Reaction Drive Energy Transfer Device
A fluid energy transfer device, including a chamber for receiving a fluid, at least a portion of the chamber comprising a movable portion relative to another portion of the chamber, the movable portion being adapted to change the volume of the chamber from a first volume to a second volume by movement of the movable portion. The device further includes a bender actuator attached to the movable portion, wherein the bender actuator is at least one of (i) connected directly to the movable portion and (ii) linked to the movable portion, to form a bender-movable portion assembly, wherein the bender is effectively not connected and effectively not linked to any other component of the device other than the movable portion, and wherein the bender-movable portion assembly is adapted to move substantially only due to oscillation of the bender at a drive frequency.
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This application claims the benefit of U.S. Provisional Application No. 60/638,195, filed Dec. 23, 2004, the contents of which are incorporated herein by reference in their entirety.
BACKGROUND OF THE INVENTION1) Field of Invention
This invention relates generally to apparatus and methods for conveying energy into a volume of fluid and more specifically to the field of linear pumps, linear compressors, and other fluidic devices.
2) Description of Related Art
For the purpose of conveying energy to fluids within a defined enclosure, prior technologies have employed a number of approaches, including positive displacement, agitation such as with mechanical stirring or the application of traveling or standing acoustic waves, the application of centrifugal forces, and the addition of thermal energy. The transfer of mechanical energy to fluids by means of these various methods can be for a variety of applications, which could include for example, compressing, pumping, mixing, atomization, synthetic jets, fluid metering, sampling, air testing for bio-warfare agents, ink jets, filtration, or driving physical changes due to chemical reactions, or other material changes in suspended particulates such as comminution or agglomeration, or a combination of any of these processes, to name a few.
Within the category of positive displacement machines, diaphragms have found widespread use. The absence of frictional energy losses makes diaphragms especially useful in downsizing positive displacement machines while trying to maintain high energy efficiency. The interest in MESO and MEMS scale devices has lead to even further reliance on diaphragm-type devices for conveying hydraulic energy into fluids within small pumps. The term “pump” as used herein refers to devices designed for providing compression and/or flow to either liquids or gases. The term “fluid” used herein is understood to include both the liquid and the gaseous states of matter.
The actuators used to drive larger diaphragm pumps have proved problematic for MESO or MEMS machines since it is difficult to maintain their efficiency and low cost as they are scaled down in size. For example, the air gaps associated with electromagnetic and voice coil type actuators must be scaled down in order to maintain high transduction efficiency and this adds manufacturing complexity and cost. Also, motor laminations become magnetically saturated as motors are scaled down while seeking to maintain a constant mechanical power output. Within acceptable product cost targets, it is widely accepted that the electro-mechanical efficiency of these transducers will drop off significantly with size reduction.
These scaling challenges, associated with magnetic actuators, have led to the widespread use of other technologies, such as piezoceramics and magnetostrictive actuators, for MESO and MEMS applications. A piezo disk naturally combines the fluid diaphragm and actuator into a single component.
The advantages of using the piezo as the fluidic diaphragm are offset by the piezo's inherent displacement limitations. Since ceramics are relatively brittle, piezoceramic diaphragms/disks can only provide a small fraction of the displacements provided by other materials such as metals, plastics, and elastomers, for example. The peak oscillatory displacements that a clamped circular piezoceramic disk can provide without failure are typically less than 1% of the disk's clamped diameter. Since diaphragm displacement is directly related to the fluidic energy transferred per stroke, piezos impose a significant limitation on the power density and overall performance of small fluidic devices such as MESO pumps and compressors. These displacement-related energy limitations are especially true for gases.
Other types of piezo actuators that depend on the bulk flexing properties of the piezo material can provide high energy transfer to liquids by operating at very high frequencies, but at even smaller strokes. These small actuator strokes make the design of pumps impractical. Further, high-performance pumps employ passive valves that open and close each pumping cycle to provide optimal pumping efficiency. These pump valves may not provide the needed performance in the kHz-MHz frequency range of the bulk-piezo actuators.
Currently, the demand is increasing for ever smaller fluidic devices which may not be attainable or functionally consistently useful with current piezo pump technology. For example, pumps and compressors are needed that can provide higher specific flow rates (i.e. fluid volume flow rate divided by the pump's physical volume) at higher pressure heads and in ever smaller sized units. Examples of applications that require high performance MESO-sized pumps include the miniaturization of fuel cells for portable electronic devices such as portable computing devices, PDAs and cell phones, self-contained thermal management systems that can fit on a circuit card and provide cooling for microprocessors and other semi-conductor electronics, and portable personal medical devices for ambulatory patients. Thus, there is a need for a compact, economically viable piezo pump that remedies at least some of the deficiencies of current piezo pumps.
SUMMARY OF THE INVENTIONTo satisfy these needs and overcome the limitations of previous efforts, the present invention is provided as a fluid energy-transfer device that uses a new reaction-drive actuator for driving diaphragm fluidic devices, such as pumps and compressors, at or near their system resonance. A fluidic energy transfer device according to one embodiment comprises a fluid chamber having an inner wall shaped so as to form a chamber volume with an opening and a fluidic diaphragm being rigidly attached to the perimeter of the opening and with a bender-type actuator being attachment to the fluidic diaphragm. The reaction-drive energy-transfer device according to some embodiments of the present invention provides a unique system for driving displacements of the fluidic diaphragm which can be an order of magnitude larger than the displacement of prior piezo diaphragms.
The reaction-drive system according to most embodiments of the present invention enables high-performance for devices such as MESO-sized pumps and compressors and synthetic jets. The pumps and compressors according to some embodiments of the present invention may include tuned ports and valves that allow low-pressure fluid to enter and high-pressure fluid to exit a compression chamber in response to the cyclic compressions. The reaction-drive system may use a variety of bender actuators, such as uni-morph, bi-morph and multilayer PZT benders, piezo-polymer composites such as PVDF, crystalline materials, magnetostrictive materials, electroactive polymer transducers (EPTs), electrostrictive polymers and various “smart materials” such as shape memory alloys (SMA), and radial field PZT diaphragm (RFD) actuators.
The fluidic devices according to the present invention are operated at a drive frequency that allows energy to be stored in the system's mechanical resonance, thereby providing diaphragm displacements that are larger and typically much larger that the actual bending displacements of the bender-actuator. The system resonance may be determined based on the effective moving mass of the diaphragm, bender actuator and related components and on the spring stiffness of the fluid, the fluidic diaphragm, and other optional mechanical springs; and or other components/environments that influence the resonant frequency.
The pumps according to some embodiments of the present invention may be utilized in a variety of applications including by way of example only the general compression of gases such as air, hydrocarbons, process gases, high-purity gases, hazardous and corrosive gases, with the compression of phase-change refrigerants for refrigeration, air-conditioning and heat pumps with liquids, and other specialty vapor-compression or phase-change heat transfer applications. The pumps according to some embodiments of the present invention may also pump liquids such as fuels, water, oils, lubricants, coolants, solvents, hydraulic fluid, toxic or reactive chemicals, depending on the particular pump design. The pumps of the present invention can also provide variable capacity for either gas or liquid operation.
More specifically, an exemplary embodiment of the present invention includes a fluid chamber having an inner wall shaped so as to form a chamber volume and having an opening. A fluidic diaphragm is rigidly attached to the perimeter of the opening in the fluid chamber and the diaphragm has a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber. The chamber is filled with a fluid that comprises part of the load of the system. The fluid within the fluid chamber comprises a spring and the fluidic diaphragm also comprises a spring. A bender actuator having an attachment point is attached to the fluidic diaphragm. A mass-spring mechanical resonance frequency is determined by the combined effective moving masses of the bender actuator and fluidic diaphragm and by the mechanical spring and the gas spring, and the bender actuator is operable at a drive frequency so as to store energy in the mass-spring mechanical resonance and provide displacements of the fluidic diaphragm that are larger (and in many instances much larger) than the bending displacements of the bender actuator, such that increased energy is transferred to the fluidic load within the fluid chamber.
