CN110848325A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN110848325A CN110848325A CN201910665094.7A CN201910665094A CN110848325A CN 110848325 A CN110848325 A CN 110848325A CN 201910665094 A CN201910665094 A CN 201910665094A CN 110848325 A CN110848325 A CN 110848325A
- Authority
- CN
- China
- Prior art keywords
- housing
- output part
- input part
- torsional vibration
- vibration damper
- 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.)
- Granted
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/13114—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by modifications for auxiliary purposes, e.g. provision of a timing mark
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/139—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by friction-damping 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
Abstract
The invention relates to a torsional vibration damper (1) having an input part (2), an output part (3) and a spring damping device (12) comprising a spring element (13), wherein the input part and the output part are arranged so as to be rotatable relative to one another, wherein the input part is rotatable relative to the output part in a defined rotational angle range against a restoring force of a spring element of the spring damping device, wherein a disk spring diaphragm (15) is provided, which is connected to the output part in a radially inner manner in a sealing manner and which bears axially against the input part in a radially outer manner, wherein the input part has a first housing (10) which is directed radially inward to the output part and against which the cup spring diaphragm bears axially, the first housing of the input part is formed radially inwardly in an axial pot-like manner towards the output part.
Description
Technical Field
The invention relates to a torsional vibration damper, in particular for a drive train of a motor vehicle.
Background
Various torsional vibration dampers are known in the prior art, for example as dual-mass flywheels, as dual-clutch dampers or clutch disc dampers. Torsional vibration dampers typically have an input member and an output member, wherein spring damper devices are typically provided in the torque flow between the input member and the output member, which spring damper devices transmit torque between the input member and the output member. The spring damper device in this case damps, for example, torsional vibrations from the drive machine which are present on the input side. In order to seal the inner space of the torsional vibration damper from the outer space, a disk spring diaphragm is optionally provided, which is fastened radially inside to the output part and bears elastically in the axial direction against the input part.
During transport or during installation or removal of the torsional vibration damper, it can happen that the input part moves undesirably quickly relative to the output part and thus damages the disk spring diaphragm, for example if the torsional vibration damper is dropped.
Disclosure of Invention
The object of the present invention is to provide a torsional vibration damper which is improved over the prior art and which protects the disk spring diaphragm better.
The object of the invention is achieved by the features of claim 1.
One embodiment of the invention relates to a torsional vibration damper having an input part, an output part and a spring damping device comprising a spring element, wherein the input part and the output part are arranged so as to be rotatable relative to one another, wherein the input part is rotatable relative to the output part in a defined rotational angle range against a restoring force of a spring element of the spring damping device, wherein a disk spring diaphragm is provided, which is connected to the output part in a radially inner manner in a sealing manner and which bears axially against the input part in a radially outer manner, wherein the input part has a first housing which is directed radially inward to the output part and the cup spring diaphragm bears axially against the first housing of the input part, wherein the first housing of the input part is embodied radially inwardly in the axial direction in the form of a basin (getopft) toward the output part. This is achieved by the basin shape, which defines the available path between the input and output members. This prevents the input part from moving more than desired in the axial and radial directions relative to the output part, for example when the torsional vibration damper is dropped. Damage caused in this respect can thus be prevented.
In one embodiment, it is also expedient for the pot-shaped region of the first housing of the input part to be axially opposite the output part, and for an axial gap to remain between the pot-shaped region of the first housing of the input part and the output part. The axial play defined thereby limits the permissible axial displacement of the input part relative to the output part or the output part relative to the input part, in order to avoid damage.
In a further embodiment, it is also advantageous if the output part has a second housing shell which extends radially outward, wherein the radially inner end of the basin-shaped region of the first housing shell of the input part is opposite the radially outer portion of the output part, and a radial gap remains between the basin-shaped region of the first housing shell of the input part and the output part. The radial play defined thereby limits the permissible radial displacement of the input part relative to the output part or the output part relative to the input part in order to avoid damage.
It is also advantageous if the output part has a hub and a flange, wherein the output part optionally also has a second housing which is connected to the hub and/or to the flange and extends radially outward. This makes it possible to provide a simple and space-optimized output component.
In a further embodiment, it is also advantageous if the pot-shaped region of the first housing of the input part is axially opposite the flange, the hub and/or the second housing of the output part, and an axial gap remains between the pot-shaped region of the first housing of the input part and the flange, the hub and/or the second housing of the output part. The axial play defined thereby limits the permissible axial displacement of the input part relative to the output part or the output part relative to the input part, in order to avoid damage.
