WO2016111925A1 - Appareils et systèmes de conversion d'énergie liquide en mouvement mécanique - Google Patents

Appareils et systèmes de conversion d'énergie liquide en mouvement mécanique Download PDF

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Publication number
WO2016111925A1
WO2016111925A1 PCT/US2016/012037 US2016012037W WO2016111925A1 WO 2016111925 A1 WO2016111925 A1 WO 2016111925A1 US 2016012037 W US2016012037 W US 2016012037W WO 2016111925 A1 WO2016111925 A1 WO 2016111925A1
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WIPO (PCT)
Prior art keywords
gear
disk
plate
fluid
coupled
Prior art date
Application number
PCT/US2016/012037
Other languages
English (en)
Inventor
David V. BOLGER
Original Assignee
Bolger David V
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US14/986,686 external-priority patent/US10753348B2/en
Application filed by Bolger David V filed Critical Bolger David V
Publication of WO2016111925A1 publication Critical patent/WO2016111925A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/26—Reciprocating-piston liquid engines adapted for special use or combined with apparatus driven thereby
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/002—Reciprocating-piston liquid engines details; components parts

Definitions

  • Fluid power systems involve using fluid under pressure to generate, control, and transmit power.
  • the fluid in such systems could be a liquid such as mineral oil or water, or could be a gas such as air or other gases.
  • the fluid could be pressurized by a pump. Pressurized fluid can be used to transmit power. For instance, energy of pressurized fluid could be converted to mechanical energy.
  • the present disclosure describes implementations that relate to apparatuses and systems for converting fluid energy to mechanical motion.
  • the present disclosure describes an apparatus.
  • the apparatus includes a plate configured to move along an underlying surface via a layer of pressurized fluid disposed in a gap between the plate and the underlying surface.
  • the apparatus further includes a first rack gear coupled to the plate and meshing with a first gear, where the first rack gear is movable with the plate.
  • the apparatus also includes a second rack gear meshing with a second gear, where the second rack gear is fixed, and where the second gear is coupled to the first gear.
  • the pressurized fluid in the gap repels the plate away from the underlying surface, thereby causing (i) the first rack gear to move linearly and the first gear to rotate, (ii) the second gear to rotate and move along the second rack gear, and (iii) the plate to move along the underlying surface.
  • the present disclosure describes an apparatus.
  • the apparatus includes a plate configured to rotate about an underlying surface of a cylindrical drum via a layer of pressurized fluid disposed in a gap between the plate and the underlying surface.
  • the apparatus further includes a rack gear coupled to the plate and meshing with a first gear.
  • the rack gear is configured to rotate with the plate as the plate rotates about the underlying surface of the cylindrical drum.
  • the apparatus also includes a ring gear coupled to a second gear. The ring gear is fixed and has external teeth meshing with teeth of the second gear, and the second gear is coupled to the first gear.
  • the pressurized fluid in the gap repels the plate away from the underlying surface of the cylindrical drum, thereby causing (i) the rack gear to extend away from the underlying surface and the first gear to rotate, (ii) the second gear to rotate and move along the ring gear, and (iii) the plate, the rack gear, the first gear, the second gear to rotate about the underlying surface.
  • the present disclosure describes an apparatus.
  • the apparatus includes a first disk having a hole disposed therein. A portion of the first disk that includes the hole is exposed to pressurized fluid.
  • the apparatus also includes a first shaft coupled to a center of the first disk, and a second disk disposed in the hole of the first disk.
  • the apparatus further includes a first rack gear coupled to the second disk at a first end of the first rack gear, and configured to mesh with a first gear at a second end of the first rack gear.
  • the apparatus also includes a second gear coupled to the first gear via a second shaft. The second gear is configured to rotate with the first gear at a particular speed, and the second shaft is configured to couple the first gear and the second gear to the first shaft.
  • the apparatus further includes a second rack gear meshing with the second gear.
  • the second rack gear is fixed.
  • the pressurized fluid repels the second disk disposed within the first disk, thereby causing (i) the first rack gear to move linearly and the first gear to rotate, (ii) the second gear to rotate and move along the second rack gear that is fixed, and (iii) the shaft and the first disk coupled thereto to rotate.
  • Figure 1A illustrates a hydraulic actuator, in accordance with an example implementation.
  • Figure 1B illustrates a change in fluid volume causing mechanical motion of a piston of the hydraulic actuator shown in Figure 1A, in accordance with an example implementation.
  • Figure 2A illustrates a front view of an apparatus for converting fluid pressure to mechanical motion, in accordance with an example implementation.
  • Figure 2B illustrates a perspective posterior view of the apparatus of Figure 2A, in accordance with an example implementation.
  • Figure 2C illustrates a horizontal spur gear coupled to a vertical spur gear, in accordance with an example implementation.
  • Figure 3A illustrates a perspective top view of another apparatus for converting fluid pressure to mechanical motion, in accordance with an example implementation.
  • Figure 3B illustrates a perspective bottom view of the apparatus of Figure 3A, in accordance with an example implementation.
  • Figure 3C illustrates a perspective top view of the apparatus of Figure 3A with a disk having multiple disks disposed therein, in accordance with an example implementation.
  • Figure 3D illustrates a perspective view of the apparatus of Figure 3C with two parallel disks, each disk having eight disks disposed therein, in accordance with an example implementation.
  • Figure 3E illustrates a split rack gear for the apparatus illustrated in Figure 3D, in accordance with an example implementation.
  • Figure 3F illustrates a shaft of the apparatus illustrated in Figure 3D coupled to another shaft that could be connected to a power source, in accordance with an example implementation.
  • Figure 3G illustrates a disk having multiple disks of varying sizes disposed therein, in accordance with an example implementation.
  • Figure 3H illustrates a perspective simplified view showing geometric relationships between elements of the apparatus illustrated in Figures 3A-3B, in accordance with an example implementation.
  • Figure 3I illustrates a side simplified view showing the geometric relationships between elements of the apparatus illustrated in Figures 3A-3B, in accordance with an example implementation.
  • Figure 3J illustrates a cross section of a disk showing the geometric relationships between elements of the apparatus illustrated in Figures 3A-3B, in accordance with an example implementation.
  • Figure 4A illustrates a partial perspective view of another apparatus for converting fluid pressure to mechanical motion, in accordance with an example implementation.
  • Figure 4B illustrates a partial perspective view of the apparatus of Figure 4A without a drum, in accordance with an example implementation.
