Patent Application
20250163880
This application claims convention priority from Australian provisional patent application 2022900497 filed on 2 Mar. 2022, the content of which is incorporated herein by reference.
The present invention relates to impulse turbines for converting hydraulic energy (amongst others) into mechanical or electrical energy, including the production of useful work from the kinetic energy of a flowing fluid, such as water, where the useful work might be useful for power generation or mechanical drive applications.
Hydroelectric power generation generally harnesses single-pass flowing fluid, typically water held in a dam, and converts kinetic energy to generate electricity. Power output involves the product of vertical head and flow rate at a particular site, with the head producing water pressure—the greater the head, the greater the pressure to drive turbines, so more head or higher flow rate typically translates to more power.
By way of explanation, turbines are rotary mechanical devices that extract kinetic energy from a fluid flow and convert that energy into useful work, with hydraulic turbines being those that extract potential energy from a flowing liquid such as water. With this in mind, turbines are then often combined with generators to turn the useful work produced into, for example, electrical power.
Although hydraulic turbomachinery has seen widespread use for over a century, most conventional equipment is optimally suited for high head applications, where the available head might be in the order of 100 to 500 metres. However, many opportunities today for the generation of hydroelectric energy, especially those with reduced environmental impacts, will be at sites or in circumstances with less than 10 metres of head.
Turbines historically finding application at low head levels have included variations of propeller type turbines such as Archimedean screw turbines or progressive cavity devices such as waterwheels, in which a bucket delivers a quantity of water from an upper elevation to a lower elevation, and the water quanta moves at the same speed as the bucket. Consequentially, these types of devices operate slowly and must be very large in order to pass large quantities of water.
Propeller turbines and their derivatives, such as Kaplan turbines, can pass large quantities of water moving at high velocity across turbine blades, but these units often need to be installed at a relatively low elevation with respect to the water level downstream of the turbine, to prevent operating problems such as cavitation.
Consequentially, conventional turbines designed to produce power from low heads have typically been highly expensive, with extensive civil works necessitated by the operation requirements of the turbines, often introducing environmental concerns, and often requiring remote location away from most users of electricity. Accordingly, there remains a need for a simple, continuous duty turbine that is capable of operating efficiently under Very Low Head (VLH) conditions, especially at heads of 10 metres or less.
Before turning to a summary of the solution provided by the present invention, it should be appreciated that reference to any prior art in this specification is not, and should not be taken as, an acknowledgment or any form of suggestion that this prior art is either well known or forms part of the common general knowledge in any country.
Also, the following description will use directional terms such as downward and downwardly, upward and upwardly, lower and upper, and above and below, which will be used with reference to the impulse turbine of the invention when positioned for rotation about its vertical axis. Further, there will also be references to inner and outer, and inwardly and outwardly, which will be radial references, again made with respect to a centrally positioned vertical axis of rotation.
A skilled addressee will understand that impulse turbines are traditionally those in which a liquid flows, typically water and typically in large volumes and at high pressures (often due to the effects of gravity), to a static nozzle where a pressurised jet of liquid impacts onto drive cups (also referred to as buckets or blades) of a rotating wheel, such as a rotating wheel of the Pelton-type, with the rotation of that wheel then producing the required torque and work output.
In this respect, there will be some references made hereafter to a Pelton-type collector assembly and collector plate, which will be understood by a skilled addressee to be a general reference to a radial arrangement of drive cups similar in nature to that found on the rotating wheel of a Pelton-type impulse turbine. However, importantly, it must be appreciated that the broadest form of the invention is not be limited to Pelton-type arrangements where static nozzles interact with rotating drive cups. The Pelton-type arrangements envisaged to be relevant to the present invention include rotating nozzles interacting with static drive cups, and rotating nozzles interacting with rotating drive cups, there thus simply being relative rotation between nozzles and drive cups.
The present invention provides a recirculating hydro-pneumatic impulse turbine, the impulse turbine including:
The above recirculating hydro-pneumatic impulse turbine might be useful in a power generation system, the power generation system including the recirculating hydro-pneumatic impulse turbine, a turbine starter system, a turbine braking system and a generator, wherein:
In relation to such a power generation system, it will be appreciated that the turbine starter and the braking system may simply be traditional components used for these same purposes, suitably sized in terms of the system's power requirements, while the generator (again suitably sized) may simply be a normal type of generator traditionally used for similar purposes. In this respect, it will also be appreciated that in the power generation system, it may be ideal to additionally include some type of traditional speed regulation device, such as a parasitic speed regulation device of the type used in standard industrial drive systems.
