奥地利专利AT513246A4 gearing

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专利摘要:
The invention relates to a gear arrangement (1) with a main gear (2) and a gear (4) rotatable relative thereto in the circumferential direction (3), with spring elements (8), with which the rotatable gear (2) in the circumferential direction (3) against the main gear (2) is biased, wherein the spring elements (8) on the one hand with the main gear (2) and on the other hand, the rotatable gear (4) are connected, and wherein the spring elements (8) each have a longitudinal central axis (19) extending obliquely to an axial end face (18) of the rotatable gear (4) are arranged.
公开号:AT513246A4
申请号:T1156/2012
申请日:2012-10-25
公开日:2014-03-15
发明作者:
申请人:Miba Sinter Austria Gmbh；
IPC主号:

专利说明:

The invention relates to a gear assembly having a main gear and a relative to this relatively circumferentially rotatable gear, with spring elements, with which the rotatable gear is biased in the circumferential direction against the main gear, wherein the spring elements are connected on the one hand to the main gear and on the other hand, the rotatable gear. Furthermore, the invention relates to a gear drive with a first gear and a second gear, wherein the first gear is arranged without play on a shaft.
The most diverse types of so-called "split gears" are already known from the prior art. The purpose of these gear designs is to reduce a backlash in intermeshing gears.
From "G. Niemann, H. Winter: machine elements, Volume II, gearbox general, gear transmission - basics, spur gear, Springer Verlag, 1989, page 366 "is such a split gear with a main gear and a rotatable gear arranged thereon known. The two gears are connected to each other via two coil springs, wherein the longitudinal central axes are aligned by the coil springs perpendicular to the shaft carrying the gear and thus the coil springs parallel to the axial end face.
Such a gear arrangement is also known from EP 0 079 184 A1. This gear assembly is part of a three-wheel gear drive, which are arranged on one axis. For backlash-free transmission of torques two such gear arrangements would have to be installed in this arrangement. To avoid this, is provided in the gear drive according to this EP-A1, that the split gear is arranged with radial play on its shaft. So- 2/20 N2012 / 16600 • · > ········································································································································································································································ the two counter-wheels, thereby allowing a backlash-free torque transmission. Since the tensioning wheel is designed to be radially movable, this split gear is only suitable for three-shaft arrangements of gear drives and only for low loads. For this reason, this gear arrangement is also provided only for the writing head of an electric typewriter.
The object of the present invention is to simplify a gear arrangement for transmitting large moments as mentioned in the introduction, which is typically used e.g. occur in motor vehicles.
This object of the invention is achieved on the one hand in the gear arrangement mentioned above in that the spring elements each have a longitudinal center axis, which are arranged obliquely to an axial end face of the rotatable gear, and on the other hand in the aforementioned gear drive characterized in that one of the gears according to the invention is.
The advantage here is that at the same time a tension in the axial direction is applied by the inclination of the spring elements in addition to a tension in the circumferential direction. Due to the axial force component of the rotatable gear (i.e., the pinch gear), an improvement in the planarity of the gear assembly can be achieved. It is thus further avoided in comparison to compression systems, the one-sided carrying the bore surface of the rotatable gear, whereby the wear can be reduced. In addition, it is thus possible to simplify the geometry of the main gear or the rotatable gear, whereby the production can be made more cost-effective. Further, a damping frictional torque can be generated by the axial force, whereby the vibrations of the rotatable gear are damped. The damping can also reduce the power loss during operation. Due to the simpler structure compared to such gear assemblies of the prior art, the space of the gear assembly can be reduced in the axial direction, since no further axial fastening means are required. 3/20 N2012 / 16600 ··· ♦ ···· < · ι · · · · I ·· ··· • ···············
To improve these effects, it is provided according to a variant embodiment that the longitudinal center axes of the spring elements extend at an angle to the axial end face, which is selected from a range with a lower limit of 3 ° and an upper limit of 80 °. With angular positions of the spring elements outside this range, the above-mentioned effects can still be observed, however, an improvement in terms of the axial component of the generated force and thus an improved seat of the gear arrangement is achieved on a shaft in the preferred angular range.
It can further be provided that the projected to the plane of the axial end face of the rotatable gear longitudinal central axes are arranged by the spring elements at an angle to each other, which is not equal to 90 0 or an integer multiple of 90 °. The advantage here is the better adjustability of the acting force components of the spring elements.
According to a preferred embodiment of the gear arrangement is provided that at least two, in particular at least three or four, spring elements are arranged. It is thus achievable a better alignment of the rotatable gear with respect to the main gear.
Preferably, the spring elements are designed as coil springs. It is thus a simple assembly of the gear arrangement possible by the springs simply hung and the rotatable gear is rotated until an optional stop engages. In addition, by the usability of different coil springs with different spring characteristics, the biasing force can be varied within wide ranges, without affecting the required space of the gear assembly is significantly affected.
Although not mandatory for the invention (this is a further advantage for component simplification), the main gear and / or the rotatable gear can have or have at least one axial stop for the rotatable gear or the main gear, whereby on the one hand a positio 4/20 N2012 / 16600 ····································································································································································································································· Restriction of the relative rotatability of the two gears to each other in the circumferential direction can be achieved. The latter can also serve as a safety measure in the event of a spring break.
The rotatable gear may partially abut in a region on the main gear, in which region the main gear and / or the rotatable gear is or are provided with a friction-changing coating. It is thus the frictional torque, which is generated due to the Axialkraftkomponente of the springs, as described above, influenced, so that is so adjustable via this coating, the damping between the two gear halves.
