CN208331137U - New energy electric logistic car rear bridge driven main reducing gear - Google Patents
New energy electric logistic car rear bridge driven main reducing gear Download PDFInfo
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- CN208331137U CN208331137U CN201820171666.7U CN201820171666U CN208331137U CN 208331137 U CN208331137 U CN 208331137U CN 201820171666 U CN201820171666 U CN 201820171666U CN 208331137 U CN208331137 U CN 208331137U
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Abstract
The utility model discloses a kind of New energy electric logistic car rear bridge driven main reducing gear, the input shaft, transmission shaft, output shaft, first gear, second gear, third gear and the 4th gear that are rotatably arranged on including reducer shell and by bearing in shell.Bearing of input shaft and motor spline connection place spacing are 9.95 centimetres；The registration of second gear and first gear is 3.03, the registration 3.05 of the 4th gear and third gear；The flank profil sliding ratio of second gear and first gear is 0.98, and the flank profil sliding ratio of the 4th gear and third gear is 0.94.The span coupled by reducing bearing of input shaft with motor spline, reduces the vibration when high-speed rotation of input shaft, noise is from 94 decibels near 72 decibels.By improving registration, the noise of gear drive engagement is reduced.Under the premise of meeting teeth bending strength, modulus is reduced, increases the number of teeth, improves the stationarity of registration and transmission, reduces the sliding ratio of the flank of tooth, abrasion is reduced, reduces noise, improve service life.
Description
Technical field
The utility model relates to a kind of New energy electric logistic car rear bridge driven main reducing gears.
Background technique
The span of existing vehicle rear bridge driven main reducing gear, high speed grade bearing of input shaft supporting point is long, and rigidity is poor,
As shown in Figure 1.And play the role of radial force when gear engagement, especially when different rotating speeds, it is easy to produce resonance,
Noise significantly increases.
Summary of the invention
The purpose of this utility model is to provide a kind of New energy electric logistic car rear bridge driven main reducing gears, solve existing
Vehicle rear axle drives the span of the high speed grade bearing of input shaft supporting point of main reducing gear long, and rigidity is poor, and gear is nibbled
There is radial force when conjunction, leads to the technical issues of noise occur.
To solve the above problems, the technical scheme adopted by the utility model is that:
New energy electric logistic car rear bridge driven main reducing gear, including reducer shell and shell is rotatably arranged on by bearing
Input shaft, transmission shaft and output shaft in body；Be provided with first gear on the input shaft, first gear and input shaft one at
Type, motor output shaft are coupled with the input shaft of the main reducing gear by spline, close to the bearing and flower of motor side on input shaft
Span between key is 9.95cm；；The spacing of two bearings on input shaft is shortened simultaneously；
Second gear and third gear are provided on the transmission shaft, wherein second gear is engaged with first gear, third
Gear and transmission shaft are integrally formed, and second gear is located at one end on transmission shaft close to motor；Is provided on the output shaft
Four gears, the 4th gear are engaged with third gear；
Bearing of input shaft and motor spline connection place span are long in the prior art, are 19cm, and input shaft rigidly compares
Difference.And there are the effects of radial force when engaging with first gear for second gear, and input shaft is made to generate concussion, bearing of input shaft and electricity
Machine spline connection place is crossed over greatly, more unstable, especially when different rotating speeds, is easy to produce resonance, noise significantly increases
Add.By the way that bearing of input shaft and motor spline connection place across being designed as 9.95cm, while being reduced two bearings span, enhance defeated
Enter axis rigidity, the concussion generated when reducing the high-speed rotation of input shaft reduces noise, is especially in input shaft rotating speed
When 8000rpm, there is apparent advantage.The motor passes through
The registration of the second gear and first gear is 3.03, the registration 3.05 of the 4th gear and third gear.
The registration of second gear and first gear is 2.36 in the prior art, the registration 3.05 of the 4th gear and third gear.It is logical
Raising registration is crossed, the noise of gear drive engagement reduces.
