CN1205059A - Planetary transmission - Google Patents
Planetary transmission Download PDFInfo
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- CN1205059A CN1205059A CN 97191251 CN97191251A CN1205059A CN 1205059 A CN1205059 A CN 1205059A CN 97191251 CN97191251 CN 97191251 CN 97191251 A CN97191251 A CN 97191251A CN 1205059 A CN1205059 A CN 1205059A
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- jack shaft
- transmission unit
- planetary
- tooth group
- gear transmission
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Abstract
A planetary gear has two axially adjacent ring gears (11, 12), several planet wheels (10) mounted inside a planet carrier (2) so as to rotate and a central sun wheel (1). Between two planet wheels (10) is provided each time an intermediate shaft (6) and each intermediate shaft has two sets of teeth (7, 8). The smaller set of teeth (8) is provided for simultaneous engagement with two adjacent planet wheels (10) between which the intermediate shaft (6) is located. The second set of teeth (7), the reference circle of which is larger than that of the first one, engages with the central sun wheel (1).
Description
The present invention relates to a kind of planetary type gear transmission unit of the type by claim 1 preamble specific definition.
This type of planetary type gear transmission unit is well-known.Wherein, planetary pinion respectively has two tooth groups to be used for meshing constantly with two hollow wheel gears.They thus constituted so-called Wolfrom coupling transmission device.Wherein, planetary carrier is called the Wolfrom velocity ratio with respect to the rotating ratio that regulation is used as that hollow wheel gear of output shaft.In these known planetary type gear transmission units, central sun gear and planetary pinion directly mesh, and that fixing hollow wheel gear forms primary ratios in planetary pinion and two hollow wheel gears.The Wolfrom velocity ratio draws resultant gear ratio mutually at convenience with primary ratios.
This type of planet tooth tires out transmission device, and especially the considerable task in the Robotics field needs for example i=170 or higher of high transmission ratio.But meanwhile expect that the diameter of central sun gear can be not too small toward contact, because it for example should be provided with hollow shaft, so that the axle head of the motor of packing into or be used to pass the member of robot.Often require restriction Wolfrom velocity ratio in addition.Yet shortcoming be for this reason just the rotating speed by the restrictions planetary gear frame in order that cause aspects such as relevant tooth rolling power, noise, efficient, heating and inertia that the value of appropriateness is arranged.On the other hand, adopt limited Wolfrom velocity ratio also to be difficult to the resultant gear ratio that reaches high.
Because in the scheme of hitherto known planetary type gear transmission unit, central sun gear and planetary pinion initiatively directly meshes, so it must be identical with planetary pinion aspect modulus and other tooth profile parameter.
In known solutions, for realize that high velocity ratio also brings another shortcoming to be except that above-mentioned shortcoming, when planet number of gears amount mostly is three most, there is a kind of low torque density (Momenfendichte), and may produces the problem of relevant output torque uniformity aspect.In addition, for reaching the few number of teeth of the desired sun gear of sufficiently high resultant gear ratio,, also produce other shortcomings of relevant profile of tooth aspect, for example undercut and/or form sharp tooth top except can having problems when parts around the robot are connected.Shortcoming comprises that also the more number of teeth of desired for this reason hollow wheel gear makes it to have less modulus, and causes the shortcoming of torque density aspect thus.
Therefore the objective of the invention is, be issued to high velocity ratio in the situation that makes full use of structure space (torque density), but meanwhile should eliminate or reduce at least significantly above-mentioned various shortcoming as far as possible.In addition also transmission quality should be improved, that is especially vibration and angle driving error minimum degree should be dropped to.Also have, this planet gear drive should be able to be produced economically and not need high assembly fee to use.
By this purpose of the present invention by reaching in the described feature of claim 1 characteristic.
