CAIXA DE ENGRENAGENS PARA UMA BOMBA

Abstract

There is described a gearbox for a pump, wherein the gearbox comprises a ring gear, a sun gear, and one or more planet gears arranged between the ring gear and the sun gear. The planet gears are arranged to move around the sun gear along a continuous path, and the ring gear, the sun gear, and the planet gears are arranged so that a radius of the path varies as the planet gears move along the path.

Description

[001] This description refers to a gearbox, in particular a gearbox suitable for use in a pump (for example, a radial hydraulic pump). This description also refers to a pump comprising the gearbox, to systems comprising the gearbox and / or the pump, and to methods of operating the gearbox and / or pump. Fundamentals of Description

[002] Radial hydraulic pumps, such as radial piston pumps, comprise one or more pistons extending radially with reference to a drive shaft. Each piston is connected at one end to the drive shaft and at the opposite end to an external tappet, also known as a stroke ring, which encircles the drive shaft. The connection of the pistons is such that as the distance between the external tappet and the drive shaft increases, a volume within the piston increases (and therefore a pressure within the piston decreases). Within such a pump, the drive shaft or the external tappet is eccentric; therefore, as the drive shaft rotates, the drive shaft and the tappet cooperate to continuously vary the volumes of each piston. The variation in these piston volumes causes a change in the pressure within the pistons, the change of which Petition 870250083817, dated 09 / 17 / 2025, page 47 / 119 2 / 54 of the pressure can be used to drive the flow of a fluid.

[003] Such a pump is shown in Figure 1, which represents a conventional radial hydraulic pump 100 comprising a drive shaft 102, an external tappet 104 and a first and second piston 106, 108. The drive shaft is fixed to rotate about a geometric axis of rotation 110. An inner end 112 of the first piston 106 is fixed to the drive shaft, while an outer end 114 of this first piston is fixed to the external tappet. Since the geometric axis of rotation of the drive shaft does not coincide with the center of the drive shaft, the rotation of the drive shaft causes the distance between the inner end and the outer end of the first piston to change throughout the cycle, with one complete rotation of the drive shaft corresponding to one cycle between the maximum and minimum distances between these two ends and the first piston.Similarly, the extension of the second piston 108 varies throughout the cycle (with the second piston being located opposite the first piston and the extension of the second piston mirroring that of the first piston). The extension and compression of the pistons alter the pressure in these pistons so that the pistons draw in and expel fluids at points in the cycle corresponding to the extension and compression, respectively.

[004] The pistons can be arranged to aspirate Petition 870250083817, dated 09 / 17 / 2025, page 48 / 119 3 / 54 fluid from an internal region of the pump, for example, pistons 106, 108 can draw fluid from their internal ends, where the internal region of the pump can be connected to the fluid supply. This configuration is known as “internally collided”. Alternatively, the pistons can be connected to a fluid supply closer to the external tappet 104, so that the external ends of the pistons are arranged to draw fluid from this reservoir.

[005] The connection of the pistons to the fluid supply may comprise a valve so that fluids can only flow through the connection in one direction. An internal impact pump may have two valved openings at the inner ends of each piston. For example, the inner end 112 of the first piston 106 may have an opening with a valve that allows fluid to enter the first piston but not exit the piston, and the outer end 114 of the first piston may have an opening with a valve that allows fluid to exit the first piston but not enter. When the piston is expanding, fluid enters through the first opening. When the piston is compressed, fluid exits only through the second opening, as the valve at the first opening does not allow fluid to exit. Summary of the Description

[006] According to one aspect of the present description, Petition 870250083817, dated 09 / 17 / 2025, page 49 / 119 4 / 54 is described: a gearbox for a pump, the gearbox comprising: a ring gear; a sun gear; and one or more planetary gears arranged between the ring gear and the sun gear, the planetary gears being arranged to move around the sun gear along a continuous path; wherein the ring gear, the sun gear and the planetary gears are arranged so that a radius of the path varies as the planetary gears move along the path.

[007] The variation in the radius of the planetary gear path can be used to drive a pump.

[008] Preferably, at least two of the ring gear, the sun gear and at least one of the planetary gears have non-circular profiles (and / or non-circular pitch circumferences and / or non-constant pitch circle diameters).

[009] The sun gear may have a non-circular pitch circumference and / or a non-circular profile, and the ring gear may also have a non-circular pitch circumference and / or a non-circular profile. The diameter, circumference, and / or profile of the ring gear may depend on the diameter, circumference, and / or profile of the sun gear. For example, the diameter of the ring gear may be equal to the sum of the diameter of the sun gear. Petition 870250083817, dated 09 / 17 / 2025, page 50 / 119 5 / 54 plus twice the diameter of a single planetary gear. Advantageously, this allows the ring gear to mesh with the planetary gears and the planetary gears to mesh with the sun gear, without imposing significant deformation on the gears.

[0010] The gearbox may comprise a plurality of planetary gears. The gearbox may comprise a pair of planetary gears. Preferably, the pair of planetary gears is arranged symmetrically around a path center and / or a center of rotation of the gearbox. Preferably, the gearbox comprises a plurality of pairs of planetary gears.

[0011] The gearbox may comprise at least two planetary gears, at least four planetary gears, at least eight planetary gears and / or at least ten planetary gears.

[0012] The gearbox may comprise a number of planetary gears that is not greater than (and / or equal to) one order of rotational symmetry of the gearbox. The gearbox may comprise a number of planetary gears that is not greater than one order of rotational symmetry of the sun gear and ring gear combination. When the gearbox comprises a number of planets that is not greater than the Petition 870250083817, dated 09 / 17 / 2025, page 51 / 119 6 / 54 rotational symmetry order of the combination of the sun gear and the ring gear, the planets can be positioned so as to follow a path of equally variable width as they orbit the sun. Each planet can be positioned so as to follow a path whose width remains constant along the planet's orbit; this allows each planet to remain geared to the sun and the ring gear without suffering significant compression at any point in the orbit.

[0013] Planetary gears can be evenly spaced along the path.

[0014] The gearbox may comprise a conveyor and planetary gears may be connected to the conveyor.

[0015] The width of the path that the planet travels between the sun and the ring gear can be substantially constant. The sun gear and the ring gear can be arranged so that a radial distance between the sun gear and the ring gear at the point of contact of each of the planetary gears remains constant as said planetary gears move along the path.

[0016] Each of the planetary gears can have a circular profile. Each planetary gear can be similar. The ring gear and the sun gear can Petition 870250083817, dated 09 / 17 / 2025, page 52 / 119 7 / 54 have non-circular profiles.

[0017] One or more of (for example, each of) the sun gear, ring gear, and planet gears may comprise a plurality of teeth. Preferably, each of the gears has a similar spacing of teeth. Preferably, the teeth are arranged regularly around the profile of a corresponding gear.

[0018] The gearbox may comprise at least one piston, wherein the piston is arranged so that an amount of piston compression changes as the planetary gears move along the path, preferably so that a radial compression of the piston changes as the planetary gears move along the path. This radial compression may be used to cause a change in piston pressure as the planet moves along the path, which may be used to drive a pump. One end of the piston may be associated with (e.g., connected to) a planetary gear. One end of the piston may be connected to a carrier.

[0019] The gearbox may comprise a plurality of pistons, wherein a first end of each piston may be associated with a respective planetary gear. Petition 870250083817, dated 09 / 17 / 2025, page 53 / 119 8 / 54

[0020] A second end of each piston can be connected to an additional component of the gearbox so that the first end of that piston moves relative to the second end of the piston as the planetary gear moves along the path, or preferably, so that the first end of the piston moves towards and / or away from the second end of the piston as the planetary gear moves along the path.

[0021] A second end of the piston may be connected to an additional planetary gear. Preferably, the second end of the piston is connected to an opposing planetary gear that is located at an opposite point along the path to the gear (for example, where the planetary gear and the opposing planetary gear are spaced 180° apart along the path as each of the gears moves along the path).

