HK1213964B

HK1213964B - Fluidic methods and devices

Info

Publication number: HK1213964B
Application number: HK16101946.5A
Authority: HK
Inventors: 马瑞森布鲁斯
Original assignee: 奥博迪克斯股份有限公司
Priority date: 2012-09-28
Filing date: 2013-09-26
Publication date: 2019-07-26

Abstract

A device for use by an individual for sexual pleasure varying in form, i.e. shape, during its use and allowing for the user to select multiple variations of form either discretely or in combination and for these dynamic variations to be controllable simultaneously and interchangeably while being transparent to the normal use of the device, including the ability to insert, withdraw, rotate, and actuate the variable features manually or remotely. According to embodiments of the invention localized and global variations of devices are implemented using fluidics and electromagnetic pumps/valves wherein a fluid is employed such that controlling the pressure of the fluid results in the movement of an element within the device or the expansion/contraction of an element within the device.

Description

Fluid method and apparatus

Cross reference to related application

This patent application claims priority to 61/705,809 entitled "method and device for fluid driven adult devices" filed on 9/26/2012.

Technical Field

The present invention relates to fluid devices, and more particularly to solenoid actuated pumps, valves and switches.

Background

With the increasing acceptance of sexual and masturbation, the market for sexual and pleasure devices (also called sex toy) has grown and evolved into "network sexual love", "telephone sexual love" and "network live sexual love". A sex toy is an article or device used primarily to promote human sexual enjoyment and is generally designed to resemble the human genitals, with or without vibration. Heretofore, there have been a wide variety of sexual pleasure devices in the old times of stoneware as early as ancient greeks to 30000 b.c., but they have been mainly pretended by using a polite name and a word of "massage". Modern devices of this type are largely divided into two categories: mechanized and non-mechanized devices. In fact, a first electric vibrator patent was obtained in 1902 by a company known as Hamilton Beach, a product commercially available at retail, which made the vibrator a fifth electrified household appliance. Mechanized devices typically vibrate, but some rotate, plug, and even circulate beads within an elastomeric housing. Non-mechanized devices are constructed of solid bodies of rigid or semi-rigid materials of various shapes.

The vibrator generally operates by operation of a motor to which a small weight is attached off-axis to cause the motor to vibrate, and the portion of the body of the vibrator is attached to the motor. The vibrator may be powered by connection to an electrical outlet, but is typically powered by a battery. The battery drive is focused on efficiency, not only is effective vibration achieved, but also the user does not feel that the battery is consumed quickly by the vibrator after a long period of time. For example, a typical vibrator uses 2 or 4 size five cells, and in the case of an alkaline cell, each cell has a nominal voltage of 1.5V and a capacity of 1800mAh to 2600mAh at a leakage current of 500 mA. Thus, each cell at this nominal leakage current can provide 0.75W for 3-5 hours, so that a vibrator containing 2 cells of five cells that can provide this life will only consume 1.5W, while a vibrator containing 4 cells of five cells will consume less than 3W. The more batteries used, which are typically placed in a relatively narrow range of physical dimensions approximately equal to the average penile insertion length and have an exterior for grasping by the user, the more space is occupied by the device, complicating the design. In general, compact sex toys have been more successful than larger size sex toys because the latter have power requirements.

However, such motors with off-axis weights do not easily operate at low frequencies when trying to induce excitement to the user in a way that simulates physical intercourse (when the frequency of stimulation is low or low and the amplitude is high or high). The user wants to obtain vibrations with low frequency and high amplitude, but prior art vibrators have failed to achieve this. For example, when operation below 40Hz, 10Hz, 4Hz, and 1Hz is not available, the smaller dc motor is not able to generate a larger torque at a lower number of Revolutions Per Minute (RPM), and thus is not able to move a larger weight to generate a larger amplitude. Generally, the RPM value in this case reaches several thousands. In this way, the reduced weight may reduce the required torque, thereby further reducing vibration. The vibrator operates in this mode with high frequency and low amplitude vibrations. It would be further advantageous if the system could be operated in a manner that switches freely between high and low frequency operation or in a manner that couples high frequency operation, and provides a user with a settable high amplitude simulation and reduced amplitude operation.