The above recirculating hydro-pneumatic impulse turbine might also be useful in a mechanical drive system, the mechanical drive system including the recirculating hydro-pneumatic impulse turbine, a turbine starter system, a turbine braking system, and a mechanical drive converter, wherein:
In relation to this mechanical drive system, it will be appreciated that the turbine starter and the braking system may simply be traditional components used for these same purposes, while the mechanical drive converter may simply be any type of mechanism that is able to mechanically convert the rotation of the impulse turbine into rotation or movement of another mechanism such that another mechanism can benefit from the work generated by the impulse turbine. In this respect, it will also be appreciated that in the mechanical drive system, it may be ideal to additionally include some type of traditional speed regulation device, such as a parasitic speed regulation device of the type used in standard industrial drive systems.
In relation to the inclusion of a ‘turbine starter’ in these power generation and mechanical drive systems, which is capable of initiating the relative rotation and then disengaging, it will be appreciated that functional references will be made in much of the following description in relation to the configuration of various aspects of the impulse turbine of the present invention, with reference to a turbine starter having played its role in providing an initial energy input and there already being relative rotation of the kind mentioned above, with the impulse turbine thus generally then in an operating mode, utilising gravity as an ongoing energy input (as occurs in traditional hydroelectric power generators),
Returning to a description of various features of the impulse turbine, as mentioned above, in the broadest form of the present invention, the fluid jets formed at the outlet nozzles engage with the drive cups to generate relative rotation therebetween, and it is this relative rotation that will be the source of the useful work. This reference to ‘relative rotation’ will be understood to include embodiments where the outlet nozzles rotate and interact with static drive cups, and also embodiments where the outlet nozzles rotate and the drive cups rotate in the opposite direction.
In all embodiments, however, the collector plate of the collector assembly has a generally horizontal upper surface and the rotation, regardless of which element rotates, will be rotation about a generally vertical axis. This is in contrast to traditional Pelton-type impulse turbines where the rotation of a Pelton-type wheel will typically occur about a horizontal axis.
With this in mind, the preferred form of relative rotation will be the embodiment where the outlet nozzles rotate and interact with static drive cups. In one embodiment, this is achieved by the collector assembly including a static upper drive plate, spaced above the collector plate, such that the drive cups are integral with or secured to the underside of the drive plate, arranged about the periphery thereof, to extend downwardly towards the collector plate to be immediately above, but not in contact with, the collector plate.
The drive cups may be integrally formed with the drive plate, such that drive plate and drive cups form a single element, or the drive cups may be removably or permanently attached to the drive plate by any suitable means, such as bolts or by welding.
In this embodiment, the collector plate will ideally be a floating plate, in that the collector plate will be mounted for rotation on bearings or the like but will not be driven for rotation. This floating function assists to dampen any energy remaining in fluid exiting the nozzles and moving across the upper surface of the collector plate, after the fluid's engagement with the drive cups. This assists with minimising any turbulence in that fluid and also minimise any subsequent interaction of that fluid with other drive cups, such as drive cups adjacent to or opposed to the drive cups that the fluid immediately interacts with when exiting the nozzles.
Also in this embodiment, the outlet nozzles of the drive assembly preferably lie outside the periphery of the collector plate and rotate about the periphery of the collector plate, with the drive plate configured to extend out beyond the periphery of the collector plate such that the drive cups also extend out beyond the periphery of the collector plate to permit fluid exiting the rotating nozzles to interact directly with the drive cups. As outlined above, that fluid then exits the drive cups, onto the upper surface of the floating collector plate, for flow thereacross towards and down the central draft tube.
In this form, the central draft tube is preferably integrally formed with the collector assembly, or at least with the collector plate, extending vertically therebelow such that the generally horizontal upper surface of the collector plate and the central draft tube together have a funnel-shaped configuration, and such that the draft tube is in fluid communication with the upper surface. Ideally then, fluid on the upper surface will flow by way of gravity from the upper surface to the centre of the collector plate and down the draft tube. It will thus be appreciated by a skilled addressee that the reference to the upper surface of the collector plate being ‘generally horizontal’ is a reference to the overall form of the upper surface, allowing for the presence of at least a slight inwardly directed incline of that surface to permit and direct flow of fluid off that surface towards and down the central draft tube.