  • Figure 4C illustrates is an exploded view of a portion of the apparatus of Figure 4A including a drum, a plate, and an elbow, in accordance with an example implementation.
  • Figure 4D illustrates a perspective view of the apparatus of Figure 4A with a rack gear and gear train at a particular rotary position, in accordance with an example implementation.
  • Figure 4E illustrates a zoomed-in view of a slide support, an elbow, and an arm, in accordance with an example implementation.
  • Figure 4F illustrates another perspective view of the apparatus as shown in Figure 4D, in accordance with an example implementation.
  • Figure 4G illustrates eccentric disposition of a drum relative to a ring gear, in accordance with an example implementation.
  • Figure 4H illustrates an inner drum split into a high pressure section and a low pressure section, in accordance with an example implementation.
  • Figure 4I illustrates an exploded view showing a drum, an inner drum, a manifold, and a pipe system, in accordance with an example implementation.
  • Figure 4J illustrates another perspective view of the apparatus illustrated in Figures 4A-4I, in accordance with an example implementation.
  • Figure 4K illustrates rotation of a rack gear relative to a plate, in accordance with an example implementation.
  • Figure 4L illustrates a spur gear disposed within a rack gear having two opposite inner surfaces when the rack gear is at a first rotational position, in accordance with an example implementation.
  • Figure 4M illustrates hinged teeth disposed on the two opposite inner surfaces shown in Figure 4L, in accordance with an example implementation.
  • Figure 4N illustrates the spur gear of Figure 4L disposed within the rack gear when the rack gear is at a second rotational position, in accordance with an example implementation.
  • Figure 4O illustrates the spur gear of Figure 4L disposed within the rack gear when the rack gear is at a third rotational position, in accordance with an example implementation.
  • Figure 4P illustrates the apparatus of Figures 4A-4O having multiple plates and associated assemblies, in accordance with an example implementation.
  • Figure 4Q illustrates telescopic cylinders connecting a manifold to respective plates, in accordance with an example implementation.
  • Figure 4R illustrates geometric relationships between a drum and a ring gear, in accordance with an example implementation.
  • any enumeration of elements, blocks, or steps in this specification or the claims is for purposes of clarity. Thus, such enumeration should not be interpreted to require or imply that these elements, blocks, or steps adhere to a particular arrangement or are carried out in a particular order.
  • Fluid energy could be converted into mechanical motion via applying pressure on a surface, causing the surface to move while expanding a volume of the fluid acting on the surface.
  • several hydraulic actuators operate based on such principle of fluid volume expansion.
  • Figure 1A illustrates a hydraulic actuator 100, in accordance with an example implementation.
  • Figure 1A illustrates a high pressure fluid source 102 configured to provide pressurized fluid to the actuator 100.
  • the high pressure fluid source 102 may be, for example, a pump, an accumulator, or a reservoir containing fluid at greater than atmospheric pressure. Fluid at the bottom of such a container may have a pressure head, which is the internal energy of a fluid due to the pressure exerted on its container. Other ways of pressurizing fluid are also possible.
  • the actuator 100 includes a piston 104 slidably accommodated within a cylinder 106 of the actuator 100.
  • the piston 104 includes a piston head 108 and a rod 110 extending from the piston head 108 along a central axis direction of the actuator 100.
  • the piston head 108 divides the inside of the cylinder 106 into two chambers, 112 and 114.
  • the pressurized fluid applies pressure on a surface of the piston 104, or more particularly, on a surface of the piston head 108. This pressure may cause the piston 104 to extend (i.e., move left in Figure 1A).
  • a hydraulic system such as the system shown in Figure 1A may include other components that are not shown such as valves regulating flow of fluid to and from the actuator 100. Valves and other components are not shown in Figure 1A to reduce visual clutter in the drawings.
  • Figure 1B illustrates a change in fluid volume causing mechanical motion of the piston 104 of the actuator 100, in accordance with an example implementation.
  • volume of the chamber 114 which is being filled by the pressurized fluid, increases as shown in Figure 1B.
  • Fluid in the chamber 112 flows to a tank or reservoir 116 having fluid at a low pressure.
  • fluid energy of the pressurized fluid flowing into the chamber 114 is converted into mechanical motion of the piston 104, while volume of the fluid in the chamber 114 is increasing.
  • mechanical motion is accompanied by fluid volume expansion.
  • the volume expansion is approximately 100% of displaceable volume within the cylinder 106.
  • the displaceable volume is the volume within the cylinder 106 excluding volume occupied by the piston head 108, and any other components (not shown in Figures 1A-1B) that accommodate ports connecting the cylinder to other components of the hydraulic system.
  • a gearing system is coupled to a moving member and turns fluid energy into motion of the moving member while fluid volume changes infinitesimally or remains substantially constant.
  • a gearing system is coupled to a moving member and turns fluid energy into motion of the moving member while fluid volume changes infinitesimally or remains substantially constant.
  • Each implementation includes an element (e.g., a plate) that is repelled under fluid pressure from an underlying surface, thus setting in motion a gearing mechanism that ultimately leads to the element itself moving along the underlying surface without a substantial change in fluid volume.
  • these implementations are examples for illustration, and are not meant to be limiting. Other example implementations that use the same principle are possible as well.
  • Figure 2A illustrates a front view of an apparatus 200 for converting fluid pressure to mechanical motion
  • Figure 2B illustrates a perspective posterior view of the apparatus 200, in accordance with an example implementation.
  • the apparatus 200 includes a plate 202 and a vertical rack gear 204 attached to the plate 202 via a vertical trolley 206.
  • a vertical spur gear 208 engages, and is configured to be driven by, the vertical rack gear 204.
  • a horizontal spur gear 210 is coupled to the vertical spur gear 208.
  • Figure 2C illustrates the horizontal spur gear 210 coupled to the vertical spur gear 208, in accordance with an example implementation. As shown in Figure 2C, both the horizontal spur gear 210 and the vertical spur gear 208 are mounted on a shaft 212. Thus, the horizontal spur gear 210 and the vertical spur gear 208 form a compound gear configured to rotate at the same speed.
  • both the horizontal spur gear 210 and the vertical spur gear 208 are attached to a horizontal trolley 214 via a gear housing 216 shown in Figure 2B.
  • the horizontal spur gear 210 is also coupled to a horizontal rack gear 218.
  • the horizontal rack gear 218 is fixedly mounted.
  • a gap 222 separates the plate 202 from an underlying inclined surface 220.
  • the apparatus 200 is configured such that pressurized fluid can be delivered to the gap 222.
