Shear thickening fluid based rotary power coupler mechanism

A power coupler for transferring rotary power from a rotary power device to a load device includes a shear thickening fluid (STF) and a chamber that contains the STF. The power coupler further includes a drive shaft housed radially within a drive side section of the chamber and protruding outward from an end of the chamber for coupling to the rotary power device. The power coupler further includes a load shaft housed radially within a load side section of the chamber and protruding outward from another end of the chamber for coupling to the load device. The power coupler further includes a drive turbine housed radially within the drive side section and coupled to the drive shaft. The power coupler further includes a load turbine housed radially within the load side section at a fixed operational distance from the drive turbine and coupled to the load shaft.

Not Applicable.

Not Applicable.

BACKGROUND OF THE INVENTION

Technical Field of the Invention

This invention relates generally to systems that measure and control mechanical movement and more particularly to sensing and controlling of a linear and/or rotary movement mechanism that includes a chamber with dilatant fluid (e.g., a shear thickening fluid).

Description of Related Art

Many mechanical mechanisms are subject to undesired movement that can lead to annoying sounds, property damage and/or loss, and personal injury and even death. Desired and undesired movements of the mechanical mechanisms may involve a wide range of forces. A need exists to control the wide range of forces to solve these problems.

DETAILED DESCRIPTION OF THE INVENTION

FIG.1Ais a schematic block diagram of an embodiment of a mechanical and computing system that includes a set of head units10-1through10-N, objects12-1through12-3, computing entities20-1through20-N associated with the head units10-1through10-N, and a computing entity22. The objects include any object that has mass and moves. Examples of an object include a door, an aircraft wing, a portion of a building support mechanism, and a particular drivetrain, etc.

The cross-sectional view ofFIG.1Aillustrates a head unit that includes a chamber16, a piston36, a plunger28, a plunger bushing32, and a chamber bypass40. The chamber16contains a shear thickening fluid (STF)42. The chamber16includes a back channel24and a front channel26, where the piston partitions the back channel24and the front channel26. The piston36travels axially within the chamber16. The chamber16may be a cylinder or any other shape that enables movement of the piston36and compression of the STF42. The STF42is discussed in greater detail with reference toFIGS.1B and1C.

The plunger bushing32guides the plunger28into the chamber16in response to force from the object12-1. The plunger bushing32facilitates containment of the STF within the chamber16. The plunger bushing32remains in a fixed position relative to the chamber16when the force from the object moves the piston36within the chamber16. In an embodiment the plunger bushing32includes an O-ring between the plunger bushing32and the chamber16. In another embodiment the plunger bushing32includes an O-ring between the plunger bushing32and the plunger28.

The piston36includes a piston bypass38between opposite sides of the piston to facilitate flow of a portion the STF between the opposite sides of the piston (e.g., between the back channel24and the front channel26) when the piston travels through the chamber in an inward or an outward direction.

Alternatively, or in addition to, the chamber bypass40is configured between opposite ends of the chamber16, wherein the chamber bypass40facilitates flow of a portion of the STF between the opposite ends of the chamber when the piston travels through the chamber in the inward or outward direction (e.g., between the back channel24and the front channel26).

In alternative embodiments, the piston bypass38and the chamber bypass40includes mechanisms to enable STF flow in one direction and not an opposite direction. In further alternative embodiments, a control valve within the piston bypass38and/or the chamber bypass controls the STF flow between the back channel24and the front channel26. Each bypass includes one or more of a one-way check valve and a variable flow valve.

The plunger28is operably coupled to a corresponding object by one of a variety of approaches. A first approach includes a direct connection of the plunger28to the object12-1such that linear motion in any direction couples from the object12-1to the plunger28. A second approach includes the plunger28coupled to a cap44which receives a one way force from a strike48attached to the object12-2. A third approach includes a pushcap46that receives a force from a rotary-to-linear motion conversion component that is attached to the object12-3. In an example, the object12-3is connected to a camshaft110which turns a cam109to strike the pushcap46.

In an embodiment, two or more of the head units are coupled by a head unit connector112. When so connected, actuation of a piston in a first head unit is essentially replicated in a piston of a second head unit. The head unit connector112includes a mechanical element between plungers of the two or more head units and/or direct connection of two or more plungers to a common object. For example, plunger28of head unit10-1and plunger28of head unit10-2are directly connected to object12-1when utilizing a direct connection.

Further associated with each head unit is a set of emitters and a set of sensors. For example, head unit10-N includes a set of emitters114-N−1 through114-N−M and a set of sensors116-N−1 through116-N−M. Emitters includes any type of energy and or field emitting device to affect the STF, either directly or indirectly via other nanoparticles suspended in the STF. Examples of emitter categories include light, audio, electric field, magnetic field, wireless field, etc. Specific examples of fluid manipulation emitters include a variable flow valve associated with a bypass or injector or similar, a mechanical vibration generator, an image generator, a light emitter, an audio transducer, a speaker, an ultrasonic sound transducer, an electric field generator, a magnetic field generator, and a radio frequency wireless field transmitter. Specific examples of magnetic field emitters include a Helmholtz coil, a Maxwell coil, a permanent magnet, a solenoid, a superconducting electromagnet, and a radio frequency transmitting coil.

Sensors include any type of energy and/or field sensing device to output a signal that represents a reaction, motion or position of the STF. Examples of sensor categories include bypass valve position, mechanical position, image, light, audio, electric field, magnetic field, wireless field, etc. Specific examples of fluid flow sensors include a valve opening detector associated with the chamber16or any type of bypass (e.g., piston bypass38, chamber bypass40, a reservoir injector, or similar), a mechanical position sensor, an image sensor, a light sensor, an audio sensor, a microphone, an ultrasonic sound sensor, an electric field sensor, a magnetic field sensor, and a radio frequency wireless field sensor. Specific examples of magnetic field sensors include a Hall effect sensor, a magnetic coil, a rotating coil magnetometer, an inductive pickup coil, an optical magnetometry sensor, a nuclear magnetic resonance sensor, and a caesium vapor magnetometer.

The computing entities20-1through20-N are discussed in detail with reference toFIG.2A. The computing entity22includes a control module30and a chamber database34to facilitate storage of history of operation, desired operations, and other aspects of the system.

In an example of operation, the head unit10-1controls motion of the object12-1and includes the chamber16filled at least in part with the shear thickening fluid42, the piston36housed at least partially radially within the chamber16, and the piston36is configured to exert pressure against the shear thickening fluid42in response to movement of the piston36from a force applied to the piston from the object12-1. The movement of the piston36includes one of traveling through the chamber16in an inward direction or traveling through the chamber16in an outward direction. The STF is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates.

The shear thickening fluid42(e.g., dilatant non-Newtonian fluid) has nanoparticles of a specific dimension that are mixed in a carrier fluid or solvent. Force applied to the shear thickening fluid42results in these nanoparticles stacking up, thus stiffening and acting more like a solid than a flowable liquid when a shear threshold is reached. In particular, viscosity of the shear thickening fluid42rises significantly when shear rate is increased to a point of the shear threshold. The relationship between viscosity and shear rates is discussed in greater detail with reference toFIGS.1A and1B.

In another example of operation, the object12-1applies an inward motion force on the plunger28which moves the piston36in words within the chamber16. As the piston moves inward, shear rate of the shear thickening fluid42changes. A sensor116-1-1associated with the chamber16of the head unit10-1outputs chamber I/O160to the computing entity20-1, where the chamber I/O160includes a movement data associated with the STF42as a result of the piston36moving inwards. Having received the chamber I/O160, the computing entity20-1interprets the chamber I/O160to reproduce the movement data.

