CN201068954Y - Gear transmission arrangement and gear - Google Patents
Gear transmission arrangement and gear Download PDFInfo
- Publication number
- CN201068954Y CN201068954Y CNU2007200902631U CN200720090263U CN201068954Y CN 201068954 Y CN201068954 Y CN 201068954Y CN U2007200902631 U CNU2007200902631 U CN U2007200902631U CN 200720090263 U CN200720090263 U CN 200720090263U CN 201068954 Y CN201068954 Y CN 201068954Y
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Abstract
The utility model provides a gear driving gear and a gear. The curves of the gear teeth of the gear are sine curves or cosine curves. The gear drive device comprises at least a driving gear and a driven gear, the modulus and the tooth addendum of the driving gear are equal to the modulus and the tooth addendum of the driven gear, and the curves of the gear teeth of the drive gear and the driven gear are all the sine curves or the cosine curves. Because the meshed gear tooth constantly cut mutually in the central connection line when the two gears in the drive device are driven according to the tooth number rate, compared with the involute gear drive in the prior art, the bending capacity of the utility model can be increased by a plurality of times or even tens of times; and the sliding ratio can be reduced to 0-1.3, the single stage transmission efficiency can be maintained over 0.98; due to the gears with continuously closed sine/cosine curves in the driving gear, the gear has simple structure and convenient process and is more favorable for program process for the gears.
Description
Technical field
The utility model relates to a kind of driving mechanism, relates in particular to a kind of gear drive and gear.
Background technique
At present, in the driving mechanism that generally uses, belt transmission, hydraulic transmission arranged, reach gear transmission or the like.Its gear-driven gear normally adopts involute tooth or cycloid tooth.
In the invention process, the inventor finds that there is following technical problem at least in above-mentioned prior art gear:
1) technical failures such as tooth fractures, damage appear in described prior art involute tooth or cycloidal gear gear easily.Cause analysis is as follows: the module of above-mentioned prior art involute tooth or cycloidal gear gear is not suitable for too big, and the number of teeth is not suitable for very little.Therefore a little less than the bending bearing capacity that the number of teeth is big, modulus causes gear for a short time, the antiscuffing capacity, so phenomenons such as fractureing often appears in transmission process in these gear teeth, damage;
2) maintenance cost height.Owing to above-mentioned flimsy reason, gear requirement material is good in addition, technological level is high, and prior art involute tooth or cycloidal gear gear are repaired very difficult after damage;
3) transmission efficiency is lower.In transmission, the sliding ratio of involute gear changes between 0～∞, generally can only be controlled between the 2-8 in the practice.The sliding ratio of worm drive gear is then between 2-10.The single staged transmission ratio of involute gear is generally below 6.3, though the velocity ratio single-stage of worm drive gear can reach 50, its sliding ratio is big, and efficient is lower.
Simultaneously, prior art gear structure complexity, its bearing capacity and transmission efficiency have not had the further space of raising.
In addition, the SU-652-394 patent disclosure of announcing on March 15th, 1979 a kind of eccentric swing pinion driving mechanism, but it is a kind of interior engagement epicyclic transmission mechanism of eccentric rotation, transmission efficiency is low, sliding ratio is big.
The model utility content
The purpose of this utility model is to provide respectively a kind of simple in structure, gear drive and gear that working efficiency is higher.
One of the purpose of this utility model is achieved in that provides a kind of gear drive, comprise at least one driving gear and a driven gear, it is characterized in that, the modulus of described driving gear and driven gear and addendum equate, and the gear teeth curve of described driving gear and driven gear is sine or cosine curve.
Two of the purpose of this utility model is achieved in that a kind of gear, it is characterized in that: the gear teeth curve of described gear is sine or cosine curve.
Specifically, described gear teeth curve is cosine curve: ρ=γ ± ecosz θ, and wherein ρ is the polar coordinates radius vector, and γ is a reference radius, and γ=mz/2, m are modulus, and z is the number of teeth, and θ is a corner, and e is addendum and equals half of whole depth.