  • the plate 202 may include a connector 224 that could be connected to a source of pressurized fluid (e.g., a pump, a reservoir of fluid, where a bottom of the reservoir is coupled to the connector 224, etc.).
  • the plate 202 may include one or more channels that then communicate fluid received at the connector 224 to the gap 222 to form a layer of pressurized fluid therein.
  • the connector 224 could be coupled to the inclined surface 220, and the inclined surface 220 may have channels through which pressurized fluid flows to the gap 222 to form the layer of pressurized fluid therein.
  • the pressurized fluid in the gap 222 repels the plate 202 away from the underlying surface 220.
  • the plate 202 may consequently begin to move infinitesimally away from the underlying surface 220, thus causing the vertical rack gear 204 to move linearly upward and the vertical spur gear 208 to rotate clockwise.
  • Rotation of the vertical spur gear 208 causes the horizontal spur gear 210 to rotate because both gears 208 and 210 are mounted to the same shaft 212.
  • the horizontal spur gear 210 engages the horizontal rack gear 218, which is fixed.
  • rotation of the horizontal spur gear 210 causes the horizontal trolley 214, the vertical trolley 206, and the plate 202 to all move horizontally, and the plate 202 therefore moves along the underlying surface 220 in a direction of an arrow 226 shown in Figure 2A.
  • Gear Ratio R is the gear ratio of the vertical spur gear 208 to the horizontal spur gear 210. Accordingly, for the plate 202 to follow the inclined surface 220 as it moves, the inclined surface 220 could be oriented with the same ratio of vertical to horizontal travels, R. In this case, the tangent of an angle ⁇ of the inclined surface 220 may be:
  • the apparatus 200 may include other components.
  • a movable adjusting plate could be coupled to a bottom of the plate 202 such that the gap 222 is disposed between the plate 202 and the movable adjusting plate.
  • the movable adjusting plate may tend to thrust away from the plate 202 toward the underlying surface 220, while the plate 202 is repelled away from the movable adjusting plate.
  • rollers may be added at the bottom of the movable adjusting plate so as to reduce friction between the movable adjusting plate and the underlying surface 220 as the movable adjusting plate moves along the underlying surface.
  • both the plate 202 and the underlying surface 220 could be magnetized with like poles to enhance repelling the plate 202 away from the underlying surface 220.
  • Other additional components are possible as well.
  • Figure 3A illustrates a perspective top view of another apparatus for converting fluid pressure to mechanical motion
  • Figure 3B illustrates a perspective bottom view of the apparatus 300, in accordance with an example implementation.
  • the apparatus 300 includes a disk 302.
  • the disk 302 includes a hole configured to receive another disk 304.
  • a container 306 may be coupled to the disk 302, such that fluid in the container 306 applies pressure on a portion 307A of the disk 302.
  • a remaining portion 307B of the disk 302 is not exposed to fluid in the container 306, and may be exposed to, for example, atmospheric pressure.
  • the disk 302 is configured to rotate. As the disk 302 rotates, different portions of the disk 302 are exposed to the fluid in the container 306. In other words, the container 306 remains fixed, while the disk 302 rotates.
  • the pressure level of fluid at the bottom of the container 306 is based on a depth“d” of the container 306, among other factors. For instance, fluid may be pumped into the container 306 at a high pressure. In this case, the pressure applied on the portion of the disk 302 that is exposed to the fluid is based on both the depth“d” and the pressure level of fluid being pumped into the container 306.
  • the disk 304 When the disk 304 is within the portion of the disk 302 that is exposed to fluid, a surface of the disk 304 is exposed to pressure of fluid in the container 306. In response to force applied to the surface of the disk 304 by fluid pressure, the disk 304 is repelled (like the plate 202 of Figure 2A is also repelled away from the surface 220) away from the container 306 (i.e., downward in Figure 3A). The disk 304 may thus begin to move infinitesimally within the disk 302.
  • the disk 304 is further coupled to a shaft 308, and at least a portion of the shaft 308 includes a rack gear 310.
  • the rack gear 310 meshes with or engages a spur gear 312, which is coupled via a shaft 314 to another spur gear 316.
  • the spur gear 312 and the spur gear 316 thus rotate at the same rate.
  • the shaft 314 extends beyond the spur gear 316 and couples both spur gears 312 and 316 to another shaft 318.
  • the shaft 318 in turn is coupled to a center region 320 (shown in Figure 3B) of the disk 302. Further, the spur gear 316 engages a fixed ring gear 321.
  • teeth of the ring gear 321 do not span an entire circumference of a circle, but span only a portion (e.g., half a circle). In other words, the ring gear 321 could be a partial ring gear. In this manner, teeth of the spur gear 316 engage the teeth of the ring gear 312 when the pressurized fluid in the container 306 repels the disk 304. However, as the disk 304 transitions away from the container 306, the teeth of the spur gear 316 do not engage any gear teeth.
  • the ring gear 321 could be a full ring gear.
  • more than one hole and more than one disk such as the disk 304 may be disposed within the disk 302 as described next.
  • Figure 3C illustrates a perspective top view of the apparatus 300 with the disk 302 having multiple disks disposed therein, in accordance with an example implementation.
  • Figure 3C illustrates the disk 302 with eight disks disposed therein.
  • a pressurized fluid source 322 may be configured to deliver high pressure fluid to the container 306 through a pipe system 324.
  • the pressurized fluid source 322 is depicted as a container; however, the pressurized fluid source 322 a pump and/or accumulator configured to store and deliver high pressure fluid to the container 306.
  • the pressurized fluid source 322 may be disposed at an elevation higher than the container 306 so as to provide fluid having a pressure head to drive the disk(s) 304.
  • the transition wiper 326 is disposed over an area of the disk 302 between the portion exposed to the high pressure fluid and the portion not exposed to high pressure. As the disk 302 rotates due to the disks 304 being repelled under fluid pressure, the disks 304 transition in and out of the portion exposed to the high pressure fluid. As a given disk of the disks 304 transitions across the transition wiper 326, any fluid on the transitioning disk is wiped away by the transition wiper 326.
  • the container 306 and the disk 304 could be magnetized to have the same pole so as to further cause the disk 304 to be repelled downward.
  • the transition wiper 326 could have an opposite pole relative to the disk 304 so as to attract the disc 304 toward the transition wiper 326.
  • FIG. 3D illustrates a perspective view of the apparatus 300 with two parallel disks, each disk having eight disks disposed therein, in accordance with an example implementation.