Registration expression turns in a tooth pitch time in gear, participates in the average log of the gear teeth of engagement, and the value is bigger,
Show that the gear teeth logarithm for simultaneously participating in engagement is more, shares the load of each pair of gear teeth under the effect of identical load with regard to small, load
Variation is small, to improve the bearing capacity of entire gear, and stable drive, reduces vibration and noise, improves transmission performance,
Therefore registration is the bigger the better.
The maximum value of helical gear registration is ε max=1.981+B × tg β/Pt.
Wherein B-facewidth, β-helical angle, pt-transverse pitch；
The flank profil sliding ratio of the second gear and first gear is 0.98, and the flank profil of the 4th gear and third gear is sliding
Dynamic rate is 0.94.
Sliding ratio is also referred to as slide coefficient, and slide coefficient is the gear of a pair of meshing, the line of two flank profils in same meshing point
Speed is not identical (except node), thus there is sliding between flank profil, so as to cause the abrasion or glued destruction of the flank of tooth.Usually use
With respect to the degree of sliding between the slide coefficient expression flank of tooth.Slide coefficient is exactly relatively tangential between two flank of tooth at tooth contact point
The ratio of speed (i.e. sliding speed) and the tangential velocity (linear velocity).The flank profil sliding ratio of first gear is equal in the prior art
It is 8.53, the flank profil sliding ratio of second gear is 1.57, and the flank profil sliding ratio of third gear is 2.91, the tooth of the 4th gear
Wide sliding ratio is 0.99, and flank of tooth sliding ratio difference is bigger, and numerical value is also bigger, and the frictional force of flank engagement becomes larger, and makes an uproar
Sound is big.The opposite sliding of gear-profile is more serious, and the abrasion of the flank of tooth is also more serious, is also more also easy to produce glued and damages, therefore
In the utility model, under the premise of meeting teeth bending strength, the modulus of gear is reduced, increases the number of teeth of gear, is improved
Registration reduces the sliding ratio of the flank of tooth, reduces abrasion, reduces noise, improves service life.
It being further improved, the first gear, second gear, third gear and the 4th gear are helical gears,
Helical angle is 21 ° -30 °.Helical gears are good with meshing characteristic, registration is big, it is more straight not generate the minimum number of teeth that root is cut
The advantages that tooth is few.
Be further improved, the first gear, second gear, third gear and the 4th gear increment, tooth top fallen
Rib, effectively avoids the generation of burr and cutting edge of a knife or a sword mouth, also prevents not engaging when assembly and assembles plucking, to avoid noise
And abnormal sound.In existing design of gears, the chamfered edge problem of increment is not considered, will lead to the flank of tooth and be easy to damage, in the mistake of gear engagement
Interference is just had in journey, generates the engagement sound of interval.
It being further improved, the first gear, second gear, third gear and the 4th gear are profile modified gear, and first
The net slip coefficient of gear and second gear and third gear and the 4th gear divides according to the principle of " waiting slip coefficients "
Match.According to gear centre away from and gear parameter, distributed according to the principle of " waiting slip coefficients ", reduce slip coefficient, reduce
The abrasion of gear.Existing gear is zero displacement, and flank of tooth sliding ratio difference is bigger, and numerical value is also bigger, and flank engagement is rubbed
It wipes power to become larger, is a factor for generating noise.
Why the effect of profile modified gear will conjugate master gear.There are three reasons:
1), the master gear of a pair of meshing, since pinion gear thickness at root of tooth is thin, the number for participating in engagement is again more, therefore
Intensity is lower, is easily damaged, and affects gear-driven bearing capacity.Profile modified gear
2), standard distance between centers is indicated with a, if center actually required is away from (being indicated with A) A < a, just at all can not
Installation；It if A > a, can install, but generate big sideshake, registration also reduces, and all affects the stationarity of transmission.
3), if less than 17 Undercutting Phenomenon can occur for the master gear number of teeth of gear hobbing cutting, influence to actually use.
