TIRE INFLATION SYSTEM

专利摘要:
tire inflation system and two-stage passive pump. it is a tire inflation system that includes a drive mechanism that has a rotational axis, a pump cavity positioned at a radial distance from the rotational axis, and a power transformer that couples the rotational axis to the pump cavity. the drive mechanism includes a cam comprising an arcuate bearing surface that has a non-uniform curvature, the cam being rotatable about the rotational axis, and an eccentric mass joint to the cam that deviates from a center of mass. of the drive mechanism of the rotational geometric axis. the pump cavity is pivotally coupled to the cam, the pump cavity including an actuation member and a chamber. the power transformer couples the arcuate bearing surface to the actuating element, the power transformer including a shaft having an arcuate position fixed to an arcuate position of the pump cavity.
公开号:BR112014022974B1
申请号:R112014022974-0
申请日:2013-03-12
公开日:2021-08-17
发明作者:Brandon Richardson；Dave Carlberg；Ace Shelander
申请人:Aperia Technologies；
IPC主号:

专利说明:

CROSS REFERENCE TO RELATED ORDERS
[001] This application claims the benefit of Provisional Application No. US 61/613,406, filed March 20, 2012, Provisional Application No. US 61/637,206, filed April 23, 2012, and Provisional Application No. US 61/ 672,223, filed on July 16, 2012, which are incorporated in their entirety by way of reference.
[002] This application is also related to Order No. 13/469,007, filed May 10, 2012, which is incorporated in its entirety by reference. FIELD OF TECHNIQUE
[003] This invention relates, in general, to the pumping field and, more specifically, to a new and useful passive pump system in the pumping field. BACKGROUND
[004] Tires that are not optimally pressurized contribute to low fuel efficiency. These effects are particularly noticeable in the trucking industry, where long distances and wide roads potentiate the effects of an underinflated tire. However, it is often inconvenient and inefficient for truck drivers to constantly stop, check and inflate vehicle tires to optimal pressure, leading to persistent less-than-optimal fuel efficiency on most trucks. This problem has led to several self-inflating tire systems. Conventional self-inflating tire systems are either central or distributed, however each suffers from its own set of disadvantages. Central inflation systems are complex and expensive and require significant labor for aftermarket installation (drilling through shafts, bypassing existing air lines, etc.). Distributed systems are mounted on each wheel and can be less expensive, however the potential for reduced cost is typically at the cost of continual device replacement (which fails due to the harsh wheel environment).
[005] Additionally, passive pressurization systems may be desirable for tire inflation applications, since programming and electrical energy storage mechanisms can be eliminated from the system. However, conventional passive booster systems suffer from several problems. First, conventional passive booster systems using reciprocating pumps often suffer from fatigue due to the high pressures and high number of pumping cycles that are required. Second, passive pressurization systems can suffer from reservoir over pressurization, in which the pressurization system continues to pump fluid into the reservoir even after the desired reservoir pressure is reached. Conventional systems typically solve this problem with a relief valve, where the relief valve vents reservoir contents to the environment when the reservoir pressure exceeds the desired pressure. This results in a loss of fluid already pressurized, resulting in additional pumping cycles to bring the fluid at ambient pressure to the desired pressure, thus resulting in a shorter pump life. Third, conventional eccentric mass driven pump systems, such as pendulum systems, experience instabilities when the rotating surface to which the eccentric mass is coupled rotates near the excitation frequency for the given eccentric mass. More specifically, the eccentric mass rotates with the system at this excitation frequency, resulting in radial oscillations that can be detrimental to the overall system or to the rotating surface to which the pump system is coupled.
[006] Thus, there is a need in the pumping field to create a new and useful pump. BRIEF DESCRIPTION OF THE FIGURES
[007] Figure 1 is a schematic representation of the pump system coupled to a rotating surface.
[008] Figures 2A and 2B are schematic representations of a variation of the pump system in the recovered and compressed positions, respectively.
[009] Figures 3A and 3B are cut views of a variation of the primary pump in the compressed and retrieved positions, respectively.
[010] Figures 4A and 4B are cross-sectional views of a variation of the pump system with the putty joint and with the cut dough joint, respectively.
[011] Figures 5A, 5B, and 5C are cut-away views of a variation of the pump system in the recovery stroke, the beginning of the compression stroke and the end of the compression stroke, respectively.
[012] Figure 6 is a perspective view of a variation of the pump system.
[013] Figures 7A and 7B are schematic representations of a variation of the pump system in which the first reservoir pressure is equal to or less than ambient pressure and in which the first reservoir pressure is greater than ambient pressure, respectively.
[014] Figures 8A and 8B are schematic representations of a variation of the torque stabilization mechanism in pumping and non-pumping mode, respectively.
[015] Figures 9A and 9B are schematic representations of a second variation of the torque stabilization mechanism in pumping and non-pumping modes, respectively.
[016] Figures 10A and 10B are schematic representations of a variation of the stabilization mechanism in pumping and non-pumping modes, respectively.
[017] Figures 11A and 11B are schematic representations of a second variation of the stabilization mechanism in pumping and non-pumping modes, respectively.
[018] Figures 12A and 12B are sectional views of a variation of the pressure regulation mechanism in pumping and non-pumping modes, respectively.
[019] Figures 13A and 13B are sectional views of a second variation of the pressure regulation mechanism in pumping and non-pumping modes, respectively.
[020] Figures 14A and 14B are sectional views of a third variation of the pressure regulation mechanism in pumping and non-pumping modes, respectively.
[021] Figures 15A and 15B are schematic flowcharts of a variation of the pressure regulation mechanism in pumping and non-pumping modes, respectively.
[022] Figure 16 is a cut away view of the valve inside the pressure regulation mechanism. DESCRIPTION OF PREFERRED MODALITIES
[023] The following description of the preferred embodiments of the invention is not intended to limit the invention to those preferred embodiments, but rather to enable any person skilled in the art to produce and use this invention. 1. PUMP SYSTEM
[024] As shown in Figure 1, the pump system 10 includes a drive mechanism that also includes a cam 120 coupled to an eccentric mass 140, a primary pump 200 that includes a reciprocating element 220 and a pump body 240, and a power transformer 300 that couples cam 120 to reciprocating element 220. Pump system 10 functions to translate rotational motion into linear motion. More preferably, the pump system 10 functions to translate relative movement between the primary pump 200 and cam 120 into a pumping force, wherein eccentric mass 140 retains the cam position relative to a gravity vector while primary pump 200 rotates with respect to cam 120 (eg with a rotating surface 20). Pump system 10 preferably additionally functions to pressurize the pumped fluid. Power transformer 300 preferably translates the relative movement between cam 120 and primary pump 200 into pumping force, which is preferably applied against reciprocal element 220. More preferably, power transformer 300 moves reciprocal element 220 through a compression stroke. Power transformer 300 can additionally facilitate a recovery stroke (return stroke). However, the pump system 10 may alternatively convert relative motion into linear force, electrical energy (e.g., via piezoelectric sensors, motion through an induced electric field, etc.), or any other suitable form of energy or movement. Pump system 10 is preferably passively controlled, but alternatively can be controlled, wherein the system further includes a power supply, a plurality of sensors, and a controller that controls valve operation based on sensor measurements.
[025] The pump system 10 is preferably attachable to a surface that rotates with respect to a gravity vector (rotating surface 20). The rotating surface 20 is preferably a wheel of a vehicle, more preferably a truck, but may alternatively be any suitable rotating system, such as a windmill, watermill or any other suitable rotating surface 20.
[026] The pump system 10 preferably receives fluid from a first reservoir 400 and pumps the fluid into a second reservoir 500. The fluid received from the first reservoir 400 preferably has a first pressure, and the fluid pumped to the second reservoir 500 preferably has a second pressure higher than the first pressure, but may alternatively have a pressure substantially similar to the first pressure. The fluid is preferably a gas, more preferably ambient air, but it may alternatively be any other suitable gas, a liquid, or any other suitable fluid. First reservoir 400 is preferably the environment, but can alternatively be a source of fluid (e.g., a fluid can), an intermediate reservoir, or any other suitable reservoir. When first reservoir 400 is an intermediate reservoir, first reservoir 400 preferably receives fluid from a fluid source, such as the environment or a fluid canister. Second reservoir 500 is preferably an inner tire, but may alternatively be any suitable reservoir. The pump system 10 can further treat the pumped fluid, preferably before the primary pump enters, but alternatively after the primary pump egress. The fluid is preferably treated (eg, filtered) to remove debris, water or any other suitable unwanted component from the fluid. The fluid is preferably treated within the intermediate reservoir, when used. Alternatively, fluid can be treated during primary pump ingress (eg where the inlet includes a filter) or at any suitable point within the fluid flow path.
[027] The drive mechanism 100 of the pump system 10 functions to generate the pumping force and to control the magnitude of the pumping force. The pumping force (occlusion force) is preferably a variable force applied in a radial direction from a rotational geometric axis of the drive mechanism 100, but may alternatively be a constant force, a force applied at any suitable angle to the geometric axis. rotational, or any other suitable force. Drive mechanism 100 preferably includes cam 120 and eccentric mass 140. Drive mechanism 100 includes a geometric rotational axis around which drive mechanism 100 rotates relative to primary pump 200 (in contrast, around which primary pump 200 rotates relative to drive mechanism 100) . The rotational axis of the drive mechanism 100 is preferably the rotational axis of the cam 120, but it may alternatively be the rotational axis of the eccentric mass 140, the rotational axis around which the primary pump 200 rotates, or any other axis suitable rotational geometric. The pump system 10 is preferably configured so that the rotational axis of the drive mechanism 100 is substantially aligned with the rotational axis of the rotation surface 20 when the pump system 10 is coupled to the rotation surface 20, however the system of pump 10 can alternatively be configured such that the rotational axis of drive mechanism 100 is offset from the rotational axis of rotation surface 20. Drive mechanism 100 additionally includes a center of mass, determined from mass and positions cam 120 and eccentric mass 140. Eccentric mass 140 is preferably coupled to cam 120 such that the center of mass of drive mechanism 100 is offset from the rotational axis of drive mechanism 100.
[028] Cam 120 of drive mechanism 100 functions to control magnitude of pumping force. Cam 120 preferably functions to provide substantially constant torque against reciprocal element 220 throughout the compression stroke, but may alternatively provide variable torque against reciprocal element 220 throughout the compression or recovery strokes. Cam 120 preferably includes a bearing surface 122, wherein the bearing surface profile 122 preferably controls the magnitude of the pumping force throughout the compression stroke. Support surface 122 is preferably continuous, but alternatively may be discontinuous. Bearing surface 122 is preferably defined on the outside of cam 120 (outer bearing surface or outer bearing surface), but may alternatively be defined on the interior of cam 120 (inner bearing surface or inner bearing surface) as shown in Figure 6, in which bearing surface 122 defines a lumen within cam 120. Bearing surface 122 is preferably arcuate and preferably has a non-uniform curvature (e.g., an oblong profile or a reniform profile as shown in Figures 2 . and 5, respectively). Alternatively, bearing surface 122 may have a uniform curvature (e.g., a circular profile), an angular profile, or any other suitable profile. The bearing surface 122 preferably includes a compression portion and a recovery portion, which correspond to the compression stroke and the recovery stroke of the primary pump 200, respectively. The compression portion is preferably continuous with the recovery section, but it can alternatively be discontinuous. Support surface 122 preferably has a first section 124 that has a low curvature (preferably positive or convex curvature, but alternatively negative or concave curvature) adjacent to a second section 126 that has a low curvature (e.g., substantially flat or which has a negative curvature compared to the first section 124). Support surface 122 preferably further includes a third section 128 connecting the first and second sections, wherein the third section 128 preferably provides a substantially smooth transition between the first and second sections having a low curvature adjacent to the first. section 124 and a low curvature adjacent to second section 126. The compression portion preferably begins at the end of second section 126 distal to first section 124, extends along third section 128, and ends at the apex of first section 124, as shown. in Figure 5B. The compression portion is preferably convex (eg when bearing surface 122 is an external bearing surface), but it may alternatively be concave. The apex of the first section 124 preferably corresponds to the top of the compression stroke (compressed position 222), as shown in Figure 5C. The recovery portion preferably begins at the apex of the first section 124, extends along the second section 126, and ends at the end of the second section 126 distal to the first section 124, as shown in Figure 5A. The recovery portion is preferably substantially flat or concave (eg when bearing surface 122 is an outer bearing surface 122), but may alternatively be convex. The end of the second section 126 preferably corresponds to the bottom of the recovery course (recovered position 224). The slope of the compression portion is preferably less than 30 degrees, but it may alternatively have any suitable angle. When a roller is used as the power transformer 300, the curvature of bearing surface 122 is preferably at least three times greater than the roller curvature or roller diameter, but may alternatively be larger or smaller. However, bearing surface 122 can have any suitable profile. Cam 120 is preferably substantially planar with bearing surface 122 defined along the side of cam 120 in a plane normal to the rotational geometric axis of cam 120 (e.g., normal to broad face of cam 120). Bearing surface 122 is preferably defined along the entire side of the cam, but may alternatively be defined along a defined portion of the side of the cam. The pump force generated is preferably directed radially away from the rotational axis, more preferably along a plane normal to the rotational axis. Alternatively, cam 120 may have a round or profiled edge segment (transition between broad face of and cam side), wherein bearing surface 122 may include the profiled edge. Alternatively, the arcuate surface is defined by a cam face parallel to the rotational axis of the cam 120, wherein the generated pump force can be directed at any suitable angle to the rotational axis, which varies from parallel to the geometric axis. rotational to normal to the rotational geometric axis. The compression portion preferably encompasses most of the cam profile, but may alternatively encompass half of the cam profile or a small portion of the cam profile. In a variation, the compression portion covers 315 degrees of the cam profile, while the recovery portion covers 45 degrees of the cam profile. However, the compression and recovery portions can cover any other suitable proportion of the cam profile.
[029] The eccentric mass 140 (suspended mass) of the drive mechanism 100 functions to shift the center of mass of the drive mechanism 100 from the rotational axis of the drive mechanism 100. This displacement can function to substantially retain the angular position of the mechanism of drive 100 with respect to a gravity vector, thereby engendering the relative movement between the drive mechanism 100 and the components of the pump system that are statically coupled to the rotating surface 20 (which rotates with respect to the vector gravity). The eccentric mass 140 is preferably a substantially homogeneous piece, but it may alternatively be heterogeneous. Eccentric mass 140 is preferably a substantially single piece, but may alternatively be made of multiple pieces or segments. in the latter variation, the multiple pieces are preferably substantially similar in shape, angular and radial position, and mass, but may alternatively be substantially different in profile, mass, angular position or radial position. Eccentric mass 140 is preferably a distributed mass (for example, it extends along a substantial portion of an arc centered around the rotational axis, as shown in Figure 4B), but it may alternatively be a point mass. In certain applications, particularly those applications with high rotational speeds, distributed mass may be preferred as distributed mass results in low oscillation frequencies, thus resulting in a low probability of eccentric mass excitation in rotating with the system in response to a linear oscillation introduced into the system (eg pumps, system pulsation, etc.). Eccentric mass 140 is preferably curved, but may alternatively be substantially flat, angled, or otherwise shaped accordingly. The radius of the eccentric mass curvature is preferably maximized so that the eccentric mass traces an arcuate section of the perimeter pump system. However, the eccentric mass 140 can have any other suitable curvature. Eccentric mass 140 preferably extends at least 90 degrees around the rotational axis of the drive mechanism 100, more preferably 180 degrees around the rotational axis, but may extend more or less than 180 degrees around the rotational axis . Eccentric mass 140 preferably has substantially more mass than cam 120, but may alternatively have substantially similar mass or a smaller mass. Eccentric mass 140 preferably imparts 2 pound-inch (0.225 Nm) of torque to cam 120, as it can alternatively impart more or less torque.