  • the apparatus 300 may include a complementary disk 328 disposed opposite to the disk 302.
  • Eight disks such as the disks 330A, 330B, and 330C are disposed within respective holes in the disk 328, and these eight disks are complementary to the eight disks 304 disposed within the disk 302.
  • one shaft such as a shaft 332, couple each disk to its complementary, such as the disks 304D and 330C.
  • a portion of the shaft 332 is configured as a rack gear 334.
  • a container 336 includes pressurized fluid and is disposed on a portion of the disk 328.
  • the container 336 is configured such that when a disk of the disks 304, such as the disk 304D, exits the wiper transition 326, the complementary disk 330C enters a portion of the disk 328 that is exposed to high pressure fluid of the container 336.
  • the disk 304D may stop contributing to rotation of the disk 302 as it transitions away from the high pressure of container 306, while the corresponding disk 330C begins contributing to rotation of the disk 328 under pressure from fluid in the container 336.
  • a fixed rack gear 337 has gear teeth facing upward along half the circumference, and gear teeth facing downward along the remaining half circumference. That way, spur gears, such as spur gears 338 and 340, engage teeth of the fixed ring gear 337 during half a revolution only, while being disengaged for the remaining half. Particularly, spur gears associated with disks being exposed to high pressure engage teeth of the ring gear 337, whereas spur gears associated with disks not being exposed to high pressure are disengaged from teeth of the ring gear 337.
  • Figure 3E illustrates a split ring gear 337 for the apparatus illustrated in Figure 3D, in accordance with an example implementation.
  • the ring gear 337 may be split into two gears, 337A and 337B, with teeth of the ring gear 337A facing upward, whereas teeth of the rack gear 337B facing downward.
  • Figure 3F illustrates the shaft 318 coupled to another shaft 342 that could be connected to a power source, in accordance with an example implementation.
  • an example power source may include an electrical generator.
  • the transition wiper 326 may have a hole disposed within which is a coupling 344 configured to couple the shaft 318 to the shaft 342.
  • the coupling 344 is configured to compensate for an offset between the shafts 318 and 342 (i.e., an offset between respective axes of rotation of the shafts 318 and 342) resulting from the plate 302 being inclined.
  • Figure 3F also depicts a pipe system 346 that is configured to deliver high pressure fluid from the pressurized fluid source 322 to the container 336.
  • the shaft 318 may be a hollow shaft. Another shaft could be disposed within the hollow shaft 318. That other shaft may be affixed to the ring gear 337, and may extend beyond one or both disks 302 and 328. That other shaft within the shaft 318 may be then be attached to a fixed structure so as to render the ring gear 337 structurally fixed.
  • the configurations shown in Figures 3A-3F are examples for illustration, and alternative configurations are possible. For example, a greater or smaller number of disks 304 and 330 could be used, i.e., greater or less than eight disks could be disposed within each of the inclined disks 302 and 328. Further, disks 304 (or 330) of varying sizes could be used to use space of the disk 302 efficiently.
  • Figure 3G illustrates the apparatus 300 with the disk 302 having multiple disks of varying sizes disposed therein, in accordance with an example implementation.
  • smaller disks such as a disk 348 are disposed within the disk 302.
  • Each of the smaller disks is attached to its own gear train.
  • the disk 348 is coupled to a shaft 350.
  • An end of the shaft 350 is a rack gear 352 that engages a spur gear 354, which is coupled to another spur gear 356.
  • the spur gear 356 engages another ring gear 358 disposed within the ring gear 321.
  • the disks 348 aid the larger disk(s) 304 in causing the disk 302 to rotate about its axis and might increase power output at the shaft.
  • teeth of the ring gear 358 do not span an entire circumference of a circle, but span only a portion (e.g., half a circle).
  • the ring gear 358 could be a partial ring gear.
  • teeth of the spur gear 356 engage the teeth of the ring gear 358 when the pressurized fluid in the container 306 repels the disk 348.
  • the teeth of the spur gear 356 do not engage any gear teeth.
  • the ring gear 358 could be a full ring gear.
  • Figures 3H, 3I, and 3J illustrate geometric relationships between elements of the apparatus illustrated in Figures 3A-3B, in accordance with an example implementation.
  • the disk 302 forms an angle T with respect to a horizontal plane.
  • the shaft 308 and the rack gear 310 which forms an end of the shaft 308, are coupled to the disk 304 and the disk 302.
  • the diameter of the spur gear 312 is D 1 , and its radius is R 1
  • the diameter of the spur gear 316 is D 2
  • its radius is R 2
  • the diameter of the ring gear 321 is D 3
  • R 3 the diameter of the ring gear 321
  • D w is a diameter of a circle centered around a center of the disk 302 and having a radius equal to a distance from the center of the disk 302 to a center of a disk 304G.
  • D w is a distance from a center of the disk 304G to a center of an opposing disk 304H. This distance is the same as a respective distance between a center 360 of a shaft 362 coupled to the disk 304G and a center 364 of a shaft 366 coupled to the disk 304H.
  • the amount of rotation (i.e., angular displacement) ⁇ 1 of the spur gear 312 can be calculated as follows:
  • an effective gear ratio R can be calculated as:
  • Figures 4A-4R illustrate another apparatus 400 for converting fluid energy to mechanical motion, in accordance with an example implementation.
  • Figure 4A illustrates a partial perspective view of the apparatus 400, in accordance with an example implementation.
  • Figure 4A shows a cylindrical drum 402 and a plate 404 configured to rotate along a surface of the drum 402.
  • a gap 406 separates the plate 404 from an underlying surface of the drum 402.
  • the apparatus 400 may include multiple plates similar to the plate 402 as described below at Figure 4P.
  • a pipeline manifold 408 includes a pipe system branching into several openings feeding fluid to the plates such as the plate 402.
  • a pipe or branch 410 of the manifold 408 has an opening 412 coupled to a telescopic supply cylinder 414 configured to communicate fluid at alternating pressures to a knuckle or elbow 416. Fluid delivered to the elbow 416 is communicated to the gap 406 through channels in the elbow 416 and corresponding channels in the plate 404.
  • Figure 4B illustrates a partial perspective view of the apparatus 400 without the drum 402, in accordance with an example implementation.
  • Figure 4B particularly illustrates communicating fluid from the elbow 416 to the gap 406. Fluid delivered through the opening 412 is communicated through a channel in the elbow 416. This channel in the elbow 416 is exposed, and delivers the fluid, to a back side 415 of the plate 404, and thus to the gap 406 separating the plate 404 from the drum 402.