There are a wide variety of vibrator types available to the market today, but they are broadly classified into the following categories:

clitoris: clitoral vibrators are fun items that provide sexual pleasure and improve orgasm quality by stimulating the clitoris. While most vibrators are available for use as clitoral vibrators, vibrators designed specifically for use as clitoral vibrators have a particular design, which is different from the shape of the vibrator, and are generally not penile-shaped. For example, the most commonly used penile vibrators are small, egg-shaped and secured within a multi-speed battery pack by flexible wires. Variations of the basic design typically include finer bullet-shaped vibrators and animal-shaped vibrators. In some cases, the clitoral vibrator is part of a vibrator having a second portion that is inserted into the vagina, often comprising a small animal, such as a rabbit, bear or dolphin, positioned near the bottom of the inserted vibrator, facing forward, providing clitoral stimulation while stimulating the vagina. In the prior art, clitoral stimulators include U.S. patents No. 7,670,280 and No. 8,109,869, and U.S. patent application No. 2011/0,124,959.

In other cases, such as the We-Vibe clitoral vibrator is part of one vibrator, while another part is designed to touch the "G-point". In the prior art, such combination vibrators include U.S. patent No. 7,931,605, U.S. design patents No. 605,779 and 652,942, and U.S. patent application No. 2011/0,124,959.

Artificial penis: typically, such devices are generally penile-shaped and may be constructed of plastic, silicon, rubber, vinyl, or latex. Artificial penis is a common name for phallus-like sex but does not provide any type of vibration. However, because vibrators are often penile in shape, there are a variety of different artificial penis vibration patterns and designs, including designs for use by two individuals having a partner at the same time, insertion into the vagina and anus, and for oral intercourse, some even double-ended designs.

Rabbit-shaped: as described above, two different sizes of vibrators are included. One is a phallic vibrator for insertion into the user's vagina and the other is a smaller clitoral stimulator with the first vibrator inserted to fit snugly against the clitoris. The rabbit vibrator is named in the shape of a clitoral stimulator as it looks like a pair of rabbit ears.

And point G: such devices are generally curved and typically have a soft jelly-like outer layer for easy application to stimulate the G-spot or prostate area. Such devices are typically curved toward the tip and are made of a material such as silicon or acrylic.

Egg-shaped: typically a small smooth vibrator designed to stimulate the clitoris or insertion. Such devices are generally considered to be less obtrusive sex items because they are no longer than 3 inches in length and are between about 1 inch and 1 inch wide, making them stand alone, and particularly at all times.

Anus: generally, anal vibrators are designed with a flared bottom or long handle for gripping to avoid slipping inside and being trapped inside the rectum. Anal vibrators come in a variety of shapes, but are typically anal insertion or penile vibrators. It is generally recommended to apply a large amount of lubricant at the time of use, and to insert gently, taking care to avoid potential damage to the rectal tissue.

Cock finger ring: generally referred to as a vibrator for insertion into or attachment to a cock ring, primarily to enhance clitoral stimulation during intercourse.

Pocket rockets (also called bullets): typically, one of the ends is cylindrical and contains a vibrating raised portion, primarily for stimulating the clitoris or nipple, rather than for insertion purposes. Typically, the pocket rocket is a small vibrator, about 3 to 5 inches long, shaped like a small travel flashlight, used as a casual fun, carried about, placed in a user's purse, or the like. Because of its small size, it is generally driven by a single battery, and its control is limited; some have even only one speed gear.

Butterfly: generally, a vibrator comprising a leg and a waist strap is used to stimulate the clitoris without using both hands during sexual intercourse. Generally, such vibrators come in three forms, traditional, remote and anal and/or vaginal stimulators, often made of silicone, soft plastic, latex or jelly.

In addition to the general categories described above, the following types are also included, but not limited to:

● dual vibrator designed to stimulate one or both of the two sexually sensitive bands simultaneously, most commonly designed to contain a clitoris and vaginal stimulator within the same vibrator;

● three-in-one vibrator designed to stimulate one or three sexual bands simultaneously;

● A multi-step vibrator, the speed of the pulsating or massaging action of which can be adjusted by the user, typically by providing a plurality of independently selectable speed settings via a button, slider, etc., or by providing a continuously variable simulation via a rotary control;

● double-ended devices, which can be used simultaneously by two users, typically two artificial penis or two vibrators, for vaginal-vaginal, vaginal-anal or anal-anal stimulation;

● nipple stimulator, designed to stimulate the nipple and/or areola by vibration, sucking and pinching;

● electrostimulator, designed to apply electrostimulation to the nerves of the body, in particular placed on the genitals for stimulation;

● A "flapping wing" stimulator having a plurality of flexible projections on a ferris wheel assembly for simulating oral crossing; and

● A male stimulator, generally a soft silicone sheath, is provided to wrap the penis and stimulate it by rhythmic movement.

