EP2864669A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée

Info

Publication number
EP2864669A1
EP2864669A1 EP13723466.2A EP13723466A EP2864669A1 EP 2864669 A1 EP2864669 A1 EP 2864669A1 EP 13723466 A EP13723466 A EP 13723466A EP 2864669 A1 EP2864669 A1 EP 2864669A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
gear set
clutch
brake
shaft
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Withdrawn
Application number
EP13723466.2A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Christian Sibla
Wolfgang Rieger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2864669A1 publication Critical patent/EP2864669A1/fr
Withdrawn legal-status Critical Current

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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing 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
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
    • 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
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • 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
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
    • 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
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the present invention relates to a planetary gear multi-speed transmission, in particular an automatic transmission for a motor vehicle, according to the preamble of patent claim 1.
  • Automatic transmissions particularly for motor vehicles, include, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.
  • friction elements such as clutches and brakes
  • slip element such as clutches and brakes
  • lockup clutch such as a hydrodynamic torque converter or a fluid coupling connected.
  • a multi-speed planetary gear transmission which has a drive and an output, which are arranged in a housing.
  • the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and at least six switching elements, comprising brakes and clutches, provided, the selective engagement causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the first and the second planetary gear set which are preferably designed as negative planetary gear sets, that is to say with a negative stationary gear ratio, form a shiftable transfer gearset, the third and the fourth planetary gear set forming a main gearset.
  • the switching elements of such executed multi-speed transmission which are usually designed as multi-plate clutches or brakes, actuated hydraulically, which leads disadvantageously to high hydraulic losses.
  • the use of alternatively operable switching elements, for example of electromechanically actuatable switching elements would be particularly advantageous.
  • the switching elements in particular the couplings from the outside must be easily accessible.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and one reverse gear with sufficient translation, in which the construction cost, the component load and the size are optimized and also improves the efficiency in terms of drag and gearing losses becomes. Furthermore, the switching elements of the transmission should be easily accessible from the outside, whereby the installation of demand-actuated switching elements is facilitated. In addition, the transmission should be suitable for both a standard and a front-transverse construction.
  • a multi-speed transmission which has a drive and an output, which are arranged in a housing.
  • at least four planetary gear sets are , hereinafter referred to as the first, second, third and fourth planetary gear set, eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and six preferably designed as a lamellar switching elements or as a form-locking switching elements
  • Switching elements comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably at least nine forward gears and one reverse gear can be realized.
  • the first planetary gear set of the transmission is preferably designed as a positive planetary gear set, wherein the second, third and fourth planetary gear set of the transmission are preferably designed as negative planetary gear sets.
  • the ring gear at a fixed web has a direction of rotation opposite to the sun and it results in a negative stationary gear ratio.
  • a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, all inner planetary gears mesh with the sun gear and all outer planet gears with the ring gear, each inner planetary gear, each with an outer Planet wheel meshes.
  • the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.
  • the sun gear of the first planetary gear set is connected to the third shaft, which is releasably connectable via a first clutch to the drive shaft and can be coupled via a first brake to the housing, wherein the drive shaft via a second clutch with the with the web of the third planetary gear set connected to the fourth wave is detachably connectable, which can be coupled via a second brake to the web of the first planetary gear set, which is coupled to the housing.
  • the drive shaft is connected to the sun gear of the fourth planetary gear set, the eighth shaft being connected to the ring gear of the first planetary gear set, the sun gear of the second planetary gear set and the sun gear of the third planetary gear set, and the fifth shaft to the land of the second planetary gear set and the ring gear connected to the third planetary gear set and via a third clutch with the connected to the ring gear of the fourth planetary gear seventh shaft is detachably connected.
  • the third clutch is preferably arranged radially in the vicinity of the housing.
  • the sixth shaft is connected to the ring gear of the second planetary gear set and via a fourth clutch, with the output shaft of the transmission detachably connectable, which is connected to the web of the fourth planetary gear set.
  • the first and second clutch are arranged on the drive shaft of the transmission
  • the fourth clutch is arranged on the output shaft and the other switching elements are designed as brakes, good accessibility of substantially all switching elements of the transmission is ensured, whereby the switching elements as needed operable switching elements can be executed.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a start with a hydrodynamic converter, an external starting clutch o- perform well with other suitable external starting elements. It is also conceivable to allow a starting operation with a start-up element integrated in the transmission.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.
  • Figure 1 is a schematic view of a preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 2 shows an exemplary circuit diagram for a multistage transmission according to FIG. 1.
  • the first planetary gear set P1 is formed in the example shown in Figure 1 as a plus planetary gear, wherein the second, third and fourth planetary gear, P2, P3, P4 are formed as negative planetary gear sets.