Beneficial effect: owing in transmission device, adopt sine or cosine curve gear structure, and the modulus of driving and driven gear and e value equate, two gears during by the gear ratio transmission meshing wheel wheel tooth perseverance be cut on the line of centres mutually, compare with the prior art Involutes Gears Transmission, in centre distance, under the identical condition of velocity ratio, module can be accomplished involute gear several times even tens times, therefore under rapidoprint condition of the same race, the gear bending bearing capacity can be greatly several times even tens times; Therefore and sliding ratio can be reduced to 0～1.3, helps reducing friction, abrasion, improves mechanical efficiency, antiscuffing capacity and increases the service life; Because sine or cosine curve gear structure make initiatively and the rotation between the driven gear more approaches pure rolling, its single-stage driving efficient can be stabilized in more than 0.98, and the mechanical efficiency of transmission device significantly improves and transmission efficiency can not reduce with the increase of velocity ratio; Because adopting gear teeth curve in transmission device is continuously the gear of the sin/cos curve of sealing, gear structure is simple, can realize grinding easily, makes it to obtain optimal flank of tooth degree of finish, thereby reduces friction loss the raising mechanical efficiency; Easy to process, more help the gear processing of programming.
Description of drawings
Fig. 1 is the structural representation of the utility model gear drive first mode of execution;
Fig. 2 is the structural representation of the utility model gear drive second mode of execution;
Fig. 3 is the schematic cross-section of prior art planetary type gear transmission unit;
Fig. 4 is the schematic cross-section of Fig. 2 middle gear transmission device.
Embodiment
It is example explanation the utility model gear drive that this paper lifts the parallel-axes gears retarder.But in the utility model spirit, described gear drive can be applied in other driving mechanisms, such as the utility model being applied in gear accelerator or the multistage driver.
The technical solution that adopts comprises:
Consult Fig. 1, provide the utility model gear drive first mode of execution, described gear drive is the parallel-axes gears retarder, comprises body, case lid, input shaft, output shaft (figure does not show), reducing gear.Wherein reducing gear is provided with less driving gear and bigger driven gear.Described driving gear is installed on the described input shaft, and adopts the cosine curve gear structure.Described driven gear is installed on the described output shaft.Engagement system engagement beyond the gear teeth of described driving gear and driven gear.Solid line shows respectively that with the Fu line gear turns to the shape in the different moment among the figure.
The gear teeth curve of described driving gear and driven gear is a cosine curve of sealing continuously, its universal equation formula is ρ=γ ± ecosz θ, wherein ρ is the polar coordinates radius vector, γ is a reference radius, γ=mz/2, m are modulus, and z is the number of teeth, θ is a corner, and e is addendum and equals half of whole depth.
The modulus of described driving gear and two gears of driven gear and e value equate, therefore can mutual meshing transmission, and two gears during by the gear ratio transmission equal perseverance be cut in the line of centres mutually, its principle is as follows:
If the driving gear number of teeth is z
1, the driven gear number of teeth is z
2, modulus is m, and addendum is e, and corner is respectively θ
1, θ
2, θ during two gear mesh transmissions
1=(z
1/ z
2) θ
2, with the above-mentioned gear teeth curve of above data substitution universal equation formula, can get:
The tooth trace equation of driving gear is: ρ
1=γ
1± ecosz
1θ
1=mz
1/ 2 ± ecosz
1θ
1
The tooth trace equation outer gearing of driven gear is: ρ
2=γ
2± ecosz
1θ
2=mz
2/2-(± ecosz
2θ
2)
Interior meshing: ρ
2=γ
2± ecosz
2θ
2=mz
2/2(± ecosz
2θ
2)
Outer meshing centre distance: al=ρ
1+ ρ
2=γ
1± ecosz
1θ
1+ γ
2-(± ecosz
1θ
1)=γ
1+ γ
2
Interior meshing centre distance: a2=ρ
1-ρ
2=γ
2± ecosz
2θ
2-(γ
1± ecosz
1θ
1)=γ
2-γ
1
Owing to can guarantee ρ
1+ ρ
2=γ
1+ γ
2And ρ
1-ρ
2=γ
2-γ
1, therefore guarantee that the engagement perseverance of driving gear and driven gear is tangential on the line of centres of two-wheeled.
According to above-mentioned gear teeth curve, state as follows to driving gear and the intermeshing principle of driven gear below:
If the reference radius of driven gear is R, the center is 0b, and the number of teeth is n, and addendum and dedendum of the tooth are e, garden, top radius is R+e; Root radius is R-e, establishes the calibration garden radius r of driving gear, and the number of teeth is 1, and addendum and dedendum of the tooth also are e, top garden radius r+e, root garden radius r-e.When driving gear drives the driven gear transmission, the polar coordinates radius vector ρ of driving gear
1Cumulative by r-e to r+e, this moment driven gear ρ
2Must be by R+e during decrescence to R-e, make ρ
1+ ρ
2Be constantly equal to R+r, driving gear drove and rotated from the tooth driving wheel this moment, but when the radius vector of the radius vector gear of driving gear during by r+e gradual change row r-e, because diminishing gradually, its ρ value can not drive the driven gear rotation, can have the 2nd driving gear that fuses with first this moment, and the ρ value of described the 2nd driving gear is changed from small to big and continued to drive the driven gear rotation.Therefore consider from more excellent design that the structure by the 2 interlaced combinations drive of above driving gear driven gears can guarantee that driven gear keeps continuous transmission.