The devices described in the above prior art are mechanically actuated by linear and/or rotary motors to achieve the desired body stimulation. In practice, however, fluids may be used to achieve the desired action and pressure, wherein elements within the structure are moved or expanded/contracted by using the fluid and controlling the fluid pressure. But until now the commercial use of fluids as fun articles has been limited to use as lubricants or glues when using the device to reduce friction and subsequent pain/discomfort when the natural lubrication of the device is low for prolonged use or the user using the device. In the prior art, such lubricating devices include, but are not limited to: U.S. patent nos. 6,749,557 and 7,534,203 and U.S. patent application nos. 2004/0,034,315 and 2004/0,127,766.

There are still limitations and disadvantages for users using the above-described prior art devices in providing enhanced functionality, dynamic device applicability in use, and user-specific configurations, for example.

As noted above, the commercial use of fluids for devices that have been developed to date has been largely limited to the release of lubricants during use of the device, although a number of prior art references use of fluids, including, for example: U.S. patent No. 3,910,262 entitled "therapeutic apparatus," Stoughton; U.S. patent No. 4,407,275 entitled "artificial erection device," Schroeder; united states patents entitled "sexual desire stimulators" and numbers 5,690,603 and 7,998,057, Kain; U.S. patent application No. 2003/0,073,881, entitled "sexual stimulation," Levy; U.S. patent application No. 2006/0,041,210 entitled "portable sealed water jet female stimulator," Regey; U.S. patent No. 7,534,203 entitled "vibrating device with inflatable, variable attachment," Gil; U.S. Pat. Nos. 2005/0,049,453 and 2005/0,234,292 entitled "hydraulically driven vibratory massager," Faulkner.

Wherein the device of the Faulkner design has the invention of vibrating and/or rhythmically deforming elements within the device. The hydraulic drive of the Faulkner design moves working fluid into and out of the device to sequentially and repeatedly inflate and deflate the elastic elements within the device. The simple hydraulic drive of the Faulkner design, such as a hydraulic cylinder, moves through an eccentric fixed to a rotating shaft to inject or remove working fluid, causing the deformation and flow to form a sinusoidal waveform. Designs also include more complex hydraulic or computer controlled actuators that employ cams where the resulting cyclic deformation is no longer a simple sinusoidal waveform. The preferred embodiment of the Faulkner design comprises a voice coil driver comprising a solenoid-like coil directly connected to the piston shaft, wherein the piston is further in turn connected to a spring for providing a substantially horizontal pressure. Thus, a low frequency alternating current is applied to the coil, which in turn drives the shaft, which in turn drives the piston to move the working fluid in and out of the piston, and ultimately the elastic stimulator. A second immersion liquid driver of the Faulkner design, such as an electro-coil driven diaphragm or a piezoelectric crystal, is used to apply higher frequency pressure oscillations from a master piston based hydraulic oscillator to low frequency cyclic pressure oscillations. The Faulkner design includes a cyclic motion of one or more components of the apparatus by a first hydraulic shaker of the cycle and the application of the vibrating component by a second immersion hydraulic shaker.

Thus, it will be apparent to those skilled in the art that the hydraulic drive designs of Faulkner, Gil, Kain, Levy, Schroeder and Stoughton do not provide the excellent functions required above, which are not present in conventional mechanically activated known devices containing electric motors. Further, with respect to fluid pumps that may be employed as part of a hydraulic device, there are, of course, a variety of pump designs in the prior art. To date, although the prior art has contemplated fluids for fluid devices and known pumps, the hydraulic devices described above have not been developed and applied to the commercial market. This may be due to the fact that fluid pumps are bulky, inefficient, and unable to operate in the modes required by such devices, such as low frequency, variable duration, and pulsed operation for size adjustment for pumps with primary pump function, or high frequency operation for vibration and other types of motion/stimulation, for example, for pumps with secondary pump function. For example, conventional rotary pumps have low pressure at low revolutions per minute (rpm), complex motor, independent pump and multiple moving parts, and are relatively large, expensive, and even with a small impeller, the effective flow from the impeller is low.

