EP2959186A1 - Mehrstufengetriebe in planetenbauweise - Google Patents
Mehrstufengetriebe in planetenbauweiseInfo
- Publication number
- EP2959186A1 EP2959186A1 EP14701083.9A EP14701083A EP2959186A1 EP 2959186 A1 EP2959186 A1 EP 2959186A1 EP 14701083 A EP14701083 A EP 14701083A EP 2959186 A1 EP2959186 A1 EP 2959186A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- designed
- gear
- clutch
- switching element
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Definitions
- the present invention relates to a planetary multi-speed transmission for a vehicle according to the closer defined in the preamble of claim 1.
- a power-shiftable multi-speed transmission is known.
- the drive shaft is connected via a torsional vibration damper fixed to a first shaft of a first shaft train.
- a parallel arranged second shaft strand includes, among others, designated as the shaft two output shaft.
- the two wave strands are connected to each other via three spur gear stages.
- On the first shaft train is a first three-shaft planetary gear.
- On the second shaft train are a second planetary gear and a third planetary gear.
- the multi-speed transmission thus comprises ten shafts, which communicate with each other via three spur gears and three planetary gears. To switch the eight forward gears and the one reverse gear five switching elements are necessary.
- the envisaged switching elements are hydraulically actuated.
- the switching elements are to be arranged easily accessible from the outside.
- a front-transverse installation of the transmission in a vehicle only a limited axial space is available.
- the present invention is based on the object to provide a multi-speed transmission with the highest possible number of gear ratios and good accessibility of the switching elements at the same time good gear efficiency and the lowest possible axial space requirement.
- a powershiftable multi-speed planetary gear or a multi-speed planetary gear for a vehicle is proposed with a housing, wherein the drive or the drive shaft and the output or the output shaft are arranged axially parallel to each other for a preferred front transverse installation.
- the multistage transmission according to the invention comprises only nine shafts, three planetary gear sets and only six shift elements in order to realize at least nine forward gears and one reverse gear can. Furthermore, preferably only two machine elements are provided for coupling drive and output.
- first shaft as a drive with the sun gears of the first and the third planetary gear and the planet carrier of the second planetary gear respectively releasably connected or connectable or connected and that the second shaft connected as an output to the first machine element and the second machine element or releasably connected or connectable, results in an inventive multi-stage transmission, which allows efficiency-enhancing and thus needs-based operation of the switching elements, the advantageously small number of gear elements of the multi-speed transmission to the front-transverse design are interleaved with each other so that a particularly axial space-saving Arrangement is made possible. In addition to the improved efficiency, there are also low component loads and low construction costs.
- the good accessibility of the switching elements can be realized, inter alia, on the one hand by the use of brakes as switching elements and on the other hand by the use of couplings as switching elements, which are preferably positioned on outer shafts preferably on the drive and the output in the multi-step transmission according to the invention. Due to the low construction costs result in an advantageous manner low production costs and low weight of the multi-speed transmission according to the invention.
- a machine element for coupling or torque transmission between the drive and output at least one spur gear or the like is used, which realizes the necessary translation to the output differential.
- other machine elements for power transmission such as chains, belts or the like may be used.
- the planetary gear sets are arranged in the order of the first planetary gear set, the second planetary gear set and the third planetary gear set when viewed in the axial direction, with preferably three minus planetary gear sets being provided.
- a minus planetary gearset has known to the planetary gear rotatably mounted planetary gears, which mesh with the sun gear and the ring gear of this planetary, so that the ring gear rotates with held planet carrier and rotating sun gear in the direction opposite to Sonnenradcard.
- a plus planetary gear set is known to be rotatably mounted on its planet and rotatably mounted in meshing inner and outer planetary gears, the sun gear of this planetary mesh with the inner planet gears and the ring gear of this planetary gear with the outer planetary gears, so that the ring gear while holding the planet and rotating sun gear in the direction of Clarradfilraum same direction turns.
- a plurality of planetary gear sets are arranged radially one above the other.
- the ring gear of the inner planetary gear and the sun gear of the outer planetary gear set may be designed as a component.