The term "friction-changing" is to be understood in relation to the friction of the base material, which consists of the main gear and / or the rotatable gear.
It is also possible that individual of the spring elements to the remaining spring elements have a different spring characteristic and / or are arranged at a different angle of the longitudinal center axes to the axial end face. It can thus be better adjusted, the tensioning torque acting between the main gear and the rotatable gear, in particular, thus relatively low Verspannmomente of 2 Nm, for example, can be realized.
For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
Each shows in a schematically simplified representation:
Figure 1 is a gear arrangement in view in the axial direction.
2 shows a sectional view through the gear arrangement according to FIG. 1 according to the section line II-II in FIG. 1; 5/20 N2012 / 16600
• · · · · · · ·
t ·
3 shows a variant of a gear arrangement in view in the axial direction;
4 shows a sectional view through the gear arrangement according to FIG. 2;
Fig. 5 is a gear drive.
By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position.
1 and 2 show a gear arrangement 1. This gear arrangement 1, also called "split gear", has a main gear 2 and a gear wheel 4 which is rotatable relative thereto in a circumferential direction 3. The main gear 2 may have a hub 5, which may preferably be formed integrally with the main gear 2. But it is also possible that both the main gear 2 and the rotatable gear 4 are arranged directly on a common shaft 6 (Fig. 4).
The rotatable gear 4 is rotatably mounted on the hub 5 or the shaft 6 (FIG. 4) of the main gear 2 or the shaft 6 (FIG. 4).
If the skin gear 2 has the hub 5, a recess 7 in the form of a bore for receiving the shaft 6 is formed therein.
The rotatable gear 4 is biased by means of spring elements 8 in the circumferential direction 3 relative to the main gear 2. In the illustrated preferred embodiment of the gear arrangement 1, four spring elements 8 are arranged. However, only three or more than four, for example, five, 6/20 N2012 / 16600 • · · ·
·· ··
• · · · «
6, etc. spring elements 8 may be present. In any case, at least two spring elements 8 are arranged.
Each of the spring elements 8 is connected on the one hand to the main gear 2 and on the other hand to the rotatable gear 4. For this purpose, these spring elements 8 in the simplest embodiment of the gear assembly 1 each in a recess 9 in the main gear 2 and a recess 10 in the rotatable gear 4 with bent Federendbereichen 11,12 - the spring elements 8 are designed as tension springs - hung, as in particular in Fig. 2 is shown. The spring end regions 11, 12 respectively point into the interior of the gear arrangement 1, i. in the direction of the other part gear. The recesses 11, 12 can be configured, for example, by bores on webs 13, 14 projecting in the direction of the spring elements 8 on the main gearwheel 2 and on the rotatable gearwheel 4. But there are also other shapes and types for the recesses 11,12 possible.
But there are also other types of attachment possible, for example, the spring elements 8 may be welded to the main gear 2 and the rotatable gear 4.
Next, the main gear 2 and the rotatable gear 4 recesses 15,16 (in particular breakthroughs), in which the spring elements 8 are each partially received, wherein in the assembled state, the spring elements 8 preferably not via an outer, axial end face 17 of the main gear and a outer, axial end surface 18 of the rotatable gear 4 protrude, although this is possible. These recesses 15,16 may be at least approximately rectangular in shape with optionally rounded corners. But there are other forms possible.
In the assembled state of the gear assembly 1, the recesses 15,16 are preferably not aligned in the axial direction of the gear arrangement to each other, as shown in FIG. 2 can be seen. It is thus possible to make these recesses 15,16 smaller. In principle, it is possible that the recesses 15,16 are the same size and have the same shape. 7/20 N2012 / 16600 • · ·. · · · · Ml
By the nature of the connection of the spring elements 8 with the main gear 2 and the rotatable gear 4 longitudinal center axes 19 extend through the spring elements 8 (shown in phantom in Fig. 2) obliquely, i. at an angle 20 to the axial end face 18 of the rotatable gear 4 (or to the axial end face 17 of the main gear 2).
The angle 20 is preferably selected from a range of + 3 ° to + 80 °, in particular from a range of + 10 0 to + 70 °, or from a range of - 3 ° to - 80 °, in particular from one area from -10 ° to - 70 With regard to the different signs of the angles, reference is made to the following explanations.
The arrangement of the spring elements 8 in the gear arrangement 1 can be designed such that in the circumferential direction 3, a connection with the main gear 2 alternately follows a connection with the rotatable gear 4, as can be seen from FIG. There is thus no reversal of the installation direction in this embodiment.
According to another embodiment, however, exactly this reverse installation direction can be beneficial. By this arrangement, the spring elements 8, wherein at least one spring element 8 is inclined in the other direction than the remaining spring elements 8 (relative to the end face 18), so that in the circumferential direction 3 at least one compound of a spring element 8 with the main gear 2 of a compound Further spring element 8 follows with the main gear 2, resulting in different moments that do not addi-dieren but subtract in the circumferential direction or, after at least one of the tension elements generated by the spring elements 8 is negative, based on the other Verspannmomente, results in a total in the circumferential direction generated by the spring elements 8 tensioning moment, which is smaller than the total tensioning moment, which is generated when all the spring elements 8 are inclined in the same direction. It is thus possible that the size of the desired Verspannmomentes can be better adjusted. In the axial direction, the spring forces also add in this embodiment, so that 8/20 N2012 / 16600 8 thus maintained a corresponding strain in the axial direction even at lower moments in the circumferential direction.
Preferably, this embodiment is applied when an even number of spring elements 8 is arranged in the gear assembly 1, so that, for example, two spring elements 8 are inclined in one direction and two spring elements 8 in the other direction. It is preferred if in each case two opposing spring elements 8 are arranged inclined in the same direction, so that therefore the direction of inclination of the spring elements 8 alternates in the circumferential direction 3.