[0022] The second end of the piston can be connected to one or more of the following: the sun gear; the ring gear; a carrier; and a point near and / or at the center of the path and / or a center of rotation of the gearbox.

[0023] One or more of the (e.g., each of the) pistons may be connected to a conveyor. Petition 870250083817, dated 09 / 17 / 2025, page 54 / 119 9 / 54

[0024] The ring gear may be arranged to remain stationary (e.g., relative to a gearbox housing) as the planetary gears move along the path. The sun gear may be arranged to remain stationary (e.g., relative to a gearbox housing) as the planetary gears move along the path.

[0025] One or more of (for example, each of) the sun gear and the ring gear may be arranged to rotate (for example, relative to a gearbox housing) as the planetary gears move along the path.

[0026] The gearbox may comprise a motor for driving a motion (for example, a rotation) of one or more of the following: the sun gear; the ring gear; one or more of the planetary gears; and a carrier associated with one or more of the planetary gears.

[0027] The sun gear may comprise one or more minimum points, wherein the radius of the sun gear at said minimum points is less than an average radius of the sun gear. For example, the radial distance from the center of the sun gear to the base of a gear tooth may be less at a minimum point than the average value of the radial distance between the center of the sun gear and the base of a Petition 870250083817, dated 09 / 17 / 2025, page 55 / 119 10 / 54 sun gear tooth.

[0028] The sun gear may comprise one or more maximum points, wherein the radius at said maximum points is greater than an average radius of the sun gear. For example, the radial distance from the center of the sun gear to the base of a gear tooth may be greater at a maximum point than the average value of the radial distance between the center of the sun gear and the base of a sun gear tooth.

[0029] The ring gear may comprise one or more minimum points, wherein the radius of the ring gear (e.g., the distance from the ring gear to the center of rotation of the ring gear and / or the gearbox) at said minimum points is less than an average radius of the ring gear. For example, the radial distance from the center of the ring gear to the base of a gear tooth may be less at a minimum point than the average value of the radial distance between the center of the ring gear and the base of a ring gear tooth.

[0030] The ring gear may comprise one or more maximum points, wherein the radius of the ring gear (e.g., the distance from the ring gear to the center of rotation of the ring gear and / or the gearbox) at said maximum points is greater than an average radius of the ring gear. For example, the radial distance from the center Petition 870250083817, dated 09 / 17 / 2025, page 56 / 119 11 / 54 of the sun gear to the base of a gear tooth can be greater at a maximum point than the average value of the radial distance between the center of the sun gear and the base of a sun gear tooth.

[0031] The ring gear may be rotationally symmetric. Alternatively and / or additionally, the sun gear may be rotationally symmetric. Preferably, both the sun and ring gears are rotationally symmetric. This allows a plurality of planetary gears to be positioned so that a radial distance between the sun gear and the ring gear at the point of contact of each of the planetary gears remains constant as said planetary gears move along the path.

[0032] The sun gear may comprise an equal number of minima and maxima; and / or the ring gear may comprise an equal number of minima and maxima.

[0033] The number of minima of the ring gear may be the same as the number of minima of the sun gear; and / or the number of maxima of the ring gear may be the same as the number of maxima of the sun gear.

[0034] The number of minima of the ring gear may be greater than the number of minima of the sun gear; and / or the number of maxima of the ring gear may be greater than the number of maxima of the sun gear. Petition 870250083817, dated 09 / 17 / 2025, page 57 / 119 12 / 54

[0035] An amplitude of the sun gear minima (for example, a distance between a mean radius of the sun gear and a radius of the sun gear at the minima) can be equal to an amplitude of the sun gear maxima (for example, a distance between a mean radius of the sun gear and a radius of the sun gear at the maxima).

[0036] Similarly, an amplitude of the ring gear minima (for example, a distance between a mean radius of the ring gear and a radius of the ring gear at the minima) can be equal to an amplitude of the ring gear maxima (for example, a distance between a mean radius of the ring gear and a radius of the ring gear at the maxima).

[0037] Preferably, a variation in the amplitude of the minimum points of the sun gear (for example, from a mean radius of the sun gear) is equal to a variation in the amplitude of the maximum points of the sun gear.

[0038] Preferably, a change in the amplitude of the minimum points of the ring gear is equal to a change in the amplitude of the maximum points of the ring gear.

[0039] Preferably, the variation in the amplitude of the minimum points of the sun gear is equal to the variation in the amplitude of the maximum points of the ring gear.

[0040] Preferably, the variation in amplitude Petition 870250083817, dated 09 / 17 / 2025, page 58 / 119 13 / 54 of the maximum points of the sun gear is equal to the variation in the amplitude of the minimum points of the ring gear.

[0041] The sun gear may have a wavy profile and / or the ring gear may have a wavy profile.

[0042] The sun gear may have a profile comprising a sinusoidal wave superimposed on an ellipse, preferably a sinusoidal wave superimposed on a circle; and / or the ring gear may have a profile comprising a sinusoidal wave superimposed on an ellipse, preferably a sinusoidal wave superimposed on a circle.

[0043] The profile of the sun gear and / or the ring gear (and, preferably, the profile of each of the sun gear and the ring gear) can be defined by the equation: r(t) = 2 + a · sin(ft) where: t is a parametric variable with values ​​from 0 to 2π; r is a gear radius (e.g., gear profile) at a value t; P is a mean diameter (e.g., pitch circle) of the gear (e.g., gear profile); a is a wave amplitude (e.g., amplitude of the sinusoidal wave and / or amplitude of a change from a minimum and / or maximum of the gear to the mean diameter); ef is a wave frequency (e.g., a number of gear waves). Petition 870250083817, dated 09 / 17 / 2025, page 59 / 119 14 / 54

[0044] The ring gear may comprise a different number of minimums and / or maximums than the sun gear. Preferably, the ring gear comprises a greater number of minimums and / or maximums than the sun gear and / or fan gear greater than fsol.

[0045] The amplitude of the minimums and / or maximums of the sun gear may be substantially equal to the amplitude of the minimums and / or maximums of the ring gear and / or the ring gear may be equal to the sun gear. When the ring gear is equal to the sun gear, it is possible to configure the gears so that a radial distance between the sun gear and the ring gear at the point of contact of each of the planetary gears remains constant as said planetary gears move along the path.

[0046] The ring gear and / or the sun gear may comprise one or more waves, a wave being a sinusoidal section (e.g., a cycle) of a perimeter of the gear and / or a wave comprising a minimum and a maximum. Preferably, the ring gear and / or the sun gear comprises an integer number of waves. The ring gear may comprise a greater number of waves than the sun gear.

[0047] The diameters and wave numbers of the sun gear and ring gear can be linked by the equation: Petition 870250083817, dated 09 / 17 / 2025, pp. 60 / 119 15 / 54 P . P .1sol _1anelfsol fanel where: Psol is an average diameter (e.g., pitch circle) of the sun gear; Panel is an average diameter (e.g., pitch circle) of the ring gear; fsol is a wave frequency (e.g., wave number) of the sun gear; and fane is a wave frequency (e.g., wave number) of the ring gear.

[0048] The sun gear may comprise eight waves (e.g., fsol= 8). The ring gear may comprise ten waves (e.g., fanel= 10).

[0049] The diameter (e.g., pitch circle) of the sun gear may be at least 100 mm, at least 200 mm and / or at least 500 mm. The diameter (e.g., pitch circle) of the sun gear may not exceed 1,000 mm, not exceed 800 mm and / or not exceed 500 mm.

[0050] The diameter of the planetary gears may be at least 50 mm, at least 100 mm and / or at least 200 mm. The diameter of the planetary gears may not exceed 500 mm, not exceed 400 mm and / or not exceed 300 mm.

[0051] The pump may comprise a radial pump and / or a radial hydraulic pump. The pump may be arranged to pump a fluid through pistons; and / or to pump a Petition 870250083817, dated 09 / 17 / 2025, pp. 61 / 119 16 / 54 fluid in a radial direction of the gearbox (e.g., perpendicular to a geometric axis of rotation of the gearbox); and / or to pump a fluid in a direction of a geometric axis of rotation of the gearbox (e.g., of the sun gear and / or ring gear).

