CN112762140A - Dual mass flywheel with pressed-in flexplates - Google Patents
Dual mass flywheel with pressed-in flexplates Download PDFInfo
- Publication number
- CN112762140A CN112762140A CN202011111275.4A CN202011111275A CN112762140A CN 112762140 A CN112762140 A CN 112762140A CN 202011111275 A CN202011111275 A CN 202011111275A CN 112762140 A CN112762140 A CN 112762140A
- Authority
- CN
- China
- Prior art keywords
- primary
- mass flywheel
- flange
- cover
- shaped region
- 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.)
- Pending
Links
- 230000009977 dual effect Effects 0.000 title claims abstract description 26
- 238000010276 construction Methods 0.000 abstract 1
- 239000007858 starting material Substances 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000003466 welding Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
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
- F16F15/13142—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 the method of assembly, production or treatment
- F16F15/1315—Multi-part primary or secondary masses, e.g. assembled from pieces of sheet steel
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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
- F16F15/30—Flywheels
-
- 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
- F16F15/30—Flywheels
- F16F15/315—Flywheels characterised by their supporting arrangement, e.g. mountings, cages, securing inertia member to shaft
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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
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Manufacturing & Machinery (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a dual mass flywheel (1) having pressed-in flexplates, having a primary side (2) and a secondary side (3) which can be rotated in a limited manner relative to one another against the force of an energy store (4), wherein the primary side (2) comprises a primary cover (6) and a rotationally fixed and axially elastic primary flange (5), in which case the axial construction dimension is reduced by fastening the primary flange (5) to the primary cover (6).
Description
Technical Field
The invention relates to a dual mass flywheel having a primary side and a secondary side which can be rotated in a limited manner relative to one another against the force of an energy store, wherein the primary side comprises a primary cover and a rotationally fixed and axially elastic primary flange.
Background
Dual-mass flywheels are used in the drive train of a motor vehicle as dampers against torsional vibrations, wherein a dual-mass flywheel is usually arranged between the crankshaft of an internal combustion engine driving the motor vehicle and a vehicle clutch or an auxiliary drive upstream of a transmission. Torsional vibrations caused by the uneven drive torque of an internal combustion engine, which is usually embodied as a piston engine, are eliminated by the primary mass part and the secondary mass part being able to rotate relative to one another counter to the spring force and, if necessary, also counter to dry friction. The primary mass part of a dual mass flywheel is designed in the prior art in multiple parts in generic dual mass flywheels and comprises a primary mass cover and a primary mass metal plate which are welded to one another. The primary mass plate comprises a primary disc which is firmly riveted to an axially flexible primary flange, a so-called flexplate. The flexplate, optionally together with further components, such as a centering hub for the secondary side, is screwed to the crankshaft.
Such a flexible plate mostly comprises a plurality of metal plate layers riveted to the primary disc.
In wet DCT (Dual Clutch Transmission) and hybrid applications, only axially narrow installation space is usually available.
Disclosure of Invention
The aim of the invention is therefore to reduce the axial dimensions of the structure.
This object is achieved by a dual mass flywheel according to claim 1. Preferred embodiments, embodiments or improvements of the invention are specified in the dependent claims.
The above-mentioned problem is solved in particular by a dual mass flywheel as follows: it has a primary side and a secondary side which can be rotated in a limited manner relative to one another against the force of the energy store, wherein the primary side comprises a primary cover and a rotationally fixed and axially elastic primary flange, wherein the primary flange is (directly) fastened to the primary cover. Instead of riveting the flexplate to the primary disk which is subsequently welded to the primary mass cover, the primary flange corresponding to the flexplate is connected directly to the primary cover in a friction-locked (reibschlussing), form-locked (formschlussig) or material-locked (stoffschlussig) manner.
The solution according to the invention improves the rotational bending fatigue strength (biegoumlausetigkeit), especially in wet DCT and hybrid applications. Furthermore, costs are reduced by using thinner raw materials for the primary flywheel mass, and the splash seal is improved.
The primary flange preferably does not have a primary staking hole.
The energy store is preferably an arc spring which is supported on at least one arc spring stop on the primary side and on at least one flange limb on the secondary side. Preferably, the primary flange contacts the arcuate spring on a side facing the crankshaft, and correspondingly the primary cover contacts the arcuate spring on a side facing away from the crankshaft. In an embodiment of the invention, at least one flange wing contacts the arc spring axially non-centrally and biased towards the crankshaft. The arc-shaped spring stop is designed axially higher in the embodiment of the invention than in the embodiment according to the prior art. Thus, the arcuate spring stop on the primary flange may be dispensed with.
In one embodiment of the invention, the primary flange comprises a substantially radially extending dished region and a substantially axially extending pot-shaped region.
In one embodiment of the invention, the pot-shaped region is fixed to the primary cap by caulking in an axially positive manner.