The computing entity20-1outputs the movement data as a system message162to the computing entity22. The control module30stores the movement data in the chamber database34and interprets the movement data to determine whether to dynamically adjust the viscosity of the shear thickening fluid. Dynamic adjustment of the viscosity results in dynamic control of the movement of the piston36, the plunger28, and ultimately the object12-1. Adjustment of the viscosity affects velocity, acceleration, and position of the piston36.

The control module30determines whether to adjust the viscosity based on one or more desired controls of the object12-1. The desired controls include accelerating, deaccelerating, abruptly stopping, continuing on a current trajectory, continuing at a constant velocity, or any other movement control. For example, the control module30determines to abruptly stop the movement of the object12-1when the object12-1is a door and the door is detected to be closing at a rate above a maximum closing rate threshold level and when the expected shear rate versus viscosity of the shear thickening fluid42requires modification (e.g., boost the viscosity now to slow the door from closing too quickly).

When determining to modify the viscosity, the control module30outputs a system message162to the computing entity20-1, where the system message162includes instructions to immediately boost the viscosity beyond the expected shear rate versus viscosity of the shear thickening fluid42. Alternatively, the system message162includes specific information on the relationship of viscosity versus shear rate.

Having received the system message162, the computing entity20-1determines a set of adjustments to make with regards to the shear thickening fluid42within the chamber16. The set of adjustments includes one or more of adjusting STF42flow through the chamber bypass40, adjusting STF42flow through the piston bypass38, and activating an emitter of a set of emitters114-1-1through114-N−1. The flow adjustments include regulating within a flow range, stopping, starting, and allowing in one particular direction. For example, the computing entity20-1determines to activate emitter114-1-1to produce a magnetic field such as to interact with magnetic nanoparticles within the STF42to raise the viscosity. The computing entity20-1issues another chamber I/O160to the emitter114-1-1to initiate a magnetic influence process to boost the viscosity of the STF42.

In an alternative embodiment, the computing entity22issues another system message162to two or more computing entities (e.g.,20-1and20-2) to boost the viscosity for corresponding head units10-1and10-2when the head unit connector112connects head units10-1and10-2and both head units are controlling the motion of the object12-1. For instance, one of the head units informs the computing entity22that the object12-1is moving too quickly inward and the predicted stopping power of the expected viscosity versus shear rate of the STF42of the head unit, even when boosted, will not be enough to slow the object12-1to a desired velocity or position. When informed that one head unit, even with a modified viscosity, is not enough to control the object12-1, the control module30determines how many other head units (e.g., connected via the head unit connector112) to apply and to dynamically modify the viscosity.

In yet another alternative embodiment, the computing entity22issues a series of system messages162to a set of computing entities associated with a corresponding set of head units to produce a cascading effect of altering of the viscosity of the STF42of each of the chambers16associated with the set of head units. For example, 3 head units are controlled by 3 corresponding computing entities to adjust viscosity in a time cascaded manner. For instance, head unit10-1abruptly changes the viscosity to attempt to slow the object12-1followed seconds later by head unit10-2abruptly changing the viscosity to attempt to further slow the object12-1, followed seconds later by head unit12-3abruptly changing the viscosity to attempt to further slow the object12-1.

In a still further alternative embodiment, the computing entity22conditionally issues each message of the series of system messages162to the set of computing entities associated with the corresponding set of head units to produce the cascading effect of altering of the viscosity of the STF42of each of the chambers16associated with the set of head units only when a most recent adaptation of viscosity is not enough to slow the object12-1with desired results. For example, the 3 head units are controlled by the 3 corresponding computing entities to adjust viscosity in a conditional time cascaded manner. For instance, head unit10-1abruptly changes the viscosity to attempt to slow the object12-1followed seconds later by head unit10-2abruptly changing the viscosity if head unit10-1was unsuccessful to attempt to further slow the object12-1, followed seconds later by head unit12-3abruptly changing the viscosity if head unit10-2was unsuccessful to attempt to further slow the object12-1.

FIG.1Bis a graph of viscosity vs. shear rate for an aspect of an embodiment of a mechanical and computing system that includes a chamber, a shear thickening fluid, and a piston that moves through the chamber applying forces on the shear thickening fluid. The shear thickening fluid includes a non-Newtonian fluid since the relationship between shear rate and viscosity is nonlinear.

A relationship between compressive impulse (e.g., shear rate) and the viscosity of the shear thickening fluid is nonlinear and may comprise one or more inflection points as the piston travels within the chamber in response to different magnitudes of forces and different accelerations. The viscosity of the STF may also be a function of other influences, such as electric fields, acoustical waves, magnetic fields, and other similar influences. As a first example of a response of a shear thickening fluid, a first range of shear rates in zone A has a decreasing viscosity as the shear rate increases and then in a second range of shear rates in zone B the viscosity increases abruptly. As a second example of a response of a diluted shear thickening fluid, the first range of shear rates in zone A extends to a higher level of shear rates with the decreasing viscosity and then in the still higher second range of shear rates in zone B the viscosity increases abruptly similar to that of the shear thickening include.

The shear thickening fluid includes particles within a solvent. Examples of particles of the shear thickening fluid include oxides, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, or a mixture thereof. Further examples of the particles of the shear thickening fluid include SiO2, polystyrene, or polymethylmethacrylate.

The particles are suspended in a solvent. Example components of the solvent include water, a salt, a surfactant, and a polymer. Further example components of the solvent include ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone or a mixture thereof. Example particle diameters range from less than 100 μm to less than 1 millimeter. In an instance, the shear thickening fluid is made of silica particles suspended in polyethylene glycol at a volume fraction of approximately 0.57 with the silica particles having an average particle diameter of approximately 446 nm. As a result, the shear thickening fluid exhibits a shear thickening transition at a shear rate of approximately 102-103 s−1.

A volume fraction of particles dispersed within the solvent distinguishes the viscosity versus shear rate of different shear thickening fluids. The viscosity of the STF changes in response to the applied shear stress. At rest and under weak applied shear stress, a STF may have a fairly constant or even slightly decreasing viscosity because the random distribution of particles causes the particles to frequently collide. However, as a greater shear stress is applied so that the shear rate increases, the particles flow in a more streamlined manner. However, as an even greater shear stress is applied so that the shear rate increases further, a hydrodynamic coupling between the particles may overcome the interparticle forces responsible for Brownian motion. The particles may be driven closer together, and the microstructure of the colloidal dispersion may change, so that particles cluster together in hydroclusters.

The viscosity curve of the STF can be fine-tuned through changes in the characteristics of the particles suspended in the solvent. For example, the particles shape, surface chemistry, ionic strength, and size affect the various interparticle forces involved, as does the properties of the solvent. However, in general, hydrodynamic forces dominate at a high shear stress, which also makes the addition of a polymer attached to the particle surface effective in limiting clumping in hydroclusters. Various factors influence this clumping behavior, including, fluid slip, adsorbed ions, surfactants, polymers, surface roughness, graft density (e.g., of a grafted polymer), molecular weight, and solvent, so that the onset of shear thickening can be modified. In general, the onset of shear thickening can be slowed by the introduction of techniques to prevent the clumping of particles. For example, influencing the STF with emissions from an emitter in proximal location to the chamber.

