EP4176131A1 - Maschine und verfahren mit einem stopfaggregat - Google Patents
Maschine und verfahren mit einem stopfaggregatInfo
- Publication number
- EP4176131A1 EP4176131A1 EP21731088.7A EP21731088A EP4176131A1 EP 4176131 A1 EP4176131 A1 EP 4176131A1 EP 21731088 A EP21731088 A EP 21731088A EP 4176131 A1 EP4176131 A1 EP 4176131A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tamping
- machine
- eccentric
- tamping units
- units
- 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
Links
- 238000000034 method Methods 0.000 title claims description 22
- 230000001360 synchronised effect Effects 0.000 claims description 5
- 230000005484 gravity Effects 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 description 9
- 241001669679 Eleotris Species 0.000 description 8
- 239000011295 pitch Substances 0.000 description 4
- 230000010355 oscillation Effects 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007654 immersion Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 206010000496 acne Diseases 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
- E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
- E01B27/13—Packing sleepers, with or without concurrent work on the track
- E01B27/16—Sleeper-tamping machines
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B27/00—Placing, renewing, working, cleaning, or taking-up the ballast, with or without concurrent work on the track; Devices therefor; Packing sleepers
- E01B27/12—Packing sleepers, with or without concurrent work on the track; Compacting track-carrying ballast
- E01B27/13—Packing sleepers, with or without concurrent work on the track
- E01B27/16—Sleeper-tamping machines
- E01B27/17—Sleeper-tamping machines combined with means for lifting, levelling or slewing the track
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B2203/00—Devices for working the railway-superstructure
- E01B2203/12—Tamping devices
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
- E01B2203/00—Devices for working the railway-superstructure
- E01B2203/12—Tamping devices
- E01B2203/122—Tamping devices for straight track
Definitions
- the invention relates to a machine with a tamping unit for the simultaneous tamping of several sleepers of a track positioned directly one behind the other by means of several tamping units arranged directly behind one another in relation to a machine longitudinal direction, each tamping unit comprising a height-adjustable tool carrier on which opposing tamping tools are stored are coupled to a vibration drive arranged on the tool carrier via auxiliary cylinders.
- the invention also relates to a method for operating the machine.
- tracks with ballast bedding are regularly processed by means of a tamping machine.
- the tamping machine drives along the track and uses a lifting / straightening unit to raise the track grid, which is made up of sleepers and rails, to a target level.
- the new track position is fixed by tamping under the sleepers using a tamping unit.
- the tamping unit comprises tamping tools with tamping tines which, when subjected to a tamping process, dip into the ballast bed and are placed next to each other.
- the ballast is compacted below the respective threshold.
- stretch tamping machines use tamping units for tamping several sleepers at the same time.
- the high processing speed achieved in this way enables a track to be worked through in short breaks.
- Modern tamping machines are also characterized by low wear effects on both the tamping unit and the ballast.
- AT 513034 A1 a generic machine with at least two tamping units arranged one behind the other is known. Each tamping unit is arranged in a height-adjustable manner in a common assembly carrier.
- a tamping cycle begins with the common lowering of the tamping units. This joint lowering of adjoining tamping units for tamping under sleepers that are adjacent in the longitudinal direction of the machine takes place with a time delay. This in particular facilitates the immersion of immediately adjacent tamping tines that immerse into a common threshold compartment.
- the invention is based on the object of improving a machine of the type mentioned at the outset in such a way that, in addition to a reduced wear effect, low noise emissions are achieved.
- the respective vibration drive comprises an eccentric shaft with a first eccentric disk and a second eccentric disk, the axes of symmetry of which span two eccentric planes with a common axis of rotation that enclose a relative angle to one another, a first auxiliary cylinder being mounted on the first eccentric disk, with a second opposite
- the auxiliary cylinder is mounted on the second eccentric disk and the cylinder axes of the opposite auxiliary cylinder enclose a position angle which approximates the relative angle of the eccentric planes.
- the angular positions of the eccentric disks and the auxiliary cylinders are matched to one another in order to achieve a mass balance in the assembly parts that are set in vibration.
- the inertial forces of the synchronously vibrating tamping tools cancel each other out. This means that the tamping unit runs more smoothly.
- the additional cylinders are not aligned horizontally, which means that the
- Relative angle is not equal to 180 °.
- the arrangement according to the invention causes the tamping tools to oscillate optimally in a synchronous counter-blow. Specifically, the vibrations of the two opposite tamping tools are subject to a phase shift that causes the respective reversal points to be reached at the same time. The acceleration and deceleration forces of the vibrating masses of the tamping tools and the vibrating partial masses of the auxiliary cylinders cancel each other out.