When the rotating speed of driven gear and driving gear is 1: during n, require two-wheeled to intersect forever and be tangential on the line of 0a, 0b, promptly when two-wheeled with 1: during the ratio transmissions of n; When driven gear turns over θ
1, driving gear must turn over n θ
1When driven gear turns over θ
2Driving gear must turn over n θ
2, the rest may be inferred by analogy.In order to make two-wheeled by 1: its arc length of passing by is equal substantially during the n ratio transmissions, slides to reduce, and general desirable R=nr, n are integer.When being meshing with each other in the driving gear of this ratio manufacturing and driven gear, its maximum sliding ratio can be less than 1.3, the minimum average B configuration sliding ratio that this value both can have been accomplished less than involute gear more is significantly smaller than the sliding ratio of cylindrical worm-gear, thereby can obtain transmission efficiency preferably.
Design rational processing scheme by above rule and can process the cosine curve wheel tooth corridor of any number of teeth more than 1 tooth accurately, to obtain different velocity ratios.For example, described driving gear is that 1 tooth velocity ratio is the integer more than 2 or 2; Perhaps described driving gear is 2 teeth, its velocity ratio be more than 1.5,2,2.5,3 or 3, O.5 to be any one numeral in the tolerance equal difference array.
In addition, driving gear and driven gear are assembled with staggered several angle more than two.Wherein the number of teeth of driving gear can be made a tooth or two teeth, and the number of teeth of driven gear is pressed the size decision of velocity ratio.
This method can be applicable to processing external gear and internal gear simultaneously.The gear teeth curve of the number of teeth, modulus, interior external gear that addendum is identical is identical.
This driving and driven gear is engaged the number of teeth as velocity ratio according to two-wheeled.Manufacture and design the intermeshing novel parallel shaftgear of a pair of large and small gear gear that a cam processes as the foundation of back and forth feed by the requirement of chord curve.The sheet number of its gear mesh can be minimum each 2, can require choose suitable sheet number according to different stationarity, all can each interlacedly open a different Θ angle according to the different of sheet number and the number of teeth between each sheet of every pair of gear.Its value is:
Θ=360 °/(number of teeth * sheet number)
The driving and driven number of gears in the following formula can have nothing in common with each other; And the sheet number is identical.So driven gear, the Θ angle difference of driving gear.The driven gear number is the integer more than or equal to 2, and driving gear number of teeth minimum can be 1, or 1 above integer.
The processing method of the flank profil of the utility model transmission device middle gear can be divided into five kinds:
1) with various automatic control machine tool such as wire cutting machine tool, numerical control milling machine or machining center, as long as can process cosine flank profil on the gear smoothly and exactly by the curvilinear equation program of having numbered;
2) on backing-off lathe, change a social system the gear teeth curve that a feed cam can process 1～40 tooth in requirement according to above-mentioned gear teeth curvilinear equation, the curvilinear equation of this feed cam is P=r+ecosQ, or middle P is the polar coordinates radius of cam, r is the calibration garden radius of cam, its value is by the requirement decision of feed gear, large and small unrestricted, but the e value should equate with the e value of cosine gear to be processed;
3) on general general purpose machine tool, design a cover feed gear voluntarily and process flank profil;
4) adopt special purpose machine tool to process;
5) adopt modes such as precision casting technology, powder metallurgy or impact briquetting not have cutting, further reduce spillage of material, grand low-cost.
Below as can be seen, the utility model is owing to the gear structure that adopts the cosine curve gear in transmission device, and the modulus of driving and driven gear equates with the e value.Time engagement gear teeth perseverance is cut on the line of centres two teeth mutually by the gear ratio transmission, compare with the prior art Involutes Gears Transmission, in centre distance, under the identical condition of velocity ratio, module can be accomplished involute gear several times even tens times, therefore under rapidoprint condition of the same race, its bending bearing capacity can be greatly several times even tens times; And, sliding ratio can be reduced to 0～1.3, therefore helps reducing friction, abrasion, improves mechanical efficiency and increases the service life, its single-stage driving efficient can be stabilized in more than 0.98, and the mechanical efficiency of transmission device significantly improves and transmission efficiency can not reduce with the increase of velocity ratio.