FIG.1Cis a graph of piston velocity vs. force applied to the piston for an aspect of an embodiment of a mechanical and computing system that includes a chamber, a shear thickening fluid, and a piston that moves through the chamber applying forces on the shear thickening fluid. The shear thickening fluid includes a non-Newtonian fluid since the relationship between shear rate and viscosity is nonlinear.

An example curve for a shear thickening fluid indicates that as more force is applied to the piston in zone A, a higher piston velocity is realized until the corresponding transition to zone B occurs where the shear threshold affect takes hold and the viscosity abruptly increases significantly. When the viscosity increases abruptly, the piston velocity slows back down and may even stop.

Another example curve for a diluted shear thickening fluid indicates that as more force is applied to the piston in zone A, an even higher piston velocity is realized until the corresponding transition to zone B occurs where the shear threshold affect takes hold and the viscosity abruptly increases significantly. When the viscosity increases abruptly, the piston velocity slows back down and may even stop.

FIG.2Ais a schematic block diagram of an embodiment of the computing entity (e.g.,20-1through20-N; and22) of the mechanical and computing system ofFIG.1. The computing entity includes one or more computing devices100-1through100-N. A computing device is any electronic device that communicates data, processes data, represents data (e.g., user interface) and/or stores data.

Computing devices include portable computing devices and fixed computing devices. Examples of portable computing devices include an embedded controller, a smart sensor, a social networking device, a gaming device, a smart phone, a laptop computer, a tablet computer, a video game controller, and/or any other portable device that includes a computing core. Examples of fixed computing devices includes a personal computer, a computer server, a cable set-top box, a fixed display device, an appliance, and industrial controller, a video game counsel, a home entertainment controller, a critical infrastructure controller, and/or any type of home, office or cloud computing equipment that includes a computing core.

FIG.2Bis a schematic block diagram of an embodiment of a computing device (e.g.,100-1through100-N) of the computing entity ofFIG.2Athat includes one or more computing cores52-1through52-N, a memory module102, a human interface module18, an environment sensor module14, and an input/output (I/O) module104. In alternative embodiments, the human interface module18, the environment sensor module14, the I/O module104, and the memory module102may be standalone (e.g., external to the computing device). An embodiment of the computing device is discussed in greater detail with reference toFIG.3.

FIG.3is a schematic block diagram of another embodiment of the computing device100-1of the mechanical and computing system ofFIG.1that includes the human interface module18, the environment sensor module14, the computing core52-1, the memory module102, and the I/O module104. The human interface module18includes one or more visual output devices74(e.g., video graphics display, 3-D viewer, touchscreen, LED, etc.), one or more visual input devices80(e.g., a still image camera, a video camera, a 3-D video camera, photocell, etc.), and one or more audio output devices78(e.g., speaker(s), headphone jack, a motor, etc.). The human interface module18further includes one or more user input devices76(e.g., keypad, keyboard, touchscreen, voice to text, a push button, a microphone, a card reader, a door position switch, a biometric input device, etc.) and one or more motion output devices106(e.g., servos, motors, lifts, pumps, actuators, anything to get real-world objects to move).

The computing core52-1includes a video graphics module54, one or more processing modules50-1through50-N, a memory controller56, one or more main memories58-1through58-N (e.g., RAM), one or more input/output (I/O) device interface modules62, an input/output (I/O) controller60, and a peripheral interface64. A processing module is as defined at the end of the detailed description.

The memory module102includes a memory interface module70and one or more memory devices, including flash memory devices92, hard drive (HD) memory94, solid state (SS) memory96, and cloud memory98. The cloud memory98includes an on-line storage system and an on-line backup system.

The I/O module104includes a network interface module72, a peripheral device interface module68, and a universal serial bus (USB) interface module66. Each of the I/O device interface module62, the peripheral interface64, the memory interface module70, the network interface module72, the peripheral device interface module68, and the USB interface modules66includes a combination of hardware (e.g., connectors, wiring, etc.) and operational instructions stored on memory (e.g., driver software) that are executed by one or more of the processing modules50-1through50-N and/or a processing circuit within the particular module.

The I/O module104further includes one or more wireless location modems84(e.g., global positioning satellite (GPS), Wi-Fi, angle of arrival, time difference of arrival, signal strength, dedicated wireless location, etc.) and one or more wireless communication modems86(e.g., a cellular network transceiver, a wireless data network transceiver, a Wi-Fi transceiver, a Bluetooth transceiver, a 315 MHz transceiver, a zig bee transceiver, a 60 GHz transceiver, etc.). The I/O module104further includes a telco interface108(e.g., to interface to a public switched telephone network), a wired local area network (LAN)88(e.g., optical, electrical), and a wired wide area network (WAN)90(e.g., optical, electrical). The I/O module104further includes one or more peripheral devices (e.g., peripheral devices1-P) and one or more universal serial bus (USB) devices (USB devices1-U). In other embodiments, the computing device100-1may include more or less devices and modules than shown in this example embodiment.

FIG.4is a schematic block diagram of an embodiment of the environment sensor module14of the computing device ofFIG.2Bthat includes a sensor interface module120to output environment sensor information150based on information communicated with a set of sensors. The set of sensors includes a visual sensor122(e.g., to the camera, 3-D camera, 360° view camera, a camera array, an optical spectrometer, etc.) and an audio sensor124(e.g., a microphone, a microphone array). The set of sensors further includes a motion sensor126(e.g., a solid-state Gyro, a vibration detector, a laser motion detector) and a position sensor128(e.g., a Hall effect sensor, an image detector, a GPS receiver, a radar system).

The set of sensors further includes a scanning sensor130(e.g., CAT scan, MRI, x-ray, ultrasound, radio scatter, particle detector, laser measure, further radar) and a temperature sensor132(e.g., thermometer, thermal coupler). The set of sensors further includes a humidity sensor134(resistance based, capacitance based) and an altitude sensor136(e.g., pressure based, GPS-based, laser-based).

The set of sensors further includes a biosensor138(e.g., enzyme, microbial) and a chemical sensor140(e.g., mass spectrometer, gas, polymer). The set of sensors further includes a magnetic sensor142(e.g., Hall effect, piezo electric, coil, magnetic tunnel junction) and any generic sensor144(e.g., including a hybrid combination of two or more of the other sensors).

FIG.5Ais a cross-section diagram of an embodiment of a rotary power coupler200that couples rotary power from a rotary power device202to a load device204. The rotary power device202includes one or more of a variety of power sources such as a fossil fuel engine, a hydro-turbine, a steam turbine, an electric motor, a servo motor, and a combination of any of the above. The load device204includes any type of device powered by and/or using rotary motion such as a vehicle, a wheel, an elevator, a conveyor system, an automatic door, etc.

The power coupler200includes a chamber206, a driveshaft208, a drive turbine210, a load turbine212, a load shaft214, and a cartridge seal216. The chamber206has an interior cylindrical shape and either an external cylindrical shape or a hexagonal external shape. In a primary embodiment the chamber206is affixed to a nonmoving structure associated with at least one of the rotary power device202, the load device204, or another stationary object. The primary embodiment is associated with free rotational movement of the driveshaft208and the load shaft214. In a second embodiment, the chamber206substantially rotates in unison with the driveshaft208(e.g., the chamber206is not fixed to a stationary object). In a third embodiment, the chamber206substantially rotates in unison with the load shaft214(e.g., the chamber206is not fixed to a stationary object).

