CN204729579U - Limited slip differential and automobile - Google Patents
Limited slip differential and automobile Download PDFInfo
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- CN204729579U CN204729579U CN201520448624.XU CN201520448624U CN204729579U CN 204729579 U CN204729579 U CN 204729579U CN 201520448624 U CN201520448624 U CN 201520448624U CN 204729579 U CN204729579 U CN 204729579U
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- differential
- helical spring
- semiaxis
- limited slip
- output flange
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Abstract
The utility model discloses a kind of limited slip differential, comprise the first output flange, second output flange, with the first semiaxis that described first output flange is fixing, and with described second output flange fixing the second semiaxis, it is inner that described first half-axile sleeve is loaded on the first differential carrier, it is inner that described second half-axile sleeve is loaded on the second differential carrier, described first semiaxis is set with the first helical spring, described second semiaxis is set with the second helical spring, described first helical spring two ends act on described first output flange and described first differential carrier respectively, described second helical spring two ends act on described second output flange and described second differential carrier respectively.Above-mentioned limited slip differential can transmit larger moment of torsion, and simultaneously it can improve the passing ability of automobile, traction property and driving safety.The invention also discloses a kind of automobile.
Description
Technical field
The utility model relates to structure design of automobile technical field, particularly relates to a kind of limited slip differential.The utility model also relates to a kind of automobile.
Background technique
Differential mechanism is the vitals in automobile drive axle, and its major function makes the left and right driving of ransaxle take turns the differential had required by automobile running kinology, and power distribution taken turns to left and right driving.But " differential is not poor to be turned round " of open differential torque distribution performance such as namely, has but had a strong impact on the passing ability of automobile, traction property and driving safety.
Most of automobile is all right to be sailed on the reasonable road surface of attachment condition, nearly all have employed that structure is simple, the common symmetric formula cone planetary gear differential mechanism of stable working, easily manufactured, good reliability; And for often travelling at the offroad vehicle of muddy, soft dirt road or cross-country locality or lorry, will limited slip differential be adopted to prevent falling into car because certain side drives wheel slip.General employing locking differential and limited slip differential improve the passing ability of automobile, traction property and driving safety, although and locking differential simply operation inconvenience, use less, be generally used on minority heavy goods vehicle.
When automobile left and right driving wheel travels on the ground that attachment condition is different, limited slip differential can in order to try (automatically or by control) make most of torque even all torque distribution to compare a good side drive wheel to attachment condition, thus improve the passing ability of automobile, traction property and driving safety.Limited slip differential has a variety of, friction-disc cone gear differential mechanism and precompressed friction-disc cone gear differential mechanism are wherein two kinds, because both have the advantages such as structure is simple, stable working, technique inheritance are good, so it is wider to belong to using scope in limited slip differential.
If T
1for the torque on differential mechanism rotating faster differential gear, ω
1for rotating the rotating speed of differential gear faster, T
2for rotating the torque on slower differential gear, ω
2for rotating the rotating speed of slower differential gear.The efficiency eta of differential mechanism
dwhen referring to that differential carrier does not turn, the ratio of output power and input power when a semiaxis drives another semiaxis, because the rotating speed of now two-semiaxle is equal, i.e. ω
1=ω
2, so
Wherein, K is locking coefficient, represents the maximum multiple that the torque of both sides driving wheel may differ, K=T
2/ T
1, that is efficiency eta of differential mechanism
dfor the inverse of its locking coefficient.From above formula, the locking coefficient K of differential mechanism and differential mechanism efficiency eta
dbe inversely proportional to.
The inner friction torque of differential mechanism is larger, and its locking coefficient is also just large, will make the efficiency eta of differential mechanism
dlower, then be more conducive to both sides and drive redistributing of wheel torque, be more conducive to the passing ability improving automobile.Although there is large internal frictional losses the efficiency of differential mechanism low showing, this situation only just occurs when left and right wheel has remarkable speed discrepancy, and this speed discrepancy is little in the ordinary course of things, and therefore the fricting loss power of differential mechanism is not remarkable.When driving wheels rotating speed is equal, the fricting loss power of differential mechanism is zero.When automobile is turned with min. turning radius, the fricting loss power of differential mechanism reaches maximum value.