Employing can obtain high primary ratios by the design of planetary type gear transmission unit of the present invention, so although Zong this height of transmission still can be selected the Wolfrom velocity ratio of an appropriateness.In addition, Nei Bu tooth rolling power, noise, efficient, heating and inertia remains in the favourable boundary.This means, for long-term continual and steady transmission device backlash provides very good premise condition.Because this appropriate Wolfrom velocity ratio also can use 4,6 or more a plurality of always paired planetary pinion under the situation of needs.A kind of appropriateness or less Wolfrom velocity ratio means that also the number of teeth of two hollow wheel gears may be selected to be bigger difference usually.According to assembly condition, planetary number number of teeth differences most and these two hollow wheel gears have direct relation.
In addition, planetary pinion quantity is more obtains high torque density.Jack shaft is contained in the planetary carrier in fact can under the situation that does not have the added space demand, realizes.In addition advantageously, also central sun gear can be designed to hollow shaft according to desired resultant gear ratio, in any case because the tooth group diameter of sun gear can both be than in these known schemes much bigger.
In addition, the modulus of second tooth group of advantageously input stage, that is sun gear/jack shaft may be selected to be with known Wolfrom assembly in different, especially less, so the problem of the little number of teeth and associated relevant profile of tooth aspect, for example problem such as undercut and/or pointed tooth no longer takes place.
In addition, what help reducing cost is that whole drive system can constitute with the Wolfrom assembly that same structure is arranged all the time, need only change the velocity ratio of input stage at this moment.
Since the Wolfrom transmission of appropriateness this, so all bear big moment but to account for the most transmission device part of gross weight motion speed lower, and thereby produce less effect of inertia.Otherwise atwirl transmission device part is subjected to less power, and it is less to be designed to quality.
Adopt the favourable design of the present invention of pressing by claim 2, equilibratory basically engaging force on first less tooth group of jack shaft is so its bearing is light and fairly simple.The accurate angle value of jack shaft configuration can and be considered number of teeth combination and the selection of planetary pinion number according to assembly condition.
Employing can obtain favourable space layout by the feature of claim 3, and this layout guarantees second bigger tooth group of jack shaft successfully is installed, and this point is favourable when high transmission ratio especially.
The measure advised in claim 4 allows the line of action between two tooth groups of jack shaft that big distance is arranged, and this makes its supporting summary.
Obviously simplified assembling by feature by claim 5.Two tooth groups of jack shaft can be beyond the planetary carrier tooth position preprocessing and preassembly exactly.
Take measure described in the claim 6, on jack shaft and central sun gear, can only establish the rolling bearing of a radial guide respectively and bearing can be located at vertically away from relevant position engaged.Can make full use of the ability of angular motion among a small circle that related rolling bearing always exists usually in this way.Therefore, the tooth group is self-regulating and self-centering.Self contering in engagement causes uniform Load distribution between the planetary pinion.In addition, the error of graduation internal compensation that this load balancing between the planetary pinion impels the tooth group to cause because of processing is so this error of graduation has only influence in a small amount to output shaft.Consequently help accurately moving and having only small vibration.
By in the enhancing described in the claim 7, can avoid because of the local rigidity that reduces planetary carrier of the additional bearing hole that is used for jack shaft.
Take the measure described in the claim 8, can guarantee to simplify assembling under the condition that the tooth position requires.
By the conical design of claim 9, can obtain the adjustability of transmission device backlash by the possibility that tooth group part moves vertically.
Can produce the operation of accurate low noise and small vibration at the helical teeth described in the claim 10.
Take feature, can design planetary axially mounting with comparalive ease by claim 11.That is to say and adopt this design to compensate the axis passing basically.
Also be applicable to the feature of claim 12 similarly.Adopt this design, the supporting of jack shaft can be simplified owing to the well balanced of power, obviously reduces because axis is passed.
By the feature described in the claim 13, the engagement that can obtain input stage that is sun gear/jack shaft second tooth group with respect to move axially, with respect to the immunity of sun gear.