The power coupler200further includes a snap ring218and a washer220combined to hold a first end of the driveshaft208in a fixed position with regards to the chamber206. Snap rings222hold the drive turbine210to the other end of the driveshaft208. The power coupler200further includes a needle bearing224to facilitate rotation of the driveshaft208within the chamber206. The power coupler200further includes a seal226and a thrust bearing228to hold the drive turbine210in the fixed position with regards to the chamber206.

The drive turbine210includes an O-ring230and a where ring232to facilitate sealing of the drive turbine210within the chamber206. A key234facilitates mounting of the drive turbine210to the driveshaft208. In an embodiment, the driveshaft208and the drive turbine210are separate components. In another embodiment, the driveshaft208and the drive turbine210are manufactured as a common component. The drive turbine210is discussed in further detail with reference toFIG.5B.

Within the chamber206and between the drive turbine210and the load turbine212is a shear thickening fluid (STF)236. Load turbine212includes O-rings242and a wear ring244to seal the load turbine212within the chamber206. The load shaft214extends from the load turbine212through the cartridge seal216and is held in place within the chamber by a washer254and snap rings260and258. In an embodiment, the load turbine212and the load shaft214are manufactured as a common component. In another embodiment, the load turbine212and the load shaft214are separate components. The cartridge seal216is held in place in an and of the chamber206in a fixed position by snap rings250and is sealed within the chamber206by o-rings252. The load shaft214rotates within the cartridge seal216facilitated by needle bearing246. The needle bearing246is secured within the cartridge seal216by a cap screw248.

The STF236is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates, wherein the second range of shear rates are greater than the first range of shear rates as discussed with reference toFIG.1B. The STF236includes a plurality of nanoparticles that includes one or more of an oxide, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, SiO2, polystyrene, polymethylmethacrylate, or a mixture of any of the above. The STF236further includes a solution to suspend the nanoparticles where the solution includes one or more of ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone, or a mixture of any of the above.

The chamber206is configured to contain a portion of the STF236, where the chamber includes a cylindrical interior channel. The cylindrical interior channel includes a drive side section and a load side section.

The drive shaft208is housed at least partially radially within the drive side section and protruding outward from a drive side section end of the chamber for coupling to the rotary power device202. The load shaft214is housed at least partially radially within the load side section and protruding outward from a load side section end of the chamber for coupling to the load device204.

The drive turbine210is housed at least partially radially within the drive side section and coupled to the drive shaft208. The drive turbine210is configured to exert pressure against the shear thickening fluid in response to rotary movement of the drive shaft from a rotary force applied to the drive shaft from the rotary power device.

The load turbine212is housed at least partially radially within the load side section at a fixed operational distance from the drive turbine and coupled to the load shaft. The load turbine configured to apply a secondary rotary force to the drive shaft in response to the pressure exerted against the shear thickening fluid from the drive turbine. The fixed operational distance between the drive turbine and the load turbine enables both the first range of shear rates and the second range of shear rates.

The cartridge seal216guides the load shaft214into the chamber206. The cartridge seal facilitates containment of the STF236within the chamber206. The cartridge seal remains in a fixed position relative to the chamber206(e.g., at an open end to facilitate manufacturability). The snap ring258serves as a retaining device to maintain the load shaft214in a fixed position within the cartridge seal216to establish the fixed operational distance between the drive turbine210and the load turbine212.

FIG.5Bis a diagram of an embodiment of the drive turbine210that includes an O-ring channel274, a wear ring channel272, and a rotary array of drive teeth270arranged in a gear pattern. The gear pattern includes one or more of spur, helical, spiral, bevel, worm drive, and herringbone.

In an embodiment, the drive teeth270include at least one of a variety of configurations. A first configuration includes a first tooth configured with at least one cylindrical tube276with substantially consistent diameter from one side of the first tooth to an opposite side of the first tooth.

A second configuration includes a second tooth configured with at least one conical shaped tube276with an increasing diameter from one side of the second tooth to an opposite side of the second tooth. A third configuration includes a third tooth configured with at least one conical shaped tube with a decreasing diameter from one side of the third tooth to the opposite side of the third tooth. This conical shaping of the diameter creates the first and second levels of shear forces of the STF when the drive turbine is rotating within the STF of the chamber.

A fourth configuration includes a fourth tooth configured with at least one venturi shaped tube278from one side of the fourth tooth to the opposite side of the fourth tooth. This Venturi shaping of the tube also creates the first and second levels of shear forces of the STF when the drive turbine is rotating within the STF of the chamber.

The arranged gear pattern of the rotary array of drive teeth is configured to provide the decreasing viscosity in response to the first range of shear rates of the STF in the chamber in response to a first range of rotary power from the rotary power device. The range gear pattern also provides the increasing viscosity in response to the second range of shear rates of the STF in the chamber in response to a second range of rotary power from the rotary power device. The second range of rotary power is greater than the first range of rotary power.

FIG.5Cis a diagram of an embodiment of the load turbine212that includes the load shaft214, a wear-ring channel282, o-ring channels284, and a rotary array of load teeth280.

The rotary array of load teeth280are arranged in a gear pattern. The gear pattern includes one or more of spur, helical, spiral, bevel, worm drive, and herringbone. The gear pattern of the load turbine212complements the gear pattern of the rotary array of drive teeth of the drive turbine210such that the pressure exerted against the shear thickening fluid from the rotary array of drive teeth causes the rotary array of load teeth to apply the secondary rotary force to the drive shaft214.

In an embodiment, the load teeth280include a variety of configurations. A first configuration includes a first tooth configured with at least one cylindrical tube with substantially consistent diameter from one side of the first tooth to an opposite side of the first tooth (e.g., like the tube276of the drive turbine210).

A second configuration includes a second tooth configured with at least one conical shaped tube with an increasing diameter from one side of the second tooth to an opposite side of the second tooth. A third configuration includes a third tooth configured with at least one conical shaped tube with a decreasing diameter from one side of the third tooth to the opposite side of the third tooth (e.g., like the conical shaped tubes276of the drive turbine210). A fourth configuration includes a fourth tooth configured with at least one venturi shaped tube from one side of the fourth tooth to the opposite side of the fourth tooth (e.g., like the venturi tube278of the drive turbine210).

In another embodiment, none of the drive teeth270and none of the load teeth280include the above variety of configurations. In yet another embodiment, the drive teeth270include one or more holes and none of the load teeth280include holes. In a still further embodiment, none of the drive teeth270include holes and one or more of the load teeth280include one or more holes.

The arranged gear pattern of the rotary array of load teeth is configured to provide a first range of rotary output power to the load shaft in response to the first range of shear rates of the STF in the chamber resulting from a first range of rotary power from the rotary power device that causes the decreasing viscosity. The arranged gear pattern of the rotary array of load teeth also provides a second range of rotary output power to the load shaft in response to the second range of shear rates of the STF in the chamber resulting from a second range of rotary power from the rotary power device that causes the increasing viscosity. The second range of rotary output power is greater than the first range of rotary output power.

FIGS.5D-5Eare graphs portraying embodiments of operation of the rotary power coupler200.FIG.5Dillustrates driveshaft revolutions per minute (RPMs) versus load shaft RPMs. As the driveshaft begins to rotate and establishes a first threshold level of RPMs, the STF experiences the first range of shear rates and caused by the drive turbine which starts to move the load turbine within the first range of viscosity and hence the load shaft begins to turn.