- the ring gear of the inner planetary gear set have an inner toothing and an outer toothing, but other embodiments are conceivable.
- the interleaved planetary gear sets are essentially chen arranged in an axial plane, so that in an advantageous manner axial space is saved.
- a hydrodynamic torque converter or a hydrodynamic coupling can be used in the multistage transmission according to the invention. It is also conceivable that an additional starting clutch or an integrated starting clutch or starting brake be used. It is also possible that an electric machine or another power / power source is arranged on at least one of the shafts. In addition, a freewheel to the housing or to another shaft can be arranged on at least one of the waves.
- nine forward gears and at least one reverse gear can be switched via the switching elements provided.
- the switching elements provided.
- switching element is to be understood as meaning a switchable connection between two elements of the transmission, wherein the torque to be transmitted between these two elements is transmitted by means of frictional connection or frictional engagement or by means of positive locking. If both elements of the switchable connection are rotatable, then the switching element is referred to as a coupling and if only one of the two elements of the switchable connection rotates, the switching element is referred to as a brake.
- the geometric position or sequence of the individual switching elements is freely selectable, as long as it allows the bindability of the elements. In this way, individual elements can be moved arbitrarily in their position.
- a plurality of wheel sets can also be arranged radially one above the other, ie nested.
- Exemplary embodiments of a force-locking switching element are multi-plate clutches or brakes, band brakes, cone clutches or brakes, electric magnetic couplings, magnetic particle clutches and electro-rheological coupling.
- Exemplary embodiments of a form-locking switching element are claw couplings or brakes and toothed couplings.
- both friction and form-locking switching elements can generally be used.
- the second shifting element designed as a clutch and the fourth shifting element designed as a clutch can be designed as claw shifting elements, whereby clear consumption advantages are achieved.
- Figure 1 is a schematic view of a first embodiment of a multi-speed transmission according to the invention
- Figure 1 A is a circuit diagram for the embodiment of Figure 1;
- Figure 2 is a schematic view of a second embodiment of the multi-speed transmission
- Figure 3 is a schematic view of a third embodiment of the multi-speed transmission
- Figure 4 is a schematic view of a fourth embodiment of the multi-speed transmission
- Figure 5 is a schematic view of a fifth embodiment of the multi-speed transmission
- Figure 6 is a schematic view of a sixth embodiment of the multi-speed transmission.
- Figure 7 is a schematic view of an alternative embodiment of the fourth embodiment of the multi-speed transmission.
- an embodiment of the multi-speed transmission according to the invention in planetary design for example, as an automatic transmission or automatic transmission, for a vehicle shown by way of example.
- the multistage transmission comprises a housing 1 1, which is indicated only schematically, with a first shaft 1 as the drive An and a second shaft 2 arranged parallel to the axis as the output Ab and further seven shafts 3, 4, 5, 6, 7, 8, 9. Furthermore, a first planetary gearset RS1, a second planetary gearset RS2 and a third planetary gearset RS3 are provided, wherein preferably the first planetary gearset RS1, the second planetary gearset RS2 and the third planetary gearset RS3 are each designed as negative planetary gear sets.
- a clutch first switching element K1 designed as a clutch second switching element K2, designed as a clutch third switching element K3, designed as a clutch fourth switching element K4, designed as a brake fifth switching element B1 and designed as a brake sixth Switching element B2 provided.
- two arbitrary machine elements are preferably provided, which in the case of the embodiment variants are designed by way of example as first spur gear stage ST1 and as second spur gear stage ST2.
- FIGS. 2 to 7 gear variants of the same effect are shown in FIGS. 2 to 7, wherein a variation possibility of the fourth embodiment variant according to FIG. 4 is shown in FIG. 7, in which the switching elements K3 and K4 assigned to the spur gear stages ST1 and ST2 are separated from the output shaft or gear . Intermediate shaft are displaced to the main shaft or drive shaft.
- the various embodiments according to Figures 1 to 7 are not functionally different from the embodiment of Figure 1 in terms of efficiency, grading, etc.