In another embodiment of the invention, there is a fluid energy transfer device comprising:
a fluid chamber adapted to receive a predetermined fluid, the fluid chamber including a fluidic diaphragm rigidly attached to structure of the fluid chamber substantially at the perimeter of the diaphragm, wherein the diaphragm includes a flexible portion adapted to move with respect to the perimeter attached to the structure, between a first position and a second position; and
a bender actuator; wherein
the bender actuator is attached to the fluid diaphragm to form a bender-diaphragm assembly;
wherein the bender actuator is adapted to bend at a frequency such that the bender-diaphragm assembly will move between the first position and the second position substantially only due to the frequency of bending of the actuator, and
wherein the distance between the first position and the second position is substantially greater than the distance of peak-to-peak bending of the actuator, and is exemplary greater than about an order of magnitude greater than the distance of peak-to-peak bending.
In another embodiment of the invention, there is a fluid energy transfer device comprising:
a fluid chamber adapted to receive a predetermined fluid, the fluid chamber including a fluidic diaphragm rigidly attached to structure of the fluid chamber substantially at the perimeter of the diaphragm, wherein the diaphragm includes a flexible portion adapted to move with respect to the attaching structure, between a first position and a second position; and
a bender actuator;
wherein the bender actuator is at least one of (i) connected directly to the fluid diaphragm and (ii) directly linked to the fluid diaphragm,
wherein the bender is effectively not connected and effectively not linked to any other component of the pump other than the diaphragm, and
wherein the bender is optionally connected to electrical leads adapted to conduct electrons to the bender.
In another embodiment of the present invention, there is a fluid energy transfer device comprising:
a fluid chamber having an inner wall shaped so as to form a chamber volume and having an opening;
a fluidic diaphragm being rigidly attached to the perimeter of the opening in the fluid chamber and the diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
a fluid within the fluid chamber;
a fluid spring comprising the fluid within the fluidic chamber;
a mechanical spring comprising the diaphragm;
a bender actuator having an attachment point being attached to the fluidic diaphragm;
wherein a mass-spring mechanical resonance frequency is determined by the combined effective moving masses of the bender actuator and the diaphragm and by the mechanical spring and the gas spring, and wherein the bender actuator is operable at a drive frequency so as to store energy in the mass-spring mechanical resonance thereby transferring energy to the fluid within the fluid chamber.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the attachment point of the bender actuator to the fluidic diaphragm comprises the power take-off point and wherein a reaction mass is attached to a point on the bender actuator that moves with opposite time phase than the power take off point.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the attachment point between the bender actuator and the fluidic diaphragm further comprises a tuning spring such that the forces created by the bender actuator are transmitted through the tuning spring to the fluidic diaphragm and wherein the stiffness of the tuning spring is chosen so as to improve the mechanical power factor.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein a first point of an axial stability member is attached to a standoff with the other end of the standoff being attached to a moving portion of the fluidic diaphragm and a second point of the axial stability component being attached to the exterior of the fluid chamber, whereby the axial stability component is axially offset from the plane of the fluidic diaphragm thereby allowing axial movement of the moving masses but impeding transverse movement of the moving masses.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the bender actuator comprises a piezoceramic bender actuator.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the bender actuator comprises a piezo-polymer composite bender actuator.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the bender actuator comprises a magnetostrictive bender actuator.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the bender actuator comprises a radial field PZT diaphragm bender actuator.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the wall of the fluid chamber further comprise a synthetic jet port which fluidically communicates the interior of the fluid chamber to the exterior of the fluid chamber, whereby the pressure within the fluid chamber oscillates at the drive frequency thereby creating a synthetic jet outside the fluid chamber causing fluid to flow away from the fluid chamber along the cylindrical axis of the synthetic jet port.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, further comprising:
an inlet port being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
an outlet port being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the inlet port has a flow rectifying profile designed to provide flow into the fluid chamber and the outlet port has a flow rectifying profile designed to provide flow into the fluid chamber;
whereby the displacements of the fluidic diaphragm create pressure oscillations within the fluid at the drive frequency thereby causing fluid to flow into the fluid chamber through the inlet port and flow out of the fluid chamber through the outlet port.
In another embodiment of the present invention, there is a fluid transfer device as described above and/or below, wherein the bender actuator comprises a piezoceramic bender actuator.
In another embodiment of the present invention, there is a pump comprising:
a fluid chamber having an inner wall shaped so as to form a chamber volume and having an opening;
a fluidic diaphragm being rigidly attached to the perimeter of the opening in the fluid chamber and the fluidic diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
an inlet port being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
an outlet port being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber;
a fluid within the fluid chamber;
a fluid spring comprising the fluid within the fluid chamber;
a mechanical spring comprising the diaphragm;
a bender actuator having an attachment point being attached to the fluidic diaphragm;
wherein a mass-spring mechanical resonance frequency is determined by the combined effective moving masses of the bender actuator and the diaphragm and by the mechanical spring and the gas spring, and wherein the bender actuator is operable at a drive frequency so as to store energy in the mass-spring mechanical resonance thereby transferring energy to the fluid within the fluid chamber.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the attachment point of the bender actuator to the fluidic diaphragm comprises the power take-off point and wherein a reaction mass is attached to a point on the bender actuator that moves with a different time phase than the power take off point.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the attachment point between the bender actuator and the fluidic diaphragm further comprises a tuning spring such that the forces created by the bender actuator are transmitted through the tuning spring to the fluidic diaphragm and wherein the stiffness of the tuning spring is chosen so as to improve the mechanical power factor.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein a first point of an axial stability member is attached to a standoff with the other end of the standoff being attached to a moving portion of the fluidic diaphragm and a second point of the axial stability component being attached to the exterior of the fluid chamber, whereby the axial stability component is axially offset from the plane of the fluidic diaphragm, thereby allowing axial movement of the moving masses but impeding transverse movement of the moving masses.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the bender actuator comprises a piezoceramic bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the bender actuator comprises a piezo-polymer composite bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the bender actuator comprises a magnetostrictive bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the bender actuator comprises a radial field PZT diaphragm bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, further comprising control means operatively connected with the bender actuator for varying the drive frequency in response to changes in the mass-spring mechanical resonance frequency.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the drive frequency is equal to the mass-spring mechanical resonance frequency.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the control means further comprises:
a means for measuring selected operating conditions in the pump;
means for varying the drive frequency of the motor in response to the measured operating conditions in order to maximize the measured operating conditions.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the operating conditions comprises the electrical power delivered to the pump.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluid is a gas.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the gas is selected from the group consisting of air, hydrocarbons, process gases, high-purity gases, hazardous and corrosive gases toxic fluids, high-purity fluids, reactive fluids and environmentally hazardous fluids.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluid is a liquid.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the liquid is selected from the group consisting of fuels, water, oils, lubricants, coolants, solvents, hydraulic fluid, toxic or reactive chemicals.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first positions of the fluidic diaphragm are proximal to the wall of the fluid chamber at the top of respective compression strokes, and the second positions are distal to the wall of the fluid chamber at the end of respective inlet strokes, and where the first and second proximal positions are at different distances from the wall of the fluid chamber and where the first and second distal positions are at different distance from the wall of the fluid chamber, and wherein the diaphragm is operably movable from oscillating between first proximal and distal positions to oscillating between second proximal and distal positions in response to changing the drive force of the bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein changing the drive force of the bender actuator operably moves the diaphragm from oscillating between first proximal and distal positions to oscillating between second proximal and distal positions and thereby provides a change in the flow rate of the fluid.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet port has a flow rectifying profile designed to provide flow into the fluid chamber and the outlet port has a flow rectifying profile designed to provide flow into the fluid chamber;