In one embodiment of the invention, the pot-shaped region is fixed to the primary cover by a weld seam.
In one embodiment of the invention, the pot-shaped region comprises a collar which rests against the end face of the primary cap. The rim may be axially welded.
In one embodiment of the invention, the end face comprises an at least partially circumferential centering ring, by means of which the primary flange is centered relative to the primary cover, which simplifies centering during welding.
In one embodiment of the invention, the primary flange comprises a rim surrounding the primary lid. The collar centers the primary flange relative to the primary cover and enables an outer circumferential weld seam.
In one embodiment of the invention, the substantially axially extending pot-shaped region of the primary flange rests with its axial edge on the primary mass cover. This enables the primary flange to be pressed in until it comes to a stop on the primary mass cover.
In one embodiment of the invention, the primary flange comprises a concavely shaped region for accommodating the arcuate springs of the energy store.
In one embodiment of the invention, the primary cap has a stop which limits the axial travel of the primary side to the secondary side.
Drawings
Embodiments of the invention are subsequently explained in detail with reference to the drawings. Here:
FIG. 1 illustrates, in cross-section, a first embodiment of a dual mass flywheel according to the present invention;
FIG. 2 illustrates, in cross-section, a portion of a second embodiment of a dual mass flywheel in accordance with the present invention;
FIG. 3 illustrates, in cross-section, a portion of a third embodiment of a dual mass flywheel in accordance with the present invention;
FIG. 4 illustrates, in cross-section, a portion of a fourth embodiment of a dual mass flywheel in accordance with the present invention;
FIG. 5 illustrates, in cross-section, a portion of a fifth embodiment of a dual mass flywheel in accordance with the present invention;
FIG. 6 shows, in cross-section, a portion of a sixth embodiment of a dual mass flywheel according to the invention;
FIG. 7 illustrates, in cross-section, a portion of a seventh embodiment of a dual mass flywheel in accordance with the present invention;
FIG. 8 shows, in cross-section, a portion of an eighth embodiment of a dual mass flywheel in accordance with the invention;
FIG. 9 illustrates, in cross-section, a portion of a ninth embodiment of a dual mass flywheel in accordance with the present invention;
fig. 10 shows a part of a tenth embodiment of a dual mass flywheel according to the invention in a sectional view.
Detailed Description
Fig. 1 shows an embodiment of a dual mass flywheel 1 according to the invention. Such a dual mass flywheel 1 is arranged in the drive train of a motor vehicle between the crankshaft of the internal combustion engine and the auxiliary drive or vehicle clutch. The axis of rotation of the dual mass flywheel is indicated by R in fig. 1. The axis of rotation R is the axis about which the dual mass flywheel 1 is rotatably mounted in the mounted position. Subsequently, the axial direction is understood as a direction parallel to the rotation axis R, the radial direction is understood as a direction perpendicular to the rotation axis R, and the circumferential direction is understood as one turn around the rotation axis R.
The dual mass flywheel 1 comprises a primary side 2 and a secondary side 3 which can be twisted relative to one another about an axis of rotation R, in a limited manner, against the force of an arc-shaped spring 4 as an energy store.
The primary side 2 comprises a torsion-resistant and axially elastic primary flange 5 and a primary cover 6. The primary flange 5 and the primary cover 6 enclose an arcuate spring receptacle 7 in which the arcuate spring 4 is arranged. The arcuate spring 4 is supported at all times with one spring end on the primary side 2, for example on an arcuate spring stop 8 shown in fig. 2 to 10, but provided with reference numerals only in fig. 2, which is arranged on the primary cover 6. The arcuate springs 4 are supported with their respective other spring ends on flange limbs of the secondary flange 10. The flange wing 10 does not contact the arc spring centrally, but is biased axially towards the crankshaft. The curved spring stop 8 is designed axially higher than the embodiments according to the prior art. No arcuate spring stop is arranged on the primary flange 5. The flange wings 9 extend radially outwards and enclose the spring ends of the arcuate springs 4. The bow spring 4 is pressed outwards during operation by the centrifugal force acting on the bow spring. Optionally, therefore, a sliding housing 9 is arranged on the radially outer side on the primary flange 5 or the primary cover 6, which reduces the wear between the arcuate springs and the primary side 2.
The secondary flange 10 is provided with a centrifugal pendulum device 11, wherein a plurality of pendulum masses 12 distributed over the circumference are mounted so as to be able to move in an oscillating manner relative to the secondary flange 10. The output hub 13 is riveted to the secondary flange 10 by means of rivets 14 and is connected to the output shaft 16 by means of a plug-in engagement 15. The disk spring diaphragm 17 is fastened to the secondary flange by riveting the output hub 13 to the secondary flange 10 and is supported by the radially outer region on the primary cover 6, in order thus to seal the receiving space for the bow spring 4 and the centrifugal force pendulum device 11 from the surroundings together with a sealing ring 18 which is arranged radially outside the crankshaft thread on the inner diameter of the secondary flange 10. The primary cover 6 projects radially inward so that it covers the outer edge of the output hub 13 and thus forms an axial stop 19.