- connection possibilities between the provided shafts 1, 2, 3, 4, 5, 6, 7, 8, 9, the planned three planetary gear sets RS1, RS2, RS3, the intended housing 1 1 and the provided switching elements K1, K2, K3, K4, B1, B2 and the proposed spur gears ST1, ST2 is by the term -verbindbar- to understand that the elements described are releasably connected, for example via a switching element, so that the connection is closed when activated switching element and open when not activated switching element.
- the detachable connection can be realized in addition to the switching element via at least one further element, such as a shaft or the like.
- the term "connected” is to be understood as meaning that the elements described are virtually non-detachably connected to one another, so to speak. It can be realized a direct or indirect connection, for example via other elements.
- the first shaft 1 is detachably connected or connectable or connected as drive with the sun gear SR1 of the first planetary gearset RS1, with the sun gear SR3 of the third planetary gearset RS3 and with the planet carrier PT2 of the second planetary gearset RS2
- the second shaft as the output Ab is connected or detachably connected or connectable to the first machine element or to the first spur gear ST1 and to the second machine element or the second spur gear ST2.
- the first shaft 1 can be connected via the first switching element K1 designed as a clutch and via the third shaft 3 to the sun gear SR1 of the first planetary gear set RS1, wherein the sun gear SR1 of the first planetary gear set RS1 is connected as a brake executed fifth switching element B1 to the housing 1 1 is connectable.
- two of the three planetary gear sets RS1, RS2, RS3 are arranged radially one above the other and thus lie substantially in a common axial plane. This is the first planetary gear set radially inward and the second planetary gear set RS2 arranged radially au Shen, wherein the ring gear HR1 of the first planetary gearset RS1 serves as a link between the two planetary gear sets RS1 and RS2.
- the first shaft 1 can be connected to the sun gear SR3 of the third planetary gearset RS3 via the second shifting element K2 designed as a clutch and via the eighth shaft 8. Furthermore, the first shaft 1 can be connected via the third switching element K3 designed as a clutch and via the seventh shaft 7 to the planet carrier PT2 of the second planetary gearset RS2. In addition, the second shaft 2 can be connected via the fourth switching element K4 designed as a clutch and via the ninth shaft 9 to the idler gear 13 of the first spur gear stage ST1. In addition, the second shaft 2 is connected to the fixed gear 1 5 of the second spur gear ST2.
- the first shaft 1 is connected to the sun gear SR3 of the third planetary gearset RS3. Furthermore, the first shaft 1 can be connected via the third switching element K3 designed as a clutch and via the eighth shaft 8 to the planet carrier PT2 of the second planetary gear set RS2. In addition, the second shaft 2 can be connected via the fourth switching element K4 designed as a clutch and via the ninth shaft 9 to the idler gear 13 of the first spur gear stage ST1. In addition, the second shaft 2 is connected to the fixed gear 15 of the second spur gear ST2.
- the first shaft 1 is connected to the planet carrier PT2 of the second planetary gearset RS2. Furthermore, the first shaft 1 can be connected via the second switching element K2 designed as a clutch and via the eighth shaft 8 to the sun gear SR3 of the third planetary gear set RS3. In addition, the second shaft 2 can be connected via the fourth switching element K4 designed as a clutch and via the ninth shaft 9 to the idler gear 13 of the first spur gear stage ST1. In addition, the second wave is 2 connected via the third switching element K3 designed as a clutch and via the seventh shaft 7 to the idler gear 15A of the second spur gear ST2.
- the first shaft 1 is connected to the sun gear SR3 of the third planetary gear set RS3 and to the planet carrier PT2 of the second planetary gearset RS2.
- the second shaft 2 can be connected via the fourth switching element K4 designed as a clutch and via the ninth shaft 9 to the idler gear 13 of the first spur gear stage ST1.
- the second shaft 2 can be connected via the third switching element K3 designed as a clutch and via the eighth shaft 8 to the idler gear 15A of the second spur gear ST2.
- the first shaft 1 is connected to the planet carrier PT2 of the second planetary gearset RS2. Furthermore, the first shaft 1 can be connected via the second switching element K2 designed as a clutch and via the eighth shaft 8 to the sun gear SR3 of the third planetary gear set RS3.