- Tamping tines arranged at the lower free ends of the tamping tools swing in opposite directions and synchronously with a maximum relative movement. This results in maximum energy input into the ballast bed without causing the tool carrier and an associated unit suspension to cause disruptive reaction vibrations. This results in a low level of vibration stress on the unit and the machine. This protects both the components of the tamping unit and the ballast grains of the ballast bed to be compacted. Together, the targeted introduction of vibrations into the ballast bed and the mass balancing result in a reduction in noise emissions compared to known designs of tamping units.
- each tamping unit comprises at least one additional cylinder, the cylinder axis of which is oriented obliquely downward, in particular with an angle of inclination greater than 20 ° with respect to a horizontal.
- the respective eccentric shaft is connected to a flywheel.
- the eccentric shaft is driven together with the flywheel at a specified speed.
- the flywheel has a stabilizing effect on the speed. Specifically, the retroactive moments of the auxiliary cylinders and tamping tools set in vibration during an oscillation cycle are compared with the in the Balance mass cached kinetic energy.
- the vibration amplitude of the tamping tools remains independent of the rigidity of the ballast bed.
- the rotation unit formed from the eccentric shaft and the flywheel is designed so that a common center of mass with respect to the axis of rotation lies opposite the axes of symmetry of the two eccentric disks. In this way, the rotation unit acts as a balancing mass for the set in motion mass of the auxiliary cylinders of the opposite tamping tools.
- the tamping unit comprises - in relation to the longitudinal direction of the machine - front and rear tamping units with asymmetrically arranged auxiliary cylinders and middle tamping units with symmetrically arranged auxiliary cylinders.
- the middle tamping units have a particularly narrow design, so that even sleepers with small sleeper spacings can be tamped at the same time.
- the front and rear tamping units also have a narrow design on a half facing the middle tamping units.
- the halves of the front and rear tamping units facing away from the middle tamping units use a wider construction in order to achieve a larger opening width between the opposite tamping tools.
- the front and rear tamping units each have an eccentric shaft with different eccentricities. Different lever ratios of the opposite tamping tools and the different eccentricities are coordinated so that the vibration amplitudes of the freely swinging tamping tine ends are the same.
- the respective opposite tamping tools of the front and rear tamping units are advantageously mounted on the associated tool carrier with vertically spaced pivot bearings.
- the bearings are preferably those facing the middle tamping units
- the tamping tools are located lower in order to achieve a narrower design with the same lever ratio.
- the front and rear tamping units each have a half facing the middle tamping units, which is constructed in accordance with a symmetry half of the middle tamping units. This simplifies the structure of the tamping unit and facilitates the control of the individual tamping units. In addition, the number of different spare parts is reduced.
- the middle tamping units and the halves of the front and rear tamping units facing the middle tamping units are each connected to a first auxiliary pressure system and the halves of the front and rear tamping units facing away from the middle tamping units are each connected to a second auxiliary printing system.
- the different auxiliary pressure systems enable the same static and dynamic ordering forces on all tamping tools.
- Another improvement provides that a half of the respective front or rear tamping unit facing away from the middle tamping units comprises an ordering cylinder with a larger stroke in order to tamp double sleepers. In this way, the tamping unit can be used universally and all sleeper arrangements occurring on a track can be processed.
- the vibration drive and the ordering cylinder of the respective tamping unit are controlled in such a way that the position angle of the auxiliary drives fluctuates in a range around the relative angle of the eccentric planes of the associated eccentric shaft. That way stays during of a stuffing process, the current position angle approximates the relative angle.
- the position angle corresponds to the relative angle.
- the masses of the respective tamping unit, which are set in vibration, then oscillate in opposite directions, synchronously, whereby a mass balance is effected. This minimizes the stress on the unit and the generation of noise.
- each eccentric shaft is driven by means of an associated vibration drive motor and that all vibration drive motors are controlled for synchronous operation by means of a common control device.
- the vibratory movements of the tamping units are coordinated with one another in order to optimize the smoothness of the entire tamping unit.
- the respective eccentric shaft is driven at a variable speed depending on a height position of the associated tamping unit.
- all tamping units are in an initial position above the track. In this position, the speed of the respective eccentric shaft remains reduced in order to further reduce the development of noise. Only when the height position is changed in the course of a lowering process does it increase to a working speed that is greater during an immersion process than during a provision process.
- Another improvement provides that additional groups arranged side by side at right angles to the machine's longitudinal direction are controlled with a common control signal. In this way, a uniform compression process takes place along a threshold.