[030] The eccentric mass 140 is preferably a separate cam part 120 and is preferably coupled to the cam 120 by a mass coupling 142. Alternatively, the eccentric mass 140 can be incorporated into the cam 120, in which the eccentric mass 140 is incorporated. along the perimeter of cam 120, embedded in one half of cam 120, or embedded along any other suitable portion of cam 120. Eccentric mass 140 may be statically coupled to cam 120 or rotatably coupled to cam 120. that the eccentric mass 140 is statically coupled to the cam 120, the eccentric mass 140 may be coupled to the cam 120 on the rotational axis of the cam 120, the rotational axis of the drive mechanism 100, displaced from the rotational axis of the cam 120 or any other suitable portion of the cam 120. Eccentric mass 140 can be permanently connected to cam 120. Alternatively, eccentric mass 140 can be transiently connected (removably coupled) to cam 120, wherein eccentric mass 140 is operable between a pumping mode in which eccentric mass 140 is coupled to cam 120 and a non-pumping mode in which eccentric mass 140 is disconnected of cam 120. Mass coupling 142 preferably has a high moment of inertia, but may alternatively have a low moment of inertia. Mass joint 142 is preferably a disk (as shown in Figure 4A), but may alternatively be a lever arm, plate or any other suitable connection. Mass coupling 142 preferably couples to cam broad face 120, but may alternatively couple to cam edge 120, along cam outer bearing surface 120, cam inner bearing surface 120, to an extending shaft of cam 120 (wherein cam 120 may be statically fixed or rotatably mounted to the shaft) or to any other suitable portion of cam 120. Mass coupling 142 may be frictionally coupled to cam 120 by a coupling mechanism transient (eg permanent or complementary electrical magnets located in cam 120 and ground union 142, in a piston, in a pin and groove mechanism, etc.), by bearings or by any other means of coupling. When mass coupling 142 couples to cam 120 by a transient coupling mechanism, mass coupling 142 is preferably operable between a coupled mode, wherein mass coupling 142 connects eccentric mass 140 to cam 120, and a mode uncoupled, wherein mass coupling 142 disconnects eccentric mass 140 from cam 120. Mass coupling 142 may additionally function as a cut-off mechanism, wherein mass coupling 142 is switched from coupled mode to uncoupled mode in response detecting a cut-off event (for example, where the reservoir pressure reaches a threshold pressure). In a variation, the mass joint 142 is a disk located in the lumen defined by an inner bearing surface of the cam 120, wherein the disk is rotatable relative to the inner bearing surface in decoupled mode and is coupled to the inner bearing surface. by a friction element in coupled mode. In another variation, mass coupling 142 is rotatably mounted on a shaft extending from cam 120 by bearings, wherein mass coupling 142 can be statistically coupled to cam 120 by one or more sets of magnets or pistons that extend from the adjacent broad faces of cam 120 and mass joint 142.
[031] The primary pump 200 of the pump system 10 functions to pressurize a fluid with the pumping force generated between the cam 120 and the reciprocal element 220. The primary pump 200 is preferably a positive displacement pump that includes a drive element and a pump cavity and is more preferably a reciprocating pump, wherein the primary pump 200 includes a reciprocal element 220 and a pump body 240. The primary pump 200 preferably includes a lumen defined between the reciprocal element 220 and the pump body 240, wherein the lumen is preferably substantially fluid impermeable. The primary pump 200 is preferably pivotally coupled to the rotational axis of the drive mechanism 100. The primary pump 200 is preferably positioned a radial distance from the rotational axis of the drive mechanism 100, wherein the first radial of the primary pump 200 is preferably fixed, but alternatively adjustable. More preferably, the primary pump 200 is preferably mounted statistically in a housing (wherein the housing is statistically coupled to the rotating surface 20) but may alternatively be transiently mounted in the housing (adjustably mounted). During operation, the primary pump 200 preferably rotates around the rotational axis. During the entire rotation, the variable bearing surface profile preferably applies a variable force to the reciprocal element 220 as the distance between the bearing surface 122 and the pump body bottom varies. The primary pump 200 preferably includes a drive axis, wherein the reciprocal element 220 preferably travels along the drive axis along the compression stroke. The reciprocal element 220 can additionally move along the same geometric drive axis during the return stroke. The primary pump 200 is preferably oriented so that the drive axis is substantially normal to the rotational axis, but may alternatively be positioned so that the drive axis is at any suitable angle to the rotational axis. Primary pump 200 and cam 120 preferably share a common plane, whereby the pumping force is preferably transmitted along the common plane, but may alternatively be substantially displaced. The system preferably includes a primary pump 200, and more preferably includes two pump cavities. However, pump system 10 can include any suitable number of pump cavities. When the pump system 10 includes multiple pump cavities, the pump cavities are preferably substantially evenly distributed around the rotational axis (e.g., have substantially similar distances between their respective angular positions), but may alternatively and non-uniformly distributed. The pump cavities preferably have substantially similar radial positions with respect to the rotational axis, but they may have alternatively different radial positions. Pump cavities can be substantially different (eg with different lumen volumes, different drive areas, etc.) or can be substantially similar.
[032] The reciprocal element 220 of the primary pump 200 works to receive the pumping force from the cam 120 and translate into the lumen, acting in relation to the pump body 240. This drive preferably creates a variable pressure within the lumen. Reciprocal element 220 is preferably operable between a compressed position 222 and a retrieved position 224, as shown in Figures 3A and 3B, respectively. In the compressed position 222, a portion of the reciprocal element 220 (e.g., the center) is preferably proximal to the bottom of the pump body. In the retrieved position 224, the reciprocal member portion 220 is preferably distal to the pump body bottom, and is preferably proximal to the pump body opening. The reciprocal element 220 preferably travels along a compression stroke to translate from the retrieved position 224 to the compressed position 222 and travels along a retrieval course to transition from the compressed position 222 to the retrieved position 224. The reciprocal element 220 may be further positioned in a pressurized position, wherein the reciprocal element 220 is located in a second position distal to the pump body bottom, where the second position is further away from the pump body bottom than the retrieved position 224. Reciprocal element 220 is preferably in the pressurized position when the force supplied by lumen pressure exceeds the force supplied by cam 120 on reciprocal element 220.
[033] The reciprocal element 220 preferably translates along a drive geometry axis within the primary pump 200 during the compression stroke and may additionally translate along the drive geometry axis during the recovery stroke. Reciprocal element 220 preferably includes a drive area that provides the pressurizing force. The actuation area is preferably the surface area of a wide face of the reciprocal element 220, more preferably the surface area of the wide face proximal to the lumen, but alternatively any other suitable wide face. Alternatively, the actuation area may be the surface area of a section of the reciprocal element 220 that translates between the compressed position 222 and the retrieved position 224 (e.g., the center portion).
[034] The reciprocal element 220 preferably forms a fluid-tight seal with the pump body 240, more preferably with the walls defining the pump body opening, so that the reciprocal element 220 substantially seals the pump body opening. Reciprocal element 220 can be sealed to pump body 240 by a retaining mechanism. The retaining mechanism is preferably a clamp that applies a compressive force against the edge of the reciprocal element and the pump body wall, but it may alternatively be screws or bolts through the edge of the reciprocal element, adhesive between the reciprocal element 220 and the wall body or on the reciprocating member 220 and the pump body wall, or any other suitable retaining mechanism. The reciprocal element 220 may also be sealed against the pump body wall by fusing the interface between the reciprocal element 220 and the pump body wall, or by any other suitable means of sealing the reciprocal element 220 against the wall of pump body.
[035] The reciprocal element 220 is preferably a flexible diaphragm, but can alternatively be a substantially rigid piston, a piston coupled to the diaphragm or any other suitable element that acts in response to the pumping force. The diaphragm is preferably a rolling diaphragm (e.g. with a rolled perimeter, wherein the diaphragm is preferably coupled to pump body 240 with the extra material distal to the lumen) but may be a flat diaphragm, a domed diaphragm (preferably coupled to pump body 240 with apex distal to lumen, but alternatively coupled to pump body 240 with apex proximal to lumen), or any other suitable diaphragm.
[036] The pump body 240 of the primary pump 200 functions to cooperatively compress a fluid with the reciprocal element 220. The pump body 240 is preferably substantially rigid, but may alternatively be flexible. Pump body 240 is preferably an open pump body with a closed end, wherein pump body 240 preferably includes a closed end (bottom), walls extending from the closed end, and an opening opposite the closed end. However, pump body 240 may alternatively have two open ends or any other suitable configuration. The closed end is preferably substantially flat, but it may alternatively be curved or have any other suitable geometry. The walls are preferably substantially flat, but can alternatively be curved or have any other suitable geometry. The walls preferably join the closed end at an angle, more preferably at a right angle, but the transition between the walls and the closed end can be alternatively and substantially smooth (for example, having a bell-shaped or paraboloid longitudinal cross-section ) . The closed end is preferably substantially parallel to the opening defined by the walls, but may alternatively be oriented at an angle relative to the opening. Pump body 240 may be a groove defined in an arcuate or prismatic part (for example, in a longitudinal or lateral radial direction), a cylinder, a prism, or any other suitable shape. Pump body 240 preferably has a substantially symmetrical side cross-section (e.g., circular, ovular or rectangular cross-section, etc.), but may alternatively have an asymmetrical cross-section. Pump body 240 is preferably oriented in pump system 10 so that the closed end is substantially normal to a radial vector extending from the rotational axis of drive mechanism 100 (e.g., the closed end normal vector is substantially parallel to the radial vector), but can alternatively be oriented with the closed end at an angle to the radial vector. Pump body 240 is preferably oriented with the opening proximal and the closed end distal to the rotational axis, particularly when the primary pump 200 rotates around the outer cam, but may alternatively be oriented with the opening distal and the closed end proximal to the rotational axis, particularly when the primary pump 200 rotates around the inner cam or oriented from any other suitable position relative to the rotational axis.
[037] The primary pump 200 may additionally include a return element 260 that functions to return the reciprocal element 220 to the retrieved position 224. The return element 260 preferably provides a restoring force that is less than the compressive force provided by the third section 128 of cam 120, but greater than the force applied by cam 120 on second section 126. The recovery force is preferably provided in a radial direction substantially parallel to a radial vector extending from the rotational geometric axis of drive mechanism 100, however it can alternatively be supplied in any suitable radial direction. Return element 260 is preferably located on the side of pump body 240 of reciprocal element 220 (distal to cam 120 opposite reciprocal element 220), wherein return element 260 preferably pushes reciprocal element 220 from the compressed position 222 , during the recovery stroke, and to the retrieved position 224. Alternatively, the return element 260 may be located on the cam side of the reciprocal element (distal to the pump body 240 opposite the reciprocal element 220), wherein the return element 260 pulls the reciprocal element 220 back to the retrieved position 224 from the compressed position 222. The return element 260 is preferably coupled to the perimeter of the reciprocal element 220 or to a component (e.g., a gusset) coupled to the element. reciprocal 220 and which extends beyond the pump body wall, but may alternatively be coupled to the body of the reciprocal element 220 (for example, to the section that fits ua between the compressed position 222 and the retrieved position 224). Return element 260 is preferably coupled to reciprocal element 220 external to pump body 240, but may alternatively be coupled to reciprocal element 220 to pump body 240. Return element 260 is preferably a spring, but may also include the intrinsic properties of the drive element (eg, the elasticity of the diaphragm) or any other suitable return element 260.
[038] The primary pump 200 is preferred and additionally includes one or more inlets that facilitate fluid ingress into the lumen of the first reservoir 400 and one or more outlets that facilitate egress from the lumen to the second reservoir 500. Alternatively, the primary pump 200 may include a fluid manifold that functions as both an inlet and an outlet, wherein said fluid manifold is fluidly connected to and selectively permits fluid flow from the first and second reservoirs. The inlet and outlet are preferably defined through the walls of the pump body 240, but may alternatively be defined through the reciprocal element 220, through the junction between the pump body 240 and the reciprocal element 220 or defined in any other suitable portion of the primary pump 200. The inlet and outlet are preferably located on opposite walls, but may alternatively be adjacent on the same wall, located at the closed end or located in any other position.
[039] The inlet and outlet of the pump 200 preferably include inlet and outlet valves that control fluid flow through the respective fluid channels. The valves are preferably passive valves, but can alternatively be active valves controlled by a controller based on system measurements made by sensors. The valves are preferably one-way valves but can alternatively be two-way valves or any other suitable valve. The valves are preferably each operable in an open mode and a closed mode, and preferably have a low threshold pressure where the valve switches from closed mode to open mode. The inlet valve located within the inlet is preferably configured to control fluid ingress into the primary pump 200 and prevent fluid egress out of the primary pump 200. The inlet valve is preferably in the open mode to allow fluid ingress when the lumen pressure is less than or equal to the pressure within the first reservoir 400. Alternatively, the inlet valve can be in open mode when the lumen pressure is negative. The inlet valve is preferably in closed mode when the lumen pressure is greater than or equal to the pressure within the first reservoir 400. The outlet valve located within the outlet is preferably configured to control fluid egress from the primary pump 200 and prevent the fluid ingress into primary pump 200. The outlet valve is preferably in the open mode to allow fluid egress when the lumen pressure exceeds the pressure within the second reservoir 500 and the threshold pressure of the outlet valve. The outlet valve is preferably in the closed mode when the lumen pressure is less than or equal to the pressure within the second reservoir 500.
[040] The power transformer 300 of the pump system 10 works to actuate the reciprocal element 220 along the compression stroke as the primary pump 200 rotates around the rotational axis and can additionally function to translate the reciprocal element 220 in the course of of the recovery course. Power transformer 300 preferably includes an axis having an arcuate position that is fixed relative to an arcuate position of the primary pump 200 (the angular position of the axis of the power transformer 300 around the rotational axis is preferably fixed at in relation to the angular position of the primary pump 200) . More preferably, the power transformer 300 or a portion thereof has a fixed angular position at and substantially similar to the angular position of the primary pump 200 about the rotational axis, so that the power transformer 300 travels with the primary pump. 200 around the rotational geometric axis.
[041] In a first variation of power transformer 300, power transformer 300 travels along arcuate bearing surface 122 of cam 120, power transformer 300 preferably maintains a substantially constant distance between arcuate bearing surface 122 and reciprocal element 220, such that power transformer 300 applies a variable force against reciprocal element 220 as power transformer 300 travels along the variable curvature of arcuate bearing surface 122 of cam 120. 300 is preferably substantially rigid and preferably has substantially fixed dimensions (e.g. diameter) that remain substantially constant throughout the movement of the power transformer relative to the cam 120. The power transformer 300 is preferably a roller or bearing, wherein the geometric axis that is fixed at the angular position of the primary pump is preferably the geometric axis rotation of the roller. Power transformer 300 is preferably in non-slip contact with arcuate bearing surface 122, but may alternatively slide along arcuate bearing surface 122. Power transformer 300 is preferably pivotally coupled to reciprocating element 220, but may alternatively be otherwise coupled to reciprocal element 220. When reciprocal element 220 is a piston, reciprocal element 220 preferably pivotally connects to the roller in the rotational geometric axis of the roller, but may connect to the roller with a semicircular cup enclosing the roller or through any other suitable coupling mechanism. When the reciprocal element 220 is a diaphragm, the reciprocal element 220 may directly contact the diaphragm, couple to the diaphragm via a piston, or couple to the diaphragm in any other suitable way.
