CN201679933U - Long tooth profile gear - Google Patents
Long tooth profile gear Download PDFInfo
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- CN201679933U CN201679933U CN2010201970746U CN201020197074U CN201679933U CN 201679933 U CN201679933 U CN 201679933U CN 2010201970746 U CN2010201970746 U CN 2010201970746U CN 201020197074 U CN201020197074 U CN 201020197074U CN 201679933 U CN201679933 U CN 201679933U
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Abstract
The utility model relates to an improved involute gear, and belongs to the technical field of mechanical transmission. The utility model provides a long tooth profile gear which is provided with gear teeth evenly arranged in the circumferential direction, wherein, two sides of each gear tooth are of involute tooth profiles; for gear teeth with basic tooth profiles, ha is between 1.25m and 1.45m (both included), in which ha refers to the addendum and m refers to the modulus of the gear; for gear teeth with better controlled tooth profiles, ha is between 1.25m and 1.35m (both included). With barely no extra material cost, process changes and manufacture demands required, the utility model makes the most of the tooth part, and achieves the purpose of conserving energy, reducing consumption and being environment-friendly, aided by 20%-30% increase in action line length, over 20% improvement to the contact bearing capacity, over 10% increase in bending resistance, and noted noise reduction performance.
Description
Technical field
The utility model relates to a kind of gear, and especially a kind of improvement of involute gear belongs to the mechanical transmissioning technology field.
Background technique
Understand according to the claimant, the common ground of existing involute gear basic rack tooth profile is: the addendum coefficient han*=1 of basic rack tooth profile, and addendum and dedendum of the tooth (not comprising bottom clearance) equate, working depth h '=2m, the addendum coefficient of a pair of phase gear equates.
In the conventional application habitually in long-term edge many times, people make traditional design cause the waste of effective involute profile owing to ignored following 3 points: the noise that the bearing capacity that the transverse contact ratio that can strengthen fails to strengthen, can improve fails to improve, can reduce fails to reduce.
1. addendum coefficient equals the active profile length that involute profile length that the processing of 1 rack type cutter generates is used greater than the reality engagement, do not use when the involute profile that i.e. processing generates has a segment length (concerning gearwheel, this segment length is often very considerable) to use and cause waste (referring to Fig. 3).Among Fig. 3, h
AFThe available flank profil length that-Gear Processing generates; h
AEThe active profile length that the actual engagement of-gear is used.Thereby can consider that under the constant situation of this gear parameter the addendum that adds the phase gear that is higher than uses the one section involute profile that originally slatterns.
2. the addendum coefficient of the actual rack type cutter during roll flute is generally all greater than 1 (the gear hobbing flank profil that has is also greater than 1), and roll flute can reach addendum coefficient usually and equal the involute that 1.1～1.14 rack type cutter processing generates and can use flank profil length.Thereby and addendum to equal one section involute profile slatterning when 1 gear is meshed longer, in the height that can increase of the addendum of phase gear also can be longer.
3. process the dedendum of the tooth of the needed hobboing cutter of addendum that addendum coefficient equals 1 gear less than 1, promptly effective dedendum of the tooth of the needed hobboing cutter of gear hobbing is less than the addendum of adding work gear.Thereby can consider not strengthen effective dedendum of the tooth of hobboing cutter, just can process the flank profil of addendum coefficient with original hobboing cutter greater than the addendum part of 1 gear.
Based on above 3 points, the Chinese patent application that application number is 200720131057.0 and 200710191750.1, name is called " gear wheel with changed tooth height " has broken through the restriction of the addendum coefficient han*=1 of basic rack tooth profile, make tooth top up to 1.05m～1.25m, obviously improved the potential of the gear teeth.But because the designing technique obstacle that is subjected to not change the thinking constraint of original cutter and further strengthens addendum, the potential of the gear teeth still is far from excavating and puts in place.In fact, the hardened face gear of carburizing and quenching roll flute is used stays the mill hobboing cutter always will redesign manufacturing, and just the difference of parameter change amount size also just there is no need to be subjected to the constraint of conventional tool parameter fully.Even modified gear, as long as cost performance is suitable, the particular design cutter should not become restriction yet.
The model utility content
The utility model wants the technical solution problem to be: the shortcoming at above prior art exists under the prerequisite that does not change existing process means, proposes a kind of long flank profil gear.