[0052] The pump may comprise a shaft, in which one or more of (preferably each of): the sun gear; the ring gear; and a carrier are arranged to rotate about the shaft.

[0053] According to another aspect of the description, a method (e.g., computer-implemented) is provided for operating the gearbox and / or pump of any embodiment of the first aspect. The method may comprise driving one or more of: the sun gear, the ring gear, and one or more of the planetary gears. The method may comprise driving said gear(s) depending on a desired pumping force.

[0054] According to another aspect of the description, a method of manufacturing the gearbox and / or pump of the first aspect is provided.

[0055] According to another aspect of the description, a parts kit is provided for the gearbox of any of the preceding claims, the parts kit comprising: the ring gear; the sun gear; and Petition 870250083817, dated 09 / 17 / 2025, pp. 62 / 119 17 / 54 one or more planetary gears.

[0056] According to another aspect of the description, it is described: a computer program product (and / or a machine-readable medium) comprising computer executable instructions which, when executed, cause a processor to control the gearbox and / or pump of any of the preceding claims.

[0057] Any feature in one aspect of the description can be applied to other aspects of the invention in any appropriate combination. In particular, aspects of the method can be applied to aspects of the apparatus and vice versa.

[0058] Furthermore, features implemented in hardware can be implemented in software and vice versa. Any reference to software and hardware features in this document should be interpreted accordingly.

[0059] Any device feature, as described in this document, may also be provided as a method feature and vice versa. As used in this document, more function features may alternatively be expressed in terms of their corresponding structure, such as a suitably programmed processor and associated memory.

[0060] It should also be appreciated that particular combinations of the various features described and defined in any aspects of the description may be implemented and / or Petition 870250083817, dated 09 / 17 / 2025, pp. 63 / 119 18 / 54 provided and / or used independently.

[0061] The description also provides a computer program and a computer program product comprising adapted software code, when executed on a data processing device, to perform any of the methods described in this document, including any or all of its component steps.

[0062] The description also provides a computer program and a computer program product comprising software code that, when executed on a data processing device, comprises any of the device features described in this document.

[0063] The description also provides a computer program and a computer program product with an operating system that supports a computer program to perform any of the methods described in this document and / or to incorporate any of the device features described in this document.

[0064] The description also provides a computer-readable medium having stored in it the computer program as mentioned above.

[0065] The description also provides a signal that carries the computer program as mentioned above and a method for transmitting such a signal.

[0066] The description extends to methods and / or devices Petition 870250083817, dated 09 / 17 / 2025, pp. 64 / 119 19 / 54 substantially as described in this document with reference to the attached drawings.

[0067] The description will now be described, by way of example, with reference to the attached drawings. Description of the Drawings

[0068] Figure 1 shows a conventional radial piston pump according to the state of the art.

[0069] Figure 2 shows a system comprising a pump.

[0070] Figure 3 shows an epicyclic gearbox.

[0071] Figures 4a and 4b show an epicyclic gearbox according to the present description.

[0072] Figures 5a and 5b show example gears.

[0073] Figure 6 shows an additional embodiment of an epicyclic gearbox according to the present description.

[0074] Figure 7 shows another embodiment of an epicyclic gearbox according to the present description. Description of Preferred Options

[0075] With reference to Figure 2, a system provided for by the present description is shown. Figure 2 shows a fluid source 252, for example, a water source. This fluid source is connected to a pump 254 at a fluid inlet. Petition 870250083817, dated 09 / 17 / 2025, pp. 65 / 119 20 / 54 262. The pump draws fluid from the fluid source through the fluid inlet and subsequently expels the fluid through a fluid outlet. This fluid outlet is connected to a fluid outlet. Typically, the pump inlet and outlet are associated with one-way valves to prevent any reverse flow through the system, for example, from the fluid outlet back to the pump or from the pump back to the fluid source.

[0076] The present description refers to a gearbox that is suitable for use in a pump, in particular a radial hydraulic pump. More specifically, the present description refers to an epicyclic (or planetary) gearbox that can be used in a pump.

[0077] With reference to Figure 3, a conventional epicyclic gearbox 300 is described comprising a sun gear 310, a first planetary gear 320, a second planetary gear 325, and a ring gear 330. Each of the gears comprises a series of teeth and grooves, so that the gears mesh. More specifically, each planetary gear meshes with the sun gear and the ring gear, so that as the planetary gears move, they roll without slipping relative to the sun gear and the ring gear. Typically, the planetary gears are Petition 870250083817, dated 09 / 17 / 2025, pp. 66 / 119 21 / 54 supported by a conveyor (which is not shown in Figure 3). Therefore, a movement of the planetary gears causes a movement (e.g., a rotation) of the conveyor, which movement can be used to power another component.

[0078] An epicyclic gearbox can be operated by driving one or more of: the sun gear 310, the ring gear 330, the carrier (not shown), and one or more of the planetary gears 320, 325. For example, a motor can be connected to one of these components and used to cause movement of said component. In operation, driving the sun gear around its central geometric axis causes the planetary gears to move in an orbit around the sun gear 310. If the ring gear 330 is held stationary (e.g., stationary relative to a gearbox housing), then the meshing contact between the ring gear and the planetary gears causes the planetary gears to rotate around their respective geometric axes (and thus causes movement of the carrier). Similarly, for example, the ring gear can be held stationary, with the planetary gears being driven.This movement of the planetary gears then causes a movement of the sun gear.

[0079] Epicyclic gearboxes Petition 870250083817, dated 09 / 17 / 2025, page 67 / 119 Conventional 22 / 54 gearboxes comprise a circular sun gear 310, circular planetary gears 320, 325 and a circular gear 330. As shown in Figures 4a and 4b, the present description considers an epicyclic gearbox 400 with a non-circular ring gear 402 and a non-circular sun gear 404.

[0080] This epicyclic gearbox 400 of the present description further comprises one or more planetary gears 406, 408, which planetary gears are located between the ring gear 402 and the sun gear 404 and are arranged to move along a path around the sun gear. Typically, each of the ring gears, the sun gear and the planetary gears comprises a series of teeth and grooves so that the gears mesh (as described above) to promote such movement.

[0081] Planetary gears 406, 408 are arranged to move along a continuous (i.e., non-circular) path defined by the ring gear 402 and the sun gear 404. Therefore, as the planetary gears move along the path, a distance between the planetary gears and a geometric axis of rotation 410 of the sun gear (and the epicyclic gearbox) changes. This can be seen as a radius of the planetary gear path changing as Petition 870250083817, dated 09 / 17 / 2025, pp. 68 / 119 23 / 54 that the planetary gears move along this path.

[0082] The sun gear 404 comprises one or more valleys (or minima) and one or more peaks (or maxima), where the sun gear has a larger radius at the peaks than at the valleys. These valleys and / or peaks cause the aforementioned change in the path radius of the planetary gears 406, 408 as the planetary gears move around the sun gear.

[0083] The ring gear 402 typically comprises similar maxima and minima (e.g., peaks and valleys), where typically the peaks of the sun gear 404 are arranged to coincide with valleys of the ring gear during normal rotation of the planetary gears 406, 408, so as to define a path of substantially constant width between the sun gear and the ring gear. Therefore, as the planetary gears move around the sun gear, they move through the peaks and valleys, so as to alter a radius of the path of the planetary gears.

[0084] The maxima / peaks of the 404 sun gear can be considered the points of the sun gear that are furthest from the geometric axis of rotation of the sun gear (or from the geometric axis of rotation of the epicyclic gearbox), with the minima / valleys of the gear Petition 870250083817, dated 09 / 17 / 2025, pp. 69 / 119 24 / 54 solar being the points on the sun gear that are closest to the geometric axis of rotation of the sun gear.