whereby the displacements of the fluidic diaphragm create pressure oscillations within the fluid at the drive frequency thereby causing fluid to flow into the fluid chamber through the inlet port and flow out of the fluid chamber through the outlet port.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the pump further comprises an inlet valve operatively connected to the inlet port and an outlet valve operatively connected to the outlet port, the inlet valve and the outlet valve each having a predetermined stiffness and a valve duty cycle, wherein the inlet valve prevents flow through the inlet port in a closed position and allows flow through the inlet port in an open position and the outlet valve prevents flow through the outlet port in a closed position and allows flow through the outlet port in an open position, and wherein the stiffness and size of the outlet valve and the inlet valve each being selected to tune the inlet valve and outlet valve such that the timing of the duty cycles of the inlet valve and the outlet valve are coordinated with the timing of the filling of fluid flow and/or the fluid flow through the inlet port and the discharge of the fluid flow through the outlet port and the pressure cycle in the compression chamber to provide a net flow in one direction of the fluid within the pump.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet valve is a reed valve and the outlet valve is a reed valve.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet reed valve and the outlet reed valve each has a spring stiffness and mass adapted to open and close in proper sequence in response to the oscillating fluid pressure within the fluid chamber, whereby proper valve timing is maintained without valve stops.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluidic diaphragm further comprises a flat section that moves in planar fashion and wherein the inlet ports and inlet valves are located on the flat section of the diaphragm, thereby providing actuation for the inlet valves.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluidic diaphragm further comprises a flat section that moves in planar fashion and wherein the outlet ports and outlet valves are located on the flat section of the diaphragm, thereby providing actuation for the outlet valves.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the pump further comprises:
a plurality of inlet ports being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
a plurality of outlet ports being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the wall of the fluid chamber further comprises a radially contoured wall section, and the flexible portion of the diaphragm being free to flex to generally conform in shape to the radially contoured section for minimizing clearance volume in the fluid chamber as the moving portion cycles to the plurality of first positions.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluidic diaphragm further includes a first face within the fluid chamber and a second face outside of an interior of the fluid chamber, and wherein the pump further comprises an exterior chamber in fluid communication with the second face of the diaphragm, a hole extending between and in communication with the fluid chamber and the exterior chamber with the hole having a geometry sized and selected to communicate a sufficient quantity of fluid through the hole between the fluid chamber and the exterior chamber for equalizing pressure on the first and second faces of the diaphragm.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the hole is positioned in the diaphragm.
In another embodiment of the present invention, there is a pump comprising:
a fluid chamber having an inner wall shaped so as to form a chamber volume and having a first and second opening;
a first fluidic diaphragm being rigidly attached to the perimeter of the first opening in the fluid chamber and the first fluidic diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
a second fluidic diaphragm being rigidly attached to the perimeter of the first opening in the fluid chamber and the second fluidic diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
at least one inlet port being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
at least one outlet port being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber;
a fluid within the fluid chamber;
a fluid spring comprising the fluid within the fluid chamber;
a first mechanical spring comprising the first diaphragm;
a second mechanical spring comprising the second diaphragm;
a first bender actuator having a first attachment point being attached to the first fluidic diaphragm;
a second bender actuator having a second attachment point being attached to the second fluidic diaphragm;
wherein a mass-spring mechanical resonance frequency is determined by the combined effective moving masses of the first bender actuator and the first diaphragm and by the first mechanical spring and the gas spring and also by the combined effective moving masses of the second bender actuator and the second diaphragm and by the second mechanical spring and the gas spring, and wherein the first and second bender actuators are operable at the same drive frequency so as to cause both first and second diaphragms to simultaneously traverse their respective compression and outlet strokes, thereby storing energy in the mass-spring mechanical resonance and transferring energy to the fluid within the fluid chamber.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the attachment point of the first bender actuator to the first fluidic diaphragm comprises the first power take-off point and wherein a first reaction mass is attached to a point on the first bender actuator that moves with a different time phase than the first power take off point, and wherein the attachment point of the second bender actuator to the second fluidic diaphragm comprises the second power take-off point and wherein a second reaction mass is attached to a point on the second bender actuator that moves with a different time phase than the second power take off point.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first attachment point between the first bender actuator and the first fluidic diaphragm further comprises a first tuning spring such that the forces created by the first bender actuator are transmitted through the first tuning spring to the first fluidic diaphragm and wherein the stiffness of the first tuning spring is chosen so as to improve the mechanical power factor of the first bender actuator, and wherein the second attachment point between the second bender actuator and the second fluidic diaphragm further comprises a second tuning spring such that the forces created by the second bender actuator are transmitted through the second tuning spring to the second fluidic diaphragm and wherein the stiffness of the second tuning spring is chosen so as to improve the mechanical power factor of the second bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein a first point of a first axial stability member is attached to a first standoff with the other end of the first standoff being attached to a moving portion of the first fluidic diaphragm and a second point of the first axial stability component being attached to the exterior of the fluid chamber, and wherein a first point of a second axial stability member is attached to a second standoff with the other end of the second standoff being attached to a moving portion of the second fluidic diaphragm and a second point of the second axial stability component being attached to the exterior of the fluid chamber,
whereby the first and second axial stability components are axially offset from the plane of their respective first and second fluidic diaphragms, thereby allowing axial movement of the moving masses but impeding transverse movement of the moving masses.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first bender actuator comprises a piezoceramic bender actuator and the second bender actuator comprises a piezoceramic bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first bender actuator comprises a piezo-polymer composite bender actuator and the second bender actuator comprises a piezo-polymer composite bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first bender actuator comprises a magnetostrictive bender actuator and the second bender actuator comprises a magnetostrictive bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first bender actuator comprises a radial field PZT diaphragm bender actuator and the second bender actuator comprises a radial field PZT diaphragm bender actuator.
In another embodiment of the present invention, there is a pump as described above and/or below, further comprising control means operatively connected with the first and second bender actuators for varying the drive frequency in response to changes in the mass-spring mechanical resonance frequency.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the drive frequency is equal to the mass-spring mechanical resonance frequency.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the control means further comprises:
a means for measuring selected operating conditions in the pump;
means for varying the drive frequency of the motor in response to the measured operating conditions in order to maximize the measured operating conditions.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the operating conditions comprises the electrical power delivered to the pump.