In order to achieve the above object, long flank profil gear of the present utility model, have the gear teeth that are uniformly distributed along the circumference, described gear teeth both sides are involute profile, concern 1.25m≤ha≤1.45m between the modulus m of the addendum ha of wherein said gear teeth basic rack tooth profile and described gear, control range is 1.25m≤ha≤1.35m preferably usually.
Further, the pass between the modulus m of the working depth of described gear teeth basic rack tooth profile and described gear is: working depth equals 2.50m～2.80m; Pass between the modulus m of the whole depth of described gear teeth basic rack tooth profile and described gear is: whole depth equals 2.75m～3.05m.And the addendum of the same gear of gear and dedendum of the tooth (not comprising bottom clearance) not necessarily equate, the addendum of the large and small gear in a pair of gear that is meshed also not necessarily equates.
The utility model can be applied to carburizing and quenching roll flute gear, also can be used for modified or normalizing gear hobbing gear.Its beneficial effect is; by strengthening flank profil length; fully excavated the potential of tooth portion; increasing the gear material cost hardly, do not changing technology, do not strengthening basically under the prerequisite of manufacture difficulty; with the architecture advances that has scientific basis, can realize improving the length of line of action about 20%～30%, the contact bearing capacity more than 20% of raising; the crooked bearing capacity 10% or more that improves also reduces the remarkable result of noise, with the purpose that reaches energy-saving and cost-reducing, protects environment.
Description of drawings
Below in conjunction with accompanying drawing the utility model is further described.
Fig. 1 is an embodiment's of the utility model a small gear flank profil schematic representation.
Fig. 2 is the flank profil schematic representation with the gearwheel of Fig. 1 pinion.
Fig. 3 gear engagement starting point E and involute starting point F position view.
Fig. 4 is for influencing the main geometrical factor of teeth bending strength: thickness at root of tooth S
Fn, bending moment arm h
f, the Fillet radius ρ at 30 ° of tangent line places
F
Fig. 5 is one of single schematic diagram to tooth meshing zone upper bound point D place for load in the nodal method plane acts on.
Two of Fig. 6 single schematic diagram to tooth meshing zone upper bound point D place for load in the nodal method plane acts on.
Embodiment
Embodiment one
The long flank profil gear of present embodiment as depicted in figs. 1 and 2.Fig. 1 for the invariant position x=0 addendum coefficient of the gear of 20 ° of numbers of teeth 27 of pressure angle be 1 flank profil, with modification coefficient x=0.65 addendum coefficient be that 1 flank profil (among the figure shown in the solid line), modification coefficient x=0.65 addendum coefficient are the comparison diagram of 1.3 flank profil (among the figure shown in the dotted line).Dotted line is depicted as the utility model flank profil among the figure.Fig. 2 for the invariant position x=0 addendum coefficient of the gear of 20 ° of numbers of teeth 61 of pressure angle be 1 flank profil, with modification coefficient x=0.7352 addendum coefficient be that 1 flank profil (among the figure shown in the solid line), modification coefficient x=0.7352 addendum coefficient are the comparison diagram of 1.35 flank profil (among the figure shown in the dotted line).Dotted line is depicted as the utility model flank profil among the figure.
Among Fig. 3, h
AFBe the useful flank profil height that processing generates, h
AEBe the actual active profile height of using of engagement.Fig. 4 has reflected the main geometrical factor that influences teeth bending strength: thickness at root of tooth S
Fn, bending moment arm h
f, the Fillet radius ρ at 30 ° of tangent line places
F
Among Fig. 5 and Fig. 6:
α '
t-working pressure angle;
α
Fen-loading angle;
R1, r2-is little, the Pitch radius of gearwheel;
Ra1, ra2-is little, the Outside radius of gearwheel;
Rb1, rb2-is little, the Base radius of gearwheel;
Pbt-base tooth pitch (base pitch);
The P-node;
B-small gear list is to tooth meshing zone lower boundary point;
D-small gear list is to the upper bound, tooth meshing zone point.