It is also advantageous if the radially inner end of the pot-shaped region of the first housing of the input part is opposite the radially outer part of the flange, hub and/or second housing of the output part, and a radial gap remains between the pot-shaped region of the first housing of the input part and the flange, hub and/or second housing of the output part. The radial play defined thereby limits the permissible axial displacement of the input part relative to the output part or the output part relative to the input part, in order to avoid damage.
It is particularly advantageous if the axial play is smaller than the wall thickness of the first housing. The axial play thus dimensioned limits the permissible axial displacement of the input part relative to the output part or the output part relative to the input part, in order to avoid damage.
It is also advantageous if the radial gap is smaller than the wall thickness of the first housing and/or the wall thickness of the second housing. The radial play thus dimensioned limits the permissible radial displacement of the input part relative to the output part or the output part relative to the input part, in order to avoid damage.
Drawings
The invention will be explained in more detail below on the basis of preferred embodiments and with reference to the drawings in which:
to this end, it is shown that:
FIG. 1, subfigure (a), shows a schematic half-sectional view of a first embodiment of a torsional vibration damper according to the invention, an
Sub-diagram (b) of fig. 1 shows an enlarged detail of a schematic partial sectional view of the torsional vibration damper according to sub-diagram (a) of fig. 1.
Detailed Description
Subfigure (a) of fig. 1 shows a torsional vibration damper 1 in a half-sectional view, which can be designed, for example, as a dual-mass flywheel. The torsional vibration damper 1 is configured to be rotatable about an axis x-x. The torsional vibration damper 1 has an input member 2 and an output member 3. The input part 2 can be configured, for example, as a primary flywheel mass and the output part 3 can be configured here as a secondary flywheel mass. Sub-diagram (b) of fig. 1 shows an enlarged detail of the torsional vibration damper 1.
The input part 2 can be connected, for example screwed, to a shaft of an internal combustion engine or a transmission or the like. In this case, the input part 2 can have a threaded bore 4 in the radial interior, through which a bolt 5 can be passed in order to be able to screw the input part 3 on the shaft.
For supporting the bolt head of the bolt 5, a cover plate 6 is optionally arranged, which likewise has an opening for passing the bolt 5.
The torsional vibration damper 1 and its input part 2 and its output part 3 are advantageously configured such that the input part 2 and the output part 3 are arranged rotatably relative to one another.
In this case, the input part 2 has a plate 7 which is formed with a radially oriented arm 8 and an axially oriented arm 9, wherein a first housing 10 is also arranged on the axially oriented arm 9 and is connected to the latter in a rotationally fixed manner, the first housing extending substantially in the radial direction. The first housing 10 is connected radially outside to the arm 9. The arms 8, 9 and the first housing 10 form a recess 11 for a spring damping device 12, which has a spring element 13, which is arranged in the recess 11. In this case, the spring element 13 is supported in the circumferential direction and optionally in the radial direction on the recess 11 or the projections of the arms 8, 9 and/or the first housing 10.
Due to the design of the spring damper 12 with the spring element 13, the input part 2 is designed to be rotatable relative to the input part 3 in a defined rotational angle range against the restoring force of the spring element 13 of the spring damper 12. Here, the flange 14 engages in the radially inner portion of the recess 11 and acts upon the spring element 13 of the spring absorber device 12. Here, the flange 14 is part of the output part 3.
In order to seal the interior of the recess 11, a disk spring diaphragm 15 is provided, which is connected radially on the inside, in particular hermetically, to the output part 3 and which bears axially on the radially outside against the input part 2. The torsional vibration damper 1 is preferably filled with a lubricant, such as a lubricating oil or grease, in the region of the recess 11. For sealing purposes, a disk spring diaphragm 15 is provided.
According to fig. 1, subfigure (a), the disk spring diaphragm 15 is connected radially inside to a hub 16, which forms the output part 3 at least in part with the flange 14. In an advantageous embodiment, the output part has a hub 16, a flange 14 and optionally a second housing 17 which is connected to the hub 16 and/or to the flange 14 and which itself extends radially outward. The connection of the hub 16, the flange 14 and, if appropriate, the second housing 17 is, for example, a rivet connection, see the illustrated rivet connection element 18.
According to the concept according to the invention, it is advantageous if the first housing 10 reaches radially inward to the output part 3, see sub-drawing (a) of fig. 1. The cup spring diaphragm 15 bears axially against the first housing 10 of the input part 2.