Theoretical according to differential mechanism, the transmission efficiency η of differential mechanism
dTfor:
Wherein, B is wheelspan, and R is radius of turn.From formula (2), the transmission efficiency η of differential mechanism
dTbe different from the efficiency eta of differential mechanism
d, the latter is only relevant with the structure of differential mechanism, and the former is also relevant with the radius of turn R of automobile back driving axle intermediate point and wheelspan B, and changes with the change of R.Can find out from formula (2), even if the efficiency eta of differential mechanism
dvery low, the transmission efficiency η of differential mechanism
dTstill higher, substantially more than 0.9.The efficiency eta of Here it is why some high-friction-type no-spin lockup
dalthough very low, but still adopted reason.
With in the cone planetary gear limited slip differential of friction disk or friction plate in conventional art, when automobile turning or single wheel trackslip on road surface, planetary pinion rotation, plays differential action, and the rotating speed of left and right half gear is not etc.Due to the existence of speed discrepancy and the effect of axial force, produce friction torque trackslipping between driving and driven friction plate simultaneously, torque and the friction plate quantity of its numerical values recited and differential mechanism transmission are directly proportional, and its direction is contrary with the rotation direction turning semiaxis soon, identical with the rotation direction of slow-speed semiaxis.The result of the inner friction torque effect of bigger numerical, makes the torque of slow-speed semiaxis transmission obviously increase.Friction disk type differential design is simple, and stable working, locking coefficient K can reach 0.6 ~ 0.7 or higher.
But the torque that can bear between friction plate or between slider cam is relatively little, can not transmitting large torque.Helical spring is then arranged between two differential gears by precompressed friction-disc cone gear differential mechanism, causes helical spring installation space more limited, causes the passing ability of automobile, traction property and driving safety not still to be very desirable.
Model utility content
The purpose of this utility model is to provide a kind of limited slip differential, and this limited slip differential can transmit larger moment of torsion, and simultaneously it can improve the passing ability of automobile, traction property and driving safety.Another object of the present utility model is to provide a kind of automobile comprising above-mentioned limited slip differential.
To achieve these goals, the utility model provides following technological scheme:
A kind of limited slip differential, comprise the first output flange, second output flange, with the first semiaxis that described first output flange is fixing, and state the second fixing semiaxis of the second output flange with described, it is inner that described first half-axile sleeve is loaded on the first differential carrier, it is inner that described second half-axile sleeve is loaded on the second differential carrier, described first semiaxis is set with the first helical spring, described second semiaxis is set with the second helical spring, described first helical spring two ends act on described first output flange and described first differential carrier respectively, described second helical spring two ends act on described second output flange and described second differential carrier respectively.
Preferably, in above-mentioned limited slip differential, also comprise the first spring seat be set on described first semiaxis, described first spring seat is disk-like structure, and described first helical spring is acted on described first differential carrier by described first spring seat.
Preferably, in above-mentioned limited slip differential, also comprise the second spring seat be set on described second semiaxis, described second spring seat is disk-like structure, and described second helical spring is acted on described second differential carrier by described second spring seat.
Preferably, in above-mentioned limited slip differential, also comprise the first friction conical ring be set on described first semiaxis, the side of described first friction conical ring is connected to described first spring seat, opposite side has the first conical surface fitted with the internal surface of described first differential carrier, relative to the surface of described first semiaxis, described first conical surface tilts near the direction on the surface of laterally closer described first semiaxis of described first differential carrier.
Preferably, in above-mentioned limited slip differential, also comprise the second friction conical ring be set on described second semiaxis, the side of described second friction conical ring is connected to described second spring seat, opposite side has the second conical surface fitted with the internal surface of described second differential carrier, relative to the surface of described second semiaxis, described second conical surface tilts near the direction on the surface of laterally closer described second semiaxis of described second differential carrier.
Preferably, in above-mentioned limited slip differential, described first conical surface and/or described second conical surface are plane.
Preferably, in above-mentioned limited slip differential, described first spring seat has the first limited ring towards described first helical spring side, and described first helical spring is positioned at the inner side of described first limited ring.
Preferably, in above-mentioned limited slip differential, described second spring seat has the second limited ring towards described second helical spring side, and described second helical spring is positioned at the inner side of described second limited ring.