In another embodiment of the present invention, there is a pump as described above and/or below, further comprising control means operatively connected with the first and second bender actuators for varying the individual drive voltage amplitudes of first and second bender actuators as needed to minimize the vibration of the pump.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluid is a gas.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the gas is selected from the group consisting of air, hydrocarbons, process gases, high-purity gases, hazardous and corrosive gases toxic fluids, high-purity fluids, reactive fluids and environmentally hazardous fluids.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the fluid is a liquid.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the liquid is selected from the group consisting of fuels, water, oils, lubricants, coolants, solvents, hydraulic fluid, toxic or reactive chemicals.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first positions of the first and second fluidic diaphragms are proximal to the wall of the fluid chamber at the top of respective compression strokes, and the second positions are distal to the wall of the fluid chamber at the end of respective inlet strokes, and where the first and second proximal positions are at different distances from the wall of the fluid chamber and where the first and second distal positions are at different distances from the wall of the fluid chamber, and wherein the first and second fluidic diaphragms are operably movable from oscillating between first proximal and distal positions to oscillating between second proximal and distal positions in response to changing the drive forces of the first and second bender actuators.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein changing the drive force of the first and second bender actuators operably moves the first and second fluidic diaphragms from oscillating between first proximal and distal positions to oscillating between second proximal and distal positions and thereby provides a change in the flow rate of the fluid.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet port has a flow rectifying profile designed to provide flow into the fluid chamber and the outlet port has a flow rectifying profile designed to provide flow into the fluid chamber;
whereby the displacements of the first and second fluidic diaphragms create pressure oscillations within the fluid at the drive frequency thereby causing fluid to flow into the fluid chamber through the inlet port and flow out of the fluid chamber through the outlet port.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the pump further comprises an inlet valve operatively connected to the inlet port and a outlet valve operatively connected to the outlet port, with the inlet valve and outlet valve each having a predetermined stiffness and a valve duty cycle, wherein the inlet valve prevents flows through the inlet port in a closed position and allows flow through the inlet port in an open position and the outlet valve prevents flow through the outlet port in a closed position and allows flow through the outlet port in an open position, and wherein the stiffness and size of the outlet valve and the inlet valve each being selected to tune the inlet valve and outlet valve such that the timing of the duty cycles of the inlet valve and the outlet valve are coordinated with the timing of the filling of fluid flow through the inlet port and the discharge of the fluid flow through the outlet port and the pressure cycle in the compression chamber to provide a net flow in one direction of the fluid within the pump.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet valve is a reed valve and the outlet valve is a reed valve.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the inlet reed valve and the outlet reed valve each has a spring stiffness and mass adapted to open and close in proper sequence in response to the oscillating fluid pressure within the fluid chamber, whereby proper valve timing is maintained without valve stops.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the first fluidic diaphragm further comprises a first flat section that moves in a planar fashion and the second fluidic diaphragm further comprises a second flat section that moves in planer fashion and wherein the inlet ports and inlet valves are located on the first flat section of the first diaphragm the outlet ports and outlet valves are located on the second flat section of the second diaphragm, thereby providing actuation for the inlet valves and the outlet valves.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the pump further comprises:
a plurality of inlet ports being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
a plurality of outlet ports being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber.
In another embodiment of the present invention, there is a pump as described above and/or below, wherein the wall of the fluid chamber further comprises a radially contoured wall section, and the flexible portion of the first and second fluidic diaphragms being free to flex and to generally conform in shape to the radially contoured section for minimizing clearance volume in the fluid chamber as the moving portions of first and second fluidic diaphragms cycle to the plurality of first positions.
In another embodiment of the present invention, there is a method of pumping a fluid comprising:
providing a pump for compressing a fluid, the pump comprising;
a fluid chamber having an inner wall shaped so as to form a chamber volume and having an opening;
a fluidic diaphragm being rigidly attached to the perimeter of the opening in the fluid chamber and the fluidic diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
an inlet port being connected in communication with the fluid chamber for flowing a fluid into the fluid chamber;
an outlet port being connected in communication with the fluid chamber for flowing a fluid out of the fluid chamber;
a fluid within the fluid chamber;
a fluid spring comprising the fluid within the fluid chamber;
a mechanical spring comprising the diaphragm;
a bender actuator having an attachment point being attached to the fluidic diaphragm; the method further comprising:
introducing a fluid into the fluid chamber at a first pressure, wherein the fluid acts as a fluid spring under varying pressure conditions;
determining a mass-spring mechanical resonance frequency by the combined moving masses of the diaphragm and bender actuator and by the mechanical spring and the fluid spring;
operating the bender actuator at a drive frequency so as to store energy in the mass-spring mechanical resonance;
oscillating the diaphragm between the plurality of first positions and second positions;
compressing the fluid to a desired second pressure; and
evacuating the fluid from the compression chamber at the second pressure.
In another embodiment of the invention, there is a fluid energy transfer device comprising:
a fluid chamber for receiving a specific fluid having an inner wall shaped so as to form a chamber volume and having an opening;
a fluidic diaphragm being rigidly attached to the perimeter of the opening in the fluid chamber and the diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
a bender actuator having an attachment point being attached to the fluid diaphragm;
wherein a mass-spring mechanical resonance frequency is determined by the combined effective moving mass and the combined effective spring stiffness of the dynamic components and specific fluid and wherein the bender actuator is operable at a drive frequency so as to store energy in the mass-spring mechanical resonance.
In another embodiment of the invention, there is a fluidic energy transfer device comprising:
a fluid chamber having an inner wall shaped so as to form a chamber volume and having an opening;
a fluidic diaphragm being rigidly attached to the perimeter of the opening in said fluid chamber and the diaphragm having a flexible portion capable of moving with respect to the outer perimeter between a plurality of first positions and a plurality of second positions, the first and second positions being of varying distances from the inner wall of the fluidic chamber;
a fluid within the fluidic chamber;
a fluidic load comprising said fluid;
a fluid spring comprising the fluid within said fluidic chamber;
a mechanical spring comprising said diaphragm; and
a bender actuator having an attachment point being attached to said fluidic diaphragm;
wherein a mass-spring mechanical resonance frequency is determined by the combined effective moving masses of said bender actuator and said diaphragm and by said mechanical spring and said gas spring, and wherein the bender actuator is operable at a drive frequency so as to store energy in the mass-spring mechanical resonance and provide displacements of the fluidic diaphragm that are larger than the bending displacements of the bender actuator, and wherein energy is transferred to the fluidic load within the fluid chamber.
In another embodiment of the invention, there is a fluid energy transfer device comprising:
a fluid chamber adapted to receive a predetermined fluid, the fluid chamber including a fluidic diaphragm rigidly attached to structure of the fluid chamber substantially at the perimeter of the diaphragm, wherein the diaphragm includes a flexible portion adapted to move with respect to the perimeter attached to the structure, between a first position and a second position;
a bender actuator; wherein
the bender actuator is attached to the fluid diaphragm to form a bender-diaphragm assembly;
wherein the bender actuator is adapted to bend at a frequency such that the bender-diaphragm assembly will move between the first position and the second position substantially only due to the frequency of bending of the actuator, and
wherein the distance between the first position and the second position is substantially greater than the distance of peak-to-peak bending of the actuator, and is exemplary about an order of magnitude greater than the distance of peak-to-peak bending.
The accompanying drawings, which are incorporated in and form a part of the specification, illustrate the embodiments of the present invention and, together with the description, serve to explain the principles of the inventions. In the drawings:
Referring now to
In operation, an alternating voltage waveform of frequency f is applied to bender disk 14 of
If a drive frequency f is chosen to be near or equal to the system's fundamental resonant frequency fo, then energy may be stored in the oscillation in proportion to the system's resonance quality factor Q at the drive frequency f. As energy is stored in the system's resonance, the displacement of diaphragm 6 can exceed the actual bending displacements of bender disk 8. In this way, a low-displacement bender disk actuator may be used to provide the higher diaphragm displacements required by current MESO and MEMS fluidics applications. Since the only substantial (or otherwise effective) mechanical connection to bender disk 14 of
For example, a system similar to that depicted in
Embodiments of the reaction-drive system are simple and robust requiring relatively little precision in assembly. In embodiments driven by bender actuators, there are no air gaps associated with electromagnetic and voice-coil type actuators, and the system is tolerant of non-axial oscillations.
As a result of using an unclamped bender actuator (or an effectively unclamped bender actuator) to drive a separate fluidic diaphragm, the bender actuator may be effectively considered a force source as opposed to a displacement source. Many different piezo bender shapes and topologies can be used within the scope of most embodiments of the present invention. For example, uni-morph and bi-morphs benders having rectangular, square, polygon symmetry may be used in some embodiments of the present invention. Bender actuator designs may be optimized for use in some embodiments of the present invention by considering the tradeoffs among bender characteristics such as actuator material, stiffness, mass, mass distribution, force output, and the bender's mechanical resonance frequency. Also, any bender that undergoes bending deflections in response to an applied voltage may be used with the reaction-drive system of most embodiments of the present invention. Uni-morph, bi-morph and multilayer benders can be constructed from a number of different classes of ceramics, piezo-polymer composites such as PVDF, crystalline materials, magnetostrictive materials, electroactive polymer transducers (EPTs), electrostrictive polymers and various “smart materials” such as shape memory alloys (SMA) actuators made from materials such as Nitinol, could be used for example. Another class of PZT bender is a radial field PZT diaphragm (RFD) which could also be employed in the present invention. In summary, any material that bends in response to the cyclic application of energy could almost certainly be employed as a bender in the reaction-drive system within the scope of the current invention and is collectively referred to as a “bender actuator” herein.
