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WO2019196971A1 - Dispositif fluidique pour transmission à courroie variable continue - Google Patents

Dispositif fluidique pour transmission à courroie variable continue Download PDF

Info

Publication number
WO2019196971A1
WO2019196971A1 PCT/DE2019/100067 DE2019100067W WO2019196971A1 WO 2019196971 A1 WO2019196971 A1 WO 2019196971A1 DE 2019100067 W DE2019100067 W DE 2019100067W WO 2019196971 A1 WO2019196971 A1 WO 2019196971A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
continuously variable
fluid arrangement
pressure
pump
Prior art date
Application number
PCT/DE2019/100067
Other languages
German (de)
English (en)
Inventor
Sebastian Köpfler
Reinhard Stehr
Markus Ciesek
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112019001862.0T priority Critical patent/DE112019001862A5/de
Priority to CN201980010579.0A priority patent/CN111801519A/zh
Publication of WO2019196971A1 publication Critical patent/WO2019196971A1/fr

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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefor
    • F16H61/0031—Supply of control fluid; Pumps therefor using auxiliary pumps, e.g. pump driven by a different power source than the engine
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/065—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions hydraulic actuating 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members

Definitions

  • the invention relates to a fluid arrangement for a continuously variable transmission, with at least one electric motor-driven fluid pump for pressing and / or adjusting a variator of the continuously variable Umslingggetriebes comprising a first set of discs and a second set of discs for torque transmission through a belt connected to each other.
  • the invention further relates to a method for operating a continuously variable belt transmission with such a fluid arrangement.
  • an electronic transmission control system for a motor vehicle with a continuously variable transmission which comprises a first and a second electric motor-driven fluid pump for pressing and adjusting a variator of the continuously variable belt transmission.
  • the object of the invention is to provide safety when operating a continuously variable belt drive, with at least one electric motor driven fluid pump for pressing and / or adjusting a variator of the continuously variable belt drive, which comprises a first pulley set and a second pulley set, which Torque transmission by a belt means are interconnected to increase.
  • the object is in a fluid arrangement for a continuously variable transmission, with at least one electric motor driven fluid pump for pressing and / or adjustment of a variator of the continuously variable order to schlingungsgetriebes comprising a first pulley and a second pulley set, for torque transmission through a belt interconnected, solved by at least one of the sets of discs for Dar- Position of a dual piston principle comprises at least one adjustment chamber and a pressure chamber.
  • the fluid arrangement is preferably operated with a hydraulic medium, such as hydraulic oil, cooling oil, lubricating oil or oil, which is provided in a hydraulic medium reservoir. Then the fluid arrangement can also be referred to as a hydraulic arrangement.
  • the continuously variable belt transmission is preferably designed as a conical-pulley transmission and is also referred to as a CVT transmission.
  • the CVT transmission comprises a variator with two pulley sets interconnected by a belt, each comprising a fixed pulley and a travel pulley movable axially on a variator shaft by applying an axial force in a sliding seat to provide sufficient contact pressure between the pulleys To ensure disc sets and the wrapping material.
  • the capital letters CVT preceding the word gear represent the English terms Continuously Variable Transmission.
  • the two pulley sets of the variator can be coupled together for torque transmission by means of a tensioning means, such as a chain.
  • the discs of the disc sets are designed, for example, as conical disk pairs.
  • the distance between the conical disks of the respective pulley set or conical pulley pair can be changed to steplessly vary the ratio of the CVT transmission.
  • the axial direction is defined by a rotation axis of the respective variator shaft. Axial means in the direction or parallel to the axis of rotation.
  • the electric motor-driven fluid pumps in particular hydraulic pumps, represent electrical pump actuators.
  • the claimed CVT transmission is actuated electrohydraulically via the electric pump actuators. Due to the double piston principle, the pressing and adjusting functions on the at least one pulley set are separated from each other.
  • the at least one electromotively driven fluid pump which represents an electric pump actuator EPA, is not permanently driven.
  • the electric pump actuator advantageously comprises a local control via which the drive of the electric motor-driven fluid pump is controlled as required.
  • a preferred embodiment of the fluid arrangement is characterized in that both disc sets each comprise at least one adjustment chamber and at least one pressure chamber for the representation of the double piston principle.
  • One of the electric motor driven fluid pumps is advantageously used to realize the contact pressure and is therefore also referred to as Anpressaktor.
  • the second electromotively driven fluid pump is preferably used for adjusting and is therefore also referred to as Verstellaktor.
  • the electromotive-driven fluid pumps bypass losses of classic fly-control concepts with mechanically driven pumps.
  • a third electric motor-driven fluid pump at least one further fluidic consumer in the fluid arrangement can advantageously be supplied with a fluid volume flow or with a fluid pressure.
  • the actuation of known single-piston CVT variators by means of electric pump actuators could, in the event of failure of an electric pump actuator, result in disadvantages in terms of functional safety. If, for example, the contactor fails, the belt could slippage and damage the belt drive or an uncontrolled vehicle behavior could occur.
  • the double piston principle in conjunction with the electric pump actuators makes emergency operation of the variator possible. As a result, transmission damage can be effectively prevented.
  • the double-piston principle separates the pressing and adjusting functions on both sets of discs.
  • a further preferred embodiment of the fluid arrangement is characterized in that an adjustment actuator is fluidically connected between the adjustment chambers of the two disc sets.
  • the adjustment advantageously takes place via separate chambers on the pulley sets.
  • the adjustment actuator is connected fluidically, in particular hydraulically, between the adjustment chambers of the two sets of disks and, with a variator adjustment, conveys volume flow between the adjustment chambers to the desired pressure levels. If the volume flows from the respective adjustment chambers are different in terms of amount due to different adjustment paths, then the adjustment actuator can advantageously be equipped with a two-pressure valve.
  • the fluid arrangement comprises a first and a second electromotively driven fluid pump for pressing and adjusting the variator of the continuously variable belt transmission.
  • the first and the second electromotively driven fluid pump represent an Anpressaktor and Verstellaktor for the variator.