[042] In another variation of the power transformer 300, the power transformer 300 is rotatably coupled to cam 120 in a fixed position on cam 120 and rotatably coupled to a fixed position on reciprocal element 220. The power transformer 300 is preferably pivotally coupled to reciprocal element 220 (e.g. on a piston), but may alternatively be slidably coupled to reciprocal element 220 or otherwise coupled to reciprocal element 220. In this variation, the power transformer 300 preferably translates the varying distance between the respective fixed ends into the varying force of occlusion. Power transformer 300 is preferably a two or more link link, but may alternatively be any suitable power transformer 300.
[043] However, the power transformer 300 may alternatively be any suitable mechanism that translates the cam rotation relative to the primary pump 200 into a variable occluding force against the reciprocal element 220.
[044] The pump system 10 is preferred and additionally includes a housing that functions to couple the components of the pump system to the rotating surface 20. The housing is preferably configured to statically and detachably couple to the rotating surface 20, however may otherwise couple to the rotating surface 20. Most preferably, the housing is configured to be mounted (eg, pin, bolt, etc.) to the hub of a tire, but may alternatively be mounted to the rim, axle or any other suitable component of a tire. The housing is preferably pivotally coupled to drive mechanism 100 and is preferably statically coupled to pump body 240 of primary pump 200 such that primary pump 200 rotates with the housing. The housing may additionally function to mechanically protect the components of the pump system, wherein the housing preferably substantially encompasses the components of the pump system. The housing is preferably substantially rigid, but it may alternatively be substantially flexible. The housing is preferably substantially fluid impermeable, but may alternatively be fluid permeable. In a variation of pump system 10, the housing functions as the first reservoir 400, where the primary pump 200 inlet is fluidly connected to and withdraws fluid from the interior housing. In this variation, the housing may include an inlet manifold that fluidly connects the interior housing to the environment. As shown in Figures 7A and 7B, the inlet manifold preferably includes a water selective membrane that preferably allows gas flow therethrough (for example, the gas flow rate through the water selective membrane is higher than the rate flow through the water selective membrane). The water selective membrane is preferably a GORETM membrane, but can alternatively be any other suitable membrane. The inlet manifold may alternatively include an inlet valve which controls fluid flow to the interior housing, but may alternatively not include any valve at all. The inlet valve is preferably a passive one-way valve operable between an open mode in response to inner housing pressure that falls below or equals ambient pressure and a closed mode in response to inner housing pressure that exceeds ambient pressure. . However, the inlet valve can be an active valve, a two-way valve, or any other suitable valve. 2. RELIEF VALVE
[045] The pump system 10 may additionally include a relief valve 700 that functions to bleed air from the interior of the second reservoir 500 (e.g. inner tire) to the pump system 10, more preferably to the pump system housing 10 (for example the first reservoir 400), but it may alternatively leak air from the second reservoir 500 to the environment. Leaking air through the 700 relief valve can provide several benefits. First, leaking air through relief valve 700 can prevent over pressurizing the second reservoir 500. Second, leaking air through relief valve 700 can allow the pump system 10 to directly measure the internal pressure of the second reservoir 500. Second, leaking air through relief valve 700 to the housing (first reservoir 400) effectively recycles already pumped air, reducing the amount of air treatment (eg desiccation) required. Relief valve 700 preferably connects to the second inner reservoir via the Schraeder valve of the second reservoir 500, but may otherwise fluidly connect to the second reservoir 500. Relief valve 700 preferably operates between an open mode in which flow of air through relief valve 700 is allowed and a closed mode in which air flow through the relief valve is impeded. The relief valve preferably includes an open threshold pressure and is preferably a closed failure relief valve. The cutoff threshold is preferably set to leak a second reservoir pressure at a rate substantially close to the pump flow rate (eg 0.164 liters (10 cubic inches)/minute), but may alternatively leak at a rate substantially close to the rate. of normal leakage from the second reservoir (eg 0.007 to 0.021 (1 to 3) per month), but may alternatively leak the second reservoir pressure at a higher or lower rate. Relief valve 700 is preferably a normally closed relief valve, but may alternatively be a normally open relief valve which is kept closed or any other suitable valve. Relief valve 700 is preferably passive but may alternatively be active. Relief valve 700 is preferably a check relief valve, but may alternatively be any other suitable relief valve 700. Examples of relief valves that can be used include a duckbill relief valve, a relief valve operated by pilot, a ball relief valve, a trigger relief valve and a diaphragm relief valve. Alternatively, any other suitable relief valve can be used.
[046] A measurement element functions to monitor an operating parameter and displays a measurement indicative of second internal reservoir pressure. The metering element is preferably located within the body of the pump system 10, but may be partially or completely external to the pump system 10. The metering element is preferably fluidly coupled to the relief valve 700 and preferably measures a parameter of the fluid flowing through relief valve 700. The measuring element is preferably passive, but in alternative embodiments the measuring element may be active.
[047] The measuring element preferably includes a sensor and a display. The sensor preferably measures the operating parameter and can be a pressure sensor, a flow rate sensor, a temperature sensor or any other suitable sensor. The sensor can be mechanical or digital (eg generating a voltage/current to be fed or leveraging a voltage/current for measurements). The display is preferably passive and can be a micrometer, ruler or any other suitable gauge. However, the display can be active (eg on, such as a digital display), where the displayed value can be calculated by a controller.
[048] In a first variation, the measuring element includes a measuring reservoir and a pressure gauge. The reservoir is fluidly coupled to relief valve 700 so that air leaks from the second inner reservoir into the metering reservoir when the valve opens. The metering vessel is preferably substantially small so that the metering vessel pressure balances with the second vessel pressure even at the low air leakage rate allowed by the relief valve. However, the measuring vessel can alternatively be of any suitable size. The measuring vessel is preferably a full space, but it can alternatively be a tube, channel or any other suitable vessel. The pressure gauge is preferably coupled to the reservoir and measures the pressure inside the reservoir. The measured pressure is preferably gauge pressure, but may alternatively be differential pressure (e.g., between the inside of the tank and the second outside/tank inflation system environment) or the absolute pressure. The pressure gauge display portion is preferably located on the outer surface of the pump system 10, more preferably parallel to the face of the wheel on which the pump system 10 is mounted.
[049] In a second variation, the measuring element includes a mass air flow meter coupled to a display. The flow meter preferably measures and fluidly couples to the inflator side of the relief valve (eg, downstream of the relief valve), but may alternatively measure flow to the relief valve (eg, side flow of the second reservoir 500) or flow through the relief valve body, wherein a portion of the flow meter is located within the relief valve. In this variation, the downstream side of the relief valve is preferably maintained at an approximately known pressure that is substantially higher than ambient but slightly less than the second expected reservoir pressure. For example, the relief valve can be coupled to a downstream reservoir that includes a relief valve with a threshold set pressure slightly less than the second expected reservoir pressure so that the downstream pressure is always approximately the set pressure borderline. In another exemplary embodiment, the relief valve may be coupled to the inflator of the second reservoir where the reservoir holds air to be pumped to the second reservoir 500. The flow meter preferably produces a voltage or current indicative of the rate of air flow , where voltage/current is fed into a controller, converted to a pressure measurement by the controller, and displayed as a pressure reading. Alternatively, the flow meter can be passive and measure the flow rate mechanically, where the position of a meter or indicator is converted to a pressure reading. The air flow meter can be a fin meter sensor, a hot wire sensor, a cold wire sensor, a Karman vortex sensor, a membrane sensor, a laminar flow element, a turbine flow meter , a rotating piston or any other suitable flowmeter. The display is preferably a digital display, but it can alternatively be an analog display.
[050] However, any other suitable relief valve may be included in the pump system 10 to facilitate second reservoir pressure regulation. 3. TORQUE STABILIZATION MECHANISM
[051] The pump system 10 may additionally include a torque stabilization mechanism 600 that compensates for the back force applied by the primary pump 200 to cam 120 at the beginning of the recovery stroke. Compensation of tail force may be desirable as the tail force can provide a radial force on cam 120 which, in turn, can be transmitted to cam 140, thereby disturbing the system. Torque stabilization mechanism 600 is preferably located on cam 120, but may alternatively be located on power transformer 300 (e.g., have an adjustable dimension that changes in response to applied force), primary pump 200, or any other suitable pump system component.
[052] In a variation of pump system 10, the cam profile functions as the 600 torque stabilization mechanism, in which the low curvature of the second segment accommodates for posterior force.
[053] In another variation of the pump system 10, the mass joint 142 functions as the torque stabilization mechanism 600, in which the mass joint 142 is operable in coupled mode during the compression stroke (through the third section 128 to the apex of the second section 126) and operable in decoupled mode during the recovery course. In one example, as shown in Figures 8A and 8B, the torque stabilization mechanism 600 includes a profiled channel 610 defined between the inner bearing surface of the cam and the mass joint 142 (e.g., where the mass joint 142 is a disk) by the inner support surface. Profiled channel 610 preferably includes a lower clearance section 612 that extends to an upper clearance section 614, where the gap is the distance between the mass surface joint and the inner bearing surface. The apex of the upper clearance section is preferably substantially radially aligned with the first section 124, more preferably with the apex of the first section 124, but may alternatively be aligned with the beginning of the second section 126, just before the apex of the first section 124, or aligned to any other suitable portion of cam 120. The beginning of the lower clearance section is preferably aligned radially within the arc defined by third section 128, but may alternatively be aligned to any suitable portion of cam 120. Torque Stabilization Mechanism 600 Preferably and additionally includes a movable element 620 located within the profiled channel 610 that couples and uncouples the mass joint 142 with the inner bearing surface. The movable element preferably couples the mass joint 142 with the inner bearing surface with friction, however it may alternatively be a ratchet mechanism or any other suitable mechanism. The movable element preferably has a dimension substantially equivalent to the distance between the mass surface joint and the inner bearing surface in the lower clearance section. The movable element is preferably stamped in the lower clearance section when the eccentric mass 140 is in coupled mode, wherein the movable element retains the position of the mass joint 142 with respect to the inner bearing surface. The movable element is preferably located in the upper clearance section when the eccentric mass 140 is in uncoupled mode, wherein the movable element is substantially free of the mass surface and/or interior bearing surface and allows for relative movement between the mass joint 142 and the inner support surface. The movable element is preferably a roller, but it can alternatively be a cylinder or any other suitable movable element. During operation, as the primary pump 200 reaches the apex of the first section 124 (compressed position 222), the reciprocal element 220 exerts a radial trailing force on the power transformer 300, pushing the cam 120 radially in the opposite direction from the primary pump 200. Additionally , as this point is reached, the angular velocity of cam 120 relative to primary pump 200 decreases. The radial movement, together with the slower angular cam speed, releases the movable element from the lower clearance section (where the movable element is still moving at the fastest angular velocity) and causes the movable element to move with the upper clearance section as primary pump 200 travels on second section 126 of arcuate surface as shown in Figure 8B. Angular cam speed preferably increases as primary pump 200 travels in second section 126, but can alternatively be substantially constant or decrease. At the end of the second section 126, the angular cam speed is preferably decreased due to the increased contact force between the cam 120, the power transformer 300 and the primary pump 200. This decreased angular speed preferably causes the movable element to wedge into the lower clearance section as shown in Figure 8A.
[054] In another variation, the torque stabilization mechanism 600 includes a slot 630 defined within the cam 120 and a pin 640 that extends from the mass joint 142 to the slot. The slot preferably functions to accommodate the radial trailing force by transforming the linear trailing force into a rapid rotation of cam 120 (relative to primary pump 200) through first section 124. The pin is preferably operable between a coupled position (shown in Figure 9A) and an uncoupled position (shown in Figure 9B) within the slot. The groove is preferably defined through the cam body in a radial direction normal to the broad cam face, but may alternatively be defined by any suitable portion of the cam body. The groove is preferably aligned with second section 126 of arcuate bearing surface 122, but may be defined in any other suitable portion of cam 120. The groove preferably traces an arc, but may alternatively be substantially linear, serpentine, or otherwise shaped adequate. During operation, the back pressure applied by the primary pump 200 to cam 120 forces the pin from the coupled position to the uncoupled position, effectively rotating the cam 120 with respect to the eccentric mass 140. When the primary pump 200 reaches the end of the second section 126, the force applied by cam 120 on primary pump 200 preferably transitions the pin back to the engaged position.
[055] However, any other suitable torque stabilization mechanism 600 that accommodates for radial force applied by the pressurized primary pump 200 to cam 120 can be utilized. 4. PASSIVE PRESSURE REGULATION MECHANISM
[056] The pump system 10 may additionally include a passive pressure regulating mechanism 800 that preferably functions to passively cease pressurizing the reservoir when a boundary reservoir pressure is reached. This is preferably achieved by passively ceasing primary pump pumping. The passive pressure regulating mechanism 800 preferably ceases pumping by ceasing application of force to reciprocal element 220, whereby the application of force can be ceased by disengaging the power transformer 300 from the cam 120, disengaging the primary pump 200 from cam 120 by decoupling power transformer 300 from primary pump 200 or eliminating relative movement between primary pump 200 and cam 120, an example of which is shown in Figures 15A and 15B. The passive pressure regulating mechanism 800 of the pump system 10 preferably includes a secondary pump 820 that includes a pump body 240 and a drive mechanism 840, and additionally includes a regulating valve 860 that has an opening and a threshold pressure of closure. Alternatively, passive pressure regulating mechanism 800 may include a regulating valve 860 and primary pump 200. Passive pressure regulating mechanism 800 is preferably fluidly connected to second reservoir 500, wherein regulating valve 860 controls selectively fluid flow to the secondary pump 820 based on the pressure of the second reservoir 500.
[057] The slave pump 820 is preferably a reciprocating pump substantially similar to that described above, wherein the drive mechanism 840 is the reciprocating element. Slave pump 820 is most preferably a piston pump, but may alternatively be a diaphragm pump. The slave pump 820 can alternatively be any other suitable positive displacement pump. The pressure regulating mechanism 800 is preferably operable in a pressurized mode and a depressurized mode. Pressurized mode is preferably achieved when the reservoir pressure exceeds the threshold pressure. More preferably, pressurized mode is achieved when the reservoir pressure exceeds the threshold opening pressure of valve 860. In pressurized mode, valve 860 is preferably in an open position and allows fluid flow from the reservoir to the pump body 240, wherein the ingress fluid pressure places the drive mechanism 840 in the pressurized position. In the pressurized position, drive mechanism 840 preferably actuates or couples against drive mechanism 100, power transformer 300, or primary pump 200 to cease application of pumping force to primary pump 200. In depressurized mode, valve 860 is preferably in a closed position and prevents fluid flow from the reservoir to the pump body 240, where a feedback mechanism places the drive mechanism 840 in a depressurized position, where the depressurized position is preferably the reclaimed position 224 but may alternatively be compressed position 222 or any other suitable position therebetween. Pump system 10 preferably includes at least one pressure regulating mechanism 800, but may alternatively include any suitable number of pressure regulating mechanisms.