[0085] On the other hand, the maxima / peaks of the ring gear 402 can be considered the points of the ring gear that are closest to the geometric axis of rotation 410 of the sun gear 404 (or the geometric axis of rotation of the epicyclic gearbox), with the minima / valleys of the ring gear being the points of the ring gear that are furthest from the geometric axis of rotation of the sun gear.

[0086] Typically, each planetary gear 406, 408 is sized so as to fit between a peak of the sun gear 404 and a valley of the ring gear 402, or between a valley of the sun gear and a peak of the ring gear.

[0087] The change described above in the path radius of the planetary gears 406, 408 can be used to implement a radial pump. Specifically, a pump may comprise the epicyclic gearbox 400 and one or more pistons, with each of the pistons being connected to (or more generally associated with) one of the planetary gears 406, 408 of the epicyclic gearbox. The drive of any of the gears in the epicyclic gearbox causes a relative motion between the planetary gears and the sun gear 402 which, due to the change in the path radius of the planetary gears, Petition 870250083817, dated 09 / 17 / 2025, pp. 70 / 119 25 / 54 causes a change in volume within the pistons (e.g., compression and / or decompression) and thus a change in pressure within the pistons.

[0088] As used in this document, the term “piston” is used to refer to any component that provides a force depending on a compression and / or extension so that the piston is capable of providing a pumping force. Therefore, although the piston typically comprises a piston head that is arranged to move so as to alter a volume in the piston (and thus provide a pumping force), the piston may equally comprise, for example, a solid material, such as a spring or a rubber component, where the compression and extension of this material can be used to provide a pumping force.

[0089] The pistons are each associated with (for example, connected to) one of the planetary gears 406, 408 at one end. In order to cause the aforementioned pressure change, the second end of each piston may be connected to one or more of: another planetary gear, the sun gear and / or other external component that moves relative to the planetary gears as the planetary gears move along their path.

[0090] As shown in Figures 4a and 4b, in some Petition 870250083817, dated 09 / 17 / 2025, pp. 71 / 119 In 26 / 54 modes, the piston is connected to a first planetary gear 406 and a second planetary gear 408, where these planetary gears are typically arranged symmetrically around the (e.g., geometric axis of rotation of the) sun gear. The planetary gears being arranged symmetrically around the sun gear comprise the planetary gears being arranged on opposite sides of the sun gear and / or at opposite points of the path.

[0091] The embodiment of Figures 4a and 4b shows ring and sun gears 402, 404 with a regular arrangement of peaks and valleys and with a plurality of ring gears. It will be appreciated that, more generally, the sun gear and / or the ring gear may comprise any number of peaks and valleys (e.g., a single peak and valley) and that the epicyclic gearbox 400 may comprise any number of planetary gears (e.g., a single planetary gear). Furthermore, although the embodiment shown in Figures 4a and 4b comprises a rotationally symmetric sun gear and a rotationally symmetric ring gear, it will be appreciated that a change in radius may be achieved with an asymmetric sun gear and / or ring gear (e.g., with a sun gear comprising a single short valley and a single long peak). However, rotationally symmetric gears Petition 870250083817, dated 09 / 17 / 2025, pp. 72 / 119 27 / 54 symmetrical gears are typically used, as these can be more easily used to provide a regular change in the radius of the planetary gear path and therefore a consistent pumping force.

[0092] With reference to Figures 4a and 4b, this embodiment comprises a first planetary gear 406 and a second planetary gear 408 which are arranged to move along a (regularly) oscillating (e.g., sinusoidal) path, where each gear moves through a series of peaks and valleys, or through a series of maximum radius points and minimum radius points. As the gears move along this path, a radial distance between the planetary gears and the geometric axis of rotation 410 of the sun gear changes and a radial distance between the planetary gears changes. In this respect, the pair of planetary gears is typically arranged so as to pass simultaneously through a pair of peaks and / or so as to pass simultaneously through a pair of valleys in order to ensure that there is such a change in the radial distance between the planetary gears.

[0093] This movement causes a change in the volume of a piston connected to one or more of the planetary gears (for example, through a conveyor connected to the planetary gears). As explained above, such Petition 870250083817, dated 09 / 17 / 2025, pp. 73 / 119 28 / 54 A change in volume causes a corresponding change in pressure, and this change in pressure can be used to apply a pumping force to a fluid.

[0094] Typically, the epicyclic gearbox 400 comprises a plurality of planetary gears 406, 408 and / or a plurality of planetary gear pairs. Typically, each pair of planetary gears is arranged symmetrically around the geometric axis of rotation 410 of the sun gear 404.

[0095] Typically, planetary gears 406, 408 are evenly spaced along the path defined by the sun gear and planetary gear 402, where this allows for the delivery of regular pressure and regular pumping force. Normally, each of the planetary gears is similar, where this also allows for the delivery of regular pressure and regular pumping force.

[0096] Typically, one or more of (and / or each of) the 406, 408 planetary gears is associated with a piston, wherein one end of the piston is arranged to move together with the associated planetary gear so as to cause compression or extension of the piston. A second end of the piston is typically connected to one or more of: another planetary gear (for example, the other planetary gear of a planetary gear pair) Petition 870250083817, dated 09 / 17 / 2025, pp. 74 / 119 29 / 54 or the 404 sun gear.

[0097] The second end of the piston can be connected to a component of the sun gear 404 and / or the planetary gear that is arranged to rotate relative to the sun gear and / or the planetary gear so as to avoid collisions between multiple pistons. In particular, the connection of the second end of a piston to the sun gear and / or the planetary gear can be arranged to rotate so as to remain radially aligned with the planetary gear associated with the piston (while the axial distance between the second end of the piston and the planetary gear changes). Connecting each piston to a pair of planetary gears allows an arrangement in which numerous pistons can be provided with the circumferential distance between each piston remaining the same (since all planetary gears and thus all pistons are rotating at the same rate).This allows the use of a combined piston carrier in which a plurality of pistons are mounted, where this piston carrier is arranged to rotate with the planetary gears and to allow only radial movements of the pistons.

[0098] To provide a pump, the first end and / or the second end of each piston can be connected to a fluid source (for example, fluid source 252 in Figure 2) so that changes in pressure in the pistons Petition 870250083817, dated 09 / 17 / 2025, pp. 75 / 119 30 / 54 cause pumping of this fluid. The connection of the piston to the fluid source can be a direct connection, where the piston extracts fluid from the fluid source and then expels the fluid, or it can be indirect, where the change in pressure in the piston is used to drive fluid movement out of the fluid source (e.g., perpendicular to the direction of the piston). For example, the second end of the piston can be connected to the sun gear, and the change in pressure within the piston can be used to drive a working fluid along a geometric axis aligned with the geometric axis of rotation of the sun gear. Parametric profiles

[0099] Typically, both the 402 ring gear and the 404 sun gear have non-circular (i.e., parametric) profiles. Specifically, each of the ring gears and the sun gear typically has a profile comprising a sinusoidal wave superimposed on an ellipse (i.e., a circle).

[00100] This profile can be defined by the following parametric equations: x(t) = ycos (t) + a · sin(. · t) · cos(t) y(t) = ^sin (t) + a · sin(. · t) · sin(t)

[00101] These Cartesian equations can also be written as a polar equation: Petition 870250083817, dated 09 / 17 / 2025, pp. 76 / 119 31 / 54 r(t) = 2 + a · sin(ft) where, t is a parametric variable, et ranges from 0 to 2π.

[00102] It will be appreciated that this polar equation (and the associated Cartesian equations) could equally be written as: r(t) = 2 + a · cos (ft) x(t) = 2cos(t) + a · cos(f · t) · cos(t) y(t) = 2 sin (t) + a · cos(f · t) · sin(t)

[00103] In the equations above: P is a mean diameter (e.g., pitch circle) of a gear around the center of rotation 410 of the epicyclic gearbox (e.g., so that (defines the mean radius of a gear and the sinusoidal term(s) define(s) a variation of the radius of said gear around this mean radius).