  • a further preferred exemplary embodiment of the fluid arrangement is characterized in that a pressure side of a pressure actuator is fluidically connected to pressure chambers of the pulley sets. About the Anpressaktor the contact pressure of the pulley sets is realized.
  • a further preferred embodiment of the fluid arrangement is characterized in that a pilot-operated check valve is fluidically connected between the contact actuator and the pressure chambers.
  • the pilot-operated check valve prevents unwanted rapid pressure drop in the contact pressure chambers if the pressure actuator fails.
  • a suction side of the Anpressaktors optionally with the interposition of at least one other consumer, such as a cooling circuit, is fluidly connected to a fluid reservoir.
  • At least one further consumer, in particular a cooling circuit can be supplied with fluid from the fluid reservoir on the suction side of the pressure actuator, permanently or as needed.
  • a further preferred exemplary embodiment of the fluid arrangement is characterized in that a further consumer upstream of the contact pressure actuator, such as the cooling circuit, comprises a fluid pump, in particular a cooling oil pump, by means of which the pressure actuator is fluidically biased. Therefore, the fluid pump, in particular cooling oil pump, also be referred to as a biasing pump for the Anpress- actuator.
  • a further preferred embodiment of the fluid arrangement is characterized in that the fluid arrangement as Anpressaktor a permanently driven ne fluid pump, which provides a system pressure for a fluid control.
  • the contact pressure is then advantageously carried out by controlling corresponding valves in the fluid control.
  • the invention further relates to a continuously variable belt transmission with a previously described fluid arrangement.
  • the above-described object is alternatively or additionally achieved by virtue of the fluidic separation of contact pressure and adjustment in the event of a failure of one or of the adjusting actuator, a contact pressure, especially on the first set of pulleys, is maintained by one or the Anpressaktor. Due to the claimed circuitry in combination with the double piston principle and the associated separation of contact pressure and adjustment, the contact pressure on the first pulley set can be maintained via the contact pressure actuator in the event of failure of the adjustment actuator. In a single-piston principle, the pressure on the first pulley set would drop very rapidly due to leaks and a possible reverse rotation of the variable displacement pump.
  • FIG. 2 is a similar fluid arrangement as in Figure 1, wherein the Verstellaktor is additionally equipped with a two-pressure valve;
  • FIG. 3 shows a fluid arrangement with an adjustment actuator and an actuation actuator, which comprises a permanently driven fluid pump, which provides a system pressure for a fluid control;
  • Figure 4 shows a similar fluid arrangement as in Figure 3, wherein the Verstellaktor is additionally equipped with a two-pressure valve;
  • Figure 5 is a similar fluid arrangement as in Figure 1, wherein, in contrast to the previous fluid arrangements, however, only the first
  • Disc set includes a double piston.
  • a fluid assembly 81; 82; 85 shown with a belt transmission 2 in three different embodiments.
  • the order schlingungsgetriebe 2 includes a variator 3, the contact pressure is provided via a driven by an electric motor 4 first fluid pump 11. An adjustment of the variator 3 takes place via a second fluid pump 12 driven by an electric motor 5.
  • the third fluid pump 13 delivers fluid from the fluid reservoir 7 to a branch 27.
  • the first fluid pump 11 is arranged between the branch 27 and a branch 24.
  • the electric motor driven fluid pump 12 is an adjusting actuator 15.
  • the electric motor driven fluid pump 11 is an Anpressaktor 16.
  • Die Electric motor driven fluid pump 13 represents a cooling oil pump and serves as a biasing pump for the Anpressaktor 16th
  • a fluid line extends into a pressure chamber 17 of a first pulley set 21.
  • a further fluid line extends from the branch 24 to a pressure chamber 19 of a second pulley set 22.
  • the Verstellaktor 15 is connected via a fluid line with an adjustment chamber 18 of the first pulley set 21. Via a further fluid line of Verstellaktor 15 is connected to an adjustment chamber 20 of the second pulley set 22.
  • a pilot-operated check valve 25 is connected between the branch 24 and a pressure side of the Anpressaktors 16.
  • the two fluidic consumers 9, 10 are for example part of a cooling circuit 26.
  • the cooling circuit 26 comprises three branches 27, 28 and 29.
  • the branch 27 is arranged between the cooling oil pump 14 and the Anpressaktor 16.
  • the branch 28 is arranged between the branches 27 and 29 and, moreover, is connected to the fluid reservoir 7 via a check valve 30.
  • the check valve 30 blocks in the direction of the fluid reservoir 7.
  • a fluid line extends in Figures 1, 2 and 5 upwards to a spray tube 31 which is associated with the two disc sets 21, 22 and the belt 23.
  • a check valve 34 is arranged, which closes 29 to the branch 29 out.
  • a spray tube 32 which is associated, for example, a transmission cooling.
  • an electromagnetically actuated proportional valve 33 with an open position and a closed position arranged.
  • the proportional valve 33 is biased by a symbolically indicated spring in its closed position.
  • the pressure actuator 16 conveys on its pressure side, that is to say in FIG. 1 above, into the contact pressure chambers 17, 19 of the pulley sets 21, 22.
  • the pressure actuator 16 is pretensioned by the cooling oil pump 14.
  • the adjustment takes place via separate adjusting chambers 18, 20 on the pulley sets 21, 22.
  • the adjusting actuator 15 is hydraulically connected between the adjusting chambers 18, 20 and, in the event of a variator adjustment, conveys volume flow between the adjusting chambers 18, 20 to the desired pressure levels.
  • the adjustment actuator as shown in FIG. 2, is additionally equipped with a two-pressure valve 37.
  • the two-pressure valve 37 shown in Figure 2 is connected via two connections with branches 35, 36. Between the branches 35 and 36 of the Verstellaktor 16 is arranged.
  • the branch 35 is connected via a fluid line to the adjustment chamber 18 of the first pulley set 21.
  • the branch 36 is connected via a fluid line to the adjustment chamber 20 of the second pulley set 22.
  • the pilot-operated check valve 25 advantageously prevents a rapid pressure drop in the pressure chambers 17, 19.
  • the contact pressure can also be effected via the permanently driven fluid pump 13.
  • Figures 3 and 4 is missing in Figures 1, 2 and 5 designated 16 Anpressaktor.
  • the permanently driven fluid pump 13 provides a system pressure for a fluid control 41. The pressure is applied by triggering speaking valves in the fluid control 41. The adjustment is analogous to the preferred variant, which is shown in Figure 1.
  • FIG. 4 shows that the adjusting actuator 15 from FIG. 3 can also be assigned a two-pressure valve 47.
  • the two-pressure valve 47 is connected to two branches 45,
  • the two-pressure valve 47 like the two-pressure valve 37 in FIG. 2, has a tank connection.
  • the first pulley set 21 has a double piston.
  • the pulley set 22 is equipped with a single piston with a working chamber 51.
  • the working space 51 is connected via a branch 50 to the pressure chamber 17 of the first pulley set 21 and to the adjusting actuator 15.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