Preferably, in above-mentioned limited slip differential:
Described first output flange has the 3rd limited ring towards described first helical spring side, and described first helical spring is positioned at the inner side of described 3rd limited ring;
And/or described second output flange has the 4th limited ring towards described second helical spring side, and described second helical spring is positioned at the inner side of described 4th limited ring.
A kind of automobile, comprise limited slip differential, described limited slip differential is the limited slip differential described in above-mentioned any one.
In technique scheme, the limited slip differential that the utility model provides comprises the first output flange, the second output flange, the first semiaxis, the second semiaxis, the first helical spring and the second helical spring, first helical spring two ends act on the first output flange and the first differential carrier respectively, and the second helical spring two ends act on the second output flange and the second differential carrier respectively.Compared to the content described in background technique, above-mentioned limited slip differential adopts the first helical spring and the second helical spring to realize anti-slip function, compared to friction-disc cone gear differential mechanism, the moment that the first helical spring and the second helical spring can transmit is larger; Simultaneously, above-mentioned first helical spring and the second helical spring are all arranged at outside the differential gear of limited slip differential, therefore the first helical spring and the second helical spring rigidity and size can be set according to demand flexibly, make the non-skid property of limited slip differential better, improve the passing ability of automobile, traction property and driving safety with this.
Because above-mentioned limited slip differential has above-mentioned technique effect, the automobile comprising this limited slip differential also should have corresponding technique effect.
Accompanying drawing explanation
In order to be illustrated more clearly in the embodiment of the present application or technological scheme of the prior art, be briefly described to the accompanying drawing used required in embodiment below, apparently, the accompanying drawing that the following describes is only some embodiments recorded in the utility model, for those of ordinary skill in the art, other accompanying drawing can also be obtained according to these accompanying drawings.
The structural representation of the limited slip differential that Fig. 1 provides for the utility model embodiment;
Fig. 2 is for the A-A of structure shown in Fig. 1 is to sectional view;
Fig. 3 is for the B-B of structure shown in Fig. 2 is to sectional view;
Fig. 4 for after the limited slip differential that adopts the utility model embodiment and provide, the efficiency eta of limited slip differential
dwith the transmission efficiency η of limited slip differential
dTbetween graph of a relation.
Description of reference numerals:
11-first output flange, 12-clutch shaft bearing, 13-first differential carrier, 14-first semiaxis, 15-first helical spring, 16-first differential gear, 17-first spring seat, 18-first rubs conical ring, 19-first end cap, 21-second output flange, 22-second bearing, 23-second differential carrier, 24-second semiaxis, 25-second helical spring, 26-second differential gear, 27-second spring seat, 28-second rubs conical ring, 29-second end cap, 31-cross axle, 32-planetary pinion, 33-master subtracts driven wheel of differential.
Embodiment
In order to make those skilled in the art understand the technical solution of the utility model better, below in conjunction with accompanying drawing, the utility model is further detailed.
As Figure 1-3, the utility model embodiment provides a kind of limited slip differential, this limited slip differential comprises the first output flange 11, clutch shaft bearing 12, first differential carrier 13, first semiaxis 14, first helical spring 15, first differential gear 16, second output flange 21, second bearing 22, second differential carrier 23, second semiaxis 24, second helical spring 25, second differential gear 26, cross axle 31, planetary pinion 32 and master and subtracts driven wheel of differential 33, wherein:
First output flange 11 and the second output flange 21 are respectively used to fix with left side wheel and right side wheels, drive left side wheel and right side wheels to rotate with this; Clutch shaft bearing 12 and the second bearing 22 are installed on the first differential carrier 13 and the second differential carrier 23 respectively; First differential carrier 13 is fixedly connected with by bolt with the second differential carrier 23, and the first differential carrier 13 subtracts driven wheel of differential 33 with master and fixes; First semiaxis 14 and the second semiaxis 24 are set with in the first differential carrier 13 and the second differential carrier 23, and both are fixedly connected with the second output flange 21 with the first output flange 11 respectively; First differential gear 16 and the second differential gear 26 are fixed on the end of the first semiaxis 14 and the second semiaxis 24 respectively by the first end cap 19 and the second end cap 29; Cross axle 31 is for installing four planetary pinions 32, each planetary pinion 32 all engages with the first differential gear 16 and the second differential gear 26, master subtracts driven wheel of differential 33 and is then fixed on the first differential carrier 13, subtracts driven wheel of differential 33 drive the first differential carrier 13 to rotate with this by master.