In the prior art, gear does not carry out tooth form, the microcosmic correction of the flank shape on teeth directional, is easy to produce in engagement, rotation process
Raw noise.In the utility model, using KISSSOFT software, actual condition is simulated, is carried out by the actual condition parameter of input
The analysis of gear load and stress judges fever deformation, practical unbalance loading and shell processing, gear manufacture error of gear etc.
Factor calculates distribution of the stress on the flank of tooth, qualified metastable stress distribution is determined, so that the correction of the flank shape of lock gear is joined
Number reaches the microcosmic correction of the flank shape that tooth form and teeth directional are carried out to gear, to avoid with these unfavorable factors of link to making an uproar in actual use
The influence of sound and vibration.KISSSOFT software is the professional software of design of gears, Design of Gear Drive System and axis, design bearing
Tool is software well known to those skilled in the art, repeats no more.
Compared with prior art, the utility model has the following beneficial effects:
1), by being 9.95 centimetres by bearing of input shaft and motor spline connection place span, span is reduced, is enhanced defeated
Enter axis rigidity, the vibration generated when reducing the high-speed rotation of input shaft reduces noise, is especially in input shaft rotating speed
When 8000rpm, there is apparent advantage, noise is from 94 decibels near 72 decibels.
2), by improving registration, the noise of gear drive engagement is reduced.In the utility model, meeting tooth root bending
Under the premise of intensity, the modulus of gear is reduced, increases the number of teeth of gear, registration is improved, reduces the sliding ratio of the flank of tooth, is reduced
Abrasion reduces noise, improves service life.
Detailed description of the invention
Fig. 1 is the schematic diagram of vehicle rear bridge driven main reducing gear in the prior art.
Fig. 2 is the schematic diagram of vehicle rear bridge driven main reducing gear described in the utility model.
Fig. 3 is the structure chart of New energy electric logistic car rear bridge driven main reducing gear described in the utility model.
Specific embodiment
The utility model in order to better understand further illustrates the content of the utility model below with reference to embodiment, but
The content of the utility model is not limited solely to the following examples.
As shown in Figure 2,3, New energy electric logistic car rear bridge driven main reducing gear, including reducer shell 1 and pass through axis
Forward input shaft 2, transmission shaft 3 and the output shaft 4 of dynamic setting in the housing；It is provided with first gear 5 on the input shaft, first
Gear 5 and input shaft 2 are integrally formed, and motor output shaft couples that (motor is in figure with the input shaft of the main reducing gear by spline
It is not shown), the span on input shaft between the bearing and spline of motor side is 9.95cm；It shortens on input shaft simultaneously
The spacing of two bearings；
It is provided with second gear 6 and third gear 7 on the transmission shaft 3, wherein second gear 6 is engaged with first gear 5,
Third gear 7 and transmission shaft 3 are integrally formed, and second gear 6 is located at one end on transmission shaft close to motor；On the output shaft 4
It is provided with the 4th gear 8, the 4th gear 8 is engaged with third gear 7；In the present embodiment, the first gear 5, second gear
6, third gear 7 and the 4th gear 8 are helical gears.
In the present embodiment, the parameter of first gear 5, second gear 6, third gear 7 and the 4th gear 8 is as follows:
First gear 5: modulus m=2.75, number of teeth z=21, helixangleβ=29 °, reference diameter d=63.7mm；
Second gear 6: modulus m=2.75, number of teeth z=43, helixangleβ=29 °, reference diameter d=130.4mm；
Third gear 7: modulus m=3, number of teeth z=17, helixangleβ=21 °, reference diameter d=54.6mm；
4th gear 8: modulus m=3, number of teeth z=67, helixangleβ=21 °, reference diameter d=215.3mm.
By being 9.95cm by bearing of input shaft and motor spline connection place span design, the two spacing, enhancing are reduced
Input shaft rigidity, the concussion generated when reducing the high-speed rotation of input shaft reduce noise, are especially in input shaft rotating speed
When 8000rpm, there is apparent advantage.