In the prior art, for example, electromechanical drives, other pumps may be provided for the devices described below with respect to the embodiments of the invention illustrated in fig. 11-17, but other limitations and disadvantages remain. For example, a so-called voice coil linear vibration motor, compatible with improved fluid pumping technology, does not produce a strong force relative to the solenoid closing force, but increases the linearity of the force with distance. Examples include long coil-short gap magnetic along the motor axis, and short coil motors magnetic perpendicular to the motor axis. Solenoids that can provide a higher force than voice coil motors are not stable enough for the forces exerted on long stroke pistons, typically a few centimeters, and therefore constant force solenoids are used, with short strokes and increased complexity in the shape of the coil, the body and the cross-section of the plunger. In the prior art, examples of actuator-based solenoids include Magnetic Innovations FFA and MMA series actuators (www.magneticinnovations.com). Such drives are primarily designed for long strokes, large load displacement, and can replace pneumatic and hydraulic cylinders.

Another prior art is the movable magnet motor described by Astratini-Enache et al in "movable magnet type drive with ring magnet" (j. electrical engineering, vol 61, pp 144-147) and by Leu et al in "features and best design of variable air gap linear force motor" (IEEE proc.pt B, vol 135, pp 341-345), but which uses neodymium and samarium cobalt rare earth magnets to minimize motor size. Petrescu et al, in "small actuator research with permanent magnets" (adv.electric. & comp.eng., volume 9, pages 3-6), add a fixed magnet to either end of a movable magnet actuator when no activation is provided due to robotics requirements to determine the movable magnet position and to determine the zero activation position of the actuator, and adjust the force of the actuator and the corresponding displacement characteristics. Vladimirescu et al in U.S. patent No. 6,870,454, entitled "linear switch actuator", provides a latching actuator for microwave switching applications in which the actuator includes an armature rod containing a permanent magnet at either end to move one or the other permanent magnet out of a structural latching coil.

There are moving iron block motors in the prior art that can replace moving ferro-electric motors, see, for example, ibbrahim et al, "design and optimization of moving iron block linear permanent magnet motors for compressor reciprocation using finite element analysis" (int.j.electric. & comp.sci.ijecs-IJENS, volume 10, pages 84-90). Like the Ibrahim design, Evans et al, "permanent magnet linear drive for static and reciprocating short stroke electromechanical systems" (IEEE/advanced. mechanics, vol. 6, pages 36-42), wherein rare earth magnets are employed to accommodate the use of lower cost magnets, solves the eddy current problem required for magnet segmentation in prior art movable magnet linear motors. The Ibrahim, by increasing the size, magnetic loading and electrical loading, results in a final reduction in the force of the reduced strength magnet, while optimizing the design for 50Hz power supply operation. A motor 100mm (4 inches) in length and 55mm (2.2 inches) in diameter is larger than many motor sizes of prior art devices, and for devices employing fluid drivers.

Also, U.S. patent No. 5,833,440 (Berling), entitled "linear motor arrangement for reciprocating pump system," discloses a moving electromagnetic actuator utilizing pole pieces of magnetically soft material abutting permanent magnets to carry out magnetic flux in two different magnetic flux paths. In one of the channels, an armature is attracted to the pole pieces to drive the coil in motion. But in the second channel the armature is not attracted to the pole piece and there is no repulsive force, so the compression spring acts to push the armature away from the pole piece. Similarly, the removable iron block controlled drive (MICA) of Cedrat Technologies uses a pair of soft magnetic pole pieces in a magnetic field where the magnetic force is secondary in nature, i.e., only produces attraction force, and is reset, where a reset spring is provided to hold it stationary in one position.

U.S. patent No. 2006/0,210,410 (Mokler) discloses a pump comprising a pair of electromagnets disposed around a tubular member, associated with each other by a magnet. A pair of permanent magnets is arranged between the two magnets, and the outer end part of each electromagnet is provided with a permanent magnet. Thus, the permanent magnet restricts the movement of the magnet under the action of the electromagnet. Hertanu et al also disclose in "magnetic piston driven novel micropump" (j.elec.eng., volume 61, pages 148-151) permanent magnets at either end to limit the movement of the movable magnet and to determine the initial position. Hertanu also employs a ferrofluid ring at either end of the movable magnet, wherein the ferrofluid conforms to the shape of the groove and seals better, controllable by external magnetic fields.