[00104] The diameter of the sun gear 404 is smaller than the diameter of the ring gear 402, with the planetary gears 406, 408 being dimensioned to fit between these diameters.

[00105] a is a wave amplitude that defines the amplitude of maxima and minima (e.g., peaks and valleys) of a gear. That is, a defines a variation of a profile. Petition 870250083817, dated 09 / 17 / 2025, pp. 77 / 119 32 / 54 of the gear from the mean diameter P. The value of a may depend on the space available for the epicyclic gearbox 400 and / or the pump and / or the required pumping force / volume.

[00106] . is a wave frequency that defines a number of maxima and minima (e.g., peaks and valleys) of a gear. In this respect, a single cycle of a sinusoidal wave (from one maximum to a subsequent maximum) can be considered a wave, where each gear has . waves.

[00107] The ring gear and the sun gear typically have profiles comprising both a constant radial term and a variable (e.g., sinusoidal) radial term. This leads to a non-circular gear profile, whereas the use of a sinusoidal radial term leads to a regular (though still non-circular) gear profile. Typically, the gear profiles are each rotationally symmetrical, where such rotational symmetry can be achieved by using an integer for the wave frequency.

[00108] Gears typically comprise a plurality of teeth so that any adjacent pair of gears is capable of meshing together. And because of these teeth, each of the gears is not normally perfectly circular. In this respect, one can consider Petition 870250083817, dated 09 / 17 / 2025, pp. 78 / 119 33 / 54 that a gear comprises a friction wheel with teeth, wherein a gear pitch circle corresponds to an outer circumference of the friction wheel, such that the pitch circle provides a reference circle for determining the pitch of the gear teeth. Specifically, the circular pitch of a gear, which is the distance from one tooth centerline to the next, can be calculated by dividing the circumference of the pitch circle by the number of teeth on that gear.

[00109] The term pitch circle diameter is therefore used to identify that gears typically comprise a series of teeth located around a circular gear. References in this document to gears being non-circular refer to gears being non-circular due to factors other than the gear teeth. The descriptions in this document are applicable to non-circular gears in general, so it should be appreciated that while the detailed description refers to gears with non-constant pitch circle diameters (e.g., where a gear profile comprises a superposition of a circular profile with a sinusoid), more generally the present descriptions refer to the supply of gears with a non-circular pitch circle.

[00110] As used in this document, the Petition 870250083817, dated 09 / 17 / 2025, pp. 79 / 119 34 / 54 “The profile of a gear refers to the shape of the gear excluding teeth. For example, Figures 4a and 4b show a ring gear 402 and a sun gear 404, each of which has non-circular profiles, as well as a pair of planetary gears 406, 408, whose planetary gears have circular profiles. In practice, each gear typically comprises a plurality of teeth so that, for example, the planetary gears may be similar to the planetary gears 320, 325 of the conventional epicyclic gearbox Figure 3. These planetary gears can be considered as comprising a series of teeth that are arranged around a circular profile. Similarly, the ring gear and the sun gear can be considered as comprising a series of teeth that are arranged around a non-circular profile.

[00111] The variables above are shown in Figures 5a and 5b.

[00112] With reference to Figure 5a, an embodiment of a conventional gear with a circular profile is shown. This gear has a pitch circle diameter P, where the gear further comprises a series of teeth arranged around this pitch circle diameter. Such a gear can, for example, be used for the planetary gears 406, 408 of the epicyclic gearbox 400 Petition 870250083817, dated 09 / 17 / 2025, pp. 80 / 119 35 / 54 of Figures 4a and 4b. Although the gear comprises teeth such that the gear is not strictly circular, the gear can be considered as having a circular profile, where the teeth are arranged around this circular profile.

[00113] With reference to Figure 5b, an embodiment of a ring gear and a sun gear according to the present description is shown. The ring gear comprises twelve waves (e.g., ring gear = 12) and the sun gear comprises six waves (sun gear = 6). The ring gear and the sun gear each have non-circular profiles, wherein the embodiment of Figure 5b shows a sun gear with a profile that is composed of a sinusoidal wave superimposed on a circle, such that the sun gear comprises a series of maximum points with a radius equal to (+) and a series of minimum points with a radius equal to (-). Typically, the sun gear and the ring gear each comprise a series of teeth that are arranged around their non-circular profiles.

[00114] With the modality of Figure 5b, )sol,minima=asol,máxima· It will be appreciated that the gears can also be provided with different values ​​of )soi,minima and ^soi,máxima.

[00115] As mentioned above, typically each of the ring gear and sun gear also comprises Petition 870250083817, dated 09 / 17 / 2025, pp. 81 / 119 36 / 54 a series of teeth arranged around the circumference of these gears. These teeth are not shown in the figures.

[00116] In the example shown, the ring gear 402 is defined with fanel= 10, while the sun gear 404 is defined with fsol= 8. It will be appreciated that several other combinations of wave frequencies can be applied.

[00117] In order to avoid damaging the planetary gears 406, 408 as they move along the path defined by the ring gear 402 and the sun gear 404, the epicyclic gearbox 400 is typically arranged so that during the use of the epicyclic gearbox, the width of this path is substantially constant. Values ​​that provide such a substantially constant path width are given below. In some embodiments, the sun gear, the ring gear and / or the planetary gears may be flexible to reduce any damage that may occur due to (small) variations in the path width.

[00118] As described above, when the sun gear 404 is driven (for example, by a motor associated with the sun gear), the planetary gears 406, 408 are propelled into orbit around the sun gear due to the interlocking teeth of each of the gears. As the planetary gears rotate, Petition 870250083817, dated 09 / 17 / 2025, pp. 82 / 119 37 / 54 They are driven towards the maxima and minima (i.e., peaks and valleys) of the parabolic curves that define the sun gear and the ring gear 402. Figure 4a shows the planetary gears when they are located at maxima of the parabolic curves that define the sun gear and the ring gear. At this point, the distance between the planetary gears is maximum. A piston fixed between the planetary gears will therefore be at a point of maximum extension and maximum volume at this point in the cycle.

[00119] Figure 4b shows the planetary gears 406, 408 when each of them is located at minima of parabolic curves that define the sun gear 404 and the ring gear 402. At this point, the distance between the planetary gears is minimal. A piston fixed between the planetary gears will therefore have maximum compression and minimum volume at this point in the cycle.

[00120] Conventional radial hydraulic pumps, as shown in Figure 1, have exactly one maximum and one minimum extension for each piston per cycle of the drive ring; therefore, the rapid cycle of the pump requires a rapid rotation of the drive ring. This means that translating an external rotational force from, for example, a large turbine, into pumping action requires additional extensive gearing to increase the rotational speed of the drive ring compared to the turbine. Petition 870250083817, dated 09 / 17 / 2025, page 83 / 119 38 / 54 drive. This additional gear reduces the overall efficiency of the system. Using the epicyclic gearbox 400 of the present description, it is possible to provide a radial hydraulic pump that has a plurality of extension cycles for each piston per drive ring cycle. This allows the efficient translation of an external rotational force into a pumping action. For example, Figures 4a and 4b show an embodiment of the gearbox in which a piston connected to the first planetary gear 406 and the second planetary gear 408 is driven through multiple maxima and minima over a single complete rotation of the sun gear 404.

[00121] In order to achieve an efficient and reliable epicyclic gearbox arrangement, in some embodiments a number of restrictions are imposed on the proportions and parameters that define the sun gear 404, the ring gear 402 and the planetary gears 406 and 408. These restrictions can be used to ensure that the planetary gears remain meshed in contact with the sun gear and the ring gear throughout their orbit.