The central draft tube may be a diverging, converging or constant diameter tube, with the preferred form being a constant diameter tube, albeit with a transitional region (a shoulder region) between the upper surface of the collector plate and an upper portion of the draft tube.
Additionally, because the general arrangement of the present invention sees the recirculating fluid coming from below the collector plate (in the form of the fluid jets that engage with the drive cups), with the fluid then moving across the upper surface of the collector plate after engaging with the drive cups, the drive cups preferably include at least a fluid-jet engaging portion that is the portion that extends outwardly beyond the periphery of the collector plate, together with a fluid return portion that returns fluid to the upper surface of the collector plate. In this form, with outlet nozzles positioned tangentially to the periphery of the collector plate and outside the periphery of the collector plate, fluid jets are able to first engage with the fluid-jet engaging portions of the drive cups, with the fluid then passing across the drive cups via the fluid return portions to be transferred to the upper surface of the collector plate.
In a preferred form, the drive cups are configured such that fluid jets are deflected through 160° to 170°, with the high velocity fluid jets impinging upon the fluid-jet engaging portions of the drive cups and the direction of the water changing to follow the contour of the drive cups. The impulse energy of the water exerts torque on the drive cups and thus provides the relative rotation between the drive cups and the outlet nozzles, in the preferred form making the outlet nozzles and the drive assembly rotate. As mentioned above, the fluid then changes direction and exits at the sides of the drive cups onto the collector plate with low velocity.
In relation to the drive assembly of the impulse turbine of the present invention, the drive assembly is preferably configured and arranged to be about the central draft tube, generally below the collector plate, with one or more fluid inlets at the lower end of the drive assembly, in fluid communication with the lower end of the draft tube where fluid exits the draft tube, and a plurality of tangentially arranged outlet nozzles configured at its upper end.
With this in mind, the drive assembly may for instance be a cylindrical drum, rotatable about its central, vertical axis, with the interior of its sidewall being a smooth surface, the sidewall being inclined away from the vertical axis of the drum, across which fluid from the drum's lower fluid inlet will flow to exit through a plurality of peripherally arranged outlet nozzles about the upper end of the drum. In this form, the drum's lower fluid inlet will be configured so as to guide the flow of fluid away from the lower fluid inlet, up the interior of the sidewall of the drum, preferably in a direction that is tangentially inclined to the sidewall of the drum.
Alternatively, the interior of the sidewall of the drum may be configured with open flow channels, such as corrugations or grooves, with the sidewall and thus these corrugations or grooves again preferably inclined from the vertical axis of the drum, and also tangentially inclined to the sidewall of the drum, each of which align with a specific outlet nozzle, to provide guided flow of the fluid from the lower fluid inlet of the drum to the upper outlet nozzles. In this form, the fluid inlet of the drum may include a lower fluid distribution manifold that distributes fluid from the fluid inlet to the lower end of each of the corrugations or grooves, again to provide guided flow of the fluid.
In yet another form, the open flow channels may be replaced by closed flow channels, either formed integrally with the interior of the side wall of the drum, or rigidly secured to the interior of the side wall of the drum, with the same vertical and tangential inclinations mentioned above.
Further still, the drive assembly may be provided without the need for a solid walled drum, where flow channels are provided in the form of a plurality of tubes, the tubes essentially forming a cage of tubes about the central draft tube, with each tube aligning with a specific upper outlet nozzle, to provide guided flow of the fluid from a lower fluid distribution manifold that distributes fluid from the central draft tube to the lower end of each of the tubes, again to provide guided flow of the fluid to respective upper outlet nozzles. Furthermore, such tubes will again preferably be configured so as to be vertically inclined from the vertical axis of the drive assembly (and thus of the collector assembly) and also tangentially inclined from the periphery of the collector plate in the same manner as outlined above, resulting in a generally helical array of tubes forming the cage-like drive assembly.