Ibrachim, in "analysis of short-stroke, single-phase tubular permanent magnet drives for reciprocating compressors" (sixth international seminar of industrial applications for linear drives, LDIA2007, 2007), discloses a movable magnet drive in which a central moving magnet is formed by a series of radially and axially magnetized trapezoidal ring magnets stacked together, with different magnetic field directions. Therefore, the final magnet is complicated in structure and expensive. Ibrahim, t.ibrahim, j.wang and d.howe adjusted the design of the magnetized ring magnet in "single-phase, quasi-Halbach magnetized tubular permanent magnet machine analysis with non-ferromagnetic support tubes" (14 th international conference on power electronics, machines and drives IET, volume 1, pages 762-766), but still required multiple rings stacked together and simply modified the trapezoid to be rectangular. Another variation is seen in Lee et al, "linear compression for air conditioning" (2004 international conference on compressor engineering, article C047), in which the magnets are again arranged around a core and are a single element, the compressor employing a resonant spring assembly and a controller for controlling the stimulation frequency to maximize linear motor efficiency via a system resonance follow-up algorithm.

Preferably, the pumps and valves that increase the range of motion of the device are provided by overall configuration and size and local deformation, and the plurality of moving elements are actuated by a fluid that ensures that the elements within the device are moved, or expanded/contracted, by controlling pressure and/or fluid flow. As noted above, the commercial use of fluids for sexual stimulation devices or sexual pleasure that have been developed to date has been largely limited to the release of lubricants during use of the device, although a number of prior art references use of fluids, including (for example) the following. Thus, there remains a need in the marketplace for methods and apparatus that provide suitable and useful functionality. In particular, it is desirable to provide a fluid device having all the above-mentioned functions with respect to the prior art and at the same time being able to provide these functions in a deformable device and/or in a device having a deformable element. Further, it is preferable to provide a device using a fluid driver, and the driver is substantially non-mechanical and is less likely to be worn, such as a peeling prevention transmission gear, etc., thereby increasing reliability and reducing noise. Advantages of the fluidic device include high efficiency, high power and particle size ratio, and low cost, limited number or single movable parts, and the mechanical inelastic design and functional reset by the provision of the piston, both as a pump and as a vibrator.

Other aspects and features of the present invention will become apparent to those ordinarily skilled in the art upon review of the following description of specific embodiments of the invention in conjunction with the accompanying figures.

Disclosure of Invention

The object of the present invention is to reduce the limitations of the prior art relating to fluid devices, in particular solenoid-driven pumps, valves and switches.

According to an embodiment of the present invention, there is provided an apparatus including:

an electromagnetically driven pump for pumping fluid from the inlet to the outlet; and

one end of the fluid container is connected with the electromagnetic drive pump, and the other end of the fluid container is connected with the fluid system; wherein

The fluid container comprises a first preset part with first preset elasticity and a second preset part with second preset elasticity, wherein the second preset elasticity is smaller than the first preset elasticity, the second preset part deforms under the action of the electromagnetic drive pump, and the electromagnetic drive pump at least cannot be close to or cannot be injected into a complete fluid system according to the fact that the fluid container is arranged on the inlet side or the outlet side of the electromagnetic drive pump.

According to an embodiment of the invention, there is provided a method including:

an electromagnetically driven pump for pumping fluid in forward and reverse piston strokes;

first and second valve assemblies respectively connected to both ends of the solenoid-actuated pump, each valve assembly including an inlet check valve, an outlet check valve, and a valve body, wherein the valve body includes a port connected to the solenoid-actuated pump for fluid control, a port connected to the inlet check valve, and a port connected to the outlet check valve; and

a first fluid reservoir disposed before the inlet check valve or after the outlet check valve; wherein

The first fluid container comprises a first preset part with first preset elasticity and a second preset part with second preset elasticity, the second preset elasticity is smaller than the first preset elasticity, the second preset part deforms under the action of the electromagnetic drive pump, and the electromagnetic drive pump at least cannot be close to or cannot be injected into a fluid system connected with the electromagnetic drive pump according to the fact that the fluid container is arranged on the inlet side or the outlet side of the electromagnetic drive pump.

the electronic coil wound on the winding drum is arranged, the winding drum is provided with an inner tubular hole opening, the diameter of the hole opening is at least the diameter of the piston, the two ends of the winding drum are both preset conical profiles, the diameters of the conical profiles are gradually increased towards the two ends of the winding drum, and the preset conical profiles are determined according to the design performance of the electromagnetic driving device.