In a specific embodiment, while the inclination angle (= angle 20) of the spring elements 8 are the same size, but the value of the inclination angle of at least one spring element 8 is positive and the value of the inclination angle of at least one further spring element 8 negative, each related to a reference point. In order to produce a resulting from the spring elements 8 Gesamtverspannmoment, it is provided that the spring characteristic of at least individual spring elements 8 differs from the other spring elements 8, in particular the spring constant. In this case, a circumferential arrangement of the spring elements 8 is again preferred, that is to say that in the circumferential direction a spring element 8 with a higher spring constant follows a spring element with a smaller spring constant. For example, in an arrangement of four spring elements 8 in the gear arrangement 1, the arrangement is such that in the circumferential direction, the sequence larger spring constant - to smaller spring constant - higher spring constant (in particular equal to the first spring constant in this sequence) -dazu smaller spring constant (in particular equal low as the second spring constant in this sequence).
So it is a combination of so-called hard spring elements 8 with soft spring elements 8 in the gear assembly 1 possible. The softer spring stores more energy than the hard one with the same force. If the deformation is predetermined, the hard spring absorbs more energy. 9/20 N2012 / 16600 • · · · · · • * ♦
In particular, this embodiment is selected for setting a low Ver-clamping torque. In this case, the spring elements 8 work with the lower spring constant against the spring element 8 with the higher spring constant, so-that in total results in a smaller Gesamtverspannmoment.
According to other embodiments also mixed variants can be provided, that on the one hand varies the spring characteristic and the other the inclination angle, the latter is not necessarily negative in relation to other inclination angle of the spring elements 8, but also the size of the inclination angle is different, so for example a spring element an inclination angle of 3 ° and another spring element 8 has an inclination angle of 5 °.
The spring elements 8 are installed in the illustrated embodiment gear arrangement 1 such that the projected to the plane of the axial end face 18 of the rotatable gear longitudinal central axes 19 are arranged by the spring elements 8 at an angle 21 and 22 to each other, not equal to 90 ° or an integer Many of these are. But there are also embodiments of the gear assembly 1 possible, in which this angle is 21 or 22 90 °.
Since embodiments with only two spring elements 8 are possible, it should be understood that in a special embodiment, the two longitudinal center axes 19 are arranged parallel to each other by the spring elements 8.
In the embodiment with four spring elements 8, the angle 21 may preferably be selected from a range of 95 0 to 140 °, in particular from a range of 95 ° to 110 °. The complementary angle 22 has the corresponding values.
In general, the angle 21 can be selected from a range of 60 ° to 180 °, in particular from a range of 95 ° to 130 °. The complementary angle 22 has the corresponding values. Essentially, the angle 21 depends on the number of arranged spring elements 8. 10/20 N2012 / 16600 • · • · · · · · · · · · · · · · · · · · 10
· About angle 20 (the so-called spring position angle), the Axialkraftanteil the spring elements 8 can be influenced, whereby the size of the axial strain of the rotatable gear 4 with respect to the main gear 2 is adjustable.
The spring elements 8 are preferably designed as Schraubenzugfedern. In principle, however, other spring elements 8 can be used.
Preferably, the spring elements 8 are made of a spring steel.
FIGS. 3 and 4 show a variant embodiment of the gear arrangement 1, wherein the same reference numerals or component designations are again used for the same parts as in the preceding FIGS. 1 and 2. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding Figs. 1 and 2 or reference.
In contrast to the previous embodiment of the gear arrangement 1, three spring elements 8 are arranged in this case, wherein the connection with the main gear 2 and the rotatable gear 4 takes place in the manner described above.
The angle 21 between the projected longitudinal center axes 19 in this embodiment is at least approximately 60 °.
There is the possibility, although this is not absolutely necessary due to the Axialverspannung of the rotatable gear 4 that on the rotatable gear 4 at least one axial projection 23 (axial stop) - it can also more as one, eg two or three, be formed - is formed, which extends in the direction of the main gear 2 and this is at least partially received in a recess 24. By this axial projection 23, which is preferably formed integrally with the rotatable gear 4, the rotatability of the rotatable gear 4 is limited in the circumferential direction 3. 11/20 N2012 / 16600
Ίϊ, · ·
But it is also the reverse embodiment possible, that is, the at least one axial projection 23 on the main gear 2 and the at least one recess 24 are formed in the rotatable gear.
Furthermore, it can be seen from FIG. 4 that it is possible that the rotatable toothed wheel 2 rests only partially in a region 25 on the main toothed wheel 2. This region 25 may be formed, for example, in the form of at least one annular web, which is arranged on the main gear 2 (and / or on the rotatable gear 4). By this training, a better leadership or better positioning of the rotatable gear 4 is achieved on the main gear 2.
It is possible that at least one of the contacting surfaces of the area 24 and the rotatable gear 4 (or the main gear 2) with a friction-reducing coating, such as a lubricating varnish, e.g. made of PTFE, is or are.
On the other hand, there is also the possibility that in this area the friction is increased by a friction-increasing coating friction, for example, with a friction particles (corundum, quartz, etc.) having coating.
For the sake of completeness, FIG. 5 shows a gear drive 26, which is known in principle from the prior art, with two meshing gears, one of the gears being formed by the gear arrangement 1 according to the invention. Both the gear assembly 1 and the other gear are rotatably mounted on each shaft 6, 27 and free of play.
The force-free assembly of the gear assembly 1 with the mating gear of a gear drive can e.g. be done by means of a pin or pin, which engages in corresponding recesses in the main gear 2 and in the rotatable gear 4 and is removed again after assembly. On the position of the spring elements 8 and a Einsteilbarkeit the axial bias is possible within certain limits. 12/20 N2012 / 16600 • · • • • • • • • • • ············································································· • • · ♦ · φ • ·· φφ
Finally, it should be pointed out that the main gear 2 and / or the rotatable gear 4 are preferably made of a sintered steel, wherein the formation of a stamped part, in particular of the rotatable gear 2, are possible.
The exemplary embodiments show possible embodiments of the gear arrangement 1.
For the sake of order, it should finally be pointed out that, for a better understanding of the construction of the gear arrangement 1, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size. 13/20 N2012 / 16600
REFERENCE NUMBERS
gearing
main gear
circumferentially
gear
hub
wave
recess
spring element
recess
recess
recess
recess
web
web
recess
recess
face
End face longitudinal central axis
angle
angle
angle
axial projection
recess
Wheel drive sector
Shaft 14/20 N2012 / 16600