By the feature of claim 14, the running clearance in input stage is little to the influence of total backlash, because by means of pressing feature of the present invention, central sun gear can design greatlyyer.In addition, during the sun gear self contering, running clearance can be selected lessly, because the influence of range error is less in engagement.This measure has also reduced the quantity of needed conical tooth group and the quantity of the transmission device part that will adjust.
By the feature described in the claim 15, reduced the Wolfrom velocity ratio in an advantageous manner effectively, and thereby reduced inner teeth rolling power, noise, friction torque, heating and moment of inertia effectively.This may accomplish by the high primary ratios that can reach based on jack shaft, therefore can reduce the Wolfrom velocity ratio in an advantageous manner in countermeasure.
Can reach the planetary processing of simplification by the feature described in the claim 16.Therefore this measure is favourable, because there are four row at least in planetary pinion in planetary type gear transmission unit.
By running shaft, can obtain jack shaft first tooth group and planetary pinion kinology and mesh accurately in the inclination described in the claim 17.
By taking the described measure of claim 18, can obtain a kind of favourable application of inventive concept in transmission device, wherein, the kinematics parameters that meshes on two hollow wheel gears can be optimized mutually independently.Usually regulation has the tangible stage in this case.
Created simple assembly condition by the described feature of claim 19.
Enumerated inventive concept favourable application in a kind of transmission device in claim 20, wherein, the kinematics parameters that meshes on two hollow wheel gears can be optimized independently of one another.Meanwhile can reduce the expense of backlash adjusting strip and the quantity of bearing.Make cost descend by the processing of avoiding inclined shaft to simplify planetary carrier in addition.Planetary pinion obtains the tooth group of two reverse tapers respectively in this case.
According to claim 21, planetary conical tooth group is designed to stepped shaft and is divided into the stage especially significantly by the present invention.
Take this measure can reduce the Wolfrom velocity ratio equally effectively and thereby reduce inner teeth rolling power, noise, friction torque, heating and moment of inertia effectively.This point is possible by improve primary ratios by the present invention.
Adopt the suitable design described in the claim 22 can simplify assembling.
By the described feature of claim 23, bearing race is combined in the hollow wheels, saved structure space significantly, so can provide how operational space to be used in narrow structure space, settling whole gears to realize high velocity ratio.
Below by means of accompanying drawing principle ground explanation embodiments of the invention.
Wherein:
Fig. 1 represents the end view by the planetary type gear transmission unit theory of engagement of the present invention;
Fig. 2 presses the section of line II-II of Fig. 1 to VI-VI, comprises cylindrical continuous planetary pinion and cylinder type hollow gear;
The corresponding sectional drawing of Fig. 3 and Fig. 2, expression has the planetary type gear transmission unit of cylinder stepped shaft planetary pinion and taper hollow wheel gear;
Fig. 4 with the corresponding section of Fig. 2 in expression have a planetary planetary type gear transmission unit of biconial;
Fig. 5 with the corresponding section of Fig. 2 in expression have the planetary type gear transmission unit of cylinder stepped shaft planetary pinion and cylinder type hollow gear; And
Fig. 6 with the corresponding section of Fig. 2 in expression have the cylindrical continuous planetary pinion and a planetary type gear transmission unit of taper hollow wheel gear.
Because this type of planetary type gear transmission unit is known basically, so following the pith that detailed description is relevant with the present invention.
This planet gear drive has a central sun gear 1 at input end, and it can be rotated to support in the planetary carrier 2.Planetary carrier 2 has two blocks of side plates 3 and 4, and they are connected to each other by dividing plate 5.Two jack shafts 6 are housed in the side plate 4 of planetary carrier 2 cantilever.Each root jack shaft 6 has two tooth groups, that is a bigger tooth group 7 and a less tooth group 8.Be contained in with can being designed to torsion pass gear on the jack shaft 6 than canine tooth group 7 and sun gear 1 engagement.Shown in Fig. 2 to 6, sun gear 1 and big tooth group 7 are positioned at outside two blocks of side plates 3 and 4 or in the outside of side plate 4 back ofs the body towards side plate 3.Little tooth group 8 can or be made one with jack shaft 6, or is designed to gear independent and that be connected with jack shaft 6 torsion passes.