Fig. 1, subfigure (a), also shows that the first housing 10 of the input part 2 is formed radially inside in the form of a basin in the axial direction toward the output part 3. This is clearly seen in subfigure (b) of fig. 1. Here, a basin-shaped region 20 of the first housing 10, which is bent forward toward the output part 3, is seen radially inward.
In this case, the pot-shaped region 20 of the first housing 10 of the input part 2 is axially opposite the output part 3, and an axial gap 19 remains between the pot-shaped region 20 of the first housing 10 of the input part 2 and the output part 3.
As can also be seen in fig. 1, subfigure (a), the output part 3 has a second housing 17 which extends radially outward, wherein the radially inner end of the pot-shaped region 20 of the first housing 10 of the input part 2 is radially opposite the output part 3, and a radial gap 21 remains between the pot-shaped region 20 of the first housing 10 of the input part 2 and the output part 3. In total, an axial gap 19 and a radial gap 21 are thereby formed between the input part 2 and the output part 3 in the region of the basin region 20.
It is also advantageous if the pot-shaped region 20 of the first housing shell 10 of the input part 2 is axially opposite the flange 14, the hub 16 and/or the second housing shell 17 of the output part 3, and an axial gap 19 is left between the pot-shaped region 20 of the first housing shell 10 of the input part 2 and the flange 14, the hub 16 and/or the second housing shell 17 of the output part 3.
It is also advantageous if the radially inner end of the pot-shaped region 20 of the first housing shell 10 of the input part 2 is diametrically opposed to the flange 14, the hub 16 and/or the second housing shell 17 of the output part 3, and a radial gap 21 is left between the pot-shaped region 20 of the first housing shell 10 of the input part 2 and the flange 14, the hub 16 and/or the second housing shell 17 of the output part 3.
The axial gap 19 is preferably smaller than the wall thickness d of the first housing 10. The radial gap 21 is preferably smaller than the wall thickness D of the first housing 10 and/or the wall thickness D of the second housing 17.
The output part 3 has a toothing 22 on the radial inside, for example for receiving a shaft.
List of reference numerals
1 torsional vibration damper
2 input part
3 output part
4 threaded hole
5 bolt
6 cover sheet
7 plate
8 radially oriented arms
9 axially oriented support arm
10 first cover
11 recess
12 spring damping device
13 spring element
14 Flange
15 disc spring diaphragm
16 disc hub
17 second cover
18 riveting element
19 axial clearance
20 basin-shaped region
21 radial clearance
22 tooth system
Claims (8)
1. A torsional vibration damper (1) having an input part (2), an output part (3) and a spring damping device (12) comprising a spring element (13), wherein the input part (2) and the output part (3) are arranged so as to be rotatable relative to one another, wherein the input part (2) is rotatable relative to the output part (3) in a defined rotational angle range counter to a restoring force of the spring element (13) of the spring damping device (12), wherein a disk spring diaphragm (15) is provided which is connected to the output part (3) in a radially inner manner in a sealing manner and which bears axially on the radially outer portion against the input part (2), wherein the input part (2) has a first housing (10), the first housing shell reaches radially inward to the output part (3), and the cup spring diaphragm (15) bears axially against the first housing shell (10) of the input part (2), characterized in that the first housing shell (10) of the input part (2) is formed axially pot-shaped radially inward to the output part (3).
2. A torsional vibration damper (1) according to claim 1, characterized in that the basin-shaped region (20) of the first housing (10) of the input part (2) is axially opposite to the output part (3) and an axial gap (19) remains between the basin-shaped region (20) of the first housing (10) of the input part (2) and the output part (3).
3. The torsional vibration damper (1) as claimed in claim 1 or 2, characterized in that the output part (3) has a second housing shell (17) which extends radially outwards, wherein the radially inner end of the basin-shaped region (20) of the first housing shell (10) of the input part (2) is opposite the radially outer portion of the output part (3), and a radial gap (3) remains between the basin-shaped region (20) of the first housing shell (10) of the input part (2) and the output part (3).
4. The torsional vibration damper (1) as claimed in claim 1, 2 or 3, characterized in that the output part (3) has a hub (16) and a flange (14), wherein the output part (3) optionally also has a second housing (17) which is connected to the hub (16) and/or to the flange (14) and extends radially outward.
5. The torsional vibration damper (1) as claimed in claim 1, 2, 3 or 4, characterized in that the tub-shaped region (20) of the first housing (10) of the input part (2) is axially opposite the flange (14), hub (16) and/or second housing (17) of the output part (3) and an axial gap (19) remains between the tub-shaped region (20) of the first housing (10) of the input part (2) and the flange (14), hub (16) and/or second housing (17) of the output part (3).