权利要求:
Claims (8)
[1]
1. gear arrangement (1) with a main gear (2) and relative to this relative in the circumferential direction (3) rotatable gear (4), with spring elements (8), with which the rotatable gear (2 ) is biased in the circumferential direction (3) against the main gear (2), wherein the spring elements (8) on the one hand with the main gear (2) and on the other hand, the rotatable gear (4) are connected, characterized in that the spring elements (8) in each case one Have longitudinal central axis (19) which are arranged obliquely to an axial end face (18) of the rotatable gear (4).
[2]
2. gear arrangement (1) according to claim 1, characterized in that the longitudinal central axes (19) of the spring elements (8) at an angle (20) to the axial end face (18) extend, which is selected from a range with a lower limit of ± 3 ° and an upper limit of ± 80
[3]
3. Gear arrangement according to claim 1 or 2, characterized in that on the plane of the axial end face (18) of the rotatable gear (4) projected longitudinal central axes (19) by the spring elements (8) at an angle (21 or 22) to each other are not equal to 90 ° or an integer multiple thereof.
[4]
4. gear arrangement (1) according to one of claims 1 to 3, characterized in that at least two, in particular at least three or four, spring elements (8) are arranged.
[5]
5. gear arrangement (1) according to one of claims 1 to 4, characterized in that the spring elements (8) are designed as coil springs. 15/20 N2012 / 16600