Reaction-Drive System TuningIn most embodiments of the present invention, tuning of the system components is performed to vary (e.g., increase/maximize) the power transferred from the bender actuator to the fluidic load and to vary the power transfer efficiency. For a given bender actuator, the power delivered to the fluid load may be optimized in a number of ways. In such embodiments, the system resonance typically should be within the useful operating range of the bender actuator. As discussed above, the system resonances may be varied through, for example, the selection of both the combined mechanical and fluidic spring stiffness and the combined effective moving masses of the system. In
The role of the reaction mass as may be used in some embodiments will now be explained. If the effective moving mass at the bender actuator's perimeter is relatively small, then much of the bender's force output may be shunted into oscillating the bender's perimeter between the displacement extremes 16 and 17 shown in
Some embodiments of the present invention may be improved by taking power factors into consideration. A typical power factor is expressed in the form of cos θ, where θ is the time phase angle between a time varying force F(t)=F cos(ωt) and the resulting velocity V of the driven component so that the delivered power is FV cos θ. For maximum power transfer to the load, the ideal power factor is unity, implying that θ is zero. For a given power-delivery design target, if the power factor cos θ drops below 1, then the product FV must increase proportionately to maintain the power-delivery target. Increasing F to maintain power transfer reduces efficiency and increasing V to maintain power transfer increase the stress, vibration, and resulting noise of the device. For the present invention, the bender's force is being delivered through a path that includes the bender's own internal spring. As such, the time phase θ between F and V for a given design will not necessarily be equal to zero at resonance. In order to optimize energy efficiency and minimize noise and vibration it is desirable to tune the system in order to keep the phase angle θ as close to zero as possible.
The performance of some embodiments of the present invention can be altered by the magnitude of the effective moving mass M as well as how M is distributed between the various moving components. Referring to
While all of the masses and spring constants described above may be changed in order to optimize the power factor, additional components may be added to further change (improve) the mechanical power factor. In
The tuning springs depicted in
Depending on the specific application and design of the present invention, the bending amplitude of the bender actuator may be less than, equal to, or greater than the displacement of the diaphragm and/or piston. For example, varying the ratio of MR/MD may result in the bending amplitude of the bender actuator being less than, equal to, or greater than the displacement of the diaphragm and/or piston. Further, the degree of linearity or nonlinearity of the mechanical and fluidic springs in the system may result in the bending amplitude of the bender actuator being less than, equal to, or greater than the displacement of the diaphragm and/or piston. The ratio of displacements between the diaphragm/piston and bender actuator is not necessarily a constant during operation. For some applications such as pumps or compressors, the ratio of bender-to-diaphragm/piston displacement may vary during operation from less than one, to unity, or to greater than 1.
The mechanical resonance frequency of a bender disk, with respect to the system resonance frequency, may also be of benefit in improving system performance and maximizing the mechanical power-factor. However, in some embodiments, care may be taken in the system design to prevent the system resonance frequency from coinciding with the bender disk resonance frequency. In many embodiments, the bender resonance frequency chosen may be above the expected operating range of the system. For applications such as pumps and compressors, where the system resonance frequency can change, a resonance controller may be used to keep the electrical drive frequency locked to the changing system resonance frequency. In some embodiments of the invention, the bender disk's mechanical resonance frequency may not be tuned close to the system resonance frequency, so that the two resonant frequencies are not likely to overlap during operation, thus reducing possible problems for the resonance controller due to resonance repulsion phenomena.
Axial StabilityFor the reaction-drive embodiments of
Transverse modes may be further discouraged by adding stabilizing components that may allow axial motion while rejecting transverse motion.
In
Referring to
In terms of compliance, the stiffness k of spring 318 could ideally be varied over a range whereby the constraint imposed on bender 314 would correspondingly vary over a compliance range from infinity (no constraint) to zero (completely rigid). Performance would increase with the compliance C=1/k of spring 318. For example, if the peak force of bender 314 were held constant while the compliance C of spring 318 was progressively reduced from an infinite value to a value of zero, then the displacement of diaphragm (or a piston) 304 would change from a maximum value (determined by all of the component values and fluid characteristics) to a value equal to the bender's maximum displacement. So for constant peak force, if the compliance C of spring 318 was reduced such that the displacement of diaphragm 304 were reduced 10%, then performance would be reduced by roughly 10%. If the compliance C of spring 318 was reduced such that the displacement of diaphragm 304 was reduced 20%, then performance would be reduced by roughly 20%. If the compliance C of spring 318 was reduced such that the displacement of diaphragm 304 was reduced 30%, then performance would be reduced by roughly 30%. If the compliance C of spring 318 was reduced such that the displacement of diaphragm 304 was reduced 40%, then performance would be reduced by roughly 40%. If the compliance C of spring 318 was reduced such that the displacement of diaphragm 304 was reduced 50%, then performance would be reduced by roughly 50% and so on until the compliance C of reaches a value of zero and the diaphragm or piston displacement becomes limited to that of bender 314. The preceding assumes of course that the system is being driven at or near its system resonance fo, which may shift with changing values of C. Accordingly, a secondary bender connection having a non-zero compliance is considered to be within the scope of the present invention.
Reaction-Drive PumpsThe reaction-drive methods described above provide a compact diaphragm actuator system for the diaphragm pumps and compressors of the present invention. The low profile topology of a reaction-drive system enables high-performance miniaturization of diaphragm type pumps down into the MESO and MEMS size range.
Pump body 80 of
In operation, an alternating voltage waveform of frequency f is applied to bender actuator 100 causing it to oscillate at frequency f between bending deflections such as, by way of example, those shown in
The inlet stroke occurs when diaphragm 90 is moving downward away from the upper surface 128 of compression chamber 108 and the discharge stroke occurs when diaphragm 90 is moving up towards the upper surface 128 of compression chamber 108. During the inlet stroke, the fluid pressure within compression cavity 108 drops below the fluid pressure within inlet plenum 112 and the resulting pressure difference will open inlet reed valve 124 thus allowing fluid to flow from inlet plenum 112 through inlet ports 116 and into compression cavity 108. When diaphragm 90 reaches the bottom of its stroke it reverses directions marking the beginning of the compression stroke and the fluid pressure within compression chamber begins to increase. When the fluid pressure within compression cavity 108 rises above the fluid pressure within inlet plenum 112 the resulting pressure difference will close inlet reed valve 124 thus sealing inlet ports 116 and halting the fluid flow from inlet plenum 112 into compression cavity 108. During the compression stroke, the fluid pressure within compression cavity 108 rises above the fluid pressure within discharge plenum 110 and the resulting pressure difference will open discharge reed valve 120 thus allowing fluid to flow from compression cavity 108 through outlet ports 114 and into discharge plenum 110. When diaphragm 90 reaches the top of its stroke it reverses directions marking the beginning of the inlet stroke and the fluid pressure within compression chamber begins to decrease. When the fluid pressure within compression cavity 108 falls below the fluid pressure within discharge plenum 110, the resulting pressure difference will close discharge reed valve 120 thus halting or effectively halting the fluid flow from compression cavity 108 into discharge plenum 110. In this way, a net fluid flow through pump 79 is created where fluid is drawn in through inlet passage 132 and discharged through discharge passage 134. Also assisting in the closing of the inlet and discharge valves is the spring stiffness of the valves, which will always tend to restore the valves to the closed position.