Always having four planetary pinions 10 is bearing in the side plate 3 and 4 of planetary carrier 2 by needle bearing and axle 9.
The hollow wheel gear 12 of a fixing hollow wheel gear 11 and a rotation and planetary pinion 10 engagements, hollow wheel gear 12 means output terminal.
Between the rotatable hollow wheel gear 12 of fixing hollow wheel gear 11 and formation transmission device output shaft, being equipped with one does not have the main bearing 13 of expression in detail, and its rolling element raceway is directly processed on these two hollow wheel gears.
In order to strengthen the side plate 4 of the planetary carrier 2 that jack shaft 6 and bearing 14 thereof wherein are housed, in bearing 14 mounting hole zones, strengthen side plates 4 (see among Fig. 1 top and Fig. 2 to 6 shown in the dotted line) by rib or contact pin 15.
Be also shown in by Fig. 1 in addition, the line 16 and 17 at spools 18 center of the center of the axle of two tooth group 8 common planet gear meshed 10 less and relevant jack shaft 6 with being positioned at jack shaft 6 in the middle of their, in section, see, form an angle D between 180 ° and 195 ° perpendicular to axis.
Fig. 2 with 6 in the expression embodiment be identical structural type basically, so symbol is consistent.Their difference only is planetary pinion, hollow wheel gear and has the design and the position of the jack shaft of its tooth group.
The planetary type gear transmission unit of for example representing in Fig. 2 has cylindrical continuous planetary pinion 10 and cylinder type hollow gear.
The planetary type gear transmission unit that Fig. 3 represents has two to be located at the cylinder stepped shaft planetary pinion tooth group 10A on each root axle 9 and the hollow wheel gear 11 and 12 of 10B and taper.As shown in the figure, the axis 19 of axle 9 slightly tilts towards the main axis 20 of planetary type gear transmission unit.The tilt angle is about 3 °, and stretches out along the direction towards side plate 3 from side plate 4.
Similarly, the longitudinal axis 21 of jack shaft 6 tilts towards the main axis 20 of planetary type gear transmission unit equally.The tilt angle is about 2 °-2.5 °, and stretches out along the direction towards side plate 4 from side plate 3 equally.
The planetary type gear transmission unit that Fig. 4 represents has biconial planetary pinion tooth group 10C and 10D, and the parallel axes of axle 9 and jack shaft 6 is in the main axis 20 of planetary type gear transmission unit.Two hollow wheel gears 11 and 12 tooth group are complementary with diconical planetary pinion tooth group 10C and 10D in this case certainly.
The planetary type gear transmission unit of representing in Fig. 5 has each two cylinder stepped shaft planetary pinion tooth group 10E and 10F and cylinder type hollow gear 11 and 12 is arranged, and the cylindrical small gear 8 on jack shaft 6 is arranged.
The planetary type gear transmission unit that Fig. 6 represents has cylindrical continuous planetary pinion 10, and this is the same with design shown in Figure 2.By the embodiment identical mode represented with Fig. 3, hollow wheel gear 11 and 12 is tapers, and the longitudinal axis 19 of four axles 9 and the longitudinal axis 21 of two jack shafts 6 all tilt with respect to the main axis 20 of planetary type gear transmission unit.
The little tooth group 8 of jack shaft 6 can mesh with the tooth group district of planetary pinion 10, the latter and hollow wheel gear 11 engagements that are positioned at away from jack shaft 6 canine tooth groups 7.But also can do opposite configuration, that is, the little tooth group 8 of jack shaft meshes with the tooth group district of planetary pinion 10, and the latter and hollow wheel gear 12 engagements that are positioned near jack shaft canine tooth group 7.
As shown in the figure, the tooth group of the little tooth group 8 of jack shaft 6 and sun gear 1 is bearing in respectively in the tooth engagement with inner meshed gears cantilever.