L'invention concerne un dispositif fluidique (81) destiné à une transmission à courroie variable continue (2) et comprenant au moins une pompe à fluide (11, 12, 13) entraînée par un moteur électrique pour presser et/ou régler un variateur (3) de la transmission à courroie variable continue (2) qui comporte un premier ensemble de poulies (21) et un deuxième ensemble de poulies (22) qui sont reliés entre eux par un moyen à courroie (23) pour la transmission de couple. Pour augmenter la sécurité pendant le fonction d'une transmission à courroie variable continue, l'un au moins des ensembles de poulies (21, 22) comprend au moins une chambre de réglage (18, 20) et une chambre de pression (17, 19) pour présenter un principe de double piston.
PCT/DE2019/100067 2018-04-12 2019-01-23 Dispositif fluidique pour transmission à courroie variable continue WO2019196971A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112019001862.0T DE112019001862A5 (de) 2018-04-12 2019-01-23 Fluidanordnung für ein stufenlos verstellbares Umschlingungsgetriebe
CN201980010579.0A CN111801519A (zh) 2018-04-12 2019-01-23 用于可无级调节皮带传动装置的流体装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018108712.8 2018-04-12
DE102018108712.8A DE102018108712A1 (de) 2018-04-12 2018-04-12 Fluidanordnung