Diaphragm 90 of pump 79 in the embodiment depicted in
Pump 79 of
It is to be understood that in many other embodiments of the invention, the relative diameters of the bender actuator and the fluidic diaphragm will be different than those recited herein by example. The diameter of the bender could be either larger than or smaller than the diameter of the fluidic diaphragm. Both the force needed to drive the fluidic diaphragm as well as the pump's flow capacity increases with the diameter of the fluidic diaphragm. The diameter of the bender actuator needed to provide the desired force will vary with the type of bender actuator.
Pressurized Operation and Pressure EqualizationO-rings 82 and 84 of
For applications of pump 79 in
Pressure-induced diaphragm distortion may be reduced by increasing the stiffness of diaphragm 90. Another method of controlling pressure-induced diaphragm distortion may be to equalize=the pressure on both sides of the fluidic diaphragm 90. As shown in
The diameter of pressure equalization hole 136 may be chosen to provide a pressure equalization time-constant that is many pumping cycles in duration. If the flow rate time-constant is to short (hole to large), then the pump's flow capacity and efficiency might be reduced since energy might be wasted pumping fluid in and out hole 136 each pumping cycle. If the flow rate time-constant is relatively long (e.g., the hole is to small), then pressure equalization could be to slow to prevent diaphragm distortion. Sizing of hole 136 may be determined from orifice flow calculations based on a given pressure differential across the hole and the volume of actuator chamber 138. As an alternative to diaphragm hole 136, drillings through the pump body 80 could be used that connect the compression chamber 108 to actuator chamber 138.
Clearance VolumeIn most embodiments of the present invention, the compression ratio that may be achieved is based on the pump's clearance volume, since the compression ratio=(Vs+Vc)/Vc where Vs is swept volume and Vc is clearance volume. The clearance volume is the volume of the compression chamber when the diaphragm is at the top of its stroke.
When diaphragm 90 of pump 79, in
The compression chamber heights and contours shown in
For some embodiments of the present invention, the particular design may represent a compromise between low clearance volume and the way in which the spring properties of fluid within the compression cavity affect the system dynamics. A low clearance volume can result in less fluid remaining at the end of a compression stroke and thus less fluid spring stiffness and associated restoring force. If a very low clearance volume is desired then mechanical springs can be added to compensate for the lost fluidic spring stiffness. Such mechanical springs can take the form of alignment disk 76 in
Many other embodiments for reducing clearance volume will occur to those that are skilled in the art for reducing clearance volume. Other variations in how a piston can interface with the compression chamber to reduce clearance volume is seen in the prior art patents U.S. Pat. No. 3,572,908, U.S. Pat. No. 6,514,047, G.B. Pat. 428,632, G.B. Pat. 700,368, and U.S. Pat. No. 4,874,299, the contents of which are incorporated herein by reference in their entirety.
ValvesThe relatively high operating frequencies of the present invention mean that passive valve designs often will take into consideration certain fluidic and mechanical dynamics issues that become increasingly important at higher frequencies. These frequency-related effects include, for example, the inertia and spring stiffness of the moving valves and related opening and closing times, inertial timing effects of the fluid as it is accelerated through the valve and valve port flow path, and the effect that the size and cross-sectional profile of the valve ports has on fluid flow timing. These parameters may be used to enhance the flow and pressure performance of a given pump design and can be successfully modeled with a number of numerical lumped-element models. In pumps of some of the embodiments, reed valves without valve stops may be used in order to provide low profile valves. When valve stops are absent the valves must be tuned by choosing the proper valve stiffness and valve mass in order to achieve good valve timing for a particular pump operating frequency, flow, and compression ratio.
Some embodiments of the present invention can operate without moving mechanical valves, such as reed valves, by proper tuning of the valve ports. Valve port tuning may take the form of various valve port types that are well known in the art such as diffuser valves, nozzle valves, and Tesla valves, to name a few. These valve ports typically present a changing cross-sectional area to the fluid flow passing through the port and are designed to present a low flow-impedance in one direction and a high flow-impedance in the opposite direction. This difference in directional flow impedances creates a rectifying effect that converts an oscillating flow into a net flow in one direction. Although tuned ports alone cannot provide the flow and pressure performance of mechanical valves, such as reed valves, they provide simplicity and reliability and can be scaled to small sizes and high frequencies.
Pumps of some embodiments of the present invention may also use actuated valves that may be actuated by bender actuators, electromagnetic actuators, electrostatic actuators, or other actuators that can provide the displacement and frequency response required by a given application. Pumps according to some embodiments may also employ valve stops that limit the opening height of valves in order to optimize valve performance as in well known in the art of pump valves.
In operation, a voltage waveform of frequency f is applied to bender actuator 176 which excites the system resonance of pump 172, as described previously, and fluidic diaphragm 180 oscillates in response between two displacement extremes, thereby causing the fluid pressure within compression cavity 196 to oscillate at frequency f. In response to the oscillating fluid pressure within compression cavity 196, inlet valve 184 and outlet valve 188 open and close in sequence once per cycle, thereby drawing a low pressure fluid in through pump body inlet 194, through actuator chamber 200, through inlet ports 182 and into compression chamber 196, and then discharging a high pressure fluid through outlet ports 186, through outlet plenum 198, and out of pump 172 through pump body outlet 192. Locating the inlet ports and inlet reed valves on standoff 178 provides design flexibility and enables further downsizing of the pump. Another advantage is that the motion of the piston will provide a natural actuation of the inlet valves, where the inertia of the valve and the motion of the piston will tend to open and close the valve in proper phase with the pressure cycle.
A simple redesign of the reed valves, for pump 172 of
In some embodiments of the present invention, the higher the fluid compression, the greater the potential vibration amplitudes of the pump.
Pump 202 is further provided with a second bender actuator 220, a second standoff 222 having its upper end rigidly connected to second bender actuator 220 and its upper end rigidly connected to second fluidic diaphragm 224. Second standoff 222 is provided with six inlet ports 226 on a circle, where only two of the six outlet ports 226 are shown in the plane of the cross-sectional view of pump 202. An inlet reed valve 228 is mounted flush to lower surface 230 of second fluidic diaphragm 224, so that the petals of inlet reed valve 228 cover inlet ports 226. The central area 232 of inlet reed valve 228 is rigidly attached to lower surface 230 of second fluidic diaphragm 224 so as to leave the petals of inlet reed valve 228 free to open and close in a cantilever fashion. Pump 202 is also provided with a pump enclosure comprising a cylindrical housing 236, an upper enclosure cap 238 and a lower enclosure cap 240. Cylindrical housing 236 has housing inlet 250 and housing outlet 248. Cylindrical housing 236 is connected to pump body 204 by a resilient annular ring 242 which provides a pressure seal between discharge plenum 244 and inlet plenum 246.
In operation, a voltage waveform of frequency f is applied to both first and second bender actuators 206 and 220, thus causing both first and second fluidic diaphragms 210 and 224 to oscillate in response between their respective displacement extremes. The voltage waveform of frequency f is applied to first and second benders actuators 206 and 220 with the same time phase, thereby assuring that each fluidic diaphragm will traverse their compression and inlet strokes in unison and thereby causing the fluid pressure within compression cavity 234 to oscillate at frequency f. In response to the oscillating fluid pressure within compression cavity 234, outlet valve 214 and inlet valve 228 will open and close in sequence once per cycle, thereby drawing a low pressure fluid in through housing inlet 250, through inlet plenum 246, through inlet ports 226 and into compression chamber 234, and then discharging a high pressure fluid through outlet ports 212, through outlet plenum 244, and out through housing outlet 248.