[058] The position of the pressure regulating mechanism 800, more preferably the position of the pump body 240, is preferably statically coupled to the primary pump position, but can alternatively be movably connected to the primary pump 200 position. of the pressure regulating mechanism 800 is preferably maintained relative to the primary pump position, but the radial or linear distance may alternatively be maintained. The drive axis of the pressure regulating mechanism 800 is preferably in the same plane as the drive axis of the primary pump 200, but may alternatively be in different planes, perpendicular to the drive axis of the primary pump 200 or arranged in any another suitable way. The pressure regulating mechanism 800 is preferably arranged with respect to the primary pump 200 so that the radial direction of the compression stroke of the pressure regulating mechanism 800 differs from the radial direction of the compression stroke of the primary pump 200. compression stroke of the pressure regulating mechanism 800 directly opposes the radial direction of the compression stroke of the primary pump 200 (for example, the closed end of the pump cavity is distal to the closed end of the pump body 240, and the drive element is proximal to reciprocating element 220, where the drive shafts are aligned or parallel), but may alternatively be at an angle to the radial direction of the compression stroke of the primary pump 200. Alternatively, the pressure regulating mechanism 800 may be arranged so that the compression stroke of the pressure regulating mechanism 800 and the compression stroke of the pressure regulating mechanism 800 have substantially the same radial direction (eg drive shafts are aligned or parallel).
[059] In a variation of the pressure regulating mechanism 800, the drive mechanism 840 decouples the primary pump 200 or a primary pump component from the drive mechanism 100 when in the pressurized position and allows the primary pump 200 to couple to the mechanism. drive 100 when in the depressurized position (as shown in Figures 12A and 12B). Drive mechanism 840 preferably decouples power transformer 300 from drive mechanism 100, but alternatively decouples reciprocating element 220 or the entire primary pump 200 from drive mechanism 100. Drive mechanism 840 preferably moves primary pump component along the geometric axis of drive of the primary pump 200 in the opposite direction of cam 120, when it transitions from the depressurized position to the pressurized position. However, drive mechanism 840 may move moves the primary pump component at an angle to the geometric axis of primary pump drive 200 in the opposite direction from cam 120 (eg, in a perpendicular radial direction). Drive mechanism 840 preferably translates the primary pump component in the plane encompassing the drive axis or pump body 240, but may alternatively translate the primary pump component out of said plane. The force exerted on the drive mechanism 840 by the return element 260 of the secondary pump 820 preferably couples the primary pump component with the drive mechanism 100 while returning the drive mechanism 840 to the depressurized position, but the pump system 10 may alternatively include a second return element 260 that couples the primary pump component with the drive mechanism 100 (e.g., a spring biased so that the spring opposes the radial direction that the drive mechanism 840 moves the primary pump component, etc.); ) . The second return element 260 preferably returns contact of the primary pump component with the drive mechanism 100 when the decoupling force of the drive mechanism falls below the return force provided by the second return element.
[060] A portion of the drive mechanism 840 is preferably statically coupled to a portion of the primary pump 200, wherein the drive of the drive mechanism results in a positional shift of the primary pump 200 or a primary pump component. More preferably, actuating drive mechanism preferably selectively couples and decouples primary pump 200 from drive mechanism 100 when drive mechanism 840 is in the depressurized and pressurized positions, respectively. Drive mechanism 840 is statically coupled to power transformer 300, but may alternatively be statically coupled to reciprocating element 220, statically coupled to primary pump 200 as a whole, or statically coupled to any other suitable primary pump component. Drive mechanism 840 is preferably statically coupled to the primary pump component by a frame 880, but may alternatively be coupled by the housing that encapsulates the pump system 10 or by any other suitable coupling mechanism. The frame 880 may be aligned in the plane enclosing the geometric axis of driving the primary pump 200, in the plane enclosing the geometric axis of the drive of the pressure regulating mechanism 800, to extend outside either of said two planes or to be otherwise oriented with respect to the pump system 10. In a specific example, the power transformer 300 is a roller, wherein the drive mechanism 840 is coupled to the rotational axis of the roller by a frame 880 aligned with a plane that encompasses both the drive axis of the pressure regulation mechanism 800 and the drive axis of the primary pump 200, wherein the pressure regulation mechanism 800 and the primary pump 200 preferably share a common plane. Alternatively, drive mechanism 840 transiently couples to the primary pump component when in the pressurized position and is retracted from the primary pump component when in the depressurized position.
[061] In another variation of the pressure regulation mechanism 800, the drive mechanism 840 decouples the power transformer 300 from the primary pump 200 in the pressurized position and allows the coupling of the power transformer 300 with the primary pump 200 when in the depressurized position . The drive mechanism 840 preferably connects and moves the position of the linear power transformer relative to the drive mechanism 100 when in the pressurized position, but may alternatively connect and move the position of the linear primary pump with respect to the power transformer 300 and the drive mechanism 100. Drive mechanism 840 preferably moves power transformer 300 out of the common plane shared by primary pump 200 and drive mechanism 100, but may alternatively move power transformer 300 out of line with the shaft drive geometry (eg perpendicular, in the common plane). Drive mechanism 840 may be statically coupled to power transformer 300 or primary pump 200 by a frame 880, a solder, adhesive, or any other suitable coupling mechanism. Alternatively, drive mechanism 840 may be transiently coupled to power transformer 300 or primary pump 200, where drive mechanism 840 may be a piston or rod that transiently couples to power transformer 300 or pump primary 200 through a coupling feature (eg a groove) or friction.
[062] In another variation of pressure regulating mechanism 800, drive mechanism 840 ceases power generation. In an alternative, the pressure regulating mechanism 800 statically couples the angular position of the drive mechanism 100 to the primary pump 200, ceasing the generation of force by eliminating the relative movement between the drive mechanism 100 and the primary pump 200 (as per shown in Figures 13A and 13B). For example, drive mechanism 840 can statically couple the angular position of cam 120 with the angular position of primary pump 200 in the pressurized position and decouple the angular position of cam 120 from the angular position of primary pump 200 in the depressurized position. In a specific example, the 840 drive mechanism is a rod that engages the wide cam face by friction. In another specific example, drive mechanism 840 is a rod that extends in a groove in the cam wide face (e.g., the wide face proximal to the housing or distal to the housing) when in the pressurized position and is retracted from the groove when in the depressurized position. In another specific example, the drive mechanism 840 statically couples to the arcuate bearing surface 122 of the cam 120. However, other mechanisms transient the cam angular position may be used. In another example, drive mechanism 840 may statically couple the angular position of eccentric mass 140 with the angular position of primary pump 200. In a specific example, drive mechanism 840 may include a rod that couples to the broad face of the mass. eccentric 140 or to the union of mass 142 by friction. In another specific example, drive mechanism 840 is a rod that extends into a groove in the eccentric mass face when in the pressurized position and is retracted from the groove when in the depressurized position. However, other mechanisms of transient retention of the angular position of eccentric mass can be devised. In another example, the pump body 240 of the primary pump 200 can be statically coupled to the drive mechanism 100 so that relative movement between the reciprocal element 220 and the pump body 240 is ceased (e.g., when a linear actuator or swivel is used). In another alternative, pressure regulating mechanism 800 decouples the power generator from the drive interface of drive mechanism 100. For example, when cam 120 and eccentric mass 140 are transiently coupled by a transient coupling mechanism , the drive mechanism 840 can actuate the cam 120, the eccentric mass 140 or the coupling mechanism to decouple the cam 120 from the eccentric mass 140. In a specific example as shown in Figures 14A and 14B, the cam 120 is coupled to the mass. eccentric 140 along respective broad faces by a ring of magnets 842 surrounding the rotational axis and drive mechanism 840 extends through a hole in cam 120 (or eccentric mass 140) and pushes against the broad face of the eccentric mass 140 (or cam 120) to decouple eccentric mass 140 from cam 120. Drive mechanism 840 can be statically coupled to power transformer 300 or primary pump 200 by an 880 frame or other coupling mechanism. Alternatively, drive mechanism 840 may be transiently coupled to power transformer 300 or primary pump 200, where drive mechanism 840 may be a piston or rod that couples to power transformer 300 or primary pump 200 .
[063] In another variation of the pressure regulating mechanism, the pressure regulating mechanism 800 switches the primary pump 200 from pumping mode and a latched mode. Primary pump 200 preferably pumps fluid in pump mode and does not pump fluid in latched mode. More preferably, components of the pump system 10 are held in static relationship to each other in the locked mode, so that the reciprocal element 220 is held substantially static. Primary pump 200 is preferably placed in latched mode when the pressure of second reservoir 500 exceeds the threshold opening pressure of valve 860 and is preferably placed in pumping mode when pressure of second reservoir 500 falls below threshold threshold pressure of valve 860. More specifically, when the pressure of the second reservoir 500 exceeds the threshold opening pressure, the valve 860 opens, allowing pressurized air to flow from the second reservoir 500 to the compression volume of the primary pump 200, substantially retaining the reciprocal member 220 in the starting position of the compression stroke (eg in the retrieved position). In this way, the increased force of pressurized air in the reciprocal element 220 substantially opposes the cam movement when the reciprocal element 220 is located in the second section 126 of the cam profile, but may alternatively or additionally oppose the cam movement when the reciprocal element 220 is located in the first section 124 or third section 128 of the cam profile. Since cam 120 is preferably configured to apply only a small force on reciprocal element 220 in second section 126, cam 120 cannot overcome the large back force applied by backflow on reciprocal element 220. These aspects of pump system 10 effectively cease the pumping inside the primary pump 200. The force applied by the counterflow prevents cam movement relative to the primary pump 200, causing the cam 120, and subsequently the eccentric mass 140, to rotate with the pump system 10. When the system of pump 10 includes multiple pumps, all pumps are preferably flooded with pressurized air. Alternatively, a single pump may be flooded with pressurized air, alternate pumps may be flooded with pressurized air, or any other suitable subset of the pumps may be flooded to cease pumping.
[064] However, any other suitable means of ceasing the application of pumping force to reciprocating element 220 may be used.
[065] Valve 860 of pressure regulating mechanism 800 functions to selectively allow fluid flow to pump body 240 of slave pump 820. Valve 860 preferably has a threshold opening pressure substantially equal to the desired reservoir pressure ( for example, the upper limit of a desired reservoir pressure range) and may additionally have a threshold closing pressure below, above or equal to the desired reservoir pressure (eg, the lower limit of a desired reservoir pressure range) . Valve 860 can additionally function as a timer and have a pump resume pressure where primary pump pumping is resumed. The pumping resumption pressure is preferably determined by the ratio of the first and second pressurizing areas within the valve. Alternatively, the pressure regulating mechanism 800 may include a timer that functions to delay the resumption of pumping after the threshold closing pressure is reached. Valve 860 is preferably located in the fluid manifold that fluidly connects second reservoir 500 with pump body 240. However, valve 860 may be located within second reservoir 500 or within inlet pump body. The threshold opening pressure is preferably a higher pressure than the threshold closing pressure, whereby the threshold opening and closing pressures are preferably determined by the return force applied by the return element. The state of the valve is preferably determined by the pressure within the second reservoir 500. The pumping resume pressure is preferably less than the threshold closing pressure, but may alternatively be greater than the threshold closing pressure or be any suitable pressure. Valve 860 is preferably operable between an open mode when the pressure of the second reservoir 500 exceeds a threshold opening pressure, wherein the valve 860 allows fluid flow from the second reservoir 500 to the pump body 240, and a closed mode when the pressure of second reservoir 500 is below the threshold closing pressure, wherein valve 860 prevents fluid flow from second reservoir 500 to pump body 240. Pumping by primary pump 200 is preferably resumed when pressure within second pump 820 is below the pumping resumption pressure, but can alternatively be resumed when the reservoir pressure is below the closing threshold. Valve 860 is preferably a trigger valve, but may alternatively be any other suitable valve 860. Valve 860 is preferably passive, but may alternatively be active. Valve 860 preferably includes a valve member 864 that seats within a valve body 862 and may additionally include a feedback mechanism (e.g., a spring) that biases valve member 864 against valve body 862. valve member 864 and valve body 862 can be different materials (e.g., to compensate for material expansion due to temperature changes) or can be made of the same material or materials with similar coefficients of expansion.
[066] In a variation of the pressure regulating mechanism 800, the trigger valve 860 is substantially similar to the valve described in Application No. 13/469,007, filed May 10, 2012.
[067] In another variation of the pressure regulating mechanism 800, as shown in Figure 16, the trigger valve 860 includes a valve body 862, a valve member 864, a spring 865, a first volume 866, a second volume 867, a reservoir channel 868, and a collector channel 869. The spring or return member 865 biases the valve body 862 against the valve member 864. The spring constant of the spring is preferably selected based on reservoir pressure desired (threshold pressure or crack pressure) and the valve operating characteristics. The first volume is preferably defined between valve body 862 and valve member 864 and preferably has a first area of normal pressurization for a radial direction of application of spring force. The second volume is preferably also defined between valve body 862 and valve member 864 and preferably has a second pressurization area normal to the radial direction of application of spring force. The second reservoir channel preferably fluidly connects the first volume to the second reservoir 500. The collection channel is preferably defined through valve body 862 and is preferably fluidly connected to pressure regulating mechanism 800. The collection channel is preferably defined along the geometric axis of application of return force, which opposes return member 260 opposite valve member 864, but may alternatively be defined in any other suitable location. Valve 860 may additionally include a timing channel that fluidly couples the second volume to an environment, wherein the timing channel has a cross section based on a desired leak rate. The ratio of the first pressurizing area to the second pressurizing area is preferably selected based on the desired amount of time that valve 860 takes to recover the closed position, but alternatively may be any suitable reason. The combined volumes of the first and second volumes are preferentially and substantially insignificant relative to the volume of the second reservoir. Valve 860 is preferably operable between an open position and a closed position. In the open position, valve body 862 and valve member 864 cooperatively define a connecting channel that fluidly connects the first volume to the second volume, wherein the valve member 864 is located distal to the valve body 862. open position is preferably achieved when a pressure force generated by a pressure within the first volume exceeds the spring force applied by the spring to the valve body 862. In closed mode, the valve member 864 and the valve body 862 cooperatively seal the connecting channel and valve member 864 substantially seals the manifold channel, wherein valve member 864 rests against valve body 862. The closed mode is preferably achieved when the pressure force is less than the applied spring force. In an alternative to valve 860, valve member 864 has a symmetrical cross-section that includes a rod configured to fit within the manifold channel, a first projection extending from the rod, and a second projection extending from the first projection. Valve body 862 includes a cross-section complementary to the cross-section of the valve member, including a first step that defines the manifold channel, a second step that extends from the first step, and walls that extend from the second step. The first volume is preferably defined between the second unevenness and the second projection, the second volume is preferably defined between the first unevenness and the first projection the connecting channel is preferably defined between a transition from the first projection to the second projection and a transition between the first gap to the second gap. Valve 860 may additionally include gaskets that cooperatively edge and defend the first and second volumes. In an alternative to valve 860, valve 860 includes a first gasket located within the connecting channel that forms a first substantially fluid impermeable seal with valve member 864 in closed mode and a second fluid impermeable seal defined between the second projection and the walls. Valve 860 may additionally include a gasket within the manifold channel that forms a fluid-tight seal with the rod when valve 860 is in closed mode (e.g., to cooperatively define the second volume) and allows fluid flow therethrough when valve 860 is in open mode. 5. STABILIZATION MECHANISM