- the second shaft 2 is connected to the fixed gear 13A of the first spur gear ST1, and the second shaft 2 is connected to the fixed gear 15 of the second spur gear ST2.
- a fixed gear 12 of a first spur gear ST1 is connected via the fifth shaft 5 with the ring gear HR1 of the first planetary gearset RS1, wherein the ring gear HR1 of the first planetary gearset RS1 on the fifth wave 5 and via the second switching element K2 designed as a clutch can be connected to the planet carrier PT3 of the third planetary gearset RS3.
- a fixed gear 12 of a first spur gear ST1 is connected via the fifth shaft 5 with the ring gear HR1 of the first planetary gearset RS1
- the ring gear HR1 of the first planetary gearset RS1 on the fifth wave 5 and via the second switching element K2 designed as a clutch can be connected to the planet carrier PT3 of the third planetary gearset RS3.
- a fixed gear 14 of a second spur gear ST2 is connected via the sixth shaft 6 with the ring gear HR2 of the second planetary gear set RS2.
- a loose wheel 14A of a second spur gear ST2 can be connected to the ring gear HR2 of the second planetary gearset RS2 via the sixth shaft 6 and via the third shifting element K3 designed as a clutch and via the seventh shaft 7.
- FIG. 1A a circuit diagram or a switching matrix for the respective transmission variant is shown in FIG. 1A.
- switching elements K1, K2, K3, K4, B1, B2 are tabulated to realize the various stages, wherein Each gear stage a ratio i and between different gear ratios of the respective gear jump ⁇ are specified.
- further additional shift combinations are indicated as alternative fourth forward gears M1, M2, M3.
- a value of about i 0 - 2.015
- the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the fourth shifting element K4 designed as a clutch are closed.
- the fifth forward gear G5 are designed as a clutch first switching element K1, which is designed as a clutch second switching element K2 and running as a clutch third switching element K3 closed.
- the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the fifth shifting element B1 designed as a brake are closed.
- the seventh forward gear G7 the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the sixth shifting element B2 designed as a brake are closed.
- the third shifting element K3 designed as a clutch, the fifth shifting element B1 designed as a brake and the sixth shifting element B2 designed as a brake are closed.
- the ninth forward gear G9 designed as a clutch first switching element K1, designed as a clutch third switching element K3 and executed as a brake sixth switching element B2 are closed.
- the reverse gear R the first shifting element K1 designed as a clutch, the fourth shifting element K4 designed as a clutch and the sixth shifting element B2 designed as a brake are closed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013202886.5A DE102013202886A1 (de) | 2013-02-22 | 2013-02-22 | Mehrstufengetriebe in Planetenbauweise |
PCT/EP2014/051171 WO2014127945A1 (de) | 2013-02-22 | 2014-01-22 | Mehrstufengetriebe in planetenbauweise |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2959186A1 true EP2959186A1 (de) | 2015-12-30 |
Family
ID=49999960
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14701083.9A Withdrawn EP2959186A1 (de) | 2013-02-22 | 2014-01-22 | Mehrstufengetriebe in planetenbauweise |
Country Status (5)
Country | Link |
---|---|
US (1) | US9638287B2 (de) |
EP (1) | EP2959186A1 (de) |
CN (1) | CN105074274B (de) |