Pump 202 of
Pump 202 of
The pump embodiments of the present invention rely on the system's mechanical resonance to provide large fluidic diaphragm displacements. Changing operating conditions may shift the system's resonance frequency. For example, the pumps of the present invention may be nonlinear mechanical oscillators in that their system resonance frequency may change with drive amplitude. As such, a resonance controller may be used when the application calls for changes in drive voltage in order to change the pump's flow capacity and pressure. One exemplary resonance controller is shown in
Many other resonance control methods can be used. For example, the parameter being maximized by the resonance controller could be a signal provided by a displacement sensor proximal to the bender actuator, a pressure sensor at the pump's outlet, or an accelerometer attached to the pump body. Another approach would be to use a phase locked loop PLL to maintain a target time phase angle between drive voltage and current that corresponds to a desired drive frequency being equal to or near the system resonance frequency.
For pumps having two opposed fluidic diaphragms, such as pump 202 of
In operation, function generator 270 provides a voltage waveform of frequency f to first and second amplifiers 264 and 266 where each amplifier delivers respective amplified voltage waveforms to the first and second bender actuator 280 and 282 of pump 262. For a given voltage amplitude Vo, microprocessor 268 measures the time varying voltage V(t) across the terminals of bender actuators 280 and 282, measures the time varying current I(t) across resistors 272 and 274, and measures the time phase angles φ between the respective V(t) and I(t) of bender actuators 280 and 282. Microprocessor 268 then calculates the electrical power factor cos φ and then calculates the delivered electrical power P=V(t)·I(t)·cos φ for each bender actuator. The delivered electrical power P reaches a maximum at the system resonance frequency fo. Thus microprocessor 268 keeps the drive frequency f of function generator 270 close to the system resonance frequency fo by continuously running a search routine that makes incremental changes in frequency f and then determines if P has increased or decreased. If P decreases for a given frequency change, then microprocessor 268 makes a step change in frequency of having an arithmetic sign that is opposite to the previous frequency change step. If P increases for a given frequency change, then microprocessor 268 makes a step change in frequency having the same arithmetic sign as the previous frequency change step.
Running simultaneously with the resonance controller of
Another application of the reaction-drive system according to some embodiments of the invention is in the actuation of synthetic jets.
In operation the bender actuator 288 drives fluidic diaphragm 292 at a frequency f so that energy is stored in the system resonance and thus allows the displacement of fluidic diaphragm 292 to exceed the bending displacement of bender actuator 288. The displacement oscillations of diaphragm 292 creates an oscillating pressures within cavity 296 at frequency f thus causing the fluid to oscillate back and forth in port 298 at frequency f. As is known in the art of synthetic jets, the oscillation of the fluid within port 298 creates a pulsating jet of flow that proceeds away from synthetic jet 286 along the cylindrical axis of port 298. One possible result of using a reaction-drive diaphragm actuator is that more energy can be transferred to the fluid in the same sized unit resulting in higher jet flows.
Fluid ApplicationsThe reaction-drive actuator according to some embodiments of the invention may be applied in a number of applications where energy needs to be applied to fluids and especially for smaller sized fluid applications. The reaction-drive actuator according to some embodiments may be employed for applications such as atomizers for any number of liquids including fuels; mixers for fuels, gases, 2-phase mixing such as with liquids and gases, and powders; micro-reactors for chemical manufacturing, mixing in connection with respiratory drug delivery. The pumps according to some embodiments may be employed wherever pumps and compressors are found in consumer, commercial, industrial, medical, and scientific applications and are particularly advantageous where small size, high performance, low noise, and low vibrations are required. Pumps of the present invention can further be employed in applications including the general compression of gases such as air, hydrocarbons, process gases, high-purity gases, hazardous and corrosive gases, as well as the compression of phase-change refrigerants for refrigeration, air-conditioning and heat pumps, and other specialty vapor-compression heat transfer applications.
Some embodiments of the pump described herein may be used with various consumer and industrial products. By way of example only, some pumps may be used with miniaturized fuel cells for portable electronic devices, such as portable computing devices, PDAs and cell phones, self-contained thermal management systems that can fit on a circuit card and provide cooling for microprocessors and other semi-conductor electronics, and portable personal medical devices for ambulatory patients, etc. Thus, the present invention extends to apparatuses and systems, and methods of using the pumps in such a manner.
The present invention includes methods of practicing the invention, software to practice the invention, and apparatuses configured to implement the present invention. Accordingly, the present invention includes a program product and hardware and firmware for implementing algorithms to practice the present invention, as well as the systems and methods described herein, and also for the control of the devices and implementation of the methods described herein. Thus, by way of example, the present invention includes a processor with logic to control a pump or a component of the pump according to the present invention. It is noted that the term “processor,” as used herein, encompasses both simple circuits and complex circuits, as well as computer processors.
While the present invention enables miniaturization, the scope of the present invention is in no way limited to embodiments of any given size. Various embodiments and enhancements of the present invention are disclosed herein and it will occur to those skilled in the art to use many different combinations of these embodiments and enhancements. All of the various combinations of these embodiments will be determined by the requirements of a given application and are considered within the scope of the present invention. For example, the number of valves used, whether or not added axial stability is required, the use of one or two diaphragms, whether or not controls are needed, the types of methods used for joining components, the type of bender actuator used, the types of seals used, and the use of pumps in series or parallel will all be determined by the performance and cost requirements of a given application. Other examples of applications within the scope of the present invention that will occur to those skilled in the art would be to locate a single bender actuator between two back-to-back fluidic diaphragms with each diaphragm having their own compression chambers so as to drive the two diaphragms with the single bender actuator in a push-pull configuration. Further, pumps of the present invention can be scaled up or down in size and can be used in closed cycle systems as well as open systems as will be evident to those skilled in the art.
The foregoing description of some of the embodiments of the present invention have been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention to a precise form disclosed, and obviously many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles of the invention and its practical application to thereby enable others skilled in the art to best utilize the invention in various embodiments and with various modifications as are suited to the particular use contemplated. Although the above description contains many specifications, these should not be construed as limitations on the scope of the invention, but rather as an exemplification of alternative embodiments thereof.
Claims
1. A fluid energy transfer device, comprising:
- a chamber for receiving a fluid, at least a portion of the chamber comprising a movable portion relative to another portion of the chamber, the movable portion being adapted to change the volume of the chamber from a first volume to a second volume by movement of the movable portion; and
- a bender actuator attached to the movable portion;
- wherein the bender actuator is at least one of (i) connected directly to the movable portion and (ii) linked to the movable portion, to form a bender-movable portion assembly;
- wherein the bender is effectively not connected and effectively not linked to any other component of the device other than the movable portion; and
- wherein the bender-movable portion assembly is adapted to move substantially only due to oscillation of the bender at a drive frequency.
2. The device of claim 1, wherein the bender is connected to electrical leads adapted to conduct electricity to the bender.
3. The device of claim 1, wherein the bender is resiliently connected to a component of the device that is separate from the movable portion.
4. The device of claim 1, wherein the bender is connected, via a non-rigid connection, to a component of the device that is separate from the movable portion.
5. The device of claim 1, wherein the bender actuator is adapted to bend at a frequency such that the bender and moving portion will move between a first position and a second position substantially only due to the bending of the actuator, and wherein the distance between the first position and the second position is substantially greater than the distance of peak-to-peak bending of the actuator.
6. The device of claim 1, wherein the bender actuator is adapted to oscillate the movable portion at a frequency so as to store energy in a system resonance of the device.
7. The device of claim 1, further comprising an axial stability structure, wherein the axial stability structure is connected to the bender-movable portion assembly and adapted to permit axial movement of the bender-movable portion assembly and impeding transverse movement of the bender-movable portion assembly.
8. The device of claim 1, further comprising a controller operatively connected to the bender, wherein the controller is adapted to vary the drive frequency in response to changes in a system resonance frequency.
9. The device of claim 1, further comprising a controller adapted to monitor performance of the device, wherein performance includes at least one of flow rate of fluid exiting the device and fluid pressure of fluid exiting through the device, wherein the controller is also adapted to automatically vary a drive force of the bender in response to the monitored performance of the device.