[068] The pump system 10 may additionally include a stabilization mechanism 900 that functions to reduce surface rotational imbalance when the eccentric mass 140 becomes excited (e.g., begins to rotate) when the pump system 10 rotates in or close to the excitation frequency of the eccentric mass 140. The stabilization mechanism 900 is preferably the eccentric mass 140, wherein the eccentric mass 140 is collectively formed from multiple sections. However, the stabilization mechanism 900 may alternatively be any other suitable stabilization mechanism 900. When the cam mass 140 begins to rotate, the composite sections of the cam mass separate. This is particularly useful when system oscillations cause the eccentric mass 140 (and the positioning mechanism) to rotate around the axis; the centrifugal forces cause the sections of the split eccentric mass 140 to separate and be evenly distributed around the geometric axis of system rotation, as shown in Figures 10A and 10B. Not only does this have the effect of dynamically balancing the system and/or the rotating surface 20, the uniform distribution of eccentric mass 140 within the system also stops system pumping. The latter effect can allow the eccentric mass 140 to additionally function as a control mechanism, whereby the resonant frequency of the eccentric mass can be tailored so that pumping is stopped when a predetermined rotational speed or vibration frequency is reached. The multiple sections are preferably each positioned at the same radial distance from the rotational geometric axis (the eccentric mass 140 is radially divided into multiple sections, where the multiple sections have different angular positions), but may alternatively be positioned at different distances radials (eg where multiple sections have substantially similar angular positions, etc.). The multiple sections preferably share a common plane, where the common plane is preferably substantially parallel to the rotational surface. The multiple sections can collectively form an arc, centered around the rotational geometric axis, which intersects with the common plane (for example, multiple sections are adjacent along an arc), form a block that intersects with the common plane, or form collectively any other suitable structure. Alternatively, multiple sections can be stacked along the section thicknesses, where the section thicknesses are preferably parallel to the rotational axis. The multiple sections preferably have substantially the same mass, but may alternatively have different masses. The center of mass for each eccentric mass section is preferably offset from the mass bonding connection point for each eccentric mass section and is preferably disposed proximal to an adjacent eccentric mass section. During operation, the eccentric mass sections separate until the centers of mass of the eccentric mass sections oppose each other in front of the geometric axis of rotation.
[069] When the eccentric mass 140 is cooperatively formed by multiple sections, the mass bond 142 preferably also includes multiple sections, wherein each mass bond section statically couples to an eccentric mass section. The mass joining sections are preferably rotatably coupled to the cam 120, but may alternatively be statically coupled to the cam 120. Each mass joining section is preferably rotatably coupled to the remaining mass joining sections, but may alternatively be statically coupled to one or more of the remaining mass joint sections. In a variation as shown in Figures 11A and 11B, the end of each mass joining section that opposes the eccentric mass section is pivotally coupled to the housing. The end mass bonding section angular positions are preferably static with respect to the housing, wherein the end mass bonding section ends are preferably evenly distributed around the geometric axis of rotation. In another variation, the end of each mass joining section that opposes the eccentric mass section includes a bearing, wherein the bearing is slidably engaged within a circumferential groove statically coupled to cam 120 and surrounding the axis. rotational. When the rotation frequency of the rotating surface 20 is below or above the excitation frequency for the cooperatively defined eccentric mass 140, the centrifugal force of the rotation preferentially retains the eccentric mass sections (and mass joining sections) in substantially positions adjacent. When the rotation frequency of the rotating surface 20 is at the excitation frequency, the centrifugal force preferably causes the bearings to slide into the groove, distributing the multiple eccentric mass sections substantially equally around the rotational axis. The bearings and/or eccentric mass sections may each additionally include magnets, disposed in repulsive relationship to adjacent magnets, which facilitate the separation of eccentric mass in response to receiving a system oscillation. In another variation, the mass joint sections pivotally engage along the longitudinal axis of an axis extending from cam 120 (e.g., mass joint sections are stacked along the axis). In another variation, one mass connecting section is statically connected to cam 120 while the remaining mass connecting sections are pivotally connected to cam 120. However, the mass connecting sections can be otherwise connected to the cam 120.
[070] When mass coupling 142 couples to cam 120 on the rotational axis, mass coupling 142 is preferably operable between coupled mode, in which mass coupling 142 connects eccentric mass 140 to cam 120, and uncoupled mode, in which the mass coupling 142 disconnects the eccentric mass 140 from the cam 120. In a variation, the mass coupling 142 is a disc located within the lumen defined by an interior bearing surface of the cam 120, in which the disc it can rotate with respect to the inner bearing surface in uncoupled mode and is coupled to the inner bearing surface by a friction element in coupled mode. The mass union sections are preferably pivotally coupled to the disc, but may alternatively be disc sections (eg concentric circles, arcuate parts, etc.). The friction element can be a high friction liner along the inner bearing surface, a high friction liner along the outside of putty joint 142, a roller or wedge, or any other suitable element with the ability to provide friction between the inner bearing surface and the mass joint 142. The friction element is preferably selected so that the cooperative centrifugal force of the eccentric mass 140 in coupled mode applies sufficient force to the mass joint 142 so that the friction between the joint of mass 142 and the inner bearing surface retains the position of the mass joint with respect to the cam 120. The friction element is preferably selected so that the cooperative centrifugal force of the eccentric mass sections in a separate or uncoupled mode does not provide force sufficient at the interface friction to retain the position of the mass joint relative to the cam 120, thereby allowing free rotation of the mass joint. In another variation, mass coupling 142 is rotatably mounted on a shaft extending from cam 120 by bearings, wherein mass coupling 142 can be statically coupled to cam 120 by one or more sets of magnets or pistons that extend from the adjacent broad faces of cam 120 and mass bond 142. However, the static mass bond connection to cam 120 to achieve coupled mode may be selectively controlled by any other suitable passive or active means.
[071] The eccentric mass 140 may additionally include a connecting mechanism that functions to couple the multiple sections together. The connection mechanism is preferably located at the interfaces of adjacent sections, but may alternatively be located within the section bodies, at the interfaces of adjacent mass joining sections, or at any other suitable location. The coupling force of the connection mechanism is preferably selected so that it is substantially equal to or less than the angular separation force experienced by the individual eccentric mass sections when the system is rotating at the excitation frequency. However, the coupling force can be any other suitable magnitude. The connection mechanism can be a mechanical connection (eg adhesive, tweezers, Velcro, etc.) with a separating force substantially equivalent to the coupling force, a magnetic connection in which adjacent eccentric mass sections or mass joints include complementary magnets or any other suitable mechanism that can selectively connect adjacent eccentric mass sections together.
[072] In an alternative, the eccentric mass 140 is collectively formed of a first and a second section (eg, the eccentric mass 140 is divided radially into two sections), wherein the first section is a reflected doubling of the second section. During operation, the first and second sections are preferably diametrically opposed and rotate around the geometric axis of rotation of the positioning mechanism when the vibration of the system reaches the resonant frequency of the eccentric mass 140. In a second alternative, the eccentric mass 140 is collectively formed by a first, a second and a third section of substantially the same mass, wherein the first, second and third sections are preferably substantially uniformly distributed around the rotational geometric axis when the rotational velocity of the system reaches the resonant frequency of eccentric mass 140. However, eccentric mass 140 can be formed from any number of constituent sections in any suitable configuration. Alternatively, stabilization mechanism 900 may be any other suitable mechanism.
[073] The pump system 10 may additionally include a damping mechanism that functions to minimize eccentric mass 140 oscillations within the system. Oscillations of eccentric mass 140 can result in eccentric mass excitation, in which eccentric mass 140 rotates within the system rather than remaining substantially static with respect to a gravity vector. Oscillations can arise from irregularities in the bearing surface (eg the road), dynamic imbalance (eg due to wheel mass distribution.), the pump pulse (eg when the pump pulse occurs at a frequency which excites the mass) or can arise from any suitable mechanism that can generate eccentric mass oscillations 140.
[074] In a first variation, the damping mechanism includes Dynabeads or other dynamic balance mechanisms located within an inner channel that surrounds the rotational axis. In a second variation, the damping mechanism is a torsional mass spring system, wherein the period of resonant vibration of the mass spring system is preferably equaled to the gravitationally induced resonant frequency of the eccentric mass oscillation 140. torsion spring is preferably coupled to cam 120 so that eccentric mass oscillations 140 cause an inertial transfer, which excites the resonant tension mass spring system in a phase shift that is 180 degrees out of phase with the oscillations of the eccentric mass 140. The torsion spring is preferably coupled between the torsion mass and cam 120, but may alternatively be positioned between cam 120 and mass coupling 142, or in any suitable position. 6. EXEMPLARY PUMP SYSTEM
[075] In an embodiment of the pump system 10, as shown in Figures 12A and 12B, the pump system 10 includes a first and a second reciprocating pump (200a and 200b, respectively), a drive mechanism 100, a first and a second power transformer (300a and 300b, respectively) connected to the first and second reciprocating pumps, respectively, wherein the first and second power transformers have a first and second axis in fixed relationship, respectively, in which a fluid manifold 202 fluidly connects the second reciprocating pump to a reservoir 500 and a valve 860 located within the fluid manifold 202. The first pump 200a preferably includes an outlet fluidly connected to the second reservoir 500, wherein the first pump 200a pumps fluid to and pressurizes second reservoir 500. First pump 200a preferably includes an inlet fluidly connected to a source of fluid, wherein the source of fluid may be the environment, the housing (eg, where the housing holds desiccated air) or any other suitable fluid source. The second pump 200b may additionally include an inlet (separate from that coupled to the fluid manifold 202 but alternatively the same) and an outlet fluidly connected to the fluid source and the reservoir, respectively, wherein the second pump 200b can pump fluid to and pressurizing the second reservoir 500. Alternatively, the inlet and outlet of the second pump 200b may be fluidly connected to the fluid source and the inlet of the first pump 200, respectively, thereby forming a two-stage pump. In that alternative, fluid is pressurized to a first pressure within the second pump 200b and pressurized to a second pressure within the first pump 200a. The first and second reciprocating pumps preferably include a first and second pump body (240a and 240b), respectively, and a first and second reciprocating element (220a and 220b), respectively. The first and second reciprocating pumps preferably share a common plane (eg the respective drive shafts share a common plane), but they can alternatively be located on different planes. The first and second reciprocating pumps are preferably evenly distributed radially around the drive mechanism 100, more preferably evenly distributed around the rotational axis of the drive mechanism 100. However, the pumps can be distributed in another way. The positions of the bodies of the first and second pump are preferably statically fixed by a housing or other component, wherein the housing statically couples the pump system 10 to a rotating surface 20 and may further encompass the pump system 10. The first and second reciprocating pumps preferably oppose each other, wherein the closed end of the first pump body 240a is distal to the closed end of the second pump body 240b and the first reciprocal element 220a is proximal to the second reciprocal element 220b. The first reciprocal element 220a preferably has a first pressurizing area (area that receives or generates a pressing force) and the second reciprocating element 220b preferably has a second pressurizing area. The first pressurization area is preferably smaller than the second pressurization area, but can alternatively be smaller or larger. Drive mechanism 100 preferably includes a rotational axis 102, a cam 120 rotatable about the rotational axis, wherein the cam 120 has a bearing surface 122 and an eccentric mass 140 coupled to the cam 120 that displaces the center of mass. of the drive mechanism 100 of the rotational geometry axis. The first power transformer 300a is preferably coupleable to the bearing surface 122 of the cam 120 in non-slip contact and is preferably statically connected to the reciprocal element 220 of the first pump along a geometric axis (e.g., rotational axis). Second power transformer 300b preferably slides relative to bearing surface 122 of cam 120, but may alternatively mate in non-slip contact with bearing surface 122. Second power transformer 300b is preferably statically connected to reciprocating member 220 of second pump along a geometry axis (eg rotational geometry axis). The first and second force transformers can each be a roller, a piston, a piston coupled to the roller on the rotational axis, or any other suitable force transformer. The positions of the first and second power transformers are preferably held statically by a frame 880, but may alternatively be held by any other suitable mechanism. Frame 880 preferably encompasses drive mechanism 100 such that drive mechanism 100 is located within the area bounded by frame 880. Frame 880, however, may be otherwise arranged relative to drive mechanism 100. frame 880 is preferably located in the common plane shared by the first and second bombs, but may alternatively be located in a separate plane (for example, it may extend normally to said plane and extend along a second plane parallel to the first). During operation, a radial or linear position of frame 880 preferably shifts from a first position to a second position with respect to a point on drive mechanism 100 (e.g., rotational axis) when second reciprocating element 220 moves from the depressurized position to the pressurized position, respectively. The distance between the first position and the second position is preferably substantially similar to the distance between the depressurized position and the pressurized position, but may alternatively be greater (eg where frame 880 amplifies the change in position of the reciprocal element) or smaller. The movement of the frame 880 preferably results in the simultaneous movement of the first and second power transformer, coupling the first power transformer 300a to the drive mechanism 100 in the first position and decoupling the first power transformer 300a from the drive mechanism 100 in the second position. of the frame. Alternatively, frame movement may result in movement of the first and second pump reciprocally relative to drive mechanism 100, wherein frame 880 statically connects the positions of the first and second pump bodies. However, the power transformers can be otherwise connected and disconnected to the drive mechanism 100. The frame 880 may additionally include features, such as arcuate grooves in the surface of the frame 880 proximal to the drive mechanism 100, that facilitate the sliding of the second power transformer 300b with respect to bearing surface 122. The fluid manifold preferably fluidly connects second reservoir 500 to an inlet of the second pump, but may additionally fluidly connect second reservoir 500 to an inlet of the first pump. In the latter alternative, the valve is preferably located upstream of the junction between the three fluid connections or within the junction. In this last alternative, the opening valve simultaneously floods the lumens of both the first and second reciprocating pumps. Because the second reciprocating pump preferably has a larger pressurization area than the first reciprocating pump, the second reciprocating pump preferably exerts a linear (e.g., radial) decoupling force on the frame 880, which is transferred by the frame 880 at a first displacement of the first power transformer 300a along the drive mechanism 100, effectively decoupling the first power transformer 300a from the drive mechanism 100.
[076] As a person skilled in the art will recognize from the foregoing detailed description and from the figures and claims, modifications and changes can be made in the preferred embodiments of the invention without departing from the scope of this invention defined in the following claims.