As the driveshaft RPMs increase, a second threshold of driveshaft RPMs is established where the STF experiences the second range of shear rates caused by the drive turbine which moves the load turbine with increased force as the second range of viscosity is established and hence the load shaft begins to turn even more rapidly. For similar patterns of teeth of the drive turbine and load turbine, and as the second range of viscosity is established, the load shaft RPMs are similar to the driveshaft RPMs (e.g., approaching a 1:1 drive ratio) when the distance between the turbines is very close. The efficiency of the drive ratio is lowered as the turbines are separated since less STF is in play to move the load turbine and the amount of STF experiencing the second range of viscosity is lowered.

FIG.5Ealso illustrates driveshaft revolutions per minute (RPMs) versus load shaft RPMs for an embodiments where the gear patterns are different between the drive turbine and the load turbine. The dotted line illustrates an embodiment where the load turbine is more efficient than the drive turbine (e.g., more teeth, more aggressive tapering of the tubes through the teeth). As the driveshaft begins to rotate and establishes a first threshold level of RPMs, the STF experiences the first range of shear rates and caused by the drive turbine which starts to move the load turbine within the first range of viscosity and hence the load shaft begins to turn.

As the driveshaft RPMs increase, a second threshold of driveshaft RPMs is established where the STF experiences the second range of shear rates caused by the drive turbine which moves the load turbine with increased force as the second range of viscosity is established and hence the load shaft begins to turn even more rapidly. For similar patterns of teeth of the drive turbine and load turbine, and as the second range of viscosity is established, the load shaft RPMs are similar to the driveshaft RPMs (e.g., approaching a 1:1 drive ratio). When the gear pattern of the load turbine is more efficient than the gear pattern of the drive turbine, the STF moved by the drive turbine moves the load turbine with more RPMs (e.g., higher than 1:1) during the utilization of the second viscosity range of the STF as illustrated by the dotted line.

FIG.6Ais a cross-section diagram of an embodiment of another rotary power coupler300. The power coupler300includes all the components of the power coupler200with the exception of the snap rings258and260. The power coupler300substitutes a shaft collar256for the snap rings258and260.

Within the chamber206of the power coupler300and between the drive turbine210and a load turbine312is a shear thickening fluid (STF)236. Load turbine312includes O-rings242and a wear ring244to seal the load turbine312within the chamber206. The load shaft214extends from the load turbine312through the cartridge seal216and is held in place within the chamber by the washer254and the shaft collar256. The cartridge seal216is held in place in an end of the chamber206in a fixed position by snap rings250and is sealed within the chamber206by o-rings252. The load shaft214rotates within the cartridge seal216facilitated by needle bearing246. The needle bearing246is secured within the cartridge seal216by a cap screw248.

The STF236is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates, wherein the second range of shear rates are greater than the first range of shear rates as discussed with reference toFIG.1B. The STF236includes a plurality of nanoparticles that includes one or more of an oxide, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, SiO2, polystyrene, polymethylmethacrylate, or a mixture of any of the above. The STF236further includes a solution to suspend the nanoparticles where the solution includes one or more of ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone, or a mixture of any of the above.

The chamber206is configured to contain a portion of the STF236, where the chamber includes a cylindrical interior channel. The cylindrical interior channel includes a drive side section and a load side section.

A drive shaft308is housed at least partially radially within the drive side section and protruding outward from a drive side section end of the chamber for coupling to the rotary power device202. The load shaft214is housed at least partially radially within the load side section and protruding outward from a load side section end of the chamber for coupling to the load device204.

The drive turbine210is housed at least partially radially within the drive side section and coupled to the drive shaft308. The drive turbine210is configured to exert pressure against the shear thickening fluid in response to rotary movement of the drive shaft from a rotary force applied to the drive shaft from the rotary power device.

The load turbine312is housed at least partially radially within the load side section at an adjustable operational distance from the drive turbine and coupled to the load shaft. The load turbine is configured to apply a secondary rotary force to the drive shaft in response to the pressure exerted against the shear thickening fluid from the drive turbine. The adjustable operational distance between the drive turbine and the load turbine enables both the first range of shear rates and the second range of shear rates.

The shaft collar256is configured to establish the adjustable operational distance from the drive turbine to the load turbine. For example, a set screw is loosened to enable sliding the load shaft214either way and tightened once a desired operational distance is established.

The cartridge seal216guides the load shaft214into the chamber206. The cartridge seal facilitates containment of the STF236within the chamber206. The cartridge seal remains in a fixed position relative to the chamber206(e.g., at an open end to facilitate manufacturability).

FIG.6Bis a graph portraying an embodiment of operation of the rotary power coupler300with closer spacing of the turbines as set by the shaft collar256illustrating driveshaft revolutions per minute (RPMs) versus load shaft RPMs. As the driveshaft begins to rotate and establishes a first threshold level of RPMs, the STF experiences the first range of shear rates and caused by the drive turbine which starts to move the load turbine within the first range of viscosity and hence the load shaft begins to turn.

As the driveshaft RPMs increase, a second threshold of driveshaft RPMs is quickly established due to the close spacing where the STF experiences the second range of shear rates caused by the drive turbine which moves the load turbine with increased force as the second range of viscosity is established and hence the load shaft begins to turn even more rapidly. For similar patterns of teeth of the drive turbine and load turbine, and as the second range of viscosity is established, the load shaft RPMs are similar to the driveshaft RPMs (e.g., approaching a 1:1 drive ratio) when the distance between the turbines is very close.

FIG.6Cis a cross-section diagram of another embodiment of the rotary power coupler300where the turbines are separated by a greater distance than as illustrated inFIG.6A. As such, lower shear forces are in play for the shear thickening fluid236between the drive turbine210and the load turbine312. The shaft collar256is field adjusted to establish the further distance between the turbines.

FIG.6Dis a graph portraying another embodiment of operation of the rotary power coupler300with further spacing of the turbines as set by the shaft collar256illustrating driveshaft revolutions per minute (RPMs) versus load shaft RPMs. As the driveshaft begins to rotate and establishes a new first threshold level of RPMs, the STF experiences the first range of shear rates and caused by the drive turbine which starts to move the load turbine within the first range of viscosity and hence the load shaft begins to turn.

As the driveshaft RPMs increase, a new second threshold of driveshaft RPMs is finally established due to the further spacing where the STF begins to experience the second range of shear rates caused by the drive turbine which moves the load turbine with some increased force as the second range of viscosity is established and hence the load shaft begins to turn more rapidly. For similar patterns of teeth of the drive turbine and load turbine, and as the second range of viscosity is at least in part established, the load shaft RPMs approach a maximum percentage of the driveshaft RPMs (e.g., approaching something less than a 1:1 drive ratio) when the distance between the turbines is further away.

FIGS.7A-7Bare cross-section diagrams of an embodiment of another rotary power coupler400illustrating an example of controlling coupling of rotary power. The power coupler400includes the components of the power coupler300with the exception of a load actuator456replacing the shaft collar256and an actuator track458associated with the load shaft214. The power coupler400further includes the computing entity20-1ofFIG.1, the environment sensor module14ofFIG.2B, the sensor116ofFIG.1, and the emitter114ofFIG.1.

The load actuator456is configured to establish an adjustable operational distance from the drive turbine to the load turbine. For example, a motor of the load actuator456moves the actuator track458to push or pull the load shaft214within the chamber206.

The sensor116includes a set of fluid flow sensors to produce a fluid response of the STF236. The set of fluid flow sensors are positioned proximal to the chamber206. The set of fluid flow sensors includes a load turbine position sensor, a load actuator position sensor, and an actuator track position sensor.