By Fig. 5 and Fig. 6 as can be seen: bending moment arm depends on that the outside, the position of the point of action that calculates the flexural strength active force-promptly is singly to the tooth contact points.This on line of contact for from coxal spur of the starting point of meshing of this Gear Root A (being the starting point that the coupling gear tooth top enters engagement) from p
BtD point position on.The addendum of gear (corresponding Outside radius ra1 among the figure) strengthens and does not change single position to tooth contact points D, the outside.After the Outside radius ra2 of coupling gear strengthens, can cause the moving down of A position, the starting point of meshing of this Gear Root, it is single to the moving down of tooth contact points D to drive the outside, can offset or adverse effect that this Gear Root of partial offset ambassador Gao Jia bending moment arm increases.Therefore, addendum adds very much not can strengthen bending moment arm, can reduce bending moment arm if the addendum of two gears all strengthens also, favourable to flexural strength.Reduce dedendum of the tooth as far as possible if satisfy under the situation that the starting point of meshing requires, just can reduce bending moment arm to greatest extent, the raising teeth bending strength at the initial circular diameter of involute that guarantee to generate.
Other of present embodiment is described as follows:
1) basic principle and design considerations
(1) flank profil selection principle
The design at first is based on controlling slip ratio.
Select normal shift can reduce the slip ratio of gear.
But normal shift can cause the addendum thickness attenuate again, and therefore, during design, the addendum thickness of small gear can be used as constraint conditio and limits.
The Profile radius of curvature of normal shift gear increases, and composite curve radius increases during two gear engagement, and working pressure angle increases, and helps reducing Contact Stress of Gear, improves contact strength of tooth surface.
The normal shift gear can increase thickness at root of tooth, improves teeth bending strength.
Will increase the length of tooth curve section as far as possible, can be increased to 1.25m～1.35m to addendum to the gear of 20 ° of pressure angles, special circumstances can reach 1.45m; Dedendum of the tooth also increases according to engagement needs appropriateness, to increase contact ratio, reduces flank of tooth stress, improves intensity.
(2) principle and the restrictive condition of modification coefficient and flank profil lengthening are to control lower slip ratio, guarantee that tooth top does not come to a point.
(3) addendum strengthens and does not change single position to tooth contact points D, the outside.The addendum of opposite coupling gear adds conference and causes moving down of inner mesh starting point A, and drive outside list moves down tooth contact points D's, can reduce bending moment arm.Therefore, addendum strengthens improving teeth bending strength favourable.
(4) increase thickness at root of tooth with big normal shift, and under the condition that guarantees normal engaged work, reduce dedendum of the tooth as far as possible and add in a large number, the design has reduced the tip clearance of 0.15m than conventional design, has reduced dedendum of the tooth as far as possible and has strengthened adverse effect to teeth bending strength.
(5) when with increase contact ratio, when reducing noise and being main design object, the control of slip ratio can suitably be relaxed, the highest can being increased to addendum～1.45m.
(6) when being main target when designing, adopt the bigger advantage of long flank profil gear tool of 25 ° of pressure angles to improve teeth bending strength.
2) designing and calculating step
(1) recommends big small gear all to adopt the angle correcting gear of normal shift, and select bigger modification coefficient sum x
∑
To the gear of 20 ° of pressure angles, press the modification coefficient sum x of small gear and gearwheel
∑Gear parameters such as modulus, the number of teeth, centre distance, helix angle are determined in=x1+x2＞1.2～1.8.
x
∑Value,, gear ratio z2/z1 more when the number of teeth of small gear hour gets the small value slightly, and be less when the number of teeth of small gear, get big value when gear ratio is big slightly.
In order to guarantee the addendum thickness of small gear, should control x1＜x2, when the number of teeth of small gear (as z1 〉=28) more for a long time, can make x2-x1＞0.12～0.15, when the number of teeth of small gear (as z1≤18) more after a little while, can make x2-x1＞0.22～0.5.
When the restriction that is subjected to original design or proposal plan causes x
∑When less than normal, can increase x by suitable adjustment modulus, the number of teeth, centre distance or helix angle
∑
(2) addendum of tentatively definite large and small gear
To the gear of 20 ° of pressure angles, addendum ha span 1.25m～1.35m.Particular design (as when with increase contact ratio, when reducing noise and being main design object) also can get 1.45m.