10. The device of claim 9, wherein the controller is further adapted to automatically change the drive force of the bender actuator to automatically change a stroke distance of the movable portion from a first stroke distance to a second stroke distance different than the first stroke distance.
11. The device of claim 1, wherein the movable portion is a diaphragm.
12. A fluid energy transfer device, comprising:
- a chamber for receiving a fluid, at least a portion of the chamber comprising a movable portion relative to another portion of the chamber, the movable portion being adapted to change the volume of the chamber from a first volume to a second volume; and
- a bender actuator attached to the movable portion, wherein the bender actuator is at least one of (i) connected directly to the movable portion and (ii) linked to the movable portion, to form a bender-movable portion assembly;
- wherein the bender actuator is adapted to bend at a frequency such that the bender-diaphragm assembly will move between the first position and the second position substantially due to bending of the actuator; and
- wherein the distance between the first position and the second position is at least one of greater than and less than the distance of peak-to-peak bending of the actuator.
13. The device of claim 12, wherein the distance between the first position and the second position is at least about an order of magnitude greater than the distance of peak-to-peak bending of the actuator.
14. A fluidic system, comprising;
- the device according to claim 12; and
- a fluid, at least a portion of which is present in the chamber;
- wherein the bender actuator is adapted to be operable at a drive frequency so as to store energy in a system resonance.
15. A fluidic system, comprising;
- the device according to claim 12; and
- a fluid, at least a portion of which is present in the chamber;
- wherein the device has a system resonance frequency governed by a combined effective moving mass of mechanical components and the fluid and a combined effective spring stiffness of the mechanical components and the fluid;
- and wherein the bender actuator is adapted to be operable at a drive frequency at or near the system resonance frequency.
16. The device of claim 12
- wherein the bender is effectively not connected and effectively not linked to any other component of the pump other than the movable portion.
17. A method of moving a fluid, comprising:
- providing a pump for pumping a fluid, the pump comprising; a chamber for receiving a fluid, at least a portion of the chamber comprising a movable portion relative to another portion of the chamber, the movable portion being adapted to change the volume of the chamber from a first volume to a second volume by movement of the movable portion; and a bender actuator attached to the movable portion;
- oscillating the bender at a drive frequency so that forces are transmitted, in reaction to the oscillations of the bender, to the movable portion, causing the movable portion to be displaced in a manner such that a displacement distance of the movable portion is at least one of greater than or less than a peak-to-peak bending displacement of the bender encountered during oscillation of the bender, and
- drawing fluid into the chamber by moving the movable component to increase the volume of the chamber.
18. The method of claim 17, further comprising oscillating the bender at a frequency to obtain a displacement distance of the movable portion that exceeds a maximum peak-to-peak bending displacement of the bender encountered during oscillation of the bender by at least about an order of magnitude.
19. The method of claim 17, further comprising oscillating the bender at a drive frequency that is at least one of near and equal to a system fundamental resonant frequency of the pump.
20. The method of claim 17, further comprising oscillating the bender at a drive frequency so that forces are transmitted in reaction to the oscillations of the bender to the movable portion causing the movable portion to be displaced in a manner to store energy in a system resonance to obtain a displacement distance of the movable component that exceeds a maximum peak-to-peak bending displacement of the bender encountered during oscillation of the bender.
21. The method of claim 17, further comprising:
- opening an inlet to the chamber and closing an outlet to the chamber;
- closing the inlet to the chamber and opening the outlet to the chamber;
- wherein, to draw fluid into the chamber, the action of opening the inlet to the chamber and closing the outlet to the chamber is coordinated temporally with a first movement of the movable portion that increases the volume of the chamber;
- wherein, to direct fluid out of the chamber, the action of closing the inlet to the chamber and opening the outlet of the chamber is coordinated temporally with a second movement of the movable portion that decreases the volume of the chamber;
- wherein fluid flows into the chamber at least during a portion of the time that the inlet is opened; and
- wherein fluid flows out of the chamber at least during a portion of the time that the outlet is opened.
22. The method of claim 17, wherein the bender actuator of the pump is at least one of (i) connected directly to the movable portion and (ii) linked to the movable portion,
- wherein the bender is effectively not connected and effectively not linked to any other component of the device other than the movable portion.
23. The method of claim 17, further comprising oscillating the bender actuator to oscillate the movable portion at a frequency so as to store energy in a system resonance of the pump.
24. The method of claim 22, wherein the bender is connected to electrical leads adapted to conduct electricity to the bender.
25. The method of claim 22, wherein the bender is resiliently connected to a component of the device that is separate from the movable portion.
26. The method of claim 17, further comprising operating the bender at a drive frequency so as to store energy in a system resonance of the pump, the system resonance frequency being governed by a combined effective moving mass of mechanical components and the fluid and a combined effective spring stiffness of the mechanical components and the fluid.
27. The method of claim 17, further comprising operating the bender at a drive frequency at or near a system resonance frequency of the pump.
28. A fluid energy transfer device, comprising:
- a chamber for receiving a fluid, at least a portion of the chamber comprising a movable portion relative to another portion of the chamber, the movable portion being adapted to change the volume of the chamber from a first volume to a second volume by movement of the movable portion; and
- a bender actuator attached to the movable portion;
- wherein the bender actuator is at least one of (i) connected directly to the movable portion and (ii) linked to the movable portion, to form a bender-movable portion assembly;
- wherein the bender is at least one of (a) not rigidly connected and (b) not rigidly linked to any other component of the device other than the movable portion; and
- wherein the bender-movable portion assembly is adapted to move substantially only due to oscillation of the bender at a drive frequency.
29. A refrigerant system, comprising:
- a refrigerant compressor including the device of claim 1;
- a condenser;
- a pressure drop capillary tube; and
- an evaporator;
- wherein the refrigerant compressor, the condenser, the pressure drop capillary tube, and the evaporator are in a refrigerant loop.
30. A refrigerant system, comprising:
- a refrigerant compressor including the device of claim 12;
- a condenser; and
- an evaporator;
- wherein the refrigerant compressor, the condenser and the evaporator are in a refrigerant loop.
31. A method of transferring heat, comprising:
- imparting movement on and providing pressure lift to a refrigerant by executing the method of claim 17, wherein the liquid is the refrigerant, to move gaseous refrigerant from an evaporator to a condenser to condense the refrigerant.
32. A pump, comprising:
- the device of claim 1;
- a fluid inlet port in fluid communication with the chamber; and
- a fluid outlet port in fluid communication with the chamber;
- wherein the device is adapted to draw fluid into the chamber through the inlet port during movement of the movable portion in a manner that increases the volume of the chamber, and
- wherein the device is adapted to expel fluid out of the chamber through the outlet port during movement of the movable portion in a manner that decreases the volume of the chamber.
33. A fluidic device, comprising:
- a synthetic jet, wherein the synthetic jet includes the device of claim 1.
34. A pump, comprising:
- the device of claim 12;
- a fluid inlet port in fluid communication with the chamber; and
- a fluid outlet port in fluid communication with the chamber;
- wherein the device is adapted to draw fluid into the chamber through the inlet port during movement of the movable portion in a manner that increases the volume of the chamber, and
- wherein the device is adapted to expel fluid out of the chamber through the outlet port during movement of the movable portion in a manner that decreases the volume of the chamber.
35. A fluidic device, comprising:
- a synthetic jet, wherein the synthetic jet includes the device of claim 12.
36. The device of claim 1, wherein, with the exception of electrical leads, the bender is not connected to a component that is separate from the movable portion.
Type: Application
Filed: Dec 22, 2005
Publication Date: Dec 11, 2008
Applicant:
Inventor: Timothy S. Lucas (Providence Forge, VA)
Application Number: 11/793,441