  • Figure 4C illustrates is an exploded view of a portion of the apparatus 400 including the drum 402, the plate 404, and the elbow 416, in accordance with an example implementation.
  • the elbow 416 includes grooves/channels 417A
  • the plate 404 includes corresponding channel openings 417B.
  • fluid delivered to the elbow 416 via the telescopic supply cylinder 414 flows through the channels 417A, then is communicated to the channel openings 417B, and is ultimately delivered to the gap 406.
  • Figure 4D illustrates a perspective view of the apparatus of Figure 4A with a rack gear 418 and gear train at a particular rotary position, in accordance with an example implementation.
  • the manifold 408 is mounted on one side of the drum 402.
  • the view shown in Figure 4D is for the other side of the drum 402.
  • Figure 4D does not show the manifold 408.
  • the plate 404 is coupled to a structure that is referred to herein as the rack gear 418.
  • Inner surfaces 420A and 420B of the rack gear 418 include rack gear teeth. Gear teeth of the inner surfaces 420A and 420B engage a spur gear 422.
  • the spur gear 422 is coupled via a shaft 424 to another spur gear 426.
  • the spur gear 426 engages another spur gear 428, which is coupled to another spur gear 430 via a shaft 432.
  • the spur gears 422 and 426 form a first compound gear configured to rotate at a first rotational speed
  • the spur gears 428 and 430 form a second compound gear configured to rotate at a second rotational speed
  • the spur gear 430 engages external teeth of a fixed rack ring gear 434.
  • the shaft 432 extends beyond the spur gear 430 and is coupled to an arm 436 via a bushing 438.
  • the arm 436 is also coupled to the shaft 424 via a bushing 440.
  • the arm 436 is further coupled to a bushing 442 disposed, and is configured to rotate, about a shaft 444 protruding from the side of the drum 402.
  • the side of the drum 402 from which the shaft 444 protrudes is opposite to the side of the drum 402 on which the manifold 408 is mounted.
  • the elbow 416 is coupled to a slide support 446 configured to slidably support the arm 436.
  • Figure 4E illustrates a zoomed-in view of the slide support 446, the elbow 416, and the arm 436, in accordance with an example implementation.
  • the shaft 444 is disposed at a center of the ring gear 434, which is eccentric to a center of the drum 402.
  • the arm 436 is configured to slide within the slide support 446.
  • the slide support 446 enables the elbow 416, the plate 404, and the rack gear 418 to slide along the arm 436 as they rotate about the drum 402.
  • Figure 4F illustrates another perspective view of the apparatus 400 as shown in Figure 4D, in accordance with an example implementation.
  • the plate 404 and the drum 402 may interact and operate similar to the plate 202 and the inclined surface 220.
  • high pressure fluid in the gap 406 may repel the plate 404 away from the underlying surface of the drum 402.
  • the repelled plate 404 causes the rack gear 418 to move outward infinitesimally. Consequently, the gear-teethed inner surface 420A causes the spur gear 422 to rotate counter- clockwise, and thus the spur gear 426 to also rotate counter-clockwise.
  • Figure 4G illustrates eccentric disposition of the drum 402 relative to the ring gear 434, in accordance with an example implementation. Particularly, Figure 4G illustrates eccentricity between a center 449A of the drum 402 and a center 449B of the ring gear 434, which is also the center of the shaft 444 surrounded by the bushing 442. As shown in Figure 4G, the center 449B of the ring gear 434 is offset from the center 449A of the drum 402 in an x-axis direction.
  • Figure 4H-4J illustrate delivering fluid at alternating pressure to the gap 406, in accordance with an example implementation.
  • Figure 4H illustrates an inner drum 450 split into a high pressure section 452A and a low pressure section 452B.
  • the inner drum 450 is coupled to the drum 402, and thus the inner drum 450 is stationary like the drum 402.
  • the high pressure section 452A is configured to be in fluid communication with high pressure fluid 454, whereas the low pressure section 452B is configured to be in fluid communication with a low pressure fluid 456.
  • the high pressure fluid 454 may be supplied via a pipe system in communication with a high pressure fluid source (e.g., a pump or accumulator configured to supply fluid at a high pressure).
  • the low pressure fluid 456 may be fluid maintained at atmospheric pressure or fluid that is in communication with a low pressure reservoir 457 containing fluid at a pressure lower than pressure of the high pressure fluid source.
  • the high pressure fluid source may be configured to provide fluid at atmospheric pressure, while pressure of fluid in the low pressure fluid 457 could be artificially lowered (e.g., by a bladder causing negative pressure). It is the differential pressure between the high pressure fluid 454 and the low pressure fluid 456 that enables the apparatus 400 to operate.
  • the high pressure fluid 454 may have a pressure of 1000-3000 pounds per square inches (psi), while the low pressure fluid 456 may have a pressure of # 0 psi.
  • the high pressure the high pressure fluid 454 may have a pressure of 100 psi, while the low pressure fluid 456 may have a pressure of # -50 psi.
  • Figure 4I illustrates an exploded view showing the drum 402, the inner drum 450, the manifold 408, and a pipe system communicating the high pressure fluid 454 and the low pressure fluid 456 to the inner drum 450, in accordance with an example implementation.
  • the high pressure section 452A of the inner drum 450 is isolated from the low pressure section 452B.
  • a separator 458 segregates a pipe containing the high pressure fluid 454 from a respective pipe containing the low pressure fluid 456.
  • Figure 4J illustrates another perspective view of the apparatus 400 illustrated in Figures 4A-4I, in accordance with an example implementation.
  • the manifold 408 is configured to rotate with the assembly 448 relative to the drum 402 and the inner drum 450.
  • a subset of its branches, such as the branch 410 is exposed to the high pressure fluid 454 communicated to the high pressure section 452A of the inner drum 450.
  • high pressure fluid is supplied to the gap 406, thus repelling the plate 404 and causing rotation of the assembly 448, which includes the plate 404, the rack gear 418, the gear train including gears 422, 426, 428, and 430 along with the arm 436.
  • the branch 410 may be exposed to the low pressure fluid 456 from the low pressure section 452B.
  • the manifold 408 is configured to provide fluid at alternating pressure, i.e., either high pressure fluid or low pressure fluid, based on the rotational position of the manifold 408 relative to the inner drum 450.
  • a valve system could be used to selectively provide high pressure fluid or low pressure fluid to the gap 406.
  • both the source of high pressure fluid and the reservoir 457 could be ported to a spool valve.