[00122] In some embodiments, these restrictions refer to the values ​​for P, a, and in the equations above, where certain values ​​are found to provide particularly effective gearboxes. Petition 870250083817, dated 09 / 17 / 2025, pp. 84 / 119 39 / 54

[00123] Typically, the sun gear 404 and the ring gear 402 are shaped so that the planetary gears 406, 408 remain in contact with the sun gear and the ring gear at all points along their path around the sun gear. Such a constraint requires that at each point in the path of a planetary gear around the sun where the profile of the sun gear is at a maximum point, for example, at each peak of the sun gear, the ring gear must have a corresponding minimum point. Similarly, at all points where the profile of the sun gear is at a minimum point, for example, at each valley of the sun gear, the ring gear must have a corresponding maximum point.

[00124] In some embodiments, in order to ensure this consistent contact, the sun gear and the ring gear comprise different numbers of maxima and minima (e.g., peaks and valleys). In some embodiments, the sun gear and the ring gear have different numbers of maxima and minima (e.g., peaks and valleys), where the sun gear and / or the ring gear may be arranged to rotate as the planetary gears move along the path, so that the planetary gears remain in contact with the sun gear and the ring gear, despite the different number of maxima and minima. Petition 870250083817, dated 09 / 17 / 2025, page 85 / 119 40 / 54 Parametric dimensions

[00125] There are three primary curves that define the operation of the epicyclic gearbox 400: the curve defined by the ring gear radius 402 (ranel(t)), the curve defined by the ring gear radius 404 (rooi(t)), and the curve defined by the path radius of the planetary gears 406, 408 (^planetarypath(t)). The value for each curve is typically determined depending on the values ​​of one or more other curves where a value is selected for one of the curves (for example, based on a desired size of the epicyclic gearbox) and the values ​​for the other curves are then determined based on this selected value. In particular, the values ​​for the ring gear dimensions can be determined based on the selected dimensions of the sun gear (or vice versa).

[00126] In a preferred embodiment, the pitch circle diameter of the planetary gears and the pitch circle diameter of the planetary gear path are determined depending on the pitch circle diameters of the ring gear and the sun gear. This allows values ​​to be chosen for the planetary gear that enable the planetary gear to mesh with both the sun gear and the ring gear.

[00127] The diameter of the pitch circle for each Petition 870250083817, dated 09 / 17 / 2025, pp. 86 / 119 41 / 54 planetary gear 406, 408 can be determined using the equation: Pplaneta _PanelPsol = 2

[00128] The diameter of the pitch circle of the path of planetary gears 406, 408 can be determined using the equation: Ptrajeto planeta _Panel +Psol 2 = 2

[00129] To calculate constraints on the ring gear 402 and the sun gear 404 that ensure a constant path width, it is possible to derive equations with respect to the angular displacement of the components.

[00130] First, consider the movement of the components with the ring held stationary between a first and a second position. The sun gear is rotated by an angle θ. As a consequence of this rotation, the planet gear rotates by an angle θ, and a carrier attached to the center of the planet rotates by an angle θ. The point of contact between the planet and sun gear, measured along the surface of the sun gear, moves a total of Ns:s + Ns:5, where Ns is the number of teeth on the sun gear, because the point of contact moves both due to rotation by the sun gear and to the movement of the contact with the planet due to the orbit of the Petition 870250083817, dated 09 / 17 / 2025, page 87 / 119 42 / 54 planet,

[00131] The point of contact between the planetary gear and the sun, measured along the surface of the planetary gear, moves a total of NP:P— NP:c, where NP is a number of teeth on the planetary gear, because the rotation of the planetary gear is accompanied by a change in the point of contact with the sun gear,

[00132] Since the distance moved by the point of contact in the sun and planet gears must be the same, we can derive the following equation: Ns:s+ Np:' — (Ns+ Np ):c= 0

[00133] Similarly, considering only the movement of the ring and the planets, with the sun stationary, we can derive the following equation: Nr:r— ​​Np:' — (Nr— Np ):c= 0

[00134] Rearranging the second equation can be used to write NP:P in terms of the other variables. This can then be substituted into the first equation to give: Ns:s+ Nr:r— ​​(Nr— Np ):c— (Ns+ Np ):c= 0

[00135] This can be rearranged to provide: Ns Nr :cNr + Ns :s+ Nr + Ns:r

[00136] If the ring is considered fixed, then the equation above can be further simplified to: Petition 870250083817, dated 09 / 17 / 2025, pp. 88 / 119 43 / 54 n :5 Nr+ Ns:s

[00137] Note that the number of teeth on the gear is directly proportional to the diameter of the gear pitch circle, which is proportional to the orbital path length L.

[00138] As discussed earlier, the profiles of sun and ring gears are typically described by the following equations: x(t) = ycos (t) + a · sin(. · t) · cos(t) y(t) = ^-sin (t) + a · sin(. · t) · sin(t)

[00139] For the maximum and minimum values ​​of the solar and planetary gears 402, 404 correspond during rotation, the solar gear must rotate by an amount :s= 87- + 7 when a planet moves from one ring maximum to the next ring maximum, for example, when the planetary gear (or equivalently, the carrier)1η moves — along its orbital path.

[00140] Substituting these two conditions into the equation by :5 gives:

[00141] This equation can be rearranged further to provide: Petition 870250083817, dated 09 / 17 / 2025, pp. 89 / 119 44 / 54 fs = Ns.1 + fsNr + ns

[00142] As noted earlier, N is proportional to P, where P is the diameter of the pitch circle or the length of the orbital path. Therefore, the equation can also be rewritten in the following terms. f . p . / . J sol __1sol __ %solfsol+fanelPsol+ Panellsol+ lanel where f = wave frequency; P = diameter of the pitch circle; l = length of the parametric curve.

[00143] For any chosen values ​​of f for the ring and sun gear, the diameters can then be chosen using the equation above to allow the planet to travel a path of constant width. The use of a path of constant width ensures that the planetary gear is not compressed during the cycle and is able to mesh with the sun and ring gears at all points along the path.

[00144] Rearranging the equation above yields the equation: PanelPsol fanel * τ— fanel

[00145] Therefore, given a selected diameter of the 404 sun gear and a selected ratio of wave frequencies of the annular gear and the 402 sun gear, it is possible to determine a suitable diameter for the gear. Petition 870250083817, dated 09 / 17 / 2025, pages 90 / 119 45 / 54 ring finger.

[00146] Returning then to the lengths, the perimeter (or length of the parametric curve) l of each gear can be determined as: f29l / dx\2_ / dv\2,l= J0 <ddt)+\dt)dt

[00147] Similarly, this length can be determined as: f29„ / dr\2 l= i A!2+Udtonde: r(t) = ' + )sin (ft), = )fcos(ft)t

[00148] As can be seen from this equation, when f = 0 (for example, there is no peak and the sun gear and ring gear are circular), the perimeter length of each gear is simply the perimeter of a circle (109^ dt). According to the present description, fanel>0 and fsoí >0 so that the perimeter length of each gear is greater than the length of a circular gear of equivalent diameter.

[00149] The parametric equations used to determine the length of each gear have three variables: the pitch circle diameter P, the wave frequency f, and the wave amplitude ).

[00150] As described above, given a diameter Petition 870250083817, dated 09 / 17 / 2025, pp. 91 / 119 By selecting the 46 / 54 ratio of the 404 sun gear and a selected ratio of wave frequencies from the ring gear and the 402 sun gear, it is possible to determine a suitable diameter for the ring gear. Notably, this diameter does not depend on the wave amplitude of either gear. Instead, this wave amplitude is independent of the ratio between the pitch circle diameters and the wave frequencies. Therefore, the wave amplitude a can be adjusted independently. As the value of a increases, the change in radius as the 406, 408 planetary gears move between the maximums and minimums of the 402 ring gear and the 404 sun gear increases. Therefore, increasing the value of a increases the pressure changes that can be driven by the gearbox. However, increasing a also increases the resistance of the system.This tends to form a limit at a usable value of a (the limit of which depends, for example, on the materials used in the 400 epicyclic gearbox and the mechanical properties associated with those materials).