The canine tooth group 7 of jack shaft 6 can be designed to the form of spur wheel separately, and it is connected with jack shaft 6 torsion passes by means of the tooth engagement that matches of shape accurately of tooth position or by shrink fit.At least on two hollow wheel gears 11 and 12 and on planetary pinion 10, the tooth group should that is to say and make involute helical teeth or involute helicoid as make helical teeth with the tooth group of the jack shaft 6 of planetary pinion 10 engagements.
The oblique angle of these tooth groups on planetary pinion 10 should have identical substantially flank line pitch at least.In like manner, the direction at two oblique angles should be consistent.
Central authorities' sun gear 1 can be made helical teeth equally with the tooth group 7 of the jack shaft 6 that is engaged with, and the oblique angle of these tooth groups 7 on jack shaft 6 has identical substantially flank line pitch at least.The direction at two oblique angles equally should be identical.
When the longitudinal axis 21 of the longitudinal axis 19 of axle 9 and jack shaft 6 tilted with respect to main axis 20, these oblique positioies should be chosen as like this, that is, make the axis of these inclinations crossing in same point at least substantially with the main axis 20 of transmission device.
When design has the planetary pinion of cylinder stepped shaft tooth group 10A, 10B or 10E, 10F (Fig. 3 and 5), should take the identical number of teeth respectively.
As seen from Figure 4, these two hollow wheel gears 11 and 12 can tilt with respect to the transmission drive shaft line, wherein, and the oblique angle oppositely extension mutually of these two hollow wheel gears 11 and 12 oblique angle and planetary pinion and the tooth group 10C and the 10D of their engagements.
The tooth group 10C and the 10D of planetary two reverse tapers have been designed to the tangible stage at the average diameter place.
Also be applicable to the planetary pinion design with cylinder stepped shaft tooth group 10A, 10B or 10E, 10F similarly, as shown in Fig. 3 and 5, wherein the stage should be tangible equally.
They should compensate mutually in the planetary design with cylinder stepped shaft tooth group basically, make them constitute the cylinder tooth group of a constant continuous.
Can stipulate in addition, in the canine tooth group 7 of some jack shafts 6, always there is a little tooth group that a fixing arbitrarily position configuration is arranged with respect to same jack shaft 6, and other tooth group of remaining one or more jack shaft 6 is designed to connect by a rotatable assembling flange and adjusts, wherein because more bigger screwing through hole produces a limited rotary gap, and the number of teeth that the quantity of screw hole is chosen as with the tooth group that will adjust can not eliminate (not shown) by integer.
Claims (23)
1. planetary type gear transmission unit has two hollow wheel gears that dispose side by side vertically, a plurality of planetary pinions is arranged, and they can be rotated to support on the planetary carrier; And a central sun gear arranged, it is characterized by: be provided with a jack shaft (6) between per two planetary pinions (10), jack shaft respectively has two tooth groups (7,8), wherein, little tooth group (8) meshes with two adjacent planetary pinions (10) simultaneously, this jack shaft (6) just is located between these two planetary pinions, and, compare second bigger tooth group (7) of its pitch circle and central sun gear (1) engagement with first.
2. according to the described planetary type gear transmission unit of claim 1, it is characterized by: two with jack shaft (6) between them on the line (16,17) at axle center and a center (18) of relevant jack shaft (6) of the common planet gear meshed (10) of little tooth group (8), with the section of axis normal in see, form an angle (D) between 180 ° and 195 °.
3. according to claim 1 or 2 described planetary type gear transmission units, it is characterized by: to be connected to each other the planetary carrier (2) of side plate (3,4) together by dividing plate (5) other there being two, and the tooth group (7) with sun gear (1) engagement that jack shaft (6) is bigger is located in side plate (3, the 4) axial plane in addition of planetary carrier (2).
4. according to the described planetary type gear transmission unit of one of claim 1 to 3, it is characterized by: the tooth group district engagement of the less first tooth group (8) of jack shaft (6) and planetary pinion (10), this planet gear and that hollow wheel gear (11) engagement away from last second the bigger tooth group (7) of jack shaft (6).