In order to guarantee the addendum thickness of small gear, general control ha1≤ha2,, gear ratio z2/z1 more when the number of teeth of small gear be hour (as z1 〉=28, z2/z1≤3) slightly, can make ha1=1.3m～1.35m, less when the number of teeth of small gear, when gear ratio z2/z1 is big slightly (as z1≤20, z2/z1 〉=4), can make to make ha1 ≈ 1.25m.
(3) check addendum thickness, slip ratio, transverse contact ratio
Addendum thickness Sa controls as constraint conditio.Past, conventional requirement to addendum thickness Sa was: normalizing or modified gear Sa＞0.25m, carburizing and quenching gear Sa＞0.4m.Along with the raising of gear accuracy of manufacturing, the widespread usage of correction of the flank shape technology, mesh impact reduces, and this limits value facts have proved it is too conservative, particularly can be much smaller than above-mentioned value to heat treatment and the stable gear of machining accuracy.Artificer's experience is desirable: normalizing or modified gear Sa＞0.2m, the desirable 0.15m of special circumstances; Carburizing and quenching gear Sa＞0.28m, the desirable 0.25m of special circumstances.For fine module gear, the actual top of may command top thickness degree 〉=1mm.
Slip ratio also as constraint conditio control, generally is controlled in 2, preferably less than 1.5.For serving as when designing major heading to increase contact ratio, to reduce noise, can be not limited.
Calculate transverse contact ratio and whether reach expected value to understand.
(4) adjustment and definite modification coefficient and addendum coefficient.
The check of process if can not meet the demands or not reach expected value, is adjusted relevant parameter again, till meeting the demands, finally determines modification coefficient and addendum coefficient.
(5) determine dedendum of the tooth and whole depth.
The root diameter df1=2 of small gear * (a '-da2/2-Cn)
The root diameter df2=2 of gearwheel * (a '-da1/2-Cn)
In last 2 formulas: a '-centre distance; Da1, da2-is little, the tip diameter of gearwheel; The Cn-bottom clearance, Cn=0.25m.This bottom clearance value not only can satisfy modified gear but also can satisfy the needs of carburizing and quenching gear.Sometimes also can be decreased to 0.15m～0.20m to modified gear bottom clearance value.
The value of the bottom clearance Cn of carburizing and quenching gear reduces～0.15m than conventional design in the past, and it is feasible that theory and Practical Calculation all prove, and use is safe and reliable.Can make dedendum of the tooth and bending moment arm shortening～0.15m like this, help improving the flexural strength of tooth root.Following application example is used data and is further specified.
The whole depth ha1=of small gear (da1-df1)/2
The whole depth ha2=of gearwheel (da2-df2)/2
(6) determine the final size of large and small addendum circle diameter of gear.
(7) calculate gear meshing line length and height
(8) other relevant check
1. because of having guaranteed to process the involute height h of generation in the Tool Design
AFH greater than engagement
AEInvolute height (see figure 3) so there is not the meshing interference problem, does not generally need to do meshing interference checking computations (concrete Tool Design is not within the scope of this patent).
2. bottom clearance will guarantee tooth top and teeth groove in hot enough oil storage space that do not brush up against mutually in service, and general 0.2m is enough, and the desirable 0.15m of special circumstances can satisfy, and the design press 0.25m, enough has more than needed.For safety, still to do check to this point.Scurrying cutter (processing displacement) when paying special attention to gear hobbing causes root diameter to increase, and carburizing and quenching gear heat treatment causes root circle and tip diameter to increase and distortion to the influence of actual bottom clearance, consider the actual bottom clearance 〉=0.10m of may command～0.15m after the above factor.For fine module gear, the actual bottom clearance 〉=1mm of may command.
3. during particular design such as other check of needs, can be undertaken by general design of gears computational methods.
The design principle of (9) 25 ° of pressure angular length flank profil gears and program and 20 ° of pressure angles are basic identical.
Because 25 ° of pressure angles are thicker than the thickness at root of tooth of the gear of 20 ° of pressure angles of identical tooth depth, identical modification coefficient, slip ratio is low, addendum thickness is thin, so the main distinction point of 25 ° of pressure angular length flank profil design of gears is:
1. do not need too big modification coefficient sum x
∑, press x
∑Can meet the demands about=x1+x2=1.0.
2. addendum ha span 1.15m～1.25m can reach 1.30m individually.