权利要求:
Claims (25)
[0001]
1. TIRE INFLATION SYSTEM, characterized in that it comprises: ■ a drive mechanism that has a rotational geometric axis, the drive mechanism comprising: a) a cam comprising an arcuate support surface that has a non-uniform curvature, where the cam is rotatable around the rotational axis; and b) a cam-coupled eccentric mass joint that is offset from the center of mass of the rotational axis drive mechanism; ■ a first pump cavity positioned at a radial distance from the rotational axis and pivotally coupled to the cam, wherein the first pump cavity comprises a first drive element and a chamber; ■ a first power transformer which couples the arcuate bearing surface to the first drive element, the first power transformer comprising a first geometric axis having an arcuate position fixed to an arcuate position of the first pump cavity; and ■ a passive pressure regulation system comprising a passive valve fluidly connected to a reservoir, wherein the reservoir is connected to an outlet of the first pump cavity, the passive valve has a threshold opening pressure and a threshold pressure. closing less than the threshold set pressure, the passive valve operable between:■ an open mode in response to a reservoir pressure that exceeds the threshold set pressure, the passive valve allowing fluid flow from the reservoir; e■ a closed mode in response to a reservoir pressure that is below the threshold closing pressure, where the passive valve prevents fluid flow from the reservoir.
[0002]
2. TIRE INFLATION SYSTEM according to claim 1, characterized in that the first power transformer comprises a geometric axis of rotation, wherein an arcuate position of the geometric axis of rotation of the first power transformer is fixed with respect to the first cavity of bomb.
[0003]
3. TIRE INFLATION SYSTEM, according to claim 2, characterized in that the first power transformer comprises a roller in non-sliding contact with the arcuate support surface of the cam.
[0004]
4. TIRE INFLATION SYSTEM according to claim 3, characterized in that the first power transformer additionally comprises a piston rotatably connected to the geometric axis of rotation of the first power transformer, wherein the first drive element comprises the piston .
[0005]
5. TIRE INFLATION SYSTEM, according to claim 4, characterized in that the first drive element comprises a diaphragm.
[0006]
6. TIRE INFLATION SYSTEM, according to claim 5, characterized in that the diaphragm comprises a rolling diaphragm.
[0007]
7. TIRE INFLATION SYSTEM according to claim 1, characterized in that the arcuate support surface has a first section that has a high curvature and adjacent to a second section that has a low curvature.
[0008]
8. TIRE INFLATION SYSTEM according to claim 7, characterized in that the arcuate support surface further comprises a third section between the first and second sections, wherein the third section has a curvature ranging from a low curvature proximal to the second section to a low curvature proximal to the first section.
[0009]
9. TIRE INFLATION SYSTEM, according to claim 8, characterized in that the arcuate support surface comprises an outer perimeter of the cam.
[0010]
10. TIRE INFLATION SYSTEM according to claim 7, characterized in that it further comprises a torque stabilization mechanism configured to accommodate a force of the first drive element on the cam during a return stroke.
[0011]
11. TIRE INFLATION SYSTEM according to claim 10, characterized in that the drive mechanism further comprises a mass joint operable in: ■ a coupled mode in which the mass joint connects the eccentric mass to the cam; e■ an uncoupled mode where the mass joint disconnects the cam eccentric mass.
[0012]
12. TIRE INFLATION SYSTEM according to claim 11, characterized in that the mass joint couples to an inner support surface of the cam, wherein: ■ in coupled mode, the mass joint is statically coupled to a support surface inside the cam, and ■ in decoupled mode, the mass joint is pivotally coupled to the inner bearing surface.
[0013]
13. TIRE INFLATION SYSTEM according to claim 12, characterized in that the torque stabilization mechanism comprises a profiled channel defined between the inner support surface and the mass joint, wherein the profiled channel has a lower clearance section and an upper clearance section, wherein the torque stabilization mechanism further comprises a movable element having a dimension equal to the lower clearance section and smaller than the upper clearance section, the movable element located in the profiled channel, wherein the torque stabilization mechanism switches the mass joint between:■ coupled mode, where the movable element is located in the lower clearance section and retains a position of the mass joint with the inner bearing surface; e■ the uncoupled mode, in which the movable element is located in the upper clearance section and allows for relative movement between the putty joint and the inner support surface.
[0014]
14. TIRE INFLATION SYSTEM, according to claim 13, characterized in that the upper clearance section is aligned radially to the first section of the arcuate support surface.
[0015]
A TIRE INFLATION SYSTEM according to claim 1, characterized in that it further comprises a second pump cavity comprising a second drive element and a second chamber; and a second power transformer which couples the arcuate bearing surface to the second drive element, the second power transformer comprising a second axis having a second arcuate position fixed to an arcuate position of the second pump cavity.
[0016]
16. TIRE INFLATION SYSTEM according to claim 15, characterized in that the passive pressure regulation system further comprises a fluid collector, the fluid collector fluidly connecting the first pump cavity, the second pump cavity and a reservoir, the reservoir fluidly coupled to the first and second pump cavities, wherein the passive valve is located in the fluid manifold, wherein: ■ in open mode, the passive valve allows fluid flow from the reservoir to the first and to the second pump cavities; and■ in closed mode, the passive valve prevents fluid flow from the reservoir to the first and second pump cavities.
[0017]
17. TIRE INFLATION SYSTEM, according to claim 16, characterized in that the second drive element comprises a drive area larger than the first drive element.
[0018]
18. TIRE INFLATION SYSTEM according to claim 17, characterized in that an inlet to the first pump cavity is fluidly connected to an outlet of the second pump cavity.
[0019]
19. TIRE INFLATION SYSTEM according to claim 18, characterized in that it additionally comprises a frame that statically connects the first axis with the second axis, the frame being operable between: ■ a pumping position at that the frame places the first power transformer in non-slip contact with the arcuate support surface, wherein the second power transformer is connected to the arcuate support surface through the first power transformer and the frame; and ■ a non-pumping position, wherein the frame disconnects the first power transformer from the arcuate bearing surface and slidably couples the second power transformer to the arcuate bearing surface.
[0020]
20. TIRE INFLATION SYSTEM according to claim 19, characterized in that a frame center is located in a first radial position in the pumping position and in a second radial position in the non-pumping position, wherein the first radial position it is different from the second radial position.
[0021]
21. A TIRE INFLATION SYSTEM according to claim 20, characterized in that the second pump cavity is operable between: ■ a compressed position wherein the second actuation element is proximal to a closed end of the second chamber; ■ a reclaimed position wherein the second drive element is located in a first position distal to a closed end of the second chamber; and ■ a pressurized position in which the second actuating element is located in a second position distal to the closed end of the second chamber, the second position farther from the closed end of the second chamber than the first position, in which the second actuating element is placed in the pressurized position in response to a reservoir pressure that exceeds the threshold opening pressure, wherein the frame is placed in the non-pumping position when the second pump cavity is placed in the pressurized position.
[0022]
22. TIRE INFLATION SYSTEM according to claim 1, further comprising a housing coupled to the drive mechanism and the first pump cavity, wherein the housing is configured to be mounted on a rotating surface, wherein the rotating surface is set to rotate relative to a gravity vector.
[0023]
23. TIRE INFLATION SYSTEM according to claim 22, characterized in that the housing surrounds the drive mechanism, the first pump cavity and the first power transformer, wherein the housing further comprises a water-selective membrane that connects fluid mode an environment to an interior housing, wherein an inlet of the first pump cavity is fluidly connected to the interior housing.
[0024]
24. TIRE INFLATION SYSTEM according to claim 23, characterized in that it comprises a relief valve operable between an open state wherein the relief valve fluidly connects a reservoir to the interior housing, wherein the reservoir is connected to fluid mode at an outlet from the first pump cavity, and a closed state where the relief valve prevents fluid flow from the reservoir to the inner housing.
[0025]
25. TIRE INFLATION SYSTEM according to claim 1, characterized in that the eccentric mass comprises a first and a second piece, the eccentric mass operable between: ■ a pumping mode in which the first piece is adjacent to the second ask; and■ a non-pumping mode where the first part is distal to the second part.