DE (1) | DE102013202886A1 (de) |
WO (1) | WO2014127945A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6511943B2 (ja) * | 2015-04-30 | 2019-05-15 | アイシン・エィ・ダブリュ株式会社 | 変速装置 |
DE102016214845A1 (de) * | 2016-08-10 | 2018-02-15 | Zf Friedrichshafen Ag | Getriebe für ein Kraftfahrzeug |
DE102017010868A1 (de) * | 2017-11-24 | 2019-05-29 | Daimler Ag | Getriebevorrichtung für ein elektrisches Antriebssystem, insbesondere eines Kraftfahrzeugs, sowie elektrisches Antriebssystem für ein Kraftfahrzeug |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007014150A1 (de) | 2007-03-23 | 2008-09-25 | EGS Entwicklungsgesellschaft für Getriebesysteme mbH | Lastschaltbares Mehrstufengetriebe |
US8113977B2 (en) * | 2007-10-12 | 2012-02-14 | GM Global Technology Operations LLC | Eight and nine speed automatic transmissions |
JP5138500B2 (ja) * | 2008-08-07 | 2013-02-06 | 本田技研工業株式会社 | 自動変速機 |
US8353803B2 (en) * | 2008-08-07 | 2013-01-15 | Honda Motor Co., Ltd. | Automatic transmission |
JP4757327B2 (ja) * | 2009-06-04 | 2011-08-24 | 本田技研工業株式会社 | 自動変速機 |
US8287497B2 (en) * | 2009-06-22 | 2012-10-16 | Tyco Healthcare Group Lp | Access assembly with flexible housing |
JP5184456B2 (ja) * | 2009-07-10 | 2013-04-17 | 本田技研工業株式会社 | 自動変速機 |
DE102010000859A1 (de) * | 2010-01-13 | 2011-07-14 | ZF Friedrichshafen AG, 88046 | Verfahren zum Betreiben einer Getriebevorrichtung mit mehreren reibschlüssigen Schaltelementen und wenigstens einem formschlüssigen Schaltelement |
JP2012127398A (ja) * | 2010-12-14 | 2012-07-05 | Honda Motor Co Ltd | 自動変速機 |
JP2012127399A (ja) * | 2010-12-14 | 2012-07-05 | Honda Motor Co Ltd | 自動変速機 |
US8371982B2 (en) * | 2011-05-20 | 2013-02-12 | GM Global Technology Operations LLC | Multi-speed transmission with at least one selectable one-way clutch |
DE102012201686A1 (de) * | 2012-02-06 | 2013-08-08 | Zf Friedrichshafen Ag | Mehrstufengetriebe |
DE102012201692A1 (de) * | 2012-02-06 | 2013-08-08 | Zf Friedrichshafen Ag | Mehrstufengetriebe |
DE102012201685A1 (de) * | 2012-02-06 | 2013-08-08 | Zf Friedrichshafen Ag | Mehrstufengetriebe |
DE102012201690A1 (de) * | 2012-02-06 | 2013-08-08 | Zf Friedrichshafen Ag | Mehrstufengetriebe |
DE102012113203A1 (de) * | 2012-10-26 | 2014-04-30 | Hyundai Motor Company | Planetengetriebezug eines Automatikgetriebes für Fahrzeuge |
DE102012221238A1 (de) * | 2012-11-21 | 2014-05-22 | Zf Friedrichshafen Ag | Getriebe |
DE102012221235A1 (de) * | 2012-11-21 | 2014-05-22 | Zf Friedrichshafen Ag | Getriebe |
DE102012221239A1 (de) * | 2012-11-21 | 2014-05-22 | Zf Friedrichshafen Ag | Getriebe |
US9644723B2 (en) * | 2014-06-05 | 2017-05-09 | Ford Global Technologies, Llc | Multi-speed transmission with lay shaft |
-
2013
- 2013-02-22 DE DE102013202886.5A patent/DE102013202886A1/de not_active Withdrawn
-
2014
- 2014-01-22 CN CN201480007496.3A patent/CN105074274B/zh not_active Expired - Fee Related
- 2014-01-22 US US14/769,583 patent/US9638287B2/en not_active Expired - Fee Related
- 2014-01-22 EP EP14701083.9A patent/EP2959186A1/de not_active Withdrawn
- 2014-01-22 WO PCT/EP2014/051171 patent/WO2014127945A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2014127945A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2014127945A1 (de) | 2014-08-28 |
CN105074274A (zh) | 2015-11-18 |
US20160003329A1 (en) | 2016-01-07 |
DE102013202886A1 (de) | 2014-08-28 |
US9638287B2 (en) | 2017-05-02 |
CN105074274B (zh) | 2017-09-26 |
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18D | Application deemed to be withdrawn |
Effective date: 20180801 |