6. The torsional vibration damper (1) as claimed in claim 4 or 5, characterized in that a radially inner end of the basin-shaped region (20) of the first housing (10) of the input part (2) is opposite a radially outer portion of the flange (14), hub (16) and/or second housing (17) of the output part (3), and a radial gap (21) remains between the basin-shaped region (20) of the first housing (10) of the input part (2) and the flange (14), hub (16) and/or second housing (17) of the output part (3).
7. The torsional vibration damper (1) as claimed in any of claims 1 to 6, characterized in that the axial gap (19) is smaller than a wall thickness of the first housing shell (10).
8. The torsional vibration damper (1) as claimed in any of claims 1 to 7, characterized in that the radial gap (21) is smaller than a wall thickness of the first housing shell (10) and/or a wall thickness of the second housing shell (17).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102018120260.1 | 2018-08-21 | ||
| DE102018120260.1A DE102018120260A1 (en) | 2018-08-21 | 2018-08-21 | torsional vibration dampers |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110848325A true CN110848325A (en) | 2020-02-28 |
| CN110848325B CN110848325B (en) | 2022-12-20 |
Family
ID=69412915
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910665094.7A Active CN110848325B (en) | 2018-08-21 | 2019-07-23 | Torsional vibration damper |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN110848325B (en) |
| DE (1) | DE102018120260A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113898699A (en) * | 2021-09-29 | 2022-01-07 | 舍弗勒技术股份两合公司 | Dual mass flywheel |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000283238A (en) * | 1999-03-29 | 2000-10-13 | Suzuki Motor Corp | Secondary balancer device of engine |
| DE3745090C2 (en) * | 1986-07-05 | 2002-03-07 | Luk Lamellen & Kupplungsbau | Flywheel with torsional vibration damping |
| CN1955507A (en) * | 2005-10-29 | 2007-05-02 | 卢克摩擦片和离合器两合公司 | Vibration reduction device for torsion vibration |
| CN101169171A (en) * | 2006-10-26 | 2008-04-30 | 卢克摩擦片和离合器两合公司 | Torsional vibration damper |
| CN101300435A (en) * | 2005-11-04 | 2008-11-05 | 博格华纳公司 | Torsional-vibration damper connected to a crankshaft and a combination of a torsional-vibration damper and a clutch |
| CN103502682A (en) * | 2011-03-08 | 2014-01-08 | 离合器实业有限公司 | Friction clutch plate with damping springs |
| CN107532678A (en) * | 2015-05-20 | 2018-01-02 | 舍弗勒技术股份两合公司 | Torsional vibration damper and hybrid drive train |
-
2018
- 2018-08-21 DE DE102018120260.1A patent/DE102018120260A1/en active Pending
-
2019
- 2019-07-23 CN CN201910665094.7A patent/CN110848325B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3745090C2 (en) * | 1986-07-05 | 2002-03-07 | Luk Lamellen & Kupplungsbau | Flywheel with torsional vibration damping |
| JP2000283238A (en) * | 1999-03-29 | 2000-10-13 | Suzuki Motor Corp | Secondary balancer device of engine |
| CN1955507A (en) * | 2005-10-29 | 2007-05-02 | 卢克摩擦片和离合器两合公司 | Vibration reduction device for torsion vibration |
| CN101300435A (en) * | 2005-11-04 | 2008-11-05 | 博格华纳公司 | Torsional-vibration damper connected to a crankshaft and a combination of a torsional-vibration damper and a clutch |
| CN101169171A (en) * | 2006-10-26 | 2008-04-30 | 卢克摩擦片和离合器两合公司 | Torsional vibration damper |
| CN103502682A (en) * | 2011-03-08 | 2014-01-08 | 离合器实业有限公司 | Friction clutch plate with damping springs |
| CN107532678A (en) * | 2015-05-20 | 2018-01-02 | 舍弗勒技术股份两合公司 | Torsional vibration damper and hybrid drive train |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113898699A (en) * | 2021-09-29 | 2022-01-07 | 舍弗勒技术股份两合公司 | Dual mass flywheel |
| CN113898699B (en) * | 2021-09-29 | 2023-10-27 | 舍弗勒技术股份两合公司 | Dual mass flywheel |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102018120260A1 (en) | 2020-02-27 |
| CN110848325B (en) | 2022-12-20 |
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