The emitter114includes a set of fluid manipulation emitters positioned proximal to the chamber206. The set of fluid manipulation emitters provide a fluid activation (e.g., selecting a shear rate range of the STF) to at least one of the STF236and the load actuator456to enable selection of the first range of shear rates and the second range of shear rates.

The computing entity20-1includes the control module30in the chamber database34ofFIG.1. The environment sensor module14senses sensed factors460associated with the load device204and provides environmental sensor information150to the computing entity20-1. The sensed factors460includes RPMs associated with the load device204, any movement of an object associated with the load device204, and anything associated with another object indirectly associated with the load device204within a common environment.

FIG.7Aillustrates steps of an example method of operation of the power coupler400where a first step includes the computing entity20-1activating the power coupler400using a baseline STF activation470. An STF activation includes creating an environment within the chamber206for the STF to experience a desired first or second range of shear rates and hence the first or second range of viscosities of the STF to provide a desired level of power coupling from the rotary power device202to the load device204. A baseline STF activation includes an initial set of STF activations that are expected to produce the desired level of power coupling.

The set of baseline STF activation includes providing a default level of power in a power control466signal to the rotary power device202, outputting a default fluid activation signal to the emitter114to modify the STF for an initial shear force versus viscosity curve, and moving the load shaft214via the load actuator456to a starting position for a default separation of the turbines that is expected to experience a desired level of shear forces of the STF between the turbines. For instance, the control module30outputs the power control466to the rotary power device202, outputs the fluid activation234to the emitter114, and outputs actuator control462to the load actuator456to achieve the desired turbine spacing.

Having activated the power coupler400using the baseline STF activation, a second step of the example method of operation includes the computing entity20-1determining a coupler status472of the power coupler400. The status of the power coupler400includes one or more of a power conversion factor between the rotary power device202and the load device204, RPMs of the rotary power device202verses RPMs of the load device204, the STF fluid response (e.g., which range of shear rates at present), position and utilization information associated with the load device204, and information with regards to the sensed factors460. The determining of the status includes a variety of alternatives.

In a first alternative example, the control module30interprets fluid response232from the sensor116to determine status of shear rates of the STF. As another alternative example, the control module30interprets load information464from the load device204to determine the position and utilization information associated with the load device204. As yet another alternative example, the control module30interprets environment sensor information150from the environment sensor module14to determine results from the sensed factors460with regards to movement of any object associated with the load device204.

FIG.7Bfurther illustrates the example method of operation where in a third step the computing entity20-1determines an updated STF activation474based on the status of the power coupler400. The determining includes identifying a desired status of the power coupler and determining changes to affect the power coupler to move from the current status to the desired status. The identifying the desired status includes at least one of performing a lookup, interpreting a received message, and determining the desired status. For example, the control module30retrieves the desired status from the chamber database34for load device204.

The determining the changes to affect the power coupler includes a variety of alternatives. A first alternative includes increasing the STF viscosity when delivered power is less than desired (e.g., an object associated with the load device204is not moving fast enough). In an instance, the control module30determines a new fluid activation234to modify the STF for a higher viscosity. As another instance, the control module30determines to reduce the gap between the turbines to increase the viscosity. As yet another example, the control module30determines to increase power to the rotary power device202to raise the delivered power.

A second alternative includes decreasing the STF viscosity when the delivered power is greater than desired (e.g., the object associated with the load device is moving too fast). In an instance, the control module30determines the new fluid activation234to modify the STF for a lower viscosity. As another instance, the control module30determines to increase the gap between the turbines to decrease the viscosity. As yet another example, the control module30determines to lower the power to the rotary power device202to lower the delivered power.

Having determined the updated STF activation, a fourth step of the example method of operation includes the computing entity20-1applying the updated STF activation to the power coupler400to facilitate the transferring of the rotary power from the rotary power device to the load device. For example, the control module30outputs an updated actuator control462to the load actuator456in accordance with the updated STF activation to facilitate an updated separation of the turbines (e.g., closer for more viscosity to transfer more power for speeding up or even hard braking, further away for less viscosity to slow down or to coast). As another example, the control module30outputs an updated fluid activation234to the emitter114to modify the viscosity of the STF in accordance with the updated STF activation (e.g., more viscosity to transfer more power for speeding up or hard braking, less viscosity to slow down or to coast). As yet another example, the control module30outputs an updated power control466to the rotary power device202to either increase or decrease the power in accordance with the updated STF activation.

FIG.7Cis a timing diagram set portraying an embodiment of operation of rotary power coupler400. With the driveshaft running turning at a reference 1.0 and the gap between the turbines at a baseline separation, the STF between the turbines engages such that the load shaft turns at a reference rate of 0.5.

When the desired power transfer is to spin the load shaft at a higher speed, the gap between the turbines is lowered to speed up the load turbine such that the load shaft turns at a reference rate of 0.9 (e.g., almost 1:1 ratio). Later, the gap between the turbines is widened such that the load turbine and load shaft spin slower at a reference rate of 0.3. Next the power to the rotary power device is turned off and the distance between the turbines is closed up to a very close gap such that the load shaft spends down very quickly in unison with the drive shaft to provide braking.

The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.7Acan alternatively be performed by other modules of the system ofFIG.7Aor by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system, cause one or more computing devices of the mechanical and computing system ofFIG.7Ato perform any or all of the method steps described above.

FIG.8Ais a cross-section diagram of an embodiment of a rotary power shunt500that includes all the components of the power coupler200along with a lock502and pins506. The power shunt500shunts rotational power from a load device504providing a braking action as desired. The load device504includes any type of device powered by and/or using rotary motion such as a vehicle, a wheel, an elevator, a conveyor system, an automatic door, etc.

The STF236is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates, wherein the second range of shear rates are greater than the first range of shear rates as discussed with reference toFIG.1B. The STF236includes a plurality of nanoparticles that includes one or more of an oxide, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, SiO2, polystyrene, polymethylmethacrylate, or a mixture of any of the above. The STF236further includes a solution to suspend the nanoparticles where the solution includes one or more of ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone, or a mixture of any of the above.

The chamber206is configured to contain a portion of the STF236, where the chamber includes a cylindrical interior channel. The cylindrical interior channel includes a drive side section and a load side section.

In an embodiment, the drive shaft208is housed at least partially radially within the drive side section and protruding outward from a drive side section end of the chamber for coupling to lock502configured to prevent rotation of the driveshaft208. The load shaft214is housed at least partially radially within the load side section and protruding outward from a load side section end of the chamber for coupling to the load device204.

In the embodiment, the drive turbine210is housed at least partially radially within the drive side section and coupled to the drive shaft208. The drive turbine210is configured to exert resistive pressure against the shear thickening fluid in response to rotary movement of the load shaft from a rotary force applied to the load shaft from the load device.

In another embodiment, a fixed position of the drive turbine210with respect to the chamber206is provided by one or more of configuring the drive turbine210and the chamber206as substantially one component and configuring the drive turbine210, the chamber206, and the driveshaft208as substantially one component. In yet another embodiment, the driveshaft208is coupled to a stationary external object to provide the fixed position of the drive turbine210. The stationary external object includes at least one of a lock, the rotary power device202locked in a stop position, and a servo motor that is held in a stopped position.