First helical spring 15 is set on the first semiaxis 14, second helical spring 25 is set on the second semiaxis 24, the two ends of the first helical spring 15 act on the first output flange 11 and the first differential carrier 13 respectively, and the two ends of the second helical spring 25 act on the second output flange 21 and the second differential carrier 23 respectively.Particularly, one end and first output flange 11 of the first helical spring 15 abut against, and the other end and the first differential carrier 13 abut against; One end and second output flange 21 of the second helical spring 25 abut against, and the other end and the second differential carrier 23 abut against.
It should be noted that, above-mentioned limited slip differential can be bilateral symmetry, and therefore each technological scheme provided above and hereinafter of the utility model embodiment all can adopt bilateral symmetry.
When the driving wheel of automobile turning or its certain side is absorbed in the less road surface of coefficient of attachment and reaches limit of adhesion and skid, left and right driving wheel produces speed discrepancy.The now rotating speed n of the first differential carrier 13
0with the rotating speed n of the first differential gear 16
2, the second differential gear 26 rotating speed n
1all unequal, work as n
1> n
2time, there is n
1> n
0> n
2rotation speed relation.Due to speed discrepancy existence and the first helical spring 15 and the second helical spring 25 compresses the first differential carrier 13 respectively and the second differential carrier 23 makes to produce friction torque between the first differential carrier 13 and the first helical spring 15, between the second differential carrier 23 and the second helical spring 25, the size of the impacting force of the size of this friction torque and the friction factor between friction element and the first helical spring 15 and the second helical spring 25 is relevant, the direction of friction torque and n
1and n
0or n
2and n
0between relative rotation speed relevant, according to n
1, n
2, n
0the rotation speed relation of three obtains: the friction torque of rotating speed differential gear side faster, and the sense of rotation of its direction and rotating speed differential gear is faster contrary, and it is negative for being worth; The friction torque of the differential gear side that rotating speed is slower, the sense of rotation of the differential gear that its direction is slower with rotating speed is identical, is worth for just.Now transfer to the slower differential gear side of rotating speed just as part driving moment by the differential gear side that rotating speed is slower.Therefore the driving moment of the differential gear that rotating speed is slower will be greater than the driving moment of rotating speed differential gear faster.So, as long as there is speed discrepancy, the limited slip differential that the utility model embodiment provides just can make most of torque even all torque distribution to compare a good side drive wheel to attachment condition, thus improve the passing ability of automobile, traction property and driving safety.
To sum up, after adopting above-mentioned limited slip differential, the rigidity of the first helical spring 15 and the second helical spring 25 can be increased, and then increase the frictional force in limited slip differential, then improve locking coefficient, realize anti-slip function when vehicle travels.Compared to friction-disc cone gear differential mechanism, the moment that the first helical spring 15 and the second helical spring 25 can transmit is larger; Simultaneously, above-mentioned first helical spring 15 and the second helical spring 25 are all arranged at outside the differential gear of limited slip differential, therefore rigidity and the size of the first helical spring 15 and the second helical spring 25 can be set according to demand flexibly, make the non-skid property of limited slip differential better, improve the passing ability of automobile, traction property and driving safety with this.
In above-mentioned limited slip differential, if only produce friction torque by the compression between the first helical spring 15 and the first differential carrier 13, then because area of contact is between the two less, the friction torque produced is relatively little.Accordingly, the limited slip differential that the utility model embodiment provides also comprises the first spring seat 17 be set on the first semiaxis 14, and this first spring seat 17 is disk-like structure, and the first helical spring 15 is acted on the first differential carrier 13 by the first spring seat 17.Now, the first helical spring 15 directly compresses the first spring seat 17, and area of contact between the first spring seat 17 and the first differential carrier 13 is larger, makes to produce larger friction torque between the first spring seat 17 and the first differential carrier 13.
In like manner, the limited slip differential that the utility model embodiment provides also can comprise the second spring seat 27 be set on the second semiaxis 24 further, this second spring seat 27 is disk-like structure, and the second helical spring 25 is acted on the second differential carrier 23 by the second spring seat 27.