  • at least one of Minus planetary gear sets P2, P3, P4 be designed as plus planetary gear set, when the web and Hohlradanulation exchanged at the same time and the amount of the stationary gear ratio is increased compared to the execution as a minus planetary gear set by 1.
  • the planetary gear sets P1, P2, P3, P4 axially arranged in the order of the first planetary gear set P1, second planetary gear set P2, third planetary gear set P3, fourth planetary gear set P4.
  • the axial order of the individual planetary gear sets and the arrangement of the switching elements are freely selectable, as long as it allows the binding of the elements of the planetary gear sets.
  • switching elements namely two brakes 03, 04 and four clutches 13, 14, 26, 57 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutches and the brakes of the transmission are preferably designed as Reibschaltemia or lamellar switching elements, but can also be designed as a form-locking switching elements.
  • the multi-speed transmission according to the invention has a total of eight rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6, 7 and 8, wherein the drive shaft, the first shaft 1 and the output shaft form the second shaft 2 of the transmission.
  • the sun gear of the first planetary gear set P1 is connected to the third shaft 3, which can be detachably connected to the drive shaft 1 via a first clutch 13 and can be coupled to the housing G via a first brake 03 , wherein the drive shaft 1 via a second clutch 14 with the connected to the web of the third planetary gear P3 fourth shaft 4 is detachably connectable, which is coupled via a second brake 04 to the web of the first planetary gear P1, which is coupled to the housing G. (Wave 0).
  • the drive shaft 1 is connected to the sun gear of the fourth planetary gear set P4, wherein the eighth shaft 8 is connected to the ring gear of the first planetary gear P1, the sun gear of the second planetary gear P2 and the sun gear of the third planetary gear set P3; the fifth shaft 5 is connected to the web of the second planetary gear set P2 and the ring gear of the third planetary gear set P3 and detachably connectable via a third clutch 57 with the seventh shaft 7 connected to the ring gear of the fourth planetary gear set P4.
  • the sixth shaft 6 of the transmission is connected to the ring gear of the second planetary gear set P2 and via a fourth clutch 26, releasably connectable to the output shaft 2 of the transmission, which is connected to the web of the fourth planetary gear set P4.
  • the second brake 04 is suitable for a design as a claw switching element, whereby the consumption is significantly improved.
  • FIG. 2 shows an exemplary circuit diagram of a multistage transmission according to FIG. For each gear three switching elements are closed.
  • the shift scheme, the respective ratios i of the individual grades and the gear ratios to be determined therefrom or increments ⁇ to the next higher gear are exemplified, the value of 9.002 represents the spread of the transmission.
  • the values for the stationary gear ratios of the first, second, third and fourth planetary gear set P1, P2, P3, P4 are in the example shown in each case 2.550, -3.425, -2.700 and -2.350. From Figure 2 it is seen that in sequential switching mode only one switching element switched on and a switching element must be switched off because two adjacent gear stages use two switching elements together. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward speed results from closing the second brake 04 and the first and third clutches 13, 57, the second forward speed by closing the first and second brakes 03, 04 and the third clutch 57, the third forward speed Closing the second brake 04 and the third and fourth clutches 57, 26, the fourth forward gear by closing the first brake 03 and the third and fourth clutch 57, 26, the fifth forward gear by closing the first, third and fourth clutch 13, 57, 26, the sixth forward gear in the example shown by closing the second, third and fourth clutch 14, 57, 26, the seventh forward gear by closing the first, second and third clutch 13, 14th , 57, the eighth forward gear by closing the first, second and fourth clutches 13, 14, 26 and the ninth forward gear is obtained by closing the first brake 03 and the second and fourth clutches ung 14, 26, wherein the reverse gear by closing the second brake 04 and the first and fourth clutch 13, 26 results.
  • an axle differential and / or a distributor differential can be arranged on the drive side or on the output side.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as the coupling element , It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.
  • a wear-free brake such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as e.g. Multi-plate clutches, band brakes and / or cone clutches are used.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une boîte de vitesses multi-étagée comprenant quatre trains planétaires (P1, P2, P3, P4), huit arbres rotatifs (1, 2, 3, 4, 5, 6, 7, 8) et six éléments de changement de vitesse (03, 04, 13, 14, 26, 7). La roue solaire du premier train planétaire (P1) est reliée au troisième arbre (3) qui peut être relié de manière libérable à l'arbre d'entrée (1) par l'intermédiaire d'un premier embrayage (13) et peut être accouplé au carter (G) par l'intermédiaire d'un premier frein (03). L'arbre d'entrée (1) peut être relié de manière libérable au quatrième arbre (4) relié à l'élément de liaison du troisième train planétaire (P3). Le quatrième arbre (4) peut être accouplé, par l'intermédiaire d'un deuxième frein (04), à l'élément de liaison du premier train planétaire (P1) qui est accouplé au carter (G). L'arbre d'entrée (1) est relié à la roue solaire du quatrième train planétaire (P4). Le huitième arbre (8) est relié à la couronne du premier train planétaire (P1), à la roue solaire du deuxième train planétaire (P2) et à la roue solaire du troisième train planétaire (P3). Le cinquième arbre (5) peut être relié de manière libérable à l'élément de liaison du deuxième train planétaire (P2) et à la couronne du troisième train planétaire (P3) et, par l'intermédiaire d'un embrayage (57) au septième arbre (7) relié à la couronne du quatrième train planétaire (P4). Le sixième arbre (6) est relié à la couronne du deuxième train planétaire (P2) et peut être relié de manière libérable à l'arbre de sortie (2) de la boîte de vitesses, par l'intermédiaire d'un quatrième embrayage (26). L'arbre de sortie (2) est relié à l'élément de liaison du quatrième train planétaire (P4).
EP13723466.2A 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée Withdrawn EP2864669A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012210860.2A DE102012210860A1 (de) 2012-06-26 2012-06-26 Mehrstufengetriebe
PCT/EP2013/059881 WO2014000944A1 (fr) 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée

Publications (1)

Publication Number Publication Date
EP2864669A1 true EP2864669A1 (fr) 2015-04-29

Family

ID=48463967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13723466.2A Withdrawn EP2864669A1 (fr) 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée

Country Status (5)

Country Link
US (1) US9618095B2 (fr)
EP (1) EP2864669A1 (fr)
CN (1) CN104364556B (fr)
DE (1) DE102012210860A1 (fr)
WO (1) WO2014000944A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015132331A (ja) * 2014-01-14 2015-07-23 アイシン・エィ・ダブリュ株式会社 多段変速機
KR101714155B1 (ko) * 2015-06-04 2017-03-09 현대자동차주식회사 차량용 변속기
KR101896331B1 (ko) * 2016-09-12 2018-09-07 현대자동차 주식회사 차량용 자동 변속기의 유성기어트레인

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115995A1 (de) * 2001-03-30 2002-10-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
DE10162888A1 (de) * 2001-12-20 2003-07-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
JP2006349153A (ja) * 2005-06-14 2006-12-28 Hiroki Kawana ９速自動変速機のギヤトレーン
US7951039B2 (en) * 2007-03-30 2011-05-31 GM Global Technology Operations LLC Eight speed automatic transmission
US7695398B2 (en) 2007-07-09 2010-04-13 Gm Global Technology Operations, Inc. 9-speed transmission
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2009293762A (ja) * 2008-06-09 2009-12-17 Kyowa Metal Work Co Ltd 多段変速遊星歯車列
US8979701B2 (en) * 2008-09-15 2015-03-17 Ford Global Technologies, Llc Multiple speed transmission
DE102009019046A1 (de) * 2009-04-28 2010-11-04 Daimler Ag Getriebevorrichtung
DE102009028669A1 (de) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102009054105A1 (de) * 2009-11-20 2011-05-26 Daimler Ag Getriebeeinheit
US8894535B2 (en) * 2011-08-10 2014-11-25 Gm Global Technology Operations, Llc Multi-speed transmission
KR101305818B1 (ko) * 2011-09-21 2013-09-06 현대자동차주식회사 차량용 변속기
DE102012210864A1 (de) * 2012-06-26 2014-01-02 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012210868A1 (de) * 2012-06-26 2014-01-02 Zf Friedrichshafen Ag Mehrstufengetriebe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014000944A1 *

Also Published As

Publication number Publication date
WO2014000944A1 (fr) 2014-01-03
US9618095B2 (en) 2017-04-11
US20150300460A1 (en) 2015-10-22
DE102012210860A1 (de) 2014-01-02
CN104364556B (zh) 2017-02-22
CN104364556A (zh) 2015-02-18

Similar Documents

Publication Publication Date Title
EP2817536B1 (fr) Boîte de vitesses multi-étagée
EP2817534B1 (fr) Boîte de vitesses multi-étagée
EP2817535B1 (fr) Boîte de vitesses multi-étagée
WO2013160003A1 (fr) Boîte de vitesses multi-étagée
EP2841806A1 (fr) Boîte de vitesses multi-étagée
EP2841803A1 (fr) Boîte de vitesses multi-étagée
WO2014000940A1 (fr) Boîte de vitesses multi-étagée
WO2013159997A1 (fr) Boîte de vitesses multi-étagée
EP2817537B1 (fr) Boîte de vitesses multi-étagée
EP2841805A1 (fr) Boîte de vitesses multi-étagée
WO2013160001A1 (fr) Boîte de vitesses multi-étagée
WO2013160002A1 (fr) Boîte de vitesses multi-étagée
WO2014000942A1 (fr) Boîte de vitesses multi-étagée
WO2013160004A1 (fr) Boîte de vitesses multi-étagée
EP2864663A1 (fr) Boîte de vitesses à plusieurs rapports
WO2013159998A1 (fr) Boîte de vitesses multi-étagée
WO2014000943A1 (fr) Boîte de vitesses multi-étagée
EP2864669A1 (fr) Boîte de vitesses multi-étagée

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141104

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20191203