In these embodiments, although not essential, the fluid flow from the lower end of the drive assembly to the upper outlet nozzles of the drive assembly will ideally be upward and generally helical, due to the preferred dual inclinations away from the vertical axis of the collector assembly and tangentially to the periphery of the collector plate. These dual inclinations, as opposed to an embodiment with no such inclinations, assist with the movement of fluid from the lower end of the drive assembly upwardly to the outlet nozzles, with the fluid jets formed at the outlet nozzles engaging with the drive cups to generate the relative rotation referred to above between the drive cups and the outlet nozzles about the vertical axis, and it is this rotation that is capable of providing the useful work.
Returning to a description of the collector assembly, including the collector plate and the central draft tube, as mentioned above the collector plate includes a generally horizontal upper surface with the central draft tube extending vertically therebelow, the collector plate being configured such that the draft tube is in fluid communication with that upper surface. With fluid flowing from the drive cups across the upper surface of the collector plate to the draft tube, and down the draft tube, the fluid enters the fluid inlet of the drive assembly for entrainment with air and recirculation back upwardly to the outlet nozzles.
With this in mind, the central draft tube includes a central air tube with an upper air inlet and a lower air distribution manifold. Preferably, the lower air distribution manifold includes at least one venturi outlet capable of entraining air in the fluid to assist movement of the fluid from the lower end of the drive assembly upwardly to the upper outlet nozzles. Noting that there are several embodiments available for the drive assembly of the impulse turbine, particularly with regard to the presence or not of fluid flow structures (namely the open or closed flow channels that can be in the form of corrugations, grooves, integral tubes or standalone tubes), it will be appreciated that the lower air distribution manifold can itself take many forms as necessary. Ideally though, for the fluid inlet of the drive assembly, and for however many structures there might be for the preferred guided fluid flow upwardly in the drive assembly, for each such structure the lower air distribution manifold will include a respective venturi outlet capable of entraining air in the fluid to assist movement of the fluid from the lower end of the drive assembly upwardly to the outlet nozzles.
With respect to the flow of air into and through the impulse turbine of the present invention, firstly, air will be drawn down the central air tube from above the collector plate via the upper air inlet, which may be in the form of a plurality of suitably positioned inlet apertures, where air entrained in the circulating fluid (exiting the outlet nozzles and flowing across the upper surface of the collector plate) will be escaping. However, air will preferably also be drawn from an external air valve above the collector assembly such that air can be drawn from atmosphere. In this respect, such an external air valve can ideally be incorporated with an air release valve and is thus preferably a passive vent to allow internal and external air pressures to equalize, ideally designed to also minimise loss of fluid from the system.
In a preferred form, the central air tube includes a plurality of inlet apertures located at a level near or just below the level of the collector plate, such that the air entering the central air tube will travel downwardly from those apertures to the lower air distribution manifold. In this respect, in one form the lower air distribution manifold can include a series of radial ports (one for each venturi outlet), each being in fluid communication with a respective venturi tube. Such venturi tubes ideally extend from the central air tube wall to a location either associated with, and in close proximity to, an open flow channel such as a corrugation or groove, or to a location within a closed flow channel such as a tube, with its outlet facing downstream to the flow so as to create a venturi through which air is entrained into the passing fluid.
After exiting these venturi outlets, the air will be compressed in the fluid by centrifugal forces in the flow channels, with the air expanding after peak compression and on its exit from the flow channels so as to pressurise the fluid to increase the velocity of the fluid up the flow channels and form an adjustable velocity.
Minor mechanical friction losses will be associated with the drive assembly rotation, given that the drive assembly will ordinarily be supported by bearings at either end of its axis. Additionally, it will be appreciated that the contra rotating fluid circulating at maximum radius to the axis, contained within flow channels of the drive assembly, acts as a compressed fluid mass. While there will also be frictional losses associated with this fluid circulation, the contra rotation of the fluid compared to the rotation of the drive assembly is such that the normal downward gravitational forces exerted on the upwardly flowing fluid within the drive assembly is largely eliminated to the point where there is little resistance to the upward movement of the fluid.
Furthermore, as the fluid travels away from the point of peak compression, air entrained within the fluid begins expanding, and ejects the fluid from the outlet nozzles at a greater velocity than that of un-entrained fluid. In this form, this ‘de-compressing’ fluid exits the outlet nozzles and is impacted into the drive cups of the collector assembly and transfers the energy (thrust) from the fluid to the rotating drive assembly, therefore providing rotational drive to the entire drive assembly.