  • Linear position of a spool disposed within a body of the spool valve determines or selects whether to deliver fluid from the source of high pressure fluid or from the reservoir 457 to the gap 406.
  • the manifold 408 could be stationary.
  • the implementation involving rotation of the manifold 408 is used as example to illustrate operation of the apparatus 400, but other implementations could be used as well.
  • Figure 4K illustrates rotation of the rack gear 418 relative to the plate 404, in accordance with an example implementation.
  • the plate 404 complies to the surface of the drum 402, while the spur gear 430 remains engaged to the ring gear 434 forcing the rack gear 418 to rotate relative to the elbow 416.
  • Figure 4K, and also Figure 4C shows that the elbow 416 is cylindrical in shape, and that the rack gear 418 has a semi cylindrical surface 460 that complies with the surface of the elbow 416. This configuration allows the rack gear 418 to rotate relative to, or about, the elbow 416 as the assembly 448 rotates thus reconciling compliance of the plate 404 to the surface of the drum 402 with the spur gear 430 remaining engaged to the ring gear 434.
  • additional components could be added to the apparatus 300 to control a magnitude of the gap 406 (distance between a surface of the drum 402 and the plate 404) and orientation of the plate 404.
  • a gearing mechanism could be implemented to maintain tangential orientation of leading and tailing edges of the plate 404 relative to the surface of the drum 402.
  • magnets could be incorporated in the leading and tailing edges of the plate 404 to help maintain a particular magnitude of the gap 406.
  • Figure 4K further illustrates eccentric positioning of the drum 402 relative to the ring gear 434 as described above with respect to Figure 4G.
  • Figure 4K illustrates a view from a perspective of a side that includes the manifold 408
  • Figure 4G illustrates a view form a perspective of a side that includes the shaft 444 and the arm 436.
  • the eccentricity allows the spur gear 422 to travel within the rack gear 418 as the rack gear 418 rotates with the plate 404 about the drum 402.
  • the assembly 448 is at a 9 O’clock position illustrated in Figures 4D and 4F, the spur gear 422 is at its outermost position farthest from the drum 402.
  • the spur gear 422 is at its innermost position closest to the drum 402.
  • the 9 O’clock position and the 3 O’clock position are described herein for a viewer of Figures 4D and 4F, i.e., a viewer looking at the side of the drum 402 that has the shaft 444.
  • the spur gear 422 travels within the rack gear 418 from its outermost position to its innermost position. Conversely, as the assembly 448 travels in the clockwise direction from the 3 O’clock position to the 9 O’clock position, the spur gear 422 travels within the rack gear 418 from its innermost position to its outermost position. As mentioned with respect to Figure 4D above, as the spur gear 422 travels within the rack gear 418, it rotates, thereby causing the whole assembly 448 to rotate as the spur gear 430 rotates about the ring gear 434.
  • Teeth on the inner surfaces 420A and 420B of the rack gear 418 have hinged gear teeth.
  • gear teeth disposed on the inner surface 420A engage the spur gear 422 in one direction, but are passive in the other direction.
  • gear teeth disposed on the inner surface 420B engage the spur gear 422 in one direction, but are passive in the other direction.
  • gear teeth of the inner surface 420A are hinged in an opposite direction relative to gear teeth of the inner surface 420B. The result of this is that, regardless of the direction of travel of the spur gear 422 within the rack gear 418, the assembly 448 rotates in the same direction.
  • Figure 4L illustrates the spur gear 422 disposed within the rack gear 418 when the rack gear is at a first rotational position, in accordance with an example implementation.
  • Figure 4L shows the spur gear 422 disposed within the rack gear 418 between the surfaces 420A and 420B while the assembly 448 is at the 9 O’clock position depicted in Figures 4D and 4F.
  • Figures 4D and 4F show a frontal perspective view of a portion of the apparatus 400
  • Figure 4L shows a back or posterior perspective view of the same portion.
  • the spur gear 422 is at its outermost position and thus farthest from the drum 402.
  • high pressure fluid in the gap 406 may repel the plate 404 away from an underlying surface of the drum 402.
  • the repelled plate 404 may consequently move infinitesimally outward, away from the underlying surface of the drum 402, thus causing the rack gear 418 to move outward, i.e., in direction of an arrow 464A shown in Figure 4L.
  • gear teeth disposed on the surface 420A of the rack gear 418 such as tooth 466, engage the spur gear 422 and cause the spur gear 422 to rotate clockwise from the perspective of a viewer of Figure 4L.
  • teeth disposed on the surface 420A apply a force on teeth of the spur gear 422 and cause the spur gear 422 to rotate.
  • gear teeth disposed on the surface 420B of the rack gear 418 such as tooth 468, are passive, i.e., do not apply a substantial force on teeth of the spur gear 422, and they bend backward about their hinges as the spur gear 422 rotates and moves with the rack gear 418.
  • Figure 4M illustrates a zoomed-in view of hinged teeth disposed on the two opposite inner surfaces 420A and 420B, in accordance with an example implementation. While the rack gear tooth 466 is upright and engages the spur gear 422, the rack gear tooth 468 is bent backward and does not hinder motion of the spur gear 422.
  • Figure 4N illustrates the spur gear 422 when the rack gear 418 is at a second rotational position, in accordance with an example implementation.
  • the assembly 448 is at a 12 O’clock position, i.e., between the 9 O’clock position and 3 O’clock position.
  • Figure 4O illustrates the spur gear 422 disposed within the rack gear 418 when the rack gear 418 is at a third rotational position, in accordance with an example implementation.
  • the spur gear 422 continues to move within the rack gear 418 until it reaches its innermost position close to the slide support 446 as shown in Figure 4O, where the assembly 448 reaches the 3 O’clock position.
  • the rack gear 418 moves relative to the spur gear 422 in direction of an arrow 464B.
  • gear teeth disposed on the surface 420B of the rack gear 418 While moving in direction of the arrow 464B, gear teeth disposed on the surface 420B of the rack gear 418, such as tooth 468, engage the spur gear 422 and cause the spur gear 422 to rotate clockwise. In other words teeth disposed on the surface 420B apply a force on teeth of the spur gear 422 and cause the gear 422 to rotate.
  • gear teeth disposed on the surface 420A of the rack gear 418, such as tooth 466 are passive and bend backward about their hinges as the spur gear 422 rotates.