[00151] To ensure a constant connection between the ring gear 402 and the sun gear 404, the epicyclic gearbox 400 is typically arranged so that the width of the path followed by the planetary gears 406, 408 is substantially constant. For Petition 870250083817, dated 09 / 17 / 2025, pp. 92 / 119 47 / 54 To achieve this, the ring gear and the sun gear are typically arranged so that the radial distance between the ring gear and the sun gear remains approximately constant. Therefore, typically, a_sun = a_ring.

[00152] An additional restriction may be applied by the space available for the planetary gears 406, 408, where this space must not exceed the space available within the limits of the ring gear 402 and the sun gear 404. To ensure that sufficient space is available, the gearbox is normally arranged so that: COGpriGSntOfiajeto planeta _ Ξ > &planet Kplanet where nplanet is the number of planetary gears. To provide a gearbox with maximum pumping power for an available space, the number of planetary gears is typically selected to be equal to the sum of the number of waves of the sun gear and the number of waves of the ring gear, that is: Kplaneta fsol + fanel

[00153] It will be appreciated that fewer planetary gears can be provided.

[00154] Given the input values ​​which are: a selected pitch circle diameter of the 404 sun gear; a selected wave amplitude of the sun gear; Petition 870250083817, dated 09 / 17 / 2025, pp. 93 / 119 48 / 54 and a selected wave frequency of the solar gear, the appropriate values ​​of the remaining components can be determined using the equations given above.

[00155] In an example that uses the following input values: Parameter Value Source Solar PCD 2 64 mm Input Solar wave amplitude 5 mm Input Solar wave frequency 8 Input Ring wave frequency 10 Input

[00156] The equations above can be satisfied using the following values. Parameter Value Parametric curve length of the planetary path -958.927 mm Arc length of the planetary path -95.8927 mm Sun rotation from maximum to maximum -1.414 radians PCD ring 330 mm Planetary path PCD 2 97 mm Parametric curve length of the sun -848.089 mm Parametric curve length of the ring -1060.089 mm

[00157] In this example, fanel= 10 and fsol= 8. Therefore, for the sun's rotation to the next maximum to correspond to the next ring maximum, the solar gear 104 must rotate (9 + (9-, which when fanel= 10 and fsol= 8 results in a required rotation of the solar gear of approximately 1.414 radians between maxima.

[00158] It will be appreciated that these values ​​are merely an example and that a variety of different values ​​can be selected in order to obtain a strength of Petition 870250083817, dated 09 / 17 / 2025, pp. 94 / 119 49 / 54 desired pumping.

[00159] For example, Figure 6 illustrates a gearbox with a ring gear and sun gear that are similar to the ring gear and sun gear of Figures 4a and 4b (fanei = 10 and fsol = 8). With the embodiment of Figure 5, the system comprises 18 planetary gears.

[00160] Another example is the embodiment of a gearbox according to the present description shown in Figure 7, which shows an epicyclic gearbox according to the present description that has fanel = 10 and fsol = 4 values. Alternatives and modifications

[00161] It will be understood that the present invention has been described above purely by way of example, and modifications of details may be made within the scope of the invention.

[00162] For example, the gearbox can have any number of planetary gears, as long as that number of planetary gears is able to fit between the ring and sun gears, so that no planets touch. For example, the gearbox can have one, two, four, or eight planetary gears.

[00163] In some embodiments, the gearbox has a number of planetary gears that is no greater than one order of rotational symmetry of the gearbox (e.g., the combination of the sun gear). Petition 870250083817, dated 09 / 17 / 2025, pages 95 / 119 50 / 54 404 and the ring gear 402). For example, if the gearbox has a rotational symmetry of order two (as in the example where fanel = 10 and fsol = 8), the gearbox may comprise one or two planetary gears. If the system has a rotational symmetry of order four (for example, if fanel = 16 and fsol = 8), the gearbox may comprise one, two, three, or four planetary gears. Such embodiments ensure that all planetary gears can be positioned at points where the radial distance between the ring and sun gears is equal to a constant value, said constant value preferably being the diameter of the planetary gear.

[00164] Similarly, although the example above employs frequency values ​​fanel= 10 and fsol= 8, it will be appreciated that many other combinations of values ​​would satisfy the above constraints.

[00165] Similarly, although the ring gear and the sun gear, in the example above, can be modeled by the parametric equations given in equations 1 and 2, in other embodiments, these gears can be modeled by alternative parametric equations.

[00166] Similarly, although the detailed description has mainly considered the use of circular planetary gears, in alternative embodiments the Petition 870250083817, dated 09 / 17 / 2025, pp. 96 / 119 51 / 54 planetary gears could have non-circular profiles. For example, planetary gear profiles can be elliptical. In this case, one of the sun and ring gears could have a circular profile.

[00167] In general, a plurality of (types of) gears have non-circular profiles. More specifically, typically two of the following: the ring gear 402, the sun gear 404 and the planetary gear(s) 406, 408 have non-circular profiles.

[00168] The piston can be connected to the center of the planetary gear. Similarly, the piston can be connected to a point that is not central to the planetary gear. For example, if the planetary gear is elliptical, the piston can be connected to a focus of the ellipse.

[00169] Although the detailed description has mainly considered embodiments in which the sun gear 404 is driven, the ring gear 402, the planetary gears 406, 408 and / or the carrier may also be driven, instead of or in addition to the sun gear drive. Similarly, any of the sun gears, ring gear and carrier may be fixed or, alternatively, none of the gears may be fixed.

[00170] Typically, the epicyclic gearbox 400 and / or the pump comprises a unit of Petition 870250083817, dated 09 / 17 / 2025, pp. 97 / 119 52 / 54 control and / or is associated with a control unit, where the control unit is arranged to drive one or more of the gearbox gears (e.g., the sun gear 402) depending on a desired pumping force. In this respect, the pumping force is typically related to the torque supplied to the gearbox and / or the speed of movement of the planetary gears 406, 408.

[00171] While in the example above, a single carrier was described, in other embodiments there may be multiple carriers, with each carrier associated with a respective subset of the planets.

[00172] The pistons can be integral or separate from the carrier. The pistons can be connected (directly or indirectly) to any one or more of the planetary gears, ring gears, a carrier, or the sun gear.

[00173] In some embodiments, the piston is connected at one end to the center of the sun and at a second end to the center of the planet. In some embodiments, the piston is connected at one end to the center of the sun and at a second end to the carrier.

[00174] In some embodiments, each planetary gear may be associated with a corresponding piston. In embodiments, each planetary gear may be associated Petition 870250083817, dated 09 / 17 / 2025, pp. 98 / 119 53 / 54 to a respective plurality (e.g., pair) of pistons.

[00175] In some embodiments, each piston may have a single opening to a fluid reservoir. In some embodiments, each piston may have a connection to each of a fluid reservoir and a fluid outlet.

[00176] Pumps can be used for a variety of applications. For example, heat pumps use the compression and expansion of the working fluid at different points in the pump cycle to cause thermal energy to be absorbed from the surroundings at one point in the cycle and emitted at another point in the cycle. This can be used to cool or heat a device, depending on the pump settings.

[00177] Pumps can also be used to maintain the pressure of a container. For example, a pump can be used to increase or decrease the pressure in a chamber to a desired level. This has applications in devices such as scanning electron microscopes, which require low pressure in the operating chamber, as well as in simple devices such as bicycle tires.

[00178] An additional use for pumps arises in the transport of fluids. For example, pumps are used to transfer molten plastic mass out of the melting reactor during plastic processing. Pumps are also used to transfer water from inside to Petition 870250083817, dated 09 / 17 / 2025, pp. 99 / 119 54 / 54 outside of ships and to move coolant around devices such as automotive engines.

[00179] Hydraulics generally refers to the use of liquid fluid energy to perform work. However, the operating principles of a hydraulic pump generally apply to pneumatic pumps, which use compressible gases as the working fluid. The epicyclic gearbox 400 described in this document can be used with a hydraulic pump, a pneumatic pump, or another type of pump.