Under Very Low Head (VLH) conditions, such as operation at heads of less than 10 m, the impulse turbine of the present invention operates ideally (in terms of preferred rates of acceleration) with a head of less than 5 m and ideally in the range of 1 to 3 m. In this respect, as the energy gained by falling fluid beyond about 5 m is insignificant in the impulse turbine of the present invention, the range of 1 to 3 m of head for this configuration of turbine is ideal. Also, with the configurations of the present invention, the greater distance that the fluid falls, the greater the distance that the fluid must be returned upwardly to the collector assembly, such that efficiencies can be maximised in the range of 1 to 3 m without an unnecessary penalty being paid for gaining any extra head of fluid.
Having briefly described the general concepts involved with the present invention, several preferred embodiments of a recirculating hydro-pneumatic impulse turbine will now be described that is in accordance with the present invention. However, it is to be understood that the following description is not to limit the generality of the above description.
In the drawings:
Illustrated in
With specific reference to
The impulse turbine 10 also includes a drive assembly 22 about the draft tube 16, the drive assembly 22 having a fluid inlet 24 (see
The impulse turbine also includes a central air tube 30 with an upper air inlet in the form of a plurality of inlet apertures 80 and a lower air distribution manifold 34, the manifold 34 (see
As mentioned more generally above, during use of the impulse turbine 10, fluid jets formed at the outlet nozzles 26 engage with the drive cups 20 to generate relative rotation between the outlet nozzles 26 and the drive cups 20 about a vertical axis A, the rotation capable of providing useful work, with fluid subsequently flowing from the drive cups 20 across the upper surface 18 of the collector plate 15 to the draft tube 16, down the draft tube 16 where the fluid enters the fluid inlet 24 of the drive assembly 22 for entrainment with air and recirculation to the outlet nozzles 26.
The impulse turbine 10 may be used in a power generation system or a mechanical drive system, in both situations utilising a turbine starter system, a turbine braking system and a generator or a mechanical drive converter. These systems and additional equipment are not generally shown in the Figures, although preferred locations for the equipment is illustrated generally at X and Y in
In this respect, and as mentioned above, a turbine starter is capable of initiating rotation of the outlet nozzles 26 of the drive assembly 22 to prime the drive assembly 22 with fluid, to generate the relative rotation between the outlet nozzles 26 and the drive cups 20, after which gravity provides ongoing energy input (as occurs in traditional hydroelectric power generators), following which the turbine starter disengages. The braking system is capable of stopping that relative rotation when necessary. When used, a generator converts the useful work of the relative rotation between the drive cups 20 and outlet nozzles 26 to electrical energy and, when used, a mechanical drive converter converts the useful work of the relative rotation between the drive cups 20 and outlet nozzles 26 to useful mechanical work.
With reference to the schematic illustrations in
The relative rotation is rotation about the vertical axis A. This is in contrast to traditional Pelton-type impulse turbines where the rotation of a Pelton-type wheel will typically occur about a horizontal axis.
The collector plate 15 is a floating plate, in that it is mounted for rotation on bearings (not shown) but is free and would normally not rotate, or at least would not rotate at anything near the speed of the drive assembly. As mentioned above, the floating function assists to dampen any energy remaining in fluid exiting the outlet nozzles 26 and moving across the upper surface 18 of the collector plate 15, after the fluid's engagement with the drive cups 20.
The outlet nozzles 26 lie outside the periphery 52 of the collector plate 15 (see
A description of the draft tube 16 and the elements in this embodiment that make up the draft tube 16 will now be provided, with particular regard to
The central draft tube 16 in this embodiment is a tube of constant diameter, with the inlet 44 having the upper portion 15a (the shoulder region) between the upper surface 18 of the collector plate 15 and the mid-portion 15b of the draft tube 16.
It can also be seen in in
The collector plate 15, including its upper and mid-portions 15a and 15b, all float in the manner described above, whereas the nozzle plate 90, including its lower portions 90a and 90b, will rotate during operation by virtue of the forced rotation of the outlet nozzles 26. In this respect, in this embodiment the lowermost portion 90b of the nozzle plate 90 extends at its lower end below the mid-portion 15b of the collector plate 15 and down to the inlet 24 of the drive assembly 22 and its tubes 70, and thus forms a lower element of the draft tube 16.