In concrete structure, because one end that the first differential carrier 13 contacts with the first spring seat 17 is less, make the area of contact between the first spring seat 17 and the first differential carrier 13 still large not, therefore, in the utility model embodiment, limited slip differential also comprises the first friction conical ring 18 be set on the first semiaxis 14, the side of this first friction conical ring 18 is connected to the first spring seat 17, opposite side has the first conical surface fitted with the internal surface of the first differential carrier 13, relative to the surface of the first semiaxis 14, aforementioned first conical surface tilts near the direction on the surface of laterally closer first semiaxis 14 of the first differential carrier 13.The internal surface of the first differential carrier 13 refers to surface relative with the first semiaxis 14 on the first differential carrier 13, and the surface of the first semiaxis 14 then refers to the annular outer surface of the first semiaxis 14.
After adopting this kind of structure, force transmission to the first is rubbed on conical ring 18 by the first spring seat 17 by the first helical spring 15, makes the first friction conical ring 18 compress the first differential carrier 13.Therefore, can to rub the tapering of conical ring 18 by reasonable design first, the area of contact between the first friction conical ring 18 and the first differential carrier 13 can be increased considerably.
In like manner, in order to strengthen aforementioned techniques effect, above-mentioned limited slip differential also can comprise the second friction conical ring 28 be set on the second semiaxis 24 further, the side of this second friction conical ring 28 is connected to the second spring seat 27, opposite side has the second conical surface fitted with the internal surface of the second differential carrier 23, relative to the surface of the second semiaxis 24, the second conical surface tilts near the surface of laterally closer second semiaxis 24 of the second differential carrier 23.The internal surface of the second differential carrier 23 refers to surface relative with the second semiaxis 24 on the second differential carrier 23, and the surface of the second semiaxis 24 then refers to the annular outer surface of the second semiaxis 24.
Aforesaid first conical surface and second conical surface all can be set to curved surface, but for the ease of processing, the one in first conical surface and second conical surface can be set to plane, or both are all set to plane.In addition, when first conical surface and/or second conical surface are the conical surface, along with the wearing and tearing that the first friction conical ring 18 and the first differential carrier 13, second rub between conical ring 28 and the second differential carrier 23, first friction conical ring 18 and the second friction conical ring 28 can move relative to the first semiaxis 14 and the second semiaxis 24 respectively, even if make both occur wearing and tearing still can respectively with the first differential carrier 13 and the second differential carrier 23 reliable contacts, then transmit friction torque better.
Alternatively, the first spring seat 17 has the first limited ring towards the side of the first helical spring 15, the first helical spring 15 is positioned at the inner side of this first limited ring.Because the first helical spring 15 is set in after on the first semiaxis 14, it can occur rocking relative to the first semiaxis 14, and the first limited ring then can limit rocking of the first helical spring 15, makes the first helical spring 15 can transmitting forces more reliably.Particularly, above-mentioned first limited ring can be processed with the first spring seat 17 one, and both are mutually vertical.In like manner, the second spring seat 27 has the second limited ring towards the side of the second helical spring 25, the second helical spring 25 is positioned at the inner side of the second limited ring.
According to above-mentioned technical conceive, also on the first output flange 11, can arrange the 3rd limited ring towards the side of the first helical spring 15, the first helical spring 15 is positioned at the inner side of the 3rd limited ring, limits the position of first helical spring 15 the other end with this.In like manner, the second output flange 21 has the 4th limited ring towards the side of the second helical spring 25, this second helical spring 25 is positioned at the inner side of the 4th limited ring.
After adopting above-mentioned each technological scheme, when vehicle is kept straight on, according to the formula (2) described in background technique, radius of turn R is infinitely great, the transmission efficiency η of differential mechanism
dTbe do not relatively rotate between the 1, first differential gear 16 and the second differential gear 26, the frictional force produced by helical spring does not cause loss.When vehicle is turned with min. turning radius, can find out according to formula (2), even if the efficiency of limited slip differential is very low, the transmission efficiency of limited slip differential still obtains higher numerical value, as shown in Figure 4, therefore the limited slip differential that provides of the utility model embodiment is little in the impact of Ackermann steer angle on transmission of power.