Fig. 1 to 6 show an embodiment with a starter ring gear 20, and fig. 6 to 10 show an embodiment without a starter ring gear 20. Different variants of the connection of the primary flange 5 and the secondary flange 6 are shown subsequently.
The primary flange 5 comprises in fig. 1, 2, 3, 4, 5, 6, 7 and 10 a substantially radially extending disc-shaped region 21 and a substantially axially extending pot-shaped region 22. The disk-shaped region 21 provides axial flexibility of the primary flange 5 and serves for fastening to a crankshaft 23 of an internal combustion engine, as shown in fig. 1. For this purpose, the primary flange 5 can be fastened to the crankshaft 23 by means of crankshaft screws 24 and a fastening ring 25 (which can be firmly connected to the primary flange 5 if necessary).
The pot-shaped region 22 of the primary flange 5 rests with its outer periphery against the inner diameter of the cylindrical part 26 of the primary cover 6. For axial securing against the pot-shaped region 22 being pulled out of the cylinder part 26, the cylinder part has in the embodiment of fig. 2 a caulking 27. Alternatively, as shown in fig. 3, the caulking can be replaced by a circumferential or partially circumferential weld seam 28, in particular made by laser welding.
Fig. 4 shows an alternative embodiment, in which the disk-shaped region 21 is concavely shaped in the radially outer region of the arcuate spring 4 and convexly merges into a pot-shaped region 22, which rests on the cylindrical part 26 of the primary cap 6 and merges into a collar 29, which rests on an end face 30 of the primary cap 6.
As shown in fig. 5, the pot-shaped region 22 can rest with its axial edge 31 on the primary cap 6.
Fig. 6 shows an embodiment without a starter ring gear, in which the primary flange 5 with the pot-shaped region 22 is pressed into the cylindrical part 26 of the primary cap 6, i.e. there is only a friction-locking connection in the axial direction and in the peripheral direction.
Fig. 7 shows an embodiment without a starter ring gear, in which, as in the embodiment of fig. 2, an axial caulking 27 is introduced into the primary cap 6.
Fig. 8 shows a further exemplary embodiment, in which the primary flange 5 has a circumferential concave bulge 32 in the region of the arcuate spring 4 and is welded on its outer circumference to the end face 30 of the primary cover 6 by means of a circumferential laser weld seam 33. In order to center the primary flange 5 relative to the primary cover 6 during welding, the primary cover 6 has an at least partially circumferential centering ring 34 on the end face 30. Alternatively, as in the embodiment of fig. 9, the centering ring 34 may be dispensed with.
Fig. 10 shows a further exemplary embodiment, in which the primary flange 5 comprises a collar 35, which on the end face of the primary cap surrounds the primary cap 6 and is welded to the latter by a circumferential laser weld 36 on the outside.
List of reference numerals
1 dual mass flywheel
2 primary side
3 secondary side
4 arc spring
5 Primary flange
6 Primary cover
7 arc spring containing part
8 arc spring stop
9 Flange wing part
11 centrifugal pendulum device
12 pendulum mass
13 output hub
14 rivet
15 mating engagement portion
16 output shaft
17 disc spring diaphragm
18 sealing ring
19 axial stop
20 starter ring gear
21 disc shaped area
22 pot shaped area
23 crankshaft
24 crankshaft screw
25 fastening ring
26 column part
27 caulking
28 weld seam
29 hoop edge
30 end side
31 axial edge
32 concave bulging part
33 laser weld
34 centering ring
35 hoop edge
36 laser weld
Claims (10)
1. Dual mass flywheel (1) having a primary side (2) and a secondary side (3) which can be rotated in a limited manner relative to one another against the force of an energy store (4), wherein the primary side (2) comprises a primary cover (6) and a rotationally fixed and axially elastic primary flange (5), characterized in that the primary flange (5) is fastened to the primary cover (6).
2. A twin mass flywheel as defined in claim 1 in which the primary flange (5) comprises a substantially radially extending dished region (21) and a substantially axially extending pot-shaped region (22).
3. A twin mass flywheel as defined in claim 2 in which the pot-shaped region (22) is axially positively secured to the primary cover (6) by caulking (27).
4. A twin mass flywheel as defined in claim 2 in which the pot shaped region (22) is secured to the primary cover (6) by a weld (28).
5. A twin mass flywheel as defined in claim 2 in which the pot-shaped region (22) comprises a rim (29) abutting against an end side (30) of the primary cover (6).
6. A twin mass flywheel as defined in claim 5 in which the end side (30) comprises an at least partially encircling centering ring (34) by means of which the primary flange (5) is centered relative to the primary cover (6).