Because adopting gear teeth curve in transmission device is continuously the gear of the cosine curve of sealing, can realize grinding easily, makes it to obtain optimal flank of tooth degree of finish, thereby reduces friction loss the raising mechanical efficiency; Gear structure is simple, easy to process, more help the gear processing of programming; Technology capability is good, and the usefulness material is less demanding etc.
The single staged transmission ratio of the utility model transmission device is generally optional between 1-50 or in the bigger scope; The velocity ratio bigger as needs can multistagely be contacted.Overcome the suitable little unsuitable big or suitable greatly unsuitable little defective of existing other driving mechanism.Because this transmission does not have axial force, do not need to adopt thrust-bearing again.
The utility model transmission device is applicable to speedup, deceleration, the gear of the various machinery of all trades and professions, needs as reality, can make big modulus gear wheel in large diameter to satisfy the demands.
Consult Fig. 2, the utility model also provides gear drive second mode of execution, revolving the mode difference with above-mentioned first reality is: described driven gear is changed to inside engaged gear, be the internal chamber wall that the gear teeth of driven gear are produced on gear, the gear teeth of driving gear are in internal chamber wall and its gear teeth meshing of the driven gear gear teeth.
Outside the various advantages of the utility model transmission device mode of execution of present embodiment engagement system combination except that having gear, also have following advantage:
1) because interior engagement more approaches pure rolling, so mechanical efficiency is higher;
2) compare with the combination of outer gearing structure gear, its centre distance was little when the Gear combination of the internal gearing structure of the same number of teeth, modulus, addendum meshed, and more saved the space:
3) frictional loss is lower.Below be the static friction test result that gear carried out to 3 kinds of dissimilar tooth form structures:
| Profile of tooth | Involute profile | Outer gearing cosine curve profile of tooth | Interior engagement cosine curve profile of tooth |
| Friction torque | 174.9g.cm | 138.6g.cm | 118.8g.cm |
| Percentage | 100％ | 79.2％ | 67.9％ |
Table one: the static friction test result of the gear of dissimilar tooth form structure
As can be seen from the above table, the frictional loss of involute gear is greater than the frictional loss of cosine curve tooth-profile of gear, and interior engagement cosine curve profile of tooth more is better than the gear of outer gearing cosine curve profile of tooth.
Consult Fig. 3 and Fig. 4, be the above-mentioned advantage of transmission device of explanation the utility model internal gearing structure, every performance of existing transmission device to the utility model internal gearing structure among NGW planetary type gear transmission unit and Fig. 4 among Fig. 3 is compared.The NGW11-6 velocity ratio equals 5 in this example, the center height is 125, the input shaft diameter of axle is 30, the output shaft diameter of axle is 50, finish identical the utility model internal gearing structure gear drive relatively with parameter, when the input shaft rotating speed was 1000 rev/mins, the input power of NGW11-6 was 16.2kw, and the input power of the utility model internal gearing structure transmission device is 21.79kw, has improved 34.5%; The output torque of NGW11-6 is 76kgf-M, and the output torque of the utility model internal gearing structure gear drive is 98.26kgf-M, has improved 29.3%.In shape, the axial of the utility model internal gearing structure gear drive reduced 5%, and owing to have only a pair of gear, gross weight has reduced 9kg, reduces 18%.
The gear teeth curve of above-mentioned the utility model gear drive middle gear also can be a sinusoidal curve, and equation can be: ρ=γ ± esinz θ.And, in the utility model spirit, described gear teeth curve can allow to do certain change on ρ=γ ± ecosz θ or γ ± esinz θ basis, perhaps, actual gear tooth curve can allow to have certain deviation, but belongs to equally in the utility model scope.In sum, this description should not be construed as restriction of the present utility model.
Claims (9)
1. gear drive, comprise at least one driving gear and a driven gear, it is characterized in that the modulus of described driving gear and driven gear and addendum equate, and the gear teeth curve of described driving gear and driven gear is sine or cosine curve.
2. loading drive gear transposition according to claim 1 is characterized in that: described cosine curve is ρ=γ ± ecosz θ, and wherein ρ is the polar coordinates radius vector, γ is a reference radius, and γ=mz/2, m are modulus, z is the number of teeth, and θ is a corner, and e is addendum and equals half of whole depth.
3. gear drive according to claim 1 is characterized in that: the composite structure of described driving gear and driven gear is that the wheel combination is nibbled in outer gearing or interior engagement.