  • teeth disposed on the surface 420A engage the spur gear 422 as the assembly 448 moves from the 9 O’clock position to the 3 O’clock position, they do not engage teeth of the spur gear 422 as the assembly 448 moves from the position 3 O’clock position to the 9 O’clock position.
  • teeth disposed on the surface 420B engage the spur gear 422 as the assembly 448 moves from the position 3 O’clock to the 9 O’clock position, they do not engage teeth of the spur gear 422 as the assembly 448 moves from the 9 O’clock position to the 3 O’clock position. In this manner, regardless of the rotational position of the assembly 448, the spur gear 422 rotates in the same direction, thereby causing the assembly 448 to rotate in the same direction about the ring gear 434.
  • the plate 404 and the drum 402 could be magnetized. Particularly, from the 9 O’clock to the 3 O’clock position, the pate 404 and the underlying surface of the drum 402 could be magnetized to have the same poles, causing the plate 404 to be repelled away from the drum 402. Conversely, from the 3 O’clock position to the 9 O’clock position charge or pole type of the drum 402 could be opposite to the pole of the plate 404 to attract the plate 404 toward the underlying surface of the drum 402.
  • one or more of the gears 422, 426, 428, and 430 could be an elliptical gear or other non-circular gears.
  • the spur gear 430 could be an elliptical gear configured to mesh properly with the ring gear 434 regardless of an angle of rotation of the arm 436.
  • Such an elliptical gear might help compensate for variation of translational speed of the spur gear 422 as it moves from its innermost position to its outermost position as opposed to when it moves from its outermost position to its innermost position.
  • the minor diameter of the elliptical gear would mesh with the ring gear 434 at the 9 O’clock position
  • the major diameter of the elliptical gear would mesh with the ring gear at the 3 O’clock position.
  • Figure 4P illustrates the apparatus of Figures 4A-4O having multiple (e.g., eight) plates and associated assemblies, in accordance with an example implementation. Particularly, Figure 4P illustrates multiple assemblies (e.g., multiple plates 404, multiple rack gears 418, etc.) disposed about the drum 402. Each of these assemblies goes through the same cycle as described above with respect to Figures 4A-4O.
  • Each branch, such as the branch 410, of the manifold 408 communicates fluid to a gap that separate a plate of a respective assembly from the drum 402. When the branch has access to fluid in the high pressure section 452A of the inner drum 450, the high pressure fluid 454 is communicated to the gap.
  • the branch transitions from having access to fluid in the high pressure section 452A to having access to fluid in the low pressure section 452B.
  • fluid in the gap 406 may be low pressure fluid.
  • Having multiple assemblies as shown in Figure 3P may ensure continuity of motion because at least some of the branches of the manifold 408 have access to the high pressure fluid 454 at any given rotational position of the manifold 408.
  • anti-backlash gears could be incorporated to accommodate tolerances present in the gear trains due to, for example, fabrication variances.
  • one or more of the gears 422, 426, 428, and 430 could incorporate a spring-loaded counter rotating gear to prevent binding during rotation.
  • Rotation of the multiple assemblies shown in Figure 4P rotate can be utilized, for example, to drive a power source.
  • the bushing 442 could be coupled to a shaft of a power source (e.g., an electric generator, an engine, a turbine, pump, a heart pump, an insulin or medication pump implanted in a body of a patient, etc.).
  • a power source e.g., an electric generator, an engine, a turbine, pump, a heart pump, an insulin or medication pump implanted in a body of a patient, etc.
  • Such an infinitesimal volume change accounts for leakage of fluid and any infinitesimal movement of the plate 404 away from the underlying surface of the drum 402 as the plate 404 is repelled away from the underlying surface under fluid pressure.
  • the term“substantially” is used herein to indicate a the fluid volume in the gap 406 remains within a threshold volume value (e.g., fluid volume changes by less than 5%) from an initial fluid volume in the gap 406 as the plate 404 moves along the underlying surface of the drum 402.
  • a movable adjusting plate could be added or coupled to a bottom of the plate 404 such that the gap 406 is disposed between the plate 404 and the movable adjusting plate.
  • the movable adjusting place may tend to thrust away from the plate 404 toward the underlying surface of the drum 402, while the plate 402 is repelled away from the movable adjusting plate.
  • rollers may be added at the bottom of the movable adjusting plate so as to reduce friction between the movable adjusting plate and the underlying surface of the drum 402 as the movable adjusting plate coupled to the plate 404 moves along the underlying surface.
  • Another way to reduce seepage includes incorporating deformable features, coupled to an edge of a perimeter of the plate 404 that would seal the gap 406.
  • deformable features include a wiper, a series of wipers, a roller, or series of rollers.
  • Figure 4Q illustrates telescopic cylinders connecting the manifold 408 to respective plates, in accordance with an example implementation. As shown in Figure 4Q, there is an eccentricity between the center 449A of the drum 402 and a center of rotation 470 of the manifold 408. The center of rotation 470 is the same as the center 449B of the ring gear 434 shown in Figure 4G; however, Figure 4Q is shown from a perspective of the side of the drum 402 where the manifold 408 is mounted.
  • each cylinder may have concentric tubular sections designed to slide into one another so as to allow variation in length of the cylinder.
  • each of the cylinders communicating fluid to the respective elbows is at a particular state of extension based on where a respective plate is relative to the manifold 408. For instance, cylinder 472 is longer, or is extended more, than the cylinder 414. Each of these cylinders goes through a cycle between a most extended position, i.e., position of cylinder 474, and a least extended position, i.e., position of cylinder 476.
  • a most extended position i.e., position of cylinder 474
  • a least extended position i.e., position of cylinder 476.
  • Such telescopic configuration of the cylinders accommodates the eccentricity between the center 449A of the drum, and the center of rotation 470 of the manifold 408.
  • Figure 4R illustrates geometric relationship between the drum 402, the plate 404, and the ring gear 434, in accordance with an example implementation.
  • the radius of the ring gear 434 is labelled as R rg
  • the radius of the drum 402 is labelled as R d .
  • the distance between the plate 404 and the ring gear at the 9 O’clock position i.e., when the spur gear 422 is at its outermost position farthest from the drum 402) is labelled d o
  • the distance between the plate 404 and the ring gear at the 3 O’clock position i.e., when the spur gear 422 is at its innermost position closest to the drum 402 is labelled d i .