The registration of the second gear 6 and first gear 5 is 3.03, the registration of the 4th gear 8 and third gear 7
3.05.The registration of second gear and first gear is 2.36 in the prior art, the registration of the 4th gear and third gear
3.05.By improving registration, the noise of gear drive engagement is reduced.
The maximum value of helical gear registration is ε max=1.981+B × tg β/Pt.
Wherein B-facewidth, β-helical angle, pt-transverse pitch；
The flank profil sliding ratio of the second gear 6 and first gear 5 is 0.98, the tooth of the 4th gear 8 and third gear 7
Wide sliding ratio is 0.94.In the utility model, under the premise of meeting teeth bending strength, the modulus of gear is reduced, is increased
The number of teeth of gear improves registration, reduces the sliding ratio of the flank of tooth, reduces abrasion, reduces noise, improves service life.
In the present embodiment, the first gear 5, second gear 3, third gear 7 and the 4th gear 8 increment, tooth top
Chamfered edge is carried out, the generation of burr and cutting edge of a knife or a sword mouth is effectively avoided, also prevents not engaging when assembly and assembles plucking, to avoid making
At noise and abnormal sound.In existing design of gears, the chamfered edge problem of increment is not considered, will lead to the flank of tooth and be easy to damage, nibble in gear
Interference is just had during conjunction, generates the engagement sound of interval.
In the present embodiment, the first gear, second gear, third gear and the 4th gear are profile modified gear, the
The net slip coefficient of one gear and second gear and third gear and the 4th gear divides according to the principle of " waiting slip coefficients "
Match.According to gear centre away from and gear parameter, distributed according to the principle of " waiting slip coefficients ", reduce slip coefficient, reduce
The abrasion of gear.
Do not done in the utility model illustrate be the prior art or can be realized by the prior art, Er Qieben
Specific implementation case described in utility model is only the preferable case study on implementation of the utility model, is not used to limit practical
Novel practical range.Equivalent changes and modifications made by i.e. all contents according to present utility model application the scope of the patents, should all make
For the technology scope of the utility model.
Claims (4)
1. New energy electric logistic car rear bridge driven main reducing gear, which is characterized in that turn including reducer shell and by bearing
Input shaft, transmission shaft and the output shaft of dynamic setting in the housing；
First gear is provided on the input shaft, first gear and input shaft are integrally formed, machine shaft and the main reducing gear
Input shaft coupled by spline, the span on input shaft between the bearing and spline of motor side is 9.95cm；
Second gear and third gear are provided on the transmission shaft, wherein second gear is engaged with first gear, third gear
It is integrally formed with transmission shaft, second gear is located at one end on transmission shaft close to motor；
The 4th gear is provided on the output shaft, the 4th gear is engaged with third gear；
The registration of the second gear and first gear is 3.03, the registration 3.05 of the 4th gear and third gear；
The flank profil sliding ratio of the second gear and first gear is 0.98, the flank profil sliding ratio of the 4th gear and third gear
It is 0.94.
2. New energy electric logistic car rear bridge driven main reducing gear according to claim 1, which is characterized in that described first
Gear, second gear, third gear and the 4th gear are helical gears, and spiral angle is 21 ° -30 °.
3. New energy electric logistic car rear bridge driven main reducing gear according to claim 1 or 2, which is characterized in that described
First gear, second gear, the increment of third gear and the 4th gear, tooth top carry out chamfered edge.
4. New energy electric logistic car rear bridge driven main reducing gear according to claim 3, which is characterized in that described first
Gear, second gear, third gear and the 4th gear are profile modified gear, first gear and second gear and third gear
It is distributed with the net slip coefficient of the 4th gear according to the principle of " waiting slip coefficients ".
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| Application Number | Priority Date | Filing Date | Title |
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| CN201820171666.7U CN208331137U (en) | 2018-01-31 | 2018-01-31 | New energy electric logistic car rear bridge driven main reducing gear |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201820171666.7U CN208331137U (en) | 2018-01-31 | 2018-01-31 | New energy electric logistic car rear bridge driven main reducing gear |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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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