It will be appreciated that with drive cups 20 and the drive plate 12 both being static, and the outlet nozzles 26 and the nozzle plate 90 thus rotating during use, so too will the upstanding side wall 96 of the nozzle plate 90. However, a suitable sealing engagement will be provided between the corner flange 94 of the drive plate 12 to permit relative rotation between the drive plate 12 and the sidewall 96 of the nozzle plate 90
The drive cups 20 in this embodiment are attached to the underside of the drive plate 12 by any suitable means, such as bolts or by welding, and in this embodiment include a mounting flange 46 for securing the drive cups 20 to the drive plate 12. Because the recirculating fluid comes from below the collector plate 15, the drive cups 20 include a fluid-jet engaging portion 50 (evident in
In this embodiment, the drive cups 20 are configured such that fluid jets are deflected through 160° to 170°, with the high velocity fluid jets impinging upon the fluid-jet engaging portions 50 of the drive cups 20 and the direction of the water changing to follow the contour of the fluid return portions 54. The impulse energy of the water exerts torque on the drive cups 20 and thus provides the relative rotation between the drive cups 20 and the outlet nozzles 26, by causing the outlet nozzles 26 and thus the drive assembly 22 to rotate. The fluid then changes direction and exits the drive cups 20 onto the upper surface 18 of the collector plate 15 with low velocity.
In relation to the drive assembly 22 of the impulse turbine of the present invention, the drive assembly 22 is preferably configured and arranged to be generally about the central draft tube 16, generally below the upper surface 18 of the collector plate 15, with a fluid inlet 24 at the lower end of the drive assembly 22, in fluid communication with the lower end of the draft tube 16, and the plurality of tangentially arranged outlet nozzles 26 configured at its upper end.
As mentioned above, and as will now be discussed in relation to the embodiments illustrated in
Alternatively, and with reference to
However, in the first embodiment illustrated in
Furthermore, such tubes 70 are configured so as to be vertically inclined from the vertical axis A of the drive assembly 22 (and thus of the collector plate 15) and also tangentially inclined in the same manner as outlined above, resulting in a generally helical array of tubes forming the cage-like drive assembly 22 of the first embodiment.
It will thus be apparent that the fluid flow in all embodiments from the lower inlet 24 to the upper outlet nozzles 26 of the drive assembly 22 will be upward and generally helical, due to the dual inclinations away from the vertical axis of the collector plate 15 and tangentially to the outer periphery 52 of the collector plate 15. These dual inclinations assist with the movement of the fluid from the lower end 72 of the tubes 70 upwardly to the outlet nozzles 26, with the fluid jets formed at the outlet nozzles 26 engaging with the drive cups 20 to generate the relative rotation referred to above.
Referring now to
Evident at the upper end of the central air tube 30 in
With respect to the flow of air into and through the impulse turbine 10, air will be drawn down the central air tube 30 from immediately above the upper surface 18 of the collector plate 15 through the apertures 80 (see
The air entering the air tube 30 travels downwardly from the apertures 80 to the lower air distribution manifold 34 that includes a series of radial ports 82 (one for each venturi outlet) to which is attached a venturi tube 36 that extends from the central air tube wall 84 to a location within a respective tube 70, with its outlet facing downstream to the flow so as to create a venturi through which air is entrained into the fluid as the fluid enters a tube 70.
After exiting the venturi outlets 36, the air will be compressed in the fluid in the tubes 70, with the air expanding after peak compression and on its exit from the venturi outlets 36 so as to pressurise the fluid to increase the velocity of the fluid up the tubes 70 and form an adjustable velocity. As the fluid travels away from the point of peak compression, air entrained within the fluid begins expanding rapidly, and ejects the fluid from the outlet nozzles 26 at a much greater velocity than that of un-entrained fluid.
In this form, this ‘de-compressing’ fluid exits the outlet nozzles 26 and is impacted into the static drive cups 50 at the periphery of the drive plate 12 and transfers the energy (as thrust) from the fluid to the rotating drive tube assembly 22, therefore providing continuous rotational drive to the entire drive tube assembly 22 and rotation of the drive shaft 100 for the production of useful work.
In conclusion, it must be appreciated that there may be other variations and modifications to the configurations described herein which are also within the scope of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2022900497 | Mar 2022 | AU | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/AU2023/050114 | 2/21/2023 | WO |