Based on said structure, the utility model embodiment also provides a kind of automobile, and this automobile comprises the limited slip differential described by above-mentioned arbitrary technological scheme.Because above-mentioned limited slip differential has above-mentioned technique effect, the automobile comprising this limited slip differential also should have corresponding technique effect, repeats no more herein.
Mode above only by illustrating describes some one exemplary embodiment of the present utility model, undoubtedly, for those of ordinary skill in the art, when not departing from spirit and scope of the present utility model, can revise described embodiment by various different mode.Therefore, above-mentioned accompanying drawing is illustrative with being described in essence, should not be construed as the restriction to the utility model claims.
Claims (10)
1. a limited slip differential, comprise the first output flange, second output flange, with the first semiaxis that described first output flange is fixing, and state the second fixing semiaxis of the second output flange with described, it is inner that described first half-axile sleeve is loaded on the first differential carrier, it is inner that described second half-axile sleeve is loaded on the second differential carrier, it is characterized in that, described first semiaxis is set with the first helical spring, described second semiaxis is set with the second helical spring, described first helical spring two ends act on described first output flange and described first differential carrier respectively, described second helical spring two ends act on described second output flange and described second differential carrier respectively.
2. limited slip differential according to claim 1, it is characterized in that, also comprise the first spring seat be set on described first semiaxis, described first spring seat is disk-like structure, and described first helical spring is acted on described first differential carrier by described first spring seat.
3. limited slip differential according to claim 2, it is characterized in that, also comprise the second spring seat be set on described second semiaxis, described second spring seat is disk-like structure, and described second helical spring is acted on described second differential carrier by described second spring seat.
4. limited slip differential according to claim 3, it is characterized in that, also comprise the first friction conical ring be set on described first semiaxis, the side of described first friction conical ring is connected to described first spring seat, opposite side has the first conical surface fitted with the internal surface of described first differential carrier, relative to the surface of described first semiaxis, described first conical surface tilts near the direction on the surface of laterally closer described first semiaxis of described first differential carrier.
5. limited slip differential according to claim 4, it is characterized in that, also comprise the second friction conical ring be set on described second semiaxis, the side of described second friction conical ring is connected to described second spring seat, opposite side has the second conical surface fitted with the internal surface of described second differential carrier, relative to the surface of described second semiaxis, described second conical surface tilts near the direction on the surface of laterally closer described second semiaxis of described second differential carrier.
6. limited slip differential according to claim 5, is characterized in that, described first conical surface and/or described second conical surface are plane.
7. the limited slip differential according to any one of claim 2-6, is characterized in that, described first spring seat has the first limited ring towards described first helical spring side, and described first helical spring is positioned at the inner side of described first limited ring.
8. the limited slip differential according to any one of claim 3-6, is characterized in that, described second spring seat has the second limited ring towards described second helical spring side, and described second helical spring is positioned at the inner side of described second limited ring.
9. the limited slip differential according to any one of claim 3-6, is characterized in that:
Described first output flange has the 3rd limited ring towards described first helical spring side, and described first helical spring is positioned at the inner side of described 3rd limited ring;
And/or described second output flange has the 4th limited ring towards described second helical spring side, and described second helical spring is positioned at the inner side of described 4th limited ring.
10. an automobile, comprises limited slip differential, it is characterized in that, the limited slip differential of described limited slip differential according to any one of claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520448624.XU CN204729579U (en) | 2015-06-26 | 2015-06-26 | Limited slip differential and automobile |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520448624.XU CN204729579U (en) | 2015-06-26 | 2015-06-26 | Limited slip differential and automobile |
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|---|---|
| CN204729579U true CN204729579U (en) | 2015-10-28 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107420518A (en) * | 2017-09-11 | 2017-12-01 | 宁波市鄞州益定机械制造有限公司 | A kind of limited-slip differential assembly |
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2015
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107420518A (en) * | 2017-09-11 | 2017-12-01 | 宁波市鄞州益定机械制造有限公司 | A kind of limited-slip differential assembly |
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Address after: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee before: Anhui Jianghuai Automobile Co., Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151028 Termination date: 20190626 |
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| CF01 | Termination of patent right due to non-payment of annual fee |