···············
[6]
6. gear arrangement (1) according to one of claims 1 to 5, characterized in that the main gear (2) and / or the rotatable gear (4) has at least one axial stop for the rotatable gear or the main gear or have.
[7]
7. gear arrangement (1) according to one of claims 1 to 6, characterized in that the rotatable gear (4) partially in a region (25) on the main gear (2) is applied, in this region (25) the main gear (2 ) and / or the rotatable gear (4) is or are provided with a friction-changing coating.
[8]
8. gear arrangement (1) according to one of claims 1 to 7, characterized in that individual one of the spring elements (8) to the remaining spring elements (8) have a different spring characteristic and / or at a different angle (20) of the longitudinal central axes (19) are arranged to the axial end face (18). 9. gear drive (26) with a first gear and a second gear, wherein the first gear is arranged without play on a shaft (6), characterized in that the first gear as a gear arrangement (1) according to one of claims 1 to 8 is formed , Miba Sinter Austria GmbH by AnwältS ^^ r ^ Partner Attorney GmbH 16/20 N2012 / 16600

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同族专利:

公开号 | 公开日

CN103775610B|2018-01-02|

US20140116174A1|2014-05-01|

CN103775610A|2014-05-07|

AT513246B1|2014-03-15|

US9322465B2|2016-04-26|

DE102013110396A1|2014-04-30|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US1449903A|1923-03-27|Geab construction |

US1648715A|1926-03-15|1927-11-08|James O Bean|Gear|

JPH08240258A|1995-03-03|1996-09-17|Canon Inc|Non-backlash gear device|CN105042034A|2014-04-30|2015-11-11|麦格纳动力系有限两合公司|Method for producing a backlash-free transmission stage|US2310232A|1941-12-12|1943-02-09|Gear Specialties|Preloaded gears|

US2343110A|1942-10-30|1944-02-29|Gear Specialties|Preloaded gear|

US2440901A|1947-01-31|1948-05-04|Leeds & Northrup Co|Antibacklash gearing|

US3359819A|1966-04-25|1967-12-26|Leo J Veillette|Bidirectional step torque filter with zero backlash characteristic|