Claims

1. Gearbox for a pump, the gearbox being characterized in that it comprises: a ring gear; a sun gear; and one or more planetary gears arranged between the ring gear and the sun gear, the planetary gears being arranged to move around the sun gear along a continuous path; wherein the ring gear, the sun gear and the planetary gears are arranged so that a radius of the path varies as the planetary gears move along the path.

2. Gearbox, according to any of the preceding claims, characterized in that it comprises a piston, wherein the piston is associated with at least one planetary gear such that an amount of compression of the piston changes as said planetary gear moves along the path.

3. Gearbox, according to claim 2, characterized in that a second end of the piston is associated with an additional component of the gearbox such that the first end of this piston moves relative to the second end of the piston as the planetary gear moves along the path.

4. Method according to claim 3, characterized in that the piston is arranged so that the first end of the piston moves towards and / or away from the second end of the piston as the planetary gear moves along the path.

5. Gearbox according to claim 3 or 4, characterized in that the second end of the piston is connected to one or more of: a sun gear; a ring gear; an additional planetary gear; and a gearbox carrier.

6. Gearbox, according to any of the preceding claims, characterized in that it comprises a plurality of pistons, wherein each piston is associated with a respective planetary gear.

7. Gearbox, according to any of the preceding claims, characterized in that at least two of the ring gears, the sun gear and one or more planetary gears have non-circular profiles.

8. Gearbox, according to Petition 870250083817, dated 09 / 17 / 2025, pp. 102 / 119 3 / 10 claim 7, characterized in that each of the sun gear and the ring gear has a non-circular profile, preferably in which the sun gear and the ring gear have corresponding non-circular profiles.

9. Gearbox, according to any of the preceding claims, characterized in that: the sun gear has a profile comprising a sinusoidal wave superimposed on an ellipse, preferably a sinusoidal wave superimposed on a circle; and / or the ring gear has a profile comprising a sinusoidal wave superimposed on an ellipse, preferably a sinusoidal wave superimposed on a circle.

10. Gearbox, according to any of the preceding claims, characterized in that the sun gear profile and / or the ring gear profile, and, preferably, the pitch circle diameter of each sun gear and ring gear, is defined by the equation: r(t) = 2 + a · sin(ft) where: t is a parametric variable with values ​​from 0 to 2π; r is a gear radius at a value t; Petition 870250083817, dated 09 / 17 / 2025, p. 103 / 119 4 / 10 P is an average gear diameter; a is a wave amplitude; ef is a wave frequency.

11. Gearbox, according to any of the preceding claims, characterized in that the ring gear comprises a different number of minimum and / or maximum gears than the sun gear.

12. Gearbox, according to claim 11, characterized in that the ring gear comprises a greater number of minimum and / or maximum gears than the sun gear.

13. Gearbox, according to any of the preceding claims, characterized in that the mean diameters and wave numbers of the sun gear and the ring gear are linked by the equation: P . P . 1 sol _ 1 annel fsol fanel where: Psol is a mean diameter of the sun gear; Panel is a mean diameter of the ring gear; fsol is a wave frequency of the sun gear; and fanel is a wave frequency of the ring gear.

14. Gearbox, according to any of the preceding claims, characterized in that it comprises a plurality of planetary gears, Petition 870250083817, dated 09 / 17 / 2025, pp. 104 / 119 5 / 10 in a preferred manner, comprising at least one pair of planetary gears, in a more preferred manner, comprising a plurality of pairs of planetary gears.

15. Gearbox, according to any of the preceding claims, characterized in that it comprises a number of planetary gears that is equal to an order of rotational symmetry of the gearbox, preferably an order of rotational symmetry of the combination of the sun gear and the ring gear.

16. Gearbox, according to any of the preceding claims, characterized in that the planetary gears are arranged symmetrically around a center of rotation of the gearbox.

17. Gearbox, according to any of the preceding claims, characterized in that: the ring gear is rotationally symmetrical; and / or the sun gear is rotationally symmetrical.

18. Gearbox, according to any of the preceding claims, characterized in that the path width is substantially constant.

19. Gearbox, according to any one of the preceding claims, characterized in that the sun gear, the ring gear and the planetary gears are arranged so that a radial distance between the sun gear and the ring gear at the point of contact of each of the planetary gears remains constant as said planetary gears move along the path.

20. Gearbox, according to any of the preceding claims, characterized in that one or more ring gears and sun gears are arranged to remain stationary as the planetary gears move along the path.

21. Gearbox, according to any one of claims 1 to 19, characterized in that each of the sun gear and ring gear are arranged to rotate as the planetary gears move along the path.

22. Gearbox, according to any of the preceding claims, characterized in that it comprises a motor for driving the motion of one or more of: the sun gear; the ring gear; one or more of the planetary gears; and a conveyor associated with one or more of the planetary gears, in a preferred manner, wherein the motor is arranged to operate in dependence on a desired pumping force.

23. Gearbox, according to any of the preceding claims, characterized in that: the sun gear comprises one or more minimum points, wherein the radius of the sun gear at said minimum points is less than an average radius of the sun gear; and / or the sun gear comprises one or more maximum points, wherein the radius of the sun gear at said maximum points is greater than an average radius of the sun gear.

24. Gearbox, according to any of the preceding claims, characterized in that: the ring gear comprises one or more minimum points, wherein the radius of the ring gear at said minimum points is less than an average radius of the ring gear; and / or wherein the ring gear comprises one or more maximum points, wherein the radius of the ring gear at said maximum points is greater than an average radius of the ring gear.

25. Gearbox, according to any of the preceding claims, characterized by the fact that: a variation in the amplitude of the minimum points of the sun gear is equal to a variation in the amplitude of the maximum points of the sun gear; and / or a variation in the amplitude of the minimum points of the ring gear is equal to a variation in the amplitude of the maximum points of the ring gear.

26. Method according to claim 25, characterized in that: the variation in the amplitude of the minimum points of the sun gear is equal to the variation in the amplitude of the maximum points of the ring gear; and / or the variation in the amplitude of the maximum points of the sun gear is equal to the variation in the amplitude of the minimum points of the ring gear.

27. Gearbox, according to any of the preceding claims, characterized in that the diameter of the sun gear is: at least 100 mm, at least 200 mm and / or at least 500 mm, and / or not more than 1,000 mm, not more than 800 mm and / or not more than 500 mm.

28. Gearbox, according to any of the preceding claims, characterized in that the diameter of the planetary gears is: Petition 870250083817, dated 09 / 17 / 2025, p. 108 / 119 9 / 10 at least 50 mm, at least 100 mm and / or at least 200 mm, and / or not more than 500 mm, not more than 400 mm and / or not more than 300 mm.

29. Gearbox, according to any of the preceding claims, characterized in that one or more of, and preferably each of, the sun gear, ring gear and planetary gears may comprise a plurality of teeth, preferably in which the teeth are regularly arranged around the profile of said gear.

30. Gearbox, according to any of the preceding claims, characterized in that it comprises at least two planetary gears, at least four planetary gears, at least eight planetary gears and / or at least ten planetary gears.

31. Pump, characterized in that it comprises the gearbox, as defined in any of the preceding claims.

32. Pump, according to claim 31, the pump being characterized in that it comprises a radial pump and / or a radial hydraulic pump.

33. Method for operating the gearbox, as defined in any one of claims 1 to 30, Petition 870250083817, dated 09 / 17 / 2025, pp. 109 / 119 10 / 10, the method being characterized in that it comprises actuating one or more of: the sun gear, the ring gear and one or more of the planetary gears.

34. Method according to claim 33, the method being characterized in that it comprises actuating said gear(s) depending on a desired pumping force.

35. Computer program product, characterized in that it comprises instructions which, when executed by a computer device, cause the computer device to execute the method as defined in claim 33 or 34.

36. Method, characterized in that it is for manufacturing the gearbox and / or pump, as defined in any of the preceding claims.

37. Gearbox parts kit, as defined in any of the preceding claims, the parts kit being characterized in that it comprises: the ring gear; the sun gear; and one or more planetary gears.

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