- the middle tamping units and the halves of the front and rear tamping units facing the middle tamping units are each subjected to a first supply pressure, the halves of the front and rear tamping units facing away from the central tamping units each being subjected to a second supply pressure.
- the different additional pressures enable the same static and dynamic additional forces on all tamping tools.
- Fig. 1 machine with tamping unit
- Fig. 2 tamping unit for the simultaneous tamping of three sleepers in a side view
- FIG. 3 middle tamping unit in side view.
- FIG. 4 kinematics according to FIG. 3
- FIG. 7 kinematics according to FIG. 6
- FIG. 8 kinematics according to FIG. 6 in several working positions.
- the machine 1 shown in FIG. 1 is designed as a track tamping machine for the simultaneous tamping of three sleepers 4 stored in a ballast bed 2 of a track 3.
- the machine 1 comprises a machine frame 6 which is supported on rail bogies 5 and on which a tamping unit 7 is fastened.
- the machine 1 comprises a lifting / straightening unit 8 for lifting and straightening the track grid formed from sleepers 4 and rails 9. A current rail position is recorded with a measuring system 10.
- the tamping unit 7 is fastened to the machine frame 6 by means of an adjusting device 11. It comprises an assembly frame 12 with guides 13 and several tamping units 14. In a variant not shown, each tamping unit 14 is assigned its own assembly frame 12. Each tamping unit 14 comprises a tool carrier 15, the is mounted on the associated guides 13 in a height-adjustable manner by means of a height adjustment drive 16. On the respective tool carrier 15, opposing tamping tools 18 are pivotably mounted in a machine longitudinal direction 17.
- a vibration drive 19 is arranged on the respective tool carrier 15, with which the tamping tools 18 are coupled via auxiliary cylinders 20.
- Each tamping tool 18 comprises a pivot lever 21 with an upper and a lower lever arm.
- the pivot lever 21 is supported by a pivot bearing 22 on the associated tool carrier 15, the upper lever arm being connected to the associated auxiliary cylinder 20.
- Two tamping tines 23 are usually attached to the free lower lever arm.
- the opposing tamping tines 23 of the respective tamping unit 14 are at the same distance from a central vertical plane 24 in an initial position (FIG. 2).
- the distance between the central vertical planes 24 of the tamping units 14 arranged one behind the other corresponds to the smallest sleeper pitch t of the sleepers 4 to be tamped under.
- the dimensioning of the tamping units 14 in the machine longitudinal direction 17 is thus based on this smallest sleeper pitch t.
- a middle tamping unit 14 arranged between a front and a rear tamping unit 14 has a narrow design in the machine longitudinal direction 17. This requirement is achieved by auxiliary cylinders 20 which are oriented obliquely downwards. In the front and rear tamping unit 14, only the half facing the central tamping unit 14 is designed accordingly. The other half has an additional cylinder 20 aligned approximately horizontally. In this way, a larger pivoting range of the associated tamping tool 18 is given.
- the enlargement of the opening width that can be achieved between the opposite tamping tines 23 enables an adaptation to larger sleeper pitches t or to double sleepers to be tamped under.
- FIG. 4 shows a kinematic model of the one in FIG. 3 shown tamping unit 14.
- FIG. 5 the kinematic model 3 is shown in three working positions.
- An eccentric shaft 25 of the vibration drive 19 is mounted on the tool carrier 15. During operation, the eccentric shaft 25 rotates about an axis of rotation 26.
- the eccentric shaft 25 comprises two eccentric disks 27, 28 offset from one another, the axes of symmetry 29, 30 of which have a respective eccentricity ei, b2 with respect to the axis of rotation 26.
- the axes of symmetry 29, 30 span two eccentric planes 31, 32 with the axis of rotation 26, which include a relative angle d to one another.
- Cylinder axes 33 of the auxiliary cylinders 20 enclose a position angle ⁇ .
- the opposing additional cylinders 20 are arranged symmetrically.
- the respective cylinder axis 33 is inclined obliquely downward at an angle of inclination ⁇ with respect to a horizontal.
- the angle of inclination a is at least 20 °.
- the angle of inclination a is set in a range between 30 ° and 50 ° in order to ensure optimal power transmission in addition to the narrow design.
- the angle of inclination ⁇ and the angle of position ⁇ change slightly during a stuffing process as a result of the vibration movements and the positioning movements.
- the various positions of the auxiliary cylinders 20 with the eccentric shaft 25 at a standstill are shown in FIG. 5.
- the solid lines show a provided position of the tamping tools 18.