5. according to the described planetary type gear transmission unit of one of claim 1 to 3, it is characterized by: the first less tooth group (8) of jack shaft (6) meshes with the tooth group district of planetary pinion (10), and this planet gear meshes with that hollow wheel gear (12) of close last second the bigger tooth group (7) of jack shaft (6).
6. according to the described planetary type gear transmission unit of one of claim 1 to 5, it is characterized by: jack shaft (6) is gone up the less tooth group (8) and/or the tooth group of central sun gear (1), is bearing in respectively in the tooth engagement of that gear that is engaged with cantilever.
7. according to the described planetary type gear transmission unit of one of claim 3 to 6, it is characterized by: planetary carrier (2) is equipped with the side plate (4) of the bearing (14) of guiding jack shaft (6), strengthens by rib, contact pin (15) or analog in bearing (14) mounting hole location.
8. according to the described planetary type gear transmission unit of one of claim 1 to 7, it is characterized by: to be designed to be independent spur wheel to bigger gear (7) in form on the jack shaft (6), and it is connected with jack shaft (6) torsion pass by means of the tooth engagement that matches of shape accurately of tooth position or by shrink fit.
9. according to the described planetary type gear transmission unit of one of claim 1 to 8, it is characterized by: two hollow wheel gears (11,12) and jack shaft (6) less tooth group (8) is designed to taper.
10. according to the described planetary type gear transmission unit of one of claim 1 to 9, it is characterized by: at least two hollow wheel gears (11,12) and in each two the tooth group on the planetary pinion (10) with on jack shaft (6) all make helical teeth with tooth group (8) planetary pinion (10) engagement.
11. according to the described planetary type gear transmission unit of claim 10, it is characterized by: there is the flank line pitch that equates at least substantially at the oblique angle of these tooth groups on planetary pinion (10); And the direction at two oblique angles is identical.
12. according to claim 10 or 11 described planetary type gear transmission units, it is characterized by: central sun gear (1) and jack shaft (6) the second tooth groups (7) that are engaged with are made helical teeth equally, and the oblique angle of the first and second tooth groups (7 and 8) on jack shaft (6) has identical substantially flank line pitch at least; And the direction at two oblique angles is identical.
13. according to the described planetary type gear transmission unit of one of claim 1 to 12, it is characterized by: central sun gear (1) is designed to columniform.
14. according to the described planetary type gear transmission unit of one of claim 1 to 13, it is characterized by: jack shaft (6) is gone up the second tooth group (7) that meshes with central sun gear (1) and is designed to cylindrical.
15. according to the described planetary type gear transmission unit of one of claim 1 to 14, it is characterized by: the difference of two hollow wheel gears (11,12) number of teeth, should be chosen as is the twice of planetary pinion (10) number of teeth or many times so big.
16. according to the described planetary type gear transmission unit of one of claim 1 to 15, it is characterized by: planetary pinion (10) has two columniform basically tooth groups (10A, 10B) and is bearing in one radially with respect on transmission drive shaft line (20) the inclination running shaft (19) at an angle.
17. according to the described planetary type gear transmission unit of claim 16, it is characterized by: jack shaft (6) is bearing in one radially with respect on transmission drive shaft line (20) the inclination running shaft (21) at an angle, wherein, planetary pinion axis (19), the same with the axis (21) of jack shaft (6), intersect on same point at least substantially with the main axis (20) of transmission device.
18. according to the described planetary type gear transmission unit of claim 16, it is characterized by: two columniform basically tooth groups (10A, 10B and 10E, 10F) of planetary pinion (10) are designed to step-like.
19. according to the described planetary type gear transmission unit of claim 18, it is characterized by: the stepped shaft cylinder tooth group (10A, 10B and 10E, 10F) of planetary pinion (10) has the identical number of teeth respectively.