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引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US1358524A|1920-11-09|Meajsts eok |

---

US2899907A|1959-08-18|Roller pump |

---

US1448248A|1921-08-31|1923-03-13|George H Anthony|Automatic tire pump|

---

GB350005A|1929-03-20|1931-06-04|Bbc Brown Boveri & Cie|Improvements in and relating to metallic vapour rectifiers|

---

US2211935A|1937-12-15|1940-08-20|Clark W Parker|Automatic tire inflater|

---

GB530005A|1939-06-05|1940-12-03|Kingman Brewster|Tyre inflating device|

---

US2415618A|1945-05-21|1947-02-11|William S West|Pump|

---

US2962119A|1957-07-08|1960-11-29|Wagner Electric Corp|Filter unit|

---

US3012820A|1959-01-19|1961-12-12|Arthur S King|Automotive wheel balancer|

---

US3047339A|1960-01-06|1962-07-31|Leland S Hamer|Wheel balancer|

---

US3152553A|1960-12-13|1964-10-13|Rydberg Sverker|Rotary pump or the like|

---

US3175507A|1961-05-05|1965-03-30|Rydberg Sverker|Device in rotary machines useful as pumps, motors and fluid meters|

---

US3249059A|1964-03-31|1966-05-03|Everpure|Peristaltic-type pump|

---

US3400074A|1965-09-15|1968-09-03|Carl A. Grenci|Centrifugal reverse osmosis for desalination|

---

US3452801A|1967-05-16|1969-07-01|George Warren Fletcher|Air compressing automotive wheel|

---

US3511294A|1967-12-18|1970-05-12|Lockheed Aircraft Corp|Emergency tire inflation system|

---

US3532449A|1968-05-07|1970-10-06|Paul I Garton|Wheel|

---

DE2308460A1|1972-03-03|1973-09-06|Curt Arnold Bjoerklund|VALVE|

---

US3730215A|1971-04-08|1973-05-01|Hydr O Matic Pump Co|Diaphragm controlled air relief valve|

---

CA1043275A|1974-04-20|1978-11-28|Hans-Joachim Hofmann|Apparatus for producing dry compressed air|

---

SE387162B|1974-06-25|1976-08-30|Ljungmans Verkstader Ab|HOSE PUMP|

---

US4030300A|1975-02-12|1977-06-21|Thompson William C|Power generating system|

---

CA1036420A|1975-09-25|1978-08-15|Baxter Travenol Laboratories|Peristaltic pump with forgiving rollers|

---

DE2553800A1|1975-11-29|1977-06-02|Koehring Gmbh Bomag Division|UNBALANCE DRIVE DEVICE|

---

US4157530A|1975-12-18|1979-06-05|Merz Ernest J|Automatic tire pressure monitoring system|

---

US4291235A|1979-02-26|1981-09-22|Bergey Jr Karl H|Windmill|

---

SE418411B|1979-07-04|1981-05-25|Rune Sturesson|EXCENTER ELEMENT PROVIDED FOR MARKET Vibrators|

---

US4256971A|1979-11-16|1981-03-17|Rodney Griffith|Wave and wind motion energy transducer|

---

GB2089297A|1980-12-12|1982-06-23|Venugopalan Chenicheri Vadakki|Tyre pressure regulators|

---

US4460006A|1982-01-19|1984-07-17|Eaton Corporation|Freeze protection valve|

---

US4536668A|1982-09-13|1985-08-20|Boyer Robert E|Vehicle mountable electrical generating system|

---

US4637152A|1983-05-11|1987-01-20|Roy David C|Rotary drive mechanism for energizing toys, kinetic sculptures, or the like|

---

US4651792A|1984-07-02|1987-03-24|Allen F. Ehle|Automatic tire pressurizing system|

---

US4606710A|1985-10-09|1986-08-19|Maguire Stephen B|Peristaltic pump|

---

AT386360B|1986-05-15|1988-08-10|Heid Ag Maschf|MASS COMPENSATION FOR VIBRATION DRIVES|

---

US4895199A|1986-07-31|1990-01-23|Paccar Inc|Tire inflation and deflation valve|

---

US4744399A|1986-07-31|1988-05-17|Paccar Inc.|Central tire inflation system|

---

FR2618102B1|1987-07-15|1990-02-16|Michelin & Cie|INFLATION OF A ROTATING TIRE|

---

NO162946C|1987-08-21|1990-03-14|Otto Soerensen|DEVICE FOR MAGNETIC SEPARATION OF CELLS.|

---

US4768542A|1987-11-04|1988-09-06|Gt Development Corporation|Drain valve|

---

US4819593A|1988-04-28|1989-04-11|Briggs & Stratton Corporation|Pivoting balancer system|

---

US4852528A|1988-06-20|1989-08-01|Magnavox Government And Industrial Electronics Company|Pneumatic actuator with permanent magnet control valve latching|

---

US4893459A|1988-07-11|1990-01-16|Fmc Corporation|Variable force shaker|

---

DE68927150T2|1988-11-14|1997-04-10|Sumitomo Electric Industries|Fluid pressure regulator|

---

US5759820A|1988-11-21|1998-06-02|Dynal As|Process for producing cDNA|

---

US5512439A|1988-11-21|1996-04-30|Dynal As|Oligonucleotide-linked magnetic particles and uses thereof|

---

GB8926269D0|1989-11-21|1990-01-10|Dynal As|Plasmid|

---

DE4031554A1|1990-02-23|1991-08-29|Standard Elektrik Lorenz Ag|HOSE PUMP|

---

GB9007966D0|1990-04-09|1990-06-06|Dynal As|Antigen/anti-antigen cleavage|

---

DE4042446C2|1990-11-15|1993-04-22|Johann 8391 Sonnen De Binder|

---

US5201968A|1991-08-27|1993-04-13|Cycloid Company|Tire pressuring and regulating apparatus|

---

US5293919A|1991-11-18|1994-03-15|Hughes Aircraft Company|Self-regulating tire pressure system and method|

---

US5342177A|1992-04-01|1994-08-30|Cheng Chen Kuang|Tire automatic pneumatic pump device|

---

DE4214917A1|1992-05-11|1993-11-18|Allweiler Ag|Peristaltic pump|

---

US5409049A|1992-05-29|1995-04-25|Cycloid Company|Tangential tire pressurizing and regulating apparatus|

---

US5325902A|1992-06-19|1994-07-05|Loewe Richard T|Automatic tire pressure monitor and inflation system|

---

FR2699863B1|1992-12-31|1995-03-17|Michelin & Cie|Method and device for stabilizing the oscillations of a vehicle, and vehicle equipped with such a device.|

---

US5388470A|1993-06-28|1995-02-14|Marsh, Jr.; Richard O.|Centrifugal force drive machine|

---

US5370711A|1993-07-21|1994-12-06|Ev Energy Systems, Inc.|Method for making an electrical energy storage device|

---

GB2285837B|1994-01-24|1998-05-13|Varian Australia|Peristaltic pump|

---

US5838792A|1994-07-18|1998-11-17|Bell Atlantic Network Services, Inc.|Computer system for centralized session key distribution, privacy enhanced messaging and information distribution using a split private key public cryptosystem|

---

US5468129A|1994-08-05|1995-11-21|Cole Parmer Instrument Company|Peristaltic pump|

---

US5538062A|1994-08-12|1996-07-23|Marks-Rms, Inc.|Pnuematic tire inflation system|

---

CN2202665Y|1994-09-29|1995-07-05|麦永光|Automatic pressure-adjustable miniature inflator for bicycle|

---

US5707215A|1994-11-14|1998-01-13|Hughes Aircraft Company|Tuned resonant oscillating mass inflation pump and method of extracting electrical energy therefrom|

---

GB9425138D0|1994-12-12|1995-02-08|Dynal As|Isolation of nucleic acid|

---

US5591281A|1995-08-09|1997-01-07|Loewe; Richard T.|Flywheel tire inflation device|

---

US5667606A|1996-07-05|1997-09-16|Cycloid Company|Tire pressurizing and regulating apparatus|

---

US5947696A|1996-07-31|1999-09-07|Hayes Lemmerz International, Inc.|Wheel mounted tire pump with a reciprocating piston|

---

DE19633178A1|1996-08-17|1998-02-19|Roediger Anlagenbau|Control for a suction and / or water valve that can be operated with negative pressure|

---

US5941696A|1996-09-10|1999-08-24|Embrex, Inc.|Peristaltic pump|

---

GB9620075D0|1996-09-26|1996-11-13|Dynal As|Method|

---

US5894757A|1997-07-25|1999-04-20|Sully; Paul Emile|Device for enhancing rotational movement|

---

US6170058B1|1997-12-23|2001-01-02|Arcot Systems, Inc.|Method and apparatus for cryptographically camouflaged cryptographic key storage, certification and use|

---

US6267450B1|1998-07-06|2001-07-31|Christopher L. Gamble|Load balancing system|

---

US6092545A|1998-09-10|2000-07-25|Hamilton Sundstrand Corporation|Magnetic actuated valve|

---

GB9822822D0|1998-10-19|1998-12-16|Dyno Particles As|Particles|

---

US6144295A|1998-12-11|2000-11-07|Case Corporation|Automatic central tire inflation system|

---

CN1189495C|1999-04-09|2005-02-16|迪纳尔生物技术公司|Process for the preparation of monodisperse polymer particles|

---

US6474832B2|1999-08-23|2002-11-05|Wayne H. Murray|Self-regulating, axle-mounted electrical generation device|

---

US6984702B2|2000-03-22|2006-01-10|Dynal Biotech Asa|Process for the preparation of functionalized polymer particles|

---

US6494693B1|2000-10-23|2002-12-17|Cole-Parmer Instrument Company|Peristatic pump|

---

US6742386B1|2000-10-30|2004-06-01|International Truck Intellectual Property Company, Llc|Wheel mounted power generator and wheel condition sensing apparatus|