- the cylinder axes 33 lie in the eccentric planes 31, 32, so that the position angle ⁇ is equal to the relative angle d.
- the eccentricities ei, b2 are shown disproportionately large compared to the remaining dimensions.
- the circular movement of the articulations of the auxiliary cylinders 20 resulting during one revolution of the eccentric shaft 25 are not taken into account in the illustration.
- FIGS. 6-8 Corresponding kinematic relationships for the front and rear tamping units 14 are shown in FIGS. 6-8.
- the auxiliary cylinders 20 and tamping tools 18 are arranged asymmetrically here.
- the pivot lever 21 assigned to the different auxiliary cylinders 20 is adapted accordingly.
- the cylinder axis 33 of the auxiliary cylinder 20 is oriented obliquely downward with respect to a horizontal with the angle of inclination ⁇ .
- Fig. 8 it can be seen that the middle positions of the two auxiliary cylinders 20 do not occur simultaneously with respect to the respective pivoting range.
- the shorter additional cylinder 20 is in the middle position and the longer additional cylinder 20 is in a downwardly pivoted end position.
- the minimum position angle ß min occurs in this position.
- the longer auxiliary cylinder 20 passes through its central position, in which the position angle ⁇ corresponds to the value of the relative angle d of the eccentric shaft 25. After the reset has taken place, the position angle ß has the greatest value ßmax.
- the value of the position angle ⁇ thus fluctuates during an ordering and return movement in the range ⁇ min- ⁇ max around the value of the relative angle d of the eccentric planes 31, 32.
- the pivot bearings 22 are arranged on the tool carrier 15 at a vertical distance. The longer design of the approximately horizontally aligned additional cylinder 20 enables a greater additional travel. As a result, the position angle ß fluctuates in a larger value range ßmin-ßmax.
- FIGS. 9 and 10 the eccentric shaft 25 for the front or rear tamping unit 14 is shown in detail.
- the first eccentric disk 27 is arranged centrally along the eccentric shaft 25.
- the shorter auxiliary cylinder 20, which is oriented obliquely downward, is mounted on this first eccentric disk 27, the shorter auxiliary cylinder 20, which is oriented obliquely downward, is mounted.
- the second eccentric disk 28 is divided into two parts, the partial eccentric disks being arranged on both sides of the first eccentric disk 27.
- the longer auxiliary cylinder 20 is mounted thereon with a fork-shaped end.
- the two auxiliary cylinders 20 are shown in FIGS. 9, 10 with dot-dash lines.
- the cylinder axes 33 of the auxiliary cylinders 20 fall into the eccentric planes 31, 32.
- the vibrational oscillations of the two auxiliary cylinders 20 simultaneously reach an external reversal point.
- the ends of the auxiliary cylinders 20 mounted on the eccentric disks 27, 28 are moved in an opposite direction. Due to the synchronous vibration oscillations, the oscillating masses largely balance each other out. This applies in particular to the tamping tines 23, which vibrate synchronously.
- the mass balance is reinforced with a flywheel 34 which rotates with the eccentric shaft 25 about the same axis of rotation 26.
- the eccentric shaft and the flywheel 34 form a rotation unit, the center of mass 35 of which lies approximately on a plane of symmetry 36 of the two eccentric planes 31, 32.
- the center of mass 35 is spaced from the axis of rotation 26 and lies opposite the axes of symmetry 29, 30 of the two eccentric disks 27, 28.
- the dimensioning of the Inertia mass 34 is matched to the mass of the auxiliary cylinder 20.
- the flywheel 34 is designed as a disk which is flattened at one point or has a groove in order to achieve the eccentric center of gravity 35.
- the differently large eccentricities ei, b2 cause the same amplitudes at the free ends of the tamping pimples 23. Due to the symmetrical arrangement, the two eccentricities ei, b2 in the eccentric shaft 25 for the middle tamping unit 14 of the same size.
- each rail 9 of the track 3 is assigned two separately lowerable tamping units 14.
- the tamping unit 7 thus comprises four tamping units 14 arranged next to one another in a row.
- the associated eccentric shaft 25 is driven by a vibration drive motor 37.
- All vibration drive motors 37 are controlled by means of a common control device 38 in order to ensure synchronous running. In this way, the vibrations of the individual tamping units 14 cancel each other out, as a result of which vibrations transmitted from the tamping unit 7 to the machine frame 6 are minimized.
- each rail 9 is assigned a combined tamping unit 14 with tamping tools 18 on the inside of the rail and tamping tools 18 on the outside of the rail.