3. bottom clearance can be by 0.2m.
Present embodiment is a pair of carburizing and quenching roll flute gear, and as shown in Figure 1, parameter is: pressure angle α=20 °, modulus m=16mm, number of teeth z1=27, z2=61, centre distance a '=740mm, helixangle=12 °, addendum coefficient han
*=1, tip clearance coefficient C
n *=0.4, the modification coefficient x1=0.65 of small gear, the modification coefficient x2=0.7352 of gearwheel, facewidth b=300mm, being designed to long flank profil gear can be according to the following steps:
(1) gear parameter and the relevant numerical value of calculating primary standard size.Try to achieve:
The standard pitch diameter d1=441.651mm of little, gearwheel, d2=997.804mm;
The tip diameter da1=490.67mm of little, gearwheel, da2=1049.549mm;
The root diameter df1=417.651mm of little, gearwheel, df2=976.53mm;
The whole depth h1=of small gear (490.67-417.651)/2=36.51mm=2.282m,
The whole depth h2=of gearwheel (1049.549-976.53)/2=36.51mm=2.282m,
Small gear and gearwheel mesh practical involute height h
E1=28.088mm=1.755m;
The practical involute height of gearwheel and pinion h
E2=26.373mm=1.648m;
Small gear, the length of line of action E during the gearwheel engagement
1E
2=65.689mm;
Transverse contact ratio ε
α=1.364.
(2) the modification coefficient sum x of small gear and gearwheel
∑=x1+x2=0.65+0.7352=1.3852 meets the scope of design requirement of long flank profil gear.
(3) select pinion gear teeth to rise 1.30m, gearwheel addendum 1.35m, try to achieve:
The addendum ha1=29.3095mm of little, gearwheel, ha2=31.4725mm;
The tip diameter da1=500.27mm of little, gearwheel, da2=1060.749mm;
(4) get as calculated:
Thick Sa1=4.447mm=0.278m＞the 0.25m of tooth top little, gearwheel;
Sa2＝6.797mm＝0.425m＞0.25m；
The slip ratio ξ 1=1.053 of little, gearwheel, ξ 2=0.937, size is approaching, and lower.
Transverse contact ratio ε
α=1.796, improve 31.7% than former 1.364;
Addendum thickness, slip ratio all meet the requirements, and transverse contact ratio reaches expected value.
(5) determine root diameter and whole depth.
Get bottom clearance Cn=0.25m=0.25 * 16=4mm
The root diameter df1=2 of small gear * (a '-da2/2-Cn)=2 * (740-1060.749/2-4)=411.251mm
The root diameter df2=2 of gearwheel * (a '-da 1/2-Cn)=2 * (740-500.27/2-4)=971.73mm
The whole depth of small gear (da1-df1)/2=(500.27-411.251)/2=44.5095mm=2.782m
The whole depth of gearwheel (da2-df2)/2=(1060.749-971.73)/2=44.5095mm=2.782m
The whole depth of large and small gear has been increased 0.5m than intrinsic 2.282m, has increased by 21.9%.
(6) calculate gear meshing line length and height
Small gear and gearwheel mesh practical involute height h
E1=36.255mm=2.266m;
The practical involute height of gearwheel and pinion h
E2=34.93mm=2.183m.
Small gear, the length of line of action E during the gearwheel engagement
1E
2=86.52mm.Improve 31.7% than intrinsic length of line of action 65.689mm.
The design obtains the length of line of action of raising 31.7% and the effect of contact ratio with the whole depth that increases by 21.9%.
(7) other relevant check
Addendum thickness, slip ratio, transverse contact ratio etc. have been done check.
Design bottom clearance 4mm now remakes following check according to cutter parameters and related process parameter:
Cutter moves back 0.097mm～0.214mm outward during the small gear gear hobbing, behind the hobbing machine on the actual root diameter difference size be 411.679mm, heat treatment causes root circle and Outside radius to increase and the irregular deformation amount is respectively 0.31mm and 0.38mm by 0.15%.
The cutter gear hobbing degree of depth is deepened 0.342mm～0.459mm during the gearwheel gear hobbing, after the gear hobbing on the actual root diameter difference size be 969.446mm, heat treatment causes root circle and Outside radius to increase and the irregular deformation amount is respectively 0.73mm and 0.80mm by 0.15%.