20. according to the described planetary type gear transmission unit of one of claim 1 to 17, it is characterized by: two hollow wheel gears (11,12) tilt with respect to the main axis of transmission device, wherein, oppositely extend mutually at the tilt angle of the tooth group (10C, 10D) that is engaged with of tilt angle of these two hollow wheel gears (11,12) and planetary pinion (10); And planetary pinion (10) and jack shaft (6) lay respectively on the substantially parallel spin axis of a main axis with respect to transmission device (20).
21. according to the described planetary type gear transmission unit of claim 20, it is characterized by: the tooth group of two reverse tapers of planetary pinion (10) (10C, 10D) average diameter is designed to step-like.
22. according to the described planetary type gear transmission unit of claim 21, it is characterized by: planetary pinion (10) the oppositely tooth group (10C, 10D) of taper respectively has the identical number of teeth.
23. according to the described planetary type gear transmission unit of one of claim 1 to 22, it is characterized by: between the rotatable hollow wheel gear (12) of fixing hollow wheel gear (11) and formation transmission device output shaft, be provided with a main bearing (13), wherein, the raceway of main bearing (13) rolling element is directly processed in two hollow wheel gears (11 and 12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97191251 CN1205059A (en) | 1996-01-27 | 1997-01-22 | Planetary transmission |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19603004.8 | 1996-01-27 | ||
| CN 97191251 CN1205059A (en) | 1996-01-27 | 1997-01-22 | Planetary transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1205059A true CN1205059A (en) | 1999-01-13 |
Family
ID=5178849
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 97191251 Pending CN1205059A (en) | 1996-01-27 | 1997-01-22 | Planetary transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1205059A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102265029A (en) * | 2008-12-23 | 2011-11-30 | 爱罗丁工程有限公司 | Planetary gear |
| CN105351503A (en) * | 2015-11-13 | 2016-02-24 | 綦江县三川齿轮有限公司 | Gear transmission device |
| CN105351459A (en) * | 2015-11-13 | 2016-02-24 | 綦江县三川齿轮有限公司 | Gear case transmission device |
| CN105370809A (en) * | 2015-11-13 | 2016-03-02 | 綦江县三川齿轮有限公司 | Novel gear case device |
| CN105387140A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | High-accuracy gear transmitting device |
| CN105387153A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | Planetary gear device |
| CN105387155A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | High-accuracy planetary gearbox device |
| CN105387154A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | Accuracy-improved gear device |
| CN107683380A (en) * | 2015-04-02 | 2018-02-09 | 舍弗勒技术股份两合公司 | Gear for a gear transmission |
-
1997
- 1997-01-22 CN CN 97191251 patent/CN1205059A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102265029A (en) * | 2008-12-23 | 2011-11-30 | 爱罗丁工程有限公司 | Planetary gear |
| CN102265029B (en) * | 2008-12-23 | 2013-12-25 | 爱罗丁工程有限公司 | Planetary gear |
| CN107683380A (en) * | 2015-04-02 | 2018-02-09 | 舍弗勒技术股份两合公司 | Gear for a gear transmission |
| CN107683380B (en) * | 2015-04-02 | 2020-10-27 | 舍弗勒技术股份两合公司 | Gear for a gear transmission |
| CN105351503A (en) * | 2015-11-13 | 2016-02-24 | 綦江县三川齿轮有限公司 | Gear transmission device |
| CN105351459A (en) * | 2015-11-13 | 2016-02-24 | 綦江县三川齿轮有限公司 | Gear case transmission device |
| CN105370809A (en) * | 2015-11-13 | 2016-03-02 | 綦江县三川齿轮有限公司 | Novel gear case device |
| CN105387140A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | High-accuracy gear transmitting device |
| CN105387153A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | Planetary gear device |
| CN105387155A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | High-accuracy planetary gearbox device |
| CN105387154A (en) * | 2015-11-13 | 2016-03-09 | 綦江县三川齿轮有限公司 | Accuracy-improved gear device |
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