US4184380A|1978-03-10|1980-01-22|Rivin Evgeny I|Gears having resilient coatings|

DE3762360D1|1986-09-24|1990-05-23|Siemens Ag|TRANSMISSION ARRANGEMENT, ESPECIALLY FOR MOTOR VEHICLE WINDOW REGULATORS.|

DE3735335A1|1987-10-19|1989-04-27|Porsche Ag|DEVICE FOR TURNING THE VIBRATION IN A GEAR GEAR|

US5056613A|1990-07-27|1991-10-15|Ford Motor Company|Vehicular speed control system with reduced gear chatter|

DE4408881C2|1993-08-12|1996-08-08|Fichtel & Sachs Ag|Clutch disc with centered control plate|

JP3269275B2|1994-09-26|2002-03-25|スズキ株式会社|Gear transmission|

US5870928A|1997-05-08|1999-02-16|Cummins Engine Company, Inc.|Anti-lash gear with alignment device|

US6386060B1|1998-11-04|2002-05-14|Iosif Epshteyn|Gearing with duplex floating toothed portions|

US7383750B2|2003-06-16|2008-06-10|Delphi Technologies, Inc.|Double flank delash gear mechanism|

JP4529456B2|2003-11-28|2010-08-25|株式会社安川電機|Arm mechanism of industrial robot|

US8695775B2|2007-06-29|2014-04-15|Yamaha Hatsudoki Kabushiki Kaisha|Centrifugal clutch and vehicle provided with the same|

JP2009103279A|2007-10-25|2009-05-14|Mitsubishi Fuso Truck & Bus Corp|Gear device|

JP2010125927A|2008-11-26|2010-06-10|Aisin Aw Co Ltd|Hybrid drive unit|

CN201739441U|2010-08-09|2011-02-09|中信重工机械股份有限公司|Parallel axis up-and-down bridge shunting type multipoint meshing reduction gear for large-scale puncher|

KR101351500B1|2012-01-18|2014-01-15|주식회사 세스코|An workrest elevator in use with grinder|

JP2013215788A|2012-04-11|2013-10-24|Kanazawa Inst Of Technology|Two-motor power processing machine|

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US9772030B2|2014-08-04|2017-09-26|Achates Power, Inc.|Split gear assembly with one-way roller clutch for controlling backlash in opposed-piston engines|

KR101646120B1|2014-12-03|2016-08-05|현대자동차 주식회사|Motor coupling device|

NL2015189B1|2015-07-18|2017-02-07|Vcst Ind Products Bvba|Scissor gear assembly.|

EP3208666B1|2016-02-19|2018-11-21|Blancpain SA|Clock wheel with backlash compensation|

AT518787B1|2016-07-18|2018-01-15|Miba Sinter Austria Gmbh|gearing|

WO2018222994A1|2017-06-02|2018-12-06|Achates Power, Inc.|Reduction of noise, vibration, and harshness in an opposed-piston engine|

DE102017220430B3|2017-11-16|2019-05-16|Zf Friedrichshafen Ag|Divided gear|

CN108374868B|2018-04-20|2019-06-07|浙江大学|A kind of low-load vibration-reduction gear with circumferential spring|

DE102018207493A1|2018-05-15|2019-11-21|Sram Deutschland Gmbh|A bicycle adjusting device and method of controlling or adjusting such adjusting devices|

AT521375B1|2018-11-15|2020-01-15|Miba Sinter Austria Gmbh|gearing|

DE102018220492A1|2018-11-28|2020-05-28|Kyros-Filippos Kontopoulos|DIVIDED GEAR WHEEL FOR AN AUTOMATIC POWER TRANSMISSION SYSTEM|

DE102019200835B3|2019-01-24|2020-06-04|Audi Ag|Bracing gear for a gear transmission|

DE102020102265A1|2020-01-30|2021-08-05|Schaeffler Technologies AG & Co. KG|Shaft adjuster|

法律状态:
2020-08-15| MM01| Lapse because of not paying annual fees|Effective date: 20191025 |

优先权:

申请号 | 申请日 | 专利标题

ATA1156/2012A|AT513246B1|2012-10-25|2012-10-25|gearing|ATA1156/2012A| AT513246B1|2012-10-25|2012-10-25|gearing|

US13/960,992| US9322465B2|2012-10-25|2013-08-07|Gear system|

CN201310357406.0A| CN103775610B|2012-10-25|2013-08-16|Geared system|

DE102013110396.0A| DE102013110396A1|2012-10-25|2013-09-20|gearing|

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