The load turbine212is housed at least partially radially within the load side section at a fixed operational distance from the drive turbine and coupled to the load shaft. The load turbine is configured to apply at least some of the rotary power from the load device via the load shaft to the STF. The STF, in response to the pressure exerted against the STF from the load turbine, exerts pressure on the drive turbine. The fixed operational distance between the drive turbine and the load turbine enables both the first range of shear rates and the second range of shear rates.

The cartridge seal216guides the load shaft214into the chamber206. The cartridge seal facilitates containment of the STF236within the chamber206. The cartridge seal remains in a fixed position relative to the chamber206(e.g., at an open end to facilitate manufacturability). The snap ring258serves as a retaining device to maintain the load shaft214in a fixed position within the cartridge seal216to establish the fixed operational distance between the drive turbine210and the load turbine212.

The drive turbine210includes the rotary array of drive teeth arranged in the gear pattern. The arranged gear pattern of the rotary array of drive teeth of the power shunt500is configured to provide a first range of rotary output power to the drive shaft in response to the first range of shear rates of the STF in the chamber resulting from a first range of rotary power from the load device that causes the decreasing viscosity.

The arranged gear pattern of the rotary array of drive teeth of the power shunt500is further configured to provide a second range of rotary output power to the drive shaft in response to the second range of shear rates of the STF in the chamber resulting from a second range of rotary power from the load device that causes the increasing viscosity. The second range of rotary output power is greater than the first range of rotary output power. The operation of the power shunt500to provide braking power is further discussed with reference toFIG.8B.

The load turbine212includes the rotary array of load teeth arranged in the gear pattern. The arranged gear pattern of the rotary array of load teeth of the power shunt500is configured to provide the decreasing viscosity in response to the first range of shear rates of the STF in the chamber in response to a first range of rotary power from the load device. The arranged gear pattern of the rotary array of load teeth of the power shunt500is further configured to provide the increasing viscosity in response to the second range of shear rates of the STF in the chamber in response to a second range of rotary power from the load device. The operation of the power shunt500to provide braking power is further discussed with reference toFIG.8B.

FIG.8Bis a graph portraying an embodiment of operation of a rotary power shunt illustrating turbine engagement versus braking force. The turbine engagement indicates proximity of the turbines, where a maximum level of turbine engagement means that the turbines are right next each other with substantially no gap. No engagement means that the turbines are separated so much that there is virtually no transfer of power via the STF between the turbines.

In an example of operation where a load speed of the load device504is a nominal level, STF engagement at a low and below threshold effect level starts as the turbine engagement is increased. Minimal braking force is achieved. Further braking force rapidly increases once the STF reaches the second threshold and the second viscosity range where the load turbine transfers more power to the drive turbine for shunting. At the closest turbine engagement, a massive STF engagement occurs where having already achieved the second range of viscosity, simply more volume of the STF is compressed and available to provide drive from the load turbine to the drive turbine to provide more braking force.

When the load speed is slower than the nominal load speed, the turbine engagement must be higher to achieve similar braking forces as illustrated by the gray line to the right. When the load speed is faster than the nominal load speed, the turbine engagement can be lowered to achieve similar braking forces as illustrated by the gray line to the left.

The power shunt500may be utilized as a governor of sorts by selecting a turbine engagement level to provide constant braking power to the load device504whenever it is above the threshold of the STF as it moves from the first range of viscosities to the second range of viscosities.

FIG.9Ais a cross-section diagram of another embodiment of a rotary power shunt600that includes all the components of the power coupler300along with the lock502and the pins506. The power shunt600shunts rotational power from a load device504providing a braking action as desired. The load device504includes any type of device powered by and/or using rotary motion such as a vehicle, a wheel, an elevator, a conveyor system, an automatic door, etc.

The STF236is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates, wherein the second range of shear rates are greater than the first range of shear rates as discussed with reference toFIG.1B. The STF236includes a plurality of nanoparticles that includes one or more of an oxide, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, SiO2, polystyrene, polymethylmethacrylate, or a mixture of any of the above. The STF236further includes a solution to suspend the nanoparticles where the solution includes one or more of ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone, or a mixture of any of the above.

The chamber206is configured to contain a portion of the STF236, where the chamber includes a cylindrical interior channel. The cylindrical interior channel includes a drive side section and a load side section.

The drive shaft208is housed at least partially radially within the drive side section and protruding outward from a drive side section end of the chamber for coupling to lock502configured to prevent rotation of the driveshaft208. The load shaft214is housed at least partially radially within the load side section and protruding outward from a load side section end of the chamber for coupling to the load device204.

The drive turbine210is housed at least partially radially within the drive side section and coupled to the drive shaft208. The drive turbine210is configured to exert resistive pressure against the shear thickening fluid in response to rotary movement of the load shaft from a rotary force applied to the load shaft from the load device.

The load turbine212is housed at least partially radially within the load side section at an adjustable operational distance from the drive turbine and coupled to the load shaft. The load turbine is configured to apply at least some of the rotary power from the load device via the load shaft to the STF. The STF, in response to the pressure exerted against the STF from the load turbine, exerts pressure on the drive turbine. The adjustable operational distance between the drive turbine and the load turbine enables both the first range of shear rates and the second range of shear rates.

The shaft collar256is configured to establish the adjustable operational distance from the drive turbine to the load turbine is a primary mechanism to establish turbine engagement and utilization of desired STF viscosity ranges. For example, a set screw can be field adjusted to enable moving and then establishing the gap between the turbines at a desired level.

The cartridge seal216guides the load shaft214into the chamber206. The cartridge seal facilitates containment of the STF236within the chamber206. The cartridge seal remains in a fixed position relative to the chamber206(e.g., at an open end to facilitate manufacturability).

The drive turbine210includes the rotary array of drive teeth arranged in the gear pattern. The arranged gear pattern of the rotary array of drive teeth of the power shunt600is configured to provide a first range of rotary output power to the drive shaft in response to the first range of shear rates of the STF in the chamber resulting from a first range of rotary power from the load device that causes the decreasing viscosity.

The arranged gear pattern of the rotary array of drive teeth of the power shunt600is further configured to provide a second range of rotary output power to the drive shaft in response to the second range of shear rates of the STF in the chamber resulting from a second range of rotary power from the load device that causes the increasing viscosity. The second range of rotary output power is greater than the first range of rotary output power. The operation of the power shunt600to provide braking power is further discussed with reference toFIG.9B.

The load turbine212includes the rotary array of load teeth arranged in the gear pattern. The arranged gear pattern of the rotary array of load teeth of the power shunt600is configured to provide the decreasing viscosity in response to the first range of shear rates of the STF in the chamber in response to a first range of rotary power from the load device. The arranged gear pattern of the rotary array of load teeth of the power shunt600is further configured to provide the increasing viscosity in response to the second range of shear rates of the STF in the chamber in response to a second range of rotary power from the load device. The operation of the power shunt600to provide braking power is further discussed with reference toFIG.9B.

FIG.9Bis a graph portraying an embodiment of operation of a rotary power shunt illustrating turbine engagement versus braking force. The turbine engagement indicates proximity of the turbines, where a maximum level of turbine engagement means that the turbines are right next each other with substantially no gap. No engagement means that the turbines are separated so much from a setting of the shaft collar256that there is virtually no transfer of power via the STF between the turbines.