7. A twin mass flywheel as defined in claim 2 in which the primary flange (5) comprises a rim (35) that surrounds the primary cover (6).
8. A twin mass flywheel as defined in any previous claim in which the substantially axially extending pot-shaped region (22) of the primary flange bears with its axial edge (31) against the primary mass cover.
9. A twin mass flywheel as defined in any previous claim in which the primary flange (5) comprises a concavely shaped region (32) for accommodating the arcuate springs (4) of the accumulator.
10. A twin mass flywheel as defined in any previous claim in which the primary cover (6) has a stop (19) which limits the axial travel of the primary side (2) to the secondary side (3).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102019128346.9 | 2019-10-21 | ||
| DE102019128346.9A DE102019128346A1 (en) | 2019-10-21 | 2019-10-21 | Dual mass flywheel with pressed-in flexplate |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112762140A true CN112762140A (en) | 2021-05-07 |
Family
ID=75268631
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011111275.4A Pending CN112762140A (en) | 2019-10-21 | 2020-10-16 | Dual mass flywheel with pressed-in flexplates |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN112762140A (en) |
| DE (1) | DE102019128346A1 (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 (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE9116571U1 (en) * | 1991-11-06 | 1993-03-25 | J.M. Voith Gmbh, 7920 Heidenheim | Dual mass flywheel for an internal combustion engine |
| US5575183A (en) * | 1992-12-10 | 1996-11-19 | Fichtel & Sachs Ag | Dual-mass flywheel |
| CN2830783Y (en) * | 2005-09-30 | 2006-10-25 | 湖北三环离合器有限公司 | Double-quality flywheel suitable for pulling clutch |
| DE102009038639A1 (en) * | 2008-09-11 | 2010-04-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Primary flywheel for use as stamping part in torsional vibration damper, has sheet provided with regions, where thicknesses of regions are asymmetrically decreased or increased with respect to initial thickness symmetrical to center plane |
| CN203297516U (en) * | 2013-04-28 | 2013-11-20 | 吉林大华机械制造有限公司 | Car and double mass flywheel with vertical welding structure |
| CN106641096A (en) * | 2016-11-29 | 2017-05-10 | 安徽江淮汽车集团股份有限公司 | Dual-mass flywheel matched with CVT gearbox |
| CN106870632A (en) * | 2017-03-21 | 2017-06-20 | 陕西国力信息技术有限公司 | Torsional vibration damper and the engine flywheel with torsional vibration damper |
| CN107869551A (en) * | 2016-09-28 | 2018-04-03 | 南京法雷奥离合器有限公司 | Particularly for the torsion transmitter of motor vehicle |
| CN108240416A (en) * | 2018-01-25 | 2018-07-03 | 海马汽车有限公司 | Torsional vibration damper, flywheel and car transmissions |
-
2019
- 2019-10-21 DE DE102019128346.9A patent/DE102019128346A1/en not_active Withdrawn
-
2020
- 2020-10-16 CN CN202011111275.4A patent/CN112762140A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE9116571U1 (en) * | 1991-11-06 | 1993-03-25 | J.M. Voith Gmbh, 7920 Heidenheim | Dual mass flywheel for an internal combustion engine |
| US5575183A (en) * | 1992-12-10 | 1996-11-19 | Fichtel & Sachs Ag | Dual-mass flywheel |
| CN2830783Y (en) * | 2005-09-30 | 2006-10-25 | 湖北三环离合器有限公司 | Double-quality flywheel suitable for pulling clutch |
| DE102009038639A1 (en) * | 2008-09-11 | 2010-04-15 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Primary flywheel for use as stamping part in torsional vibration damper, has sheet provided with regions, where thicknesses of regions are asymmetrically decreased or increased with respect to initial thickness symmetrical to center plane |
| CN203297516U (en) * | 2013-04-28 | 2013-11-20 | 吉林大华机械制造有限公司 | Car and double mass flywheel with vertical welding structure |
| CN107869551A (en) * | 2016-09-28 | 2018-04-03 | 南京法雷奥离合器有限公司 | Particularly for the torsion transmitter of motor vehicle |
| CN106641096A (en) * | 2016-11-29 | 2017-05-10 | 安徽江淮汽车集团股份有限公司 | Dual-mass flywheel matched with CVT gearbox |
| CN106870632A (en) * | 2017-03-21 | 2017-06-20 | 陕西国力信息技术有限公司 | Torsional vibration damper and the engine flywheel with torsional vibration damper |
| CN108240416A (en) * | 2018-01-25 | 2018-07-03 | 海马汽车有限公司 | Torsional vibration damper, flywheel and car transmissions |
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 |
|---|---|
| DE102019128346A1 (en) | 2021-04-22 |
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| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
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| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20210507 |