- the tamping unit 7 comprises two combined tamping units 14 arranged next to one another in a row.
- the tamping units 14 arranged next to one another form additional groups, the tamping tines 23 of which are lowered together and provided together (two additional groups per row).
- a tamping unit 7 with four rows of tamping units 14 arranged directly one behind the other is shown in FIG. There are eight additional groups, each of which is controlled together.
- the supplementary groups of the middle tamping units 14 and the supplementary groups of the front and rear tamping units 14 facing them are supplied by means of a first auxiliary printing system 39.
- the foremost provision group and the rearmost auxiliary group are supplied by means of a second auxiliary pressure system 40.
- auxiliary groups are subjected to different auxiliary pressures during a provision process.
- the additional pressures are coordinated with one another in such a way that the same static and dynamic additional forces are set at all tamping tines 23.
- the respective provision group is controlled with a common control signal.
Landscapes
- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Machines For Laying And Maintaining Railways (AREA)
- Diaphragms For Electromechanical Transducers (AREA)
- Casting Devices For Molds (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ATA50566/2020A AT523825B1 (de) | 2020-07-03 | 2020-07-03 | Maschine und Verfahren mit einem Stopfaggregat |
PCT/EP2021/064804 WO2022002520A1 (de) | 2020-07-03 | 2021-06-02 | Maschine und verfahren mit einem stopfaggregat |
Publications (3)
Publication Number | Publication Date |
---|---|
EP4176131A1 true EP4176131A1 (de) | 2023-05-10 |
EP4176131C0 EP4176131C0 (de) | 2024-03-13 |
EP4176131B1 EP4176131B1 (de) | 2024-03-13 |
Family
ID=76355472
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP21731088.7A Active EP4176131B1 (de) | 2020-07-03 | 2021-06-02 | Maschine und verfahren mit einem stopfaggregat |
Country Status (9)
Country | Link |
---|---|
US (1) | US20230257939A1 (de) |
EP (1) | EP4176131B1 (de) |
JP (1) | JP2023531810A (de) |
CN (1) | CN115885073A (de) |
AT (1) | AT523825B1 (de) |
AU (1) | AU2021299878A1 (de) |
BR (1) | BR112023000090A2 (de) |
CA (1) | CA3186152A1 (de) |
WO (1) | WO2022002520A1 (de) |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH650819A5 (de) * | 1980-10-29 | 1985-08-15 | Canron Inc Crissier | Gleisstopfvorrichtung. |
DE58905683D1 (de) * | 1988-11-30 | 1993-10-28 | Asea Brown Boveri | Exzenterwelle mit Gegengewicht. |
AT513034B1 (de) | 2012-10-24 | 2014-01-15 | Plasser Bahnbaumasch Franz | Verfahren zum Unterstopfen eines Gleises |
AT513277B1 (de) * | 2012-10-24 | 2014-03-15 | Plasser Bahnbaumasch Franz | Maschine zum Unterstopfen eines Gleises |
US9731324B2 (en) * | 2013-09-25 | 2017-08-15 | Nordco Inc. | Drive for railroad ballast tamper apparatus |
-
2020
- 2020-07-03 AT ATA50566/2020A patent/AT523825B1/de active
-
2021
- 2021-06-02 AU AU2021299878A patent/AU2021299878A1/en active Pending
- 2021-06-02 CN CN202180044336.6A patent/CN115885073A/zh active Pending
- 2021-06-02 BR BR112023000090A patent/BR112023000090A2/pt unknown
- 2021-06-02 WO PCT/EP2021/064804 patent/WO2022002520A1/de active Application Filing
- 2021-06-02 CA CA3186152A patent/CA3186152A1/en active Pending
- 2021-06-02 JP JP2022581491A patent/JP2023531810A/ja active Pending
- 2021-06-02 US US18/004,094 patent/US20230257939A1/en active Pending
- 2021-06-02 EP EP21731088.7A patent/EP4176131B1/de active Active
Also Published As
Publication number | Publication date |
---|---|
WO2022002520A1 (de) | 2022-01-06 |
BR112023000090A2 (pt) | 2023-01-31 |
AU2021299878A1 (en) | 2023-01-19 |
AT523825A4 (de) | 2021-12-15 |
EP4176131C0 (de) | 2024-03-13 |
JP2023531810A (ja) | 2023-07-25 |
AT523825B1 (de) | 2021-12-15 |
EP4176131B1 (de) | 2024-03-13 |
CN115885073A (zh) | 2023-03-31 |
US20230257939A1 (en) | 2023-08-17 |
CA3186152A1 (en) | 2022-01-06 |
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