---

US20030115452A1|2000-12-19|2003-06-19|Ravi Sandhu|One time password entry to access multiple network sites|

---

US6463798B2|2001-01-17|2002-10-15|Microchip Technology Incorporated|Tire inflation pressure monitoring and location determining method and apparatus|

---

US6394159B1|2001-01-26|2002-05-28|Meritor Heavy Vehicle Technology, Llc|Hub cap filter for tire inflation system|

---

DE10105181C1|2001-02-06|2002-07-11|Aerodyn Eng Gmbh|Wind-powered energy plant for water desalination has mechanical energy provided by rotor used for driving pressure pump for reverse osmosis system|

---

CN2496691Y|2001-08-17|2002-06-26|徐长寿|Bicycle middle axle driving air pump|

---

AU2002361924A1|2001-12-11|2003-06-23|Frantisek Hrabal|Device for monitoring, maintenance and adjustment of pressure in a tyre|

---

CA2473376A1|2002-01-16|2003-07-31|Dynal Biotech Asa|Method for isolating nucleic acids and protein from a single sample|

---

US7146009B2|2002-02-05|2006-12-05|Surety, Llc|Secure electronic messaging system requiring key retrieval for deriving decryption keys|

---

US6939111B2|2002-05-24|2005-09-06|Baxter International Inc.|Method and apparatus for controlling medical fluid pressure|

---

US6744356B2|2002-07-11|2004-06-01|Autoliv Asp, Inc.|Tire pressure maintenance and monitoring system|

---

US7828101B2|2002-12-03|2010-11-09|Radtke Jeffrey L|Self-propelled wheel for bicycles and similar vehicles|

---

EP1609630A1|2003-03-28|2005-12-28|Takaji Nakano|Automatic air-feeding mechanism for pneumatic tire|

---

US6994136B2|2003-05-02|2006-02-07|Arvinmeritor Technology, Llc|Wheel end tire air pump|

---

EP1649284B1|2003-07-17|2007-12-05|Invitrogen Dynal AS|Process for preparing coated magnetic particles|

---

DE10335244A1|2003-08-01|2005-03-10|Bayerische Motoren Werke Ag|Device for air filling a rotating pneumatic tire|

---

FR2859507B1|2003-09-08|2006-02-17|Athena Innovations|PERISTALTIC PUMP WITH DEFORMABLE REMOVABLE RACK|

---

JP2005231573A|2004-02-23|2005-09-02|Kobayashi Uchinuki Kogei Kk|Tire automatic pump device|

---

CN100585181C|2004-03-10|2010-01-27|成再君|Planetary wheel driven creepage pump with orbicular track|

---

US7498683B2|2004-09-01|2009-03-03|Wilhelm Landwehr|Device for converting flow energy into electrical energy|

---

FR2876751B1|2004-10-15|2007-01-19|Centre Nat Rech Scient Cnrse|APPARATUS FOR CONVERTING WAVE ENERGY INTO ELECTRICAL ENERGY|

---

CA2586319C|2004-11-12|2015-01-13|Richard Loewe|Tire pressure maintenance device|

---

US7784513B2|2004-11-12|2010-08-31|Richard Thomas Loewe|Tire pressure maintenance device|

---

CA2597340A1|2005-02-09|2006-08-17|Baker Hughes Incorporated|Electromagmetic actuator|

---

US20060182283A1|2005-02-14|2006-08-17|Tricipher, Inc.|Architecture for asymmetric crypto-key storage|

---

US7599493B2|2005-02-14|2009-10-06|Tricipher Inc.|Asymmetric key pair having a kiosk mode|

---

GB0512503D0|2005-06-18|2005-07-27|Jkid Ltd|A portable device|

---

US20070018458A1|2005-07-22|2007-01-25|Martinez Melaquias E|Method and apparatus for wave energy conversion using a floating pulley and counterweight|

---

US7255323B1|2005-08-19|2007-08-14|Praetorian, Inc.|Pressure activated valve|

---

US7302837B2|2005-09-27|2007-12-04|Cnh America Llc|Tire inflation system for use with an agricultural implement|

---

US7985340B2|2005-12-02|2011-07-26|Invitrogen Dynal As|Magnetic separator|

---

CN100410092C|2005-12-24|2008-08-13|杨晓立|Vehicle wheel capable of producing regenerative power|

---

US7222487B1|2006-03-10|2007-05-29|Hinkley William G|Portable electricity generating gravity driven wheel system|

---

US20070250914A1|2006-04-19|2007-10-25|Avaya Technology Llc|Method and system for resetting secure passwords|

---

US7506663B2|2006-07-20|2009-03-24|Fleetguard, Inc.|Magnetic check valve|

---

US7856871B2|2006-07-28|2010-12-28|Pirelli Tyre S.P.A.|Wheel for vehicles|

---

JP2008038856A|2006-08-10|2008-02-21|Toyota Industries Corp|Control valve for variable displacement compressor|

---

JP4238894B2|2006-08-11|2009-03-18|トヨタ自動車株式会社|Motor and in-wheel motor structure using the same|

---

JP4438779B2|2006-08-11|2010-03-24|トヨタ自動車株式会社|In-wheel motor structure|

---

US7453165B2|2006-10-24|2008-11-18|Seadyne Energy Systems, Llc|Method and apparatus for converting ocean wave energy into electricity|

---

US7847421B2|2007-01-19|2010-12-07|Willowview Systems, Inc.|System for generating electrical energy from ambient motion|

---

DE112008001428T5|2007-05-21|2010-04-29|Bol, Stephen J., Muskegon|Radical pump for self-inflating tires|

---

US8233624B2|2007-05-25|2012-07-31|Splitstreem Oy|Method and apparatus for securing data in a memory device|

---

US20090055906A1|2007-08-20|2009-02-26|Infineon Technologies Ag|Method and apparatus for embedded memory security|

---

GB0718008D0|2007-09-14|2007-10-24|Imp Innovations Ltd|Electrical generator|

---

US8083503B2|2007-09-27|2011-12-27|Curlin Medical Inc.|Peristaltic pump assembly and regulator therefor|

---

US7784487B2|2007-10-24|2010-08-31|Honeywell International Inc.|Fuel metering valve assembly including thermal compensation mechanism|

---

US7810582B2|2007-11-19|2010-10-12|Webb Charles T|Counterbalance enabled power generator for horizontal directional drilling systems|

---

US7931817B2|2008-02-15|2011-04-26|Honeywell International Inc.|Additive dispensing device and a thermally activated additive dispensing filter having the additive dispensing device|

---

WO2009105011A1|2008-02-20|2009-08-27|Ocean Harvesting Technologies Ab|Wave power plant and transmission|

---

WO2009110001A1|2008-03-05|2009-09-11|Council Of Scientific & Industrial Research|A polymeric hybrid membrane|

---

US8022561B2|2008-04-11|2011-09-20|Schlumberger Technology Corporation|Kinetic energy harvesting in a drill string|

---

US7931061B2|2008-12-15|2011-04-26|Arvinmeritor Technology, Llc|Tire inflation system with integrated wheel seal|

---

US8335933B2|2009-02-13|2012-12-18|Microsoft Corporation|Two-party storage of encrypted sensitive information|

---

US8713329B2|2009-02-26|2014-04-29|Red Hat, Inc.|Authenticated secret sharing|

---

US8186402B2|2009-03-24|2012-05-29|Pressure Sentinel, Inc|Device for automatically maintaining tire pressure|

---

US8646426B2|2009-09-14|2014-02-11|Atlas Copco Tools & Assemble Systems LLC|Valve lash setting process|

---

US8113254B2|2009-12-21|2012-02-14|The Goodyear Tire & Rubber Company|Self-inflating tire|

---

US8042586B2|2009-12-21|2011-10-25|The Goodyear Tire & Rubber Company|Self-inflating tire assembly|

---

US8801910B2|2010-06-21|2014-08-12|Massachusetts Institute Of Technology|Method and apparatus for desalination and purification|

---

EP2596243A4|2010-07-21|2018-01-10|Aperia Technologies|Tire inflation system|

---

US8747084B2|2010-07-21|2014-06-10|Aperia Technologies, Inc.|Peristaltic pump|

---

EP2442484A1|2010-10-15|2012-04-18|Certicom Corp.|Authenticated encryption for digital signatures with message recovery|

---

PL2828103T3|2012-03-20|2017-09-29|Aperia Technologies|Tire inflation system|US10144254B2|2013-03-12|2018-12-04|Aperia Technologies, Inc.|Tire inflation system|

---

US9604157B2|2013-03-12|2017-03-28|Aperia Technologies, Inc.|Pump with water management|

---

PL2828103T3|2012-03-20|2017-09-29|Aperia Technologies|Tire inflation system|

---

AU2013337652B2|2012-11-01|2017-05-25|FlowBelow Aero, Inc.|Aerodynamic system and adjustable fairings|

---

US9985501B2|2013-08-16|2018-05-29|Hamilton Sundstrand Corporation|Generators with open loop active cooling|

---

US10052923B2|2013-08-27|2018-08-21|Arvinmeritor Technology, Llc|Tire inflation system with peristaltic pump|

---

US9114673B2|2013-11-05|2015-08-25|The Goodyear Tire & Rubber Company|Air maintenance tire and relief valve assembly|

---

CN105705348B|2013-11-05|2018-01-19|麦格纳覆盖件有限公司|Automatic load motor vehicle assembly tire inflation system with double pump|

---

WO2015075656A1|2013-11-22|2015-05-28|NDLOVU, Raymond|Device for controlling the pressure in a vehicle tyre|

---

US20150147200A1|2013-11-27|2015-05-28|The Goodyear Tire & Rubber Company|Air maintenance tire assembly|

---

US20150147201A1|2013-11-27|2015-05-28|The Goodyear Tire & Rubber Company|Air maintenance tire assembly|

---

US20170282656A9|2014-05-05|2017-10-05|The Goodyear Tire & Rubber Company|Air maintenance tire assembly|

---

US9809066B2|2014-05-05|2017-11-07|The Goodyear Tire & Rubber Company|System for an air maintenance tire assembly|

---

US20170072752A1|2014-10-21|2017-03-16|The Goodyear Tire & Rubber Company|Air maintenance pump assembly|

---

US9783015B2|2014-08-12|2017-10-10|The Goodyear Tire & Rubber Company|Control regulator and pumping system for an air maintenance tire|

---

US9744816B2|2014-08-12|2017-08-29|The Goodyear Tire & Rubber Company|Air maintenance tire|

---

US9505278B1|2015-08-13|2016-11-29|The Goodyear Tire & Rubber Company|Air maintenance pump|

---

US20170101983A1|2015-10-12|2017-04-13|Allen Mark Jones|Pendulum powered energy and water devices and method|

---

US10465815B2|2016-01-23|2019-11-05|Dana Heavy Vehicle Systems Group, Llc|Extended stroke, high flow, valve and the assembly made therewith|

---

WO2018048885A1|2016-09-06|2018-03-15|Aperia Technologies, Inc.|System for tire inflation|

---

DE102016119272A1|2016-10-11|2018-04-12|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Mechanically driven tire pressure generation|

---

CN110023109A|2016-10-20|2019-07-16|伊夸莱尔系统公司|Tire inflation system vision flow director|

---

DE102016122738A1|2016-11-24|2018-05-24|Kt Projektentwicklungs-Gmbh|Compressor arrangement with radial piston|

---

US10807422B2|2016-12-22|2020-10-20|The Goodyear Tire & Rubber Company|Inlet control valve for an air maintenance tire|

---

US10759236B2|2017-05-04|2020-09-01|The Goodyear Tire & Rubber Company|Wheel for an air maintenance tire system|

---

US10654529B2|2017-06-24|2020-05-19|FlowBelow Aero, Inc.|Aerodynamic systems and fairings with fairing caps|

---

US10882571B2|2017-07-30|2021-01-05|FlowBelow Aero, Inc.|Rotatable aerodynamic fairing system|

---

WO2019089466A1|2017-10-30|2019-05-09|University Of Utah Research Foundation|Motion-based energy harvester for wearable electronics|

---

US10406869B2|2017-11-10|2019-09-10|Aperia Technologies, Inc.|Inflation system|

---

US10487817B1|2018-11-02|2019-11-26|Baoxiang Shan|Methods for creating an undulating structure|

---

US11001109B1|2019-05-13|2021-05-11|Unicus Innovations Llc|Tire stem having breather|

---

CN111231587B|2020-02-18|2021-12-14|浙江福林国润汽车零部件有限公司|Self-inflating constant-pressure tire burst prevention system|

法律状态:
2017-07-04| B08F| Application dismissed because of non-payment of annual fees [chapter 8.6 patent gazette]|

---

2017-09-05| B08G| Application fees: restoration [chapter 8.7 patent gazette]|

---

2018-12-04| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

---

2019-11-12| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

---

2020-12-08| B07A| Application suspended after technical examination (opinion) [chapter 7.1 patent gazette]|

---

2021-06-08| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

---

2021-08-17| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 12/03/2013, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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US201261613406P| true| 2012-03-20|2012-03-20|

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US61/613,406|2012-03-20|

---

US201261637206P| true| 2012-04-23|2012-04-23|

---

US61/637,206|2012-04-23|

---

US201261672223P| true| 2012-07-16|2012-07-16|

---

US61/672,223|2012-07-16|

---

PCT/US2013/030604|WO2013142158A1|2012-03-20|2013-03-12|Tire inflation system|

---