The actual bottom clearance of small gear tooth root is during engagement: the cutter amount of moving back 0.214-small gear heat treatment outward causes the heat treatment of root radius increase 0.31-gearwheel to cause Outside radius increase 0.80=2.67mm=0.167m＞0.15m during the Cn1=4-gear hobbing, meets the requirements.
The actual bottom clearance of gearwheel tooth root is during engagement: cutter rolls the heat treatment of dark amount 0.342-gearwheel and causes the heat treatment of root radius increase 0.73-small gear to cause Outside radius increase 0.38=3.23mm=0.20m＞0.15m during the Cn2=4+ gear hobbing, meets the requirements.
(8) calculate through intensity, this to the long tooth Profile Design of gear after the contact strength safety coefficient of small gear bring up to 1.492 by original 1.31, the contact strength bearing capacity improves 29.7%; The contact strength safety coefficient of gearwheel brings up to 1.515 by original 1.334, and the contact strength bearing capacity improves 29%; The flexural strength safety coefficient of small gear brings up to 2.314 by original 1.99, and the flexural strength bearing capacity improves 16.3%, and the flexural strength safety coefficient of gearwheel brings up to 2.236 by original 1.954, and the flexural strength bearing capacity improves 14.4%.
Small gear original weight 727kg, pts wt only increases～1kg after the long tooth Profile Design, and tooth base material increases 19kg, increases by 1.5%; Gearwheel original weight 1865kg, design back pts wt only increases～4.5kg, and tooth base material increases 44kg, increases by 1.3%.The utility model embodiment uses increases by～1.5% gear material, obtain improve 31.7% transverse contact ratio, improve 29% contact strength bearing capacity, improve the remarkable benefit of 14%～16% flexural strength bearing capacity and can obviously improve running stability, reduction anti noise.
Claims (4)
1. one kind long flank profil gear has the gear teeth that are uniformly distributed along the circumference, and described gear teeth both sides are involute profile, it is characterized in that: concern 1.25m≤ha≤1.45m between the modulus m of the addendum ha of described gear teeth basic rack tooth profile and described gear.
2. according to the described long flank profil gear of claim 1, it is characterized in that: concern 1.25m≤ha≤1.35m between the modulus m of the addendum ha of described gear teeth basic rack tooth profile and described gear.
3. according to the described long flank profil gear of claim 1, it is characterized in that: it is 1.45m that the relation between the modulus m of the addendum ha of described gear teeth basic rack tooth profile and described gear is got ha.
4. according to the described long flank profil gear of claim 1, it is characterized in that: the pass between the modulus m of the working depth of described gear teeth basic rack tooth profile and described gear is: working depth equals 2.50m～2.80m; Pass between the modulus m of the whole depth of described gear teeth basic rack tooth profile and described gear is: whole depth equals 2.75m～3.05m.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106481780A (en) * | 2016-10-12 | 2017-03-08 | 湖南工业大学 | A kind of face polishing gear edge by use height and tip relief method for determination of amount |
| CN106704349A (en) * | 2015-07-17 | 2017-05-24 | 泰州市创新电子有限公司 | Multi-axis intersecting connecting-rod-linkage type smooth opening and closing mechanism with gears with positive addendum modification |
| CN108223699A (en) * | 2018-01-31 | 2018-06-29 | 上齿集团有限公司 | New energy electric logistic car rear bridge driven main reducing gear |
-
2010
- 2010-05-20 CN CN2010201970746U patent/CN201679933U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704349A (en) * | 2015-07-17 | 2017-05-24 | 泰州市创新电子有限公司 | Multi-axis intersecting connecting-rod-linkage type smooth opening and closing mechanism with gears with positive addendum modification |
| CN106481780A (en) * | 2016-10-12 | 2017-03-08 | 湖南工业大学 | A kind of face polishing gear edge by use height and tip relief method for determination of amount |
| CN106481780B (en) * | 2016-10-12 | 2018-11-27 | 湖南工业大学 | A kind of face gear tip relief height and tip relief method for determination of amount |
| CN108223699A (en) * | 2018-01-31 | 2018-06-29 | 上齿集团有限公司 | New energy electric logistic car rear bridge driven main reducing gear |
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