4. gear drive according to claim 1 is characterized in that: described driving gear is 1 tooth, and velocity ratio is the integer more than 2 or 2; Perhaps described driving gear is 2 teeth, and its velocity ratio is 1.5,2,2.5,3, or velocity ratio be more than 3, be any one numeral in the tolerance equal difference array with 0.5.
5. gear drive according to claim 1 is characterized in that: described gear drive is parallel axes deceleration, speedup or variable speed drive.
6. gear drive according to claim 1 is characterized in that: described driving gear and driven gear are assembled with staggered several angle more than two, and the sheet number of described driving gear and driven gear is consistent.
7. gear, it is characterized in that: the gear teeth curve of described gear is sine or cosine curve.
8. gear according to claim 7 is characterized in that: described gear teeth curve is cosine curve: ρ=γ ± ecosz θ, and wherein ρ is the polar coordinates radius vector, γ is a reference radius, and γ=mz/2, m are modulus, z is the number of teeth, and θ is a corner, and e is addendum and equals half of whole depth.
9. gear according to claim 8 is characterized in that: the number of teeth of described gear is the integer more than 1 or 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200902631U CN201068954Y (en) | 2007-05-08 | 2007-05-08 | Gear transmission arrangement and gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200902631U CN201068954Y (en) | 2007-05-08 | 2007-05-08 | Gear transmission arrangement and gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201068954Y true CN201068954Y (en) | 2008-06-04 |
Family
ID=39490338
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007200902631U Expired - Fee Related CN201068954Y (en) | 2007-05-08 | 2007-05-08 | Gear transmission arrangement and gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201068954Y (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103122971A (en) * | 2013-02-05 | 2013-05-29 | 西安理工大学 | Externally meshed gear pair |
| CN103758749A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN103758753A (en) * | 2014-01-27 | 2014-04-30 | 浙江水利水电学院 | Six-blade differential speed pump driven by Pascal non-circular gears |
| CN105121910A (en) * | 2012-12-18 | 2015-12-02 | 伦策驱动有限公司 | Gear and transmission comprising such a gear |
| CN109404493A (en) * | 2018-12-18 | 2019-03-01 | 西华大学 | Heavy-load type cosine gear double enveloped hourglass worm drives |
| CN112228529A (en) * | 2020-10-12 | 2021-01-15 | 燕山大学 | Novel full-series string gear and gear set thereof |
| CN112377574A (en) * | 2020-12-03 | 2021-02-19 | 福建思普计量检测科技有限公司 | Gear transmission structure |
| CN112377572A (en) * | 2020-12-03 | 2021-02-19 | 福建思普计量检测科技有限公司 | Multistage gear drive structure |
| CN112555356A (en) * | 2020-12-03 | 2021-03-26 | 福建思普计量检测科技有限公司 | Gear acceleration transmission unit |
-
2007
- 2007-05-08 CN CNU2007200902631U patent/CN201068954Y/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105121910A (en) * | 2012-12-18 | 2015-12-02 | 伦策驱动有限公司 | Gear and transmission comprising such a gear |
| CN103122971A (en) * | 2013-02-05 | 2013-05-29 | 西安理工大学 | Externally meshed gear pair |
| CN103122971B (en) * | 2013-02-05 | 2015-11-18 | 西安理工大学 | External gear pump is secondary |
| CN103758749A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN103758753A (en) * | 2014-01-27 | 2014-04-30 | 浙江水利水电学院 | Six-blade differential speed pump driven by Pascal non-circular gears |
| CN103758749B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN109404493A (en) * | 2018-12-18 | 2019-03-01 | 西华大学 | Heavy-load type cosine gear double enveloped hourglass worm drives |
| CN112228529A (en) * | 2020-10-12 | 2021-01-15 | 燕山大学 | Novel full-series string gear and gear set thereof |
| CN112228529B (en) * | 2020-10-12 | 2021-09-28 | 燕山大学 | Full-series string gear and gear set thereof |
| CN112377574A (en) * | 2020-12-03 | 2021-02-19 | 福建思普计量检测科技有限公司 | Gear transmission structure |
| CN112377572A (en) * | 2020-12-03 | 2021-02-19 | 福建思普计量检测科技有限公司 | Multistage gear drive structure |
| CN112555356A (en) * | 2020-12-03 | 2021-03-26 | 福建思普计量检测科技有限公司 | Gear acceleration transmission unit |
| CN112377572B (en) * | 2020-12-03 | 2022-02-11 | 福建思普计量检测科技有限公司 | Multistage gear drive structure |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080604 Termination date: 20110508 |