Publications (1)

Publication Number Publication Date
WO2019196971A1 true WO2019196971A1 (fr) 2019-10-17

Family

ID=65493768

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2019/100067 WO2019196971A1 (fr) 2018-04-12 2019-01-23 Dispositif fluidique pour transmission à courroie variable continue

Country Status (3)

Country Link
CN (1) CN111801519A (fr)
DE (2) DE102018108712A1 (fr)
WO (1) WO2019196971A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1043880B1 (en) * 2020-12-24 2022-07-20 Bosch Gmbh Robert Hydraulically actuated continuously variable transmission for an electric vehicle

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19900852A1 (de) * 1998-01-16 1999-07-22 Atlas Fahrzeugtechnik Gmbh Getriebe mit einer Einrichtung zur Betätigung des Drehmomentenübertragungssystems und der Getriebebetätigungselemente
US6219608B1 (en) 1998-12-25 2001-04-17 Nissan Motor Co., Ltd. Electronic transmission control system for automotive vehicle with continuously variable automatic transmission
EP1253353A2 (fr) * 2001-04-27 2002-10-30 JATCO Ltd Transmission à variation continue de type à courroie
US20030047410A1 (en) * 2001-09-07 2003-03-13 Zf Sachs Ag Clutch system
WO2015067259A1 (fr) * 2013-11-08 2015-05-14 Schaeffler Technologies AG & Co. KG Ensemble fluidique
DE102015215604A1 (de) * 2015-08-17 2017-02-23 Schaeffler Technologies AG & Co. KG Stufenlos verstellbares Getriebe (CVT) mit elektronischem Drehmomentfühler, Antriebstrang und Verfahren zum Steuern / Regeln eines stufenlosen Getriebes

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19909348A1 (de) * 1998-03-19 1999-09-23 Luk Getriebe Systeme Gmbh Drehmomentfühler
WO2006016797A1 (fr) * 2004-08-13 2006-02-16 Robert Bosch Gmbh Boite de vitesses a variation continue equipee d'un ensemble de pompes hydrauliques
NL1039930C2 (en) * 2012-12-06 2014-06-10 Bosch Gmbh Robert Hydraulically actuated continously variable transmission for a vehicular drive line provided with an internal combustion engine.
JP2017072194A (ja) * 2015-10-07 2017-04-13 ジヤトコ株式会社 自動変速機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19900852A1 (de) * 1998-01-16 1999-07-22 Atlas Fahrzeugtechnik Gmbh Getriebe mit einer Einrichtung zur Betätigung des Drehmomentenübertragungssystems und der Getriebebetätigungselemente
US6219608B1 (en) 1998-12-25 2001-04-17 Nissan Motor Co., Ltd. Electronic transmission control system for automotive vehicle with continuously variable automatic transmission
EP1253353A2 (fr) * 2001-04-27 2002-10-30 JATCO Ltd Transmission à variation continue de type à courroie
US20030047410A1 (en) * 2001-09-07 2003-03-13 Zf Sachs Ag Clutch system
WO2015067259A1 (fr) * 2013-11-08 2015-05-14 Schaeffler Technologies AG & Co. KG Ensemble fluidique
DE102015215604A1 (de) * 2015-08-17 2017-02-23 Schaeffler Technologies AG & Co. KG Stufenlos verstellbares Getriebe (CVT) mit elektronischem Drehmomentfühler, Antriebstrang und Verfahren zum Steuern / Regeln eines stufenlosen Getriebes

Also Published As

Publication number Publication date
DE102018108712A1 (de) 2019-10-17
DE112019001862A5 (de) 2020-12-31
CN111801519A (zh) 2020-10-20

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