worm screw hoisting mechanism |
| CN108775379A (en) * | 2018-06-01 | 2018-11-09 | 江苏理工学院 | A kind of large pressure angle double worm mechanism |
| CN108775379B (en) * | 2018-06-01 | 2023-04-28 | 江苏理工学院 | Big pressure angle double worm drive mechanism |
| CN108561519B (en) * | 2018-06-01 | 2023-04-28 | 江苏理工学院 | Large-pressure-angle worm transmission mechanism |
| CN108775378B (en) * | 2018-06-01 | 2023-04-28 | 江苏理工学院 | Large-pressure-angle worm lifting mechanism |
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