  • the diameter of the ring gear (D rg ) and the diameter of the drum (D d ) can be related as follows:
  • Half a circumference (C d ) of the drum 402 can be calculated as:
  • the distance (L 0 ) of the plate 404 from the center 449B of the ring gear 434 when the plate is at the 9 O’clock position can be calculated using the radius R rg of the ring gear as:
  • the distance (L i ) of the plate 404 from the center 449B of the ring gear 434 when the plate is at the 3 O’clock position can be calculated as:
  • a difference in location of the plate 404 relative to the center 449B can thus be calculated as:
  • a ratio R can therefore be calculated as:
  • the ratio R defines a difference in location of the plate 404 relative to the center 449B between the 9 O’clock position and the 3 O’clock position divided by a circular distance 478 that separates these two locations.
  • the ratio R can also be calculated using diameters of the gears 422, 426, 428, and 430. Assuming that D 1 is a diameter of the gear 422, D 2 is a diameter of the gear 426, D 3 is a diameter of the gear 428, and D 4 is a diameter of the gear 430, the ratio R can also be calculated as:
  • the apparatuses 200, 300, and 400 work on the same principle. Instead of a fluid volume change as described in Figures 1A-1B, the apparatuses 200, 300, 400 operate based on high pressure applied on the surface area of a plate with fluid volume remaining substantially the same. Instead the volume change is mechanical in the form of the travel of the plate (e.g., the plate 202 or 404 or the disk 304) made possible by the gearing configurations.
  • a moving rack gear e.g., the rack gears 204, 310, and 418) intersects with a surface on which the plate travels, thus establishing the travel distance of the plate while it is under pressure.
  • each implementation comprises an element (e.g., a plate) being repelled under fluid pressure from an underlying surface, thus setting in motion a gearing mechanism that ultimately leads to the element itself moving along the underlying surface without a substantial change in fluid volume.
  • a unifying equation can describe all these implementations. This equation relates an arm travel, a plate travel, and a gear ratio. The equation can be expressed as:
  • the term“plate” is used in equation (20) to include any element similar to the plate 202 or 404 or the disk 304.
  • the gear ratio can also be expressed as a ratio of an input displacement of an arm to an output displacement of the plate.
  • Arm travel is a total distance that the arm moves between an extended position and a retracted position.
  • the plate travel is a total distance that the plate travels as the arm traverses its total travel distance.
  • the arm travel is expressed in equation (1) as the distance 'y travelled by the vertical rack gear 204, and the plate travel is the distance 'x travelled by the plate 202.
  • the gear ratio for the apparatus 100 is also defined by equation (1).
  • the arm travel is expressed by the displacement 'H defined in equation (4), and the plate travel is defined in equation (10) by the term“Disk Travel.”
  • An effective gear ratio R for the apparatus 300 is expressed above by equation (11).
  • the arm travel is expressed by the term ' defined by equation (16), and the plate travel is half the circumference of the drum 402 as defined by equation (13).
  • the gear ratio for the apparatus 400 is expressed by equation (17).
  • the gear ratio could also be calculated from the specific gear train (i.e., diameters of the various gears) associated with each apparatus as expressed by equations (1), (11), and (18).
  • the unifying equation (20) illustrates that these various apparatuses are based on the same principle. Thus, other apparatuses or systems that involve this same principle are contemplated herein.
  • spur gears have been used throughout this disclosure as examples of gear types that could be used.
  • other gear types e.g., helical, bevel, rack and pinion, worm, etc.
  • gear types e.g., helical, bevel, rack and pinion, worm, etc.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)

Abstract

Un exemple d'appareil comprend : une plaque conçue pour se déplacer le long d'une surface sous-jacente par l'intermédiaire d'une couche de fluide disposée dans un espace entre la plaque et la surface sous-jacente, où un fluide sous pression forme la couche de fluide dans l'espace ; un premier engrenage à crémaillère couplé à la plaque et s'engrenant avec un premier engrenage ; et un second engrenage à crémaillère couplé à un second engrenage. Le second engrenage à crémaillère est fixé, et le second engrenage est couplé au premier engrenage. Le fluide sous pression dans l'espace repousse la plaque à l'opposé de la surface sous-jacente, ce qui permet d'amener (i) le premier engrenage à crémaillère à se déplacer de façon linéaire et le premier engrenage à tourner, (ii) le second engrenage à tourner et à se déplacer le long du second engrenage à crémaillère, et (iii) la plaque à se déplacer le long de la surface sous-jacente.
PCT/US2016/012037 2015-01-05 2016-01-04 Appareils et systèmes de conversion d'énergie liquide en mouvement mécanique WO2016111925A1 (fr)

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US201562100026P 2015-01-05 2015-01-05
US62/100,026 2015-01-05
US201662274248P 2016-01-02 2016-01-02
US62/274,248 2016-01-02
US14/986,686 2016-01-03
US14/986,686 US10753348B2 (en) 2015-01-05 2016-01-03 Apparatuses and systems for converting fluid energy to mechanical motion

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2018235688A1 (ja) * 2017-06-23 2020-04-09 富士フイルム株式会社 硬化性組成物、半硬化物、硬化物、光学部材、レンズ及び化合物

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392060A (en) * 1980-10-27 1983-07-05 Ivy Jessie T Wind and water power generator
KR19990059458A (ko) * 1997-12-30 1999-07-26 정몽규 차량의 에어클러치 시스템
JPH11303602A (ja) * 1998-04-17 1999-11-02 Homare Shoji:Kk 圧縮空気を用いた歯車伝動装置
US7768143B2 (en) * 2006-04-25 2010-08-03 Mccague James Movement and power generation apparatus
US7948107B2 (en) * 2005-10-19 2011-05-24 Marine Current Turbines Limited Conversion of energy in waves and in tidal flow

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392060A (en) * 1980-10-27 1983-07-05 Ivy Jessie T Wind and water power generator
KR19990059458A (ko) * 1997-12-30 1999-07-26 정몽규 차량의 에어클러치 시스템
JPH11303602A (ja) * 1998-04-17 1999-11-02 Homare Shoji:Kk 圧縮空気を用いた歯車伝動装置
US7948107B2 (en) * 2005-10-19 2011-05-24 Marine Current Turbines Limited Conversion of energy in waves and in tidal flow
US7768143B2 (en) * 2006-04-25 2010-08-03 Mccague James Movement and power generation apparatus

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2018235688A1 (ja) * 2017-06-23 2020-04-09 富士フイルム株式会社 硬化性組成物、半硬化物、硬化物、光学部材、レンズ及び化合物
US10954183B2 (en) 2017-06-23 2021-03-23 Fujifilm Corporation Curable composition, semi-cured product, cured product, optical member, lens, and compound

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