In an example of operation where a load speed of the load device504is a nominal level, STF engagement at a low and below threshold effect level starts as the turbine engagement is increased utilizing shaft collar256. Minimal braking force is achieved. Further braking force rapidly increases once the STF reaches the second threshold and the second viscosity range where the load turbine transfers more power to the drive turbine for shunting. At the closest turbine engagement set by shaft collar256, a massive STF engagement occurs where having already achieved the second range of viscosity, simply more volume of the STF is compressed and available to provide drive from the load turbine to the drive turbine to provide more braking force.

When the load speed is slower than the nominal load speed, the turbine engagement must be higher to achieve similar braking forces as illustrated by the gray line to the right. When the load speed is faster than the nominal load speed, the turbine engagement can be lowered to achieve similar braking forces as illustrated by the gray line to the left.

The power shunt600may be utilized as a governor of sorts by selecting a turbine engagement level to provide constant braking power to the load device504whenever it is above the threshold of the STF as it moves from the first range of viscosities to the second range of viscosities. The governor can be adjusted by moving the shaft collar256to achieve a desired level of engagement of the governor.

FIGS.10A-10Bare cross-section diagrams of an embodiment of another rotary power shunt700illustrating an example of controlling shunting of rotary power. The power shunt700includes all the components of the power coupler400along with the lock502and the pins506. The power shunt700shunts rotational power from a load device504providing an automation of braking action as desired. The load device504includes any type of device powered by and/or using rotary motion such as a vehicle, a wheel, an elevator, a conveyor system, an automatic door, etc.

The STF236is configured to have a decreasing viscosity in response to a first range of shear rates and an increasing viscosity in response to a second range of shear rates, wherein the second range of shear rates are greater than the first range of shear rates as discussed with reference toFIG.1B. The STF236includes a plurality of nanoparticles that includes one or more of an oxide, calcium carbonate, synthetically occurring minerals, naturally occurring minerals, polymers, SiO2, polystyrene, polymethylmethacrylate, or a mixture of any of the above. The STF236further includes a solution to suspend the nanoparticles where the solution includes one or more of ethylene glycol, polyethylene glycol, ethanol, silicon oils, phenyltrimethicone, or a mixture of any of the above.

The chamber206is configured to contain a portion of the STF236, where the chamber includes a cylindrical interior channel. The cylindrical interior channel includes a drive side section and a load side section.

The drive shaft208is housed at least partially radially within the drive side section and protruding outward from a drive side section end of the chamber for coupling to lock502configured to prevent rotation of the driveshaft208. The load shaft214is housed at least partially radially within the load side section and protruding outward from a load side section end of the chamber for coupling to the load device204.

The drive turbine210is housed at least partially radially within the drive side section and coupled to the drive shaft208. The drive turbine210is configured to exert resistive pressure against the shear thickening fluid in response to rotary movement of the load shaft from a rotary force applied to the load shaft from the load device.

The load turbine212is housed at least partially radially within the load side section at an adjustable operational distance from the drive turbine and coupled to the load shaft. The load turbine is configured to apply at least some of the rotary power from the load device via the load shaft to the STF. The STF, in response to the pressure exerted against the STF from the load turbine, exerts pressure on the drive turbine. The adjustable operational distance between the drive turbine and the load turbine enables both the first range of shear rates and the second range of shear rates.

The load actuator456is configured to establish the adjustable operational distance from the drive turbine to the load turbine. For example, a motor of the load actuator456moves the actuator track458to push or pull the load shaft214within the chamber206.

The cartridge seal216guides the load shaft214into the chamber206. The cartridge seal facilitates containment of the STF236within the chamber206. The cartridge seal remains in a fixed position relative to the chamber206(e.g., at an open end to facilitate manufacturability).

FIG.10Aillustrates an example method of operation of the shunting of the power where a first step includes the computing entity20-1determining a shunt status772of the power shunt700. The determining of the status of the power shunt includes one or more of interpreting the fluid response232from the sensor116, interpreting load information464from the load device204, and interpreting environment sensor information150from the environment sensor module14with regards to sensed factors460. For example, the control module30determines a speed of an object associated with the load device204from the load information464. The determining of the status further includes recovering the baseline STF activation470from the chamber database34.

FIG.10Billustrates a second step of the example method of operation of the shunting of the power where the computing entity20-1determines an updated STF activation or74based on the power shunt status772. For example, the control module30determines to increase the STF viscosity when braking power is less than desired or when an object associated with the load device204is moving too fast. As another example, the control module30determines to decrease viscosity when the braking power is greater than desired or when the object associated with the load device is moving too slow. The updated STF activation includes one or more of an updated fluid activation234to directly adjust the viscosity of the STF by way of the emitter114and an updated actuator control462to adjust the separation of the turbines to change the viscosity range.

Having determined the updated STF activation474, a third step of the example method of operation includes the computing entity20-1activating the power shunt700using the updated STF activation474. For example, the control module30outputs the fluid activation234to the emitter114for an updated shear force versus viscosity to add or reduce braking power. As another example, the control module30outputs the actuator control462to power the load actuator456to move the load shaft214for an adjusted separation of the turbines. For instance, the turbines are moved closer to increase the braking power and are moved further apart to lower the braking power to coast or speed up on its own.

FIG.10Cis a timing diagram set portraying an embodiment of operation of the rotary power shunt700where a baseline separation of the turbines provides a baseline load shaft speed. When a closer gap between the turbines is produced the load shaft revolutions is reduced. When the gap between the turbines is increased beyond the baseline the load shaft revolutions speeds up faster than the baseline speed. When the gap between the turbines is significantly reduced the load shaft experiences hard braking.

The method described above in conjunction with a processing module of any computing entity of the mechanical and computing system ofFIG.10Acan alternatively be performed by other modules of the system ofFIG.10Aor by other devices. In addition, at least one memory section that is non-transitory (e.g., a non-transitory computer readable storage medium, a non-transitory computer readable memory organized into a first memory element, a second memory element, a third memory element, a fourth element section, a fifth memory element, a sixth memory element, etc.) that stores operational instructions can, when executed by one or more processing modules of the one or more computing entities of the computing system, cause one or more computing devices of the mechanical and computing system ofFIG.10Ato perform any or all of the method steps described above.

As may further be used herein, a computer readable memory includes one or more memory elements. A memory element may be a separate memory device, multiple memory devices, or a set of memory locations within a memory device. Such a memory device may be a read-only memory, random access memory, volatile memory, non-volatile memory, static memory, dynamic memory, flash memory, cache memory, a quantum register or other quantum memory and/or any other device that stores data in a non-transitory manner. Furthermore, the memory device may be in a form of a solid-state memory, a hard drive memory or other disk storage, cloud memory, thumb drive, server memory, computing device memory, and/or other non-transitory medium for storing data. The storage of data includes temporary storage (i.e., data is lost when power is removed from the memory element) and/or persistent storage (i.e., data is retained when power is removed from the memory element). As used herein, a transitory medium shall mean one or more of: (a) a wired or wireless medium for the transportation of data as a signal from one computing device to another computing device for temporary storage or persistent storage; (b) a wired or wireless medium for the transportation of data as a signal within a computing device from one element of the computing device to another element of the computing device for temporary storage or persistent storage; (c) a wired or wireless medium for the transportation of data as a signal from one computing device to another computing device for processing the data by the other computing device; and (d) a wired or wireless medium for the transportation of data as a signal within a computing device from one element of the computing device to another element of the computing device for processing the data by the other element of the computing device. As may be used herein, a non-transitory computer readable memory is substantially equivalent to a computer readable memory. A non-transitory computer readable memory can also be referred to as a non-transitory computer readable storage medium.