Providing a pair of electrically insulating thin washers such that the assembly is directly connected on either side of the coil, each washer having an inner diameter at least equal to the maximum predetermined diameter of the bobbin;

providing a pair of inner washers on either side of the coil, each inner washer being closely adjacent to an electrically insulating thin washer, wherein each inner washer includes a disc having a predetermined thickness and a protrusion on an inner edge of the coil matching a predetermined tapered profile of the bobbin;

providing a pair of magnets on either side of the coil, each magnet being located adjacent to one of the inner washers;

providing a pair of outer washers on either side of the coil, each washer being adjacent to one of the magnets;

assembling the electric coil, the pair of electrically insulating thin washers, the pair of inner washers, the pair of magnets, and the pair of outer washers in a correct order in a jig, wherein the jig includes a central annular rod for determining a minimum diameter of the cylinder, which is smaller than the minimum diameter of the bobbin by a preset amount;

sealing the assembled components in a fixture; and

the seal assembly is disassembled for subsequent insertion of a piston of predetermined dimensions into a cylinder formed in the seal material to place the electromagnetic drive under appropriate electrical control.

According to one embodiment of the invention, there is provided a method of:

providing an electromagnetic drive device comprising at least one piston having a predetermined outer diameter profile along its length and a predetermined gap and tolerance relative to a cylinder formed within an electromagnetic drive motor within which the piston moves; wherein

The outer diameter of the piston is profiled at least in accordance with the characteristics of the piston stroke in the electromagnetic drive, and the fluid in which the piston moves is ensured to be above a predetermined minimum piston velocity to generate sufficient hydrodynamic pressure to generate sufficient lift on the piston to counteract the magnetic attraction of the offset positioning of the shaft and avoid surface-to-surface contact between the outer surface of the piston and the inner surface of the cylinder.

According to one of the embodiments of the present invention, there is provided a method including:

simulating the dynamics of a piston moving in a fluid within an electromagnetically driven device, with at least the current induced force as an output, the simulation being operable to determine piston position, fluid pressure, and piston velocity over time;

establishing a force signal profile that transfers energy to the entire stroke and allows the piston to traverse the entire desired piston length;

drawing a force signal curve by an optimization method, wherein the average current of a specific force curve is the minimum value;

and converting the finally formed force signal curve into an applied electric driving signal curve so as to provide a signal for an electronic control circuit to control current distribution and drive the electromagnetic driving device.

an electromagnetic drive apparatus, the apparatus comprising:

a piston of a predetermined shape including a plurality of grooves of a predetermined depth formed along an axis thereof;

a pair of washer-magnet-washer assemblies, each disposed on either side of an electromagnetic coil of the electromagnetic drive, wherein each washer has a groove cut through the thickness of the inner rim to the outer rim; wherein

The grooves formed in the pistons and the washers reduce the formation of radial or annular vortices in the respective pistons and washers.

an electromagnetic drive device;

a fluid reservoir which acts as a low pass fluid filter in combination with other components of the fluid system to smooth out pressure fluctuations caused by operation of the electromagnetic drive within a first predetermined frequency range; and

a control circuit providing a first signal to drive the electromagnetic drive and a second signal to drive the electromagnetic drive at a frequency within a first predetermined frequency range, wherein the oscillating signal is higher than the low aeration short frequency of the low pass fluid filter; wherein

The pulsating fluid output generated by the second signal is connected to the fluid system, but the pulsating fluid output generated by the first signal is filtered to provide a preset fluctuating constant fluid flow from the electromagnetic drive.

a pressure valve, wherein when the applied fluid pressure exceeds a preset value, the pressure valve is opened such that an elastic force of a spring connected to a ball bearing located in the seat and sealing an inlet in the pressure valve cannot hold the ball bearing at a prescribed position in the seat;

a drive pin operated by the driver between a first position that prevents movement of the ball bearing and a second position that allows movement of the ball bearing and having an end profile that resets the ball bearing into the base upon transition to the first position; and

and the control circuit is used for receiving an external control signal and controlling the driver therein.

a) providing a setup program that performs the act of associating the functional elements of the personalized device;

b) automatically changing the orientation of an action associated with a functional element of the device between a first predetermined value and a second predetermined value in a predetermined number of steps until an input is received from the individual; and

c) the step (b) is terminated when the individual provides an input in one of the plurality of graphs associated with the device, the individual input is received and the value associated with the action aspect is stored.

Drawings

Embodiments of the invention are described below, by way of example, and with reference to the accompanying drawings, in which:

FIG. 1 is a schematic diagram of parallel and series element actuation using fluidic elements in conjunction with a fluid pump, reservoir, and valve according to an embodiment of the present invention;

FIG. 2 is a series element configuration utilizing a secondary fluid pump and fluid elements in combination with a primary fluid pump, reservoir and valve, according to an embodiment of the present invention;

FIG. 3 is a diagram of an apparatus for adjusting the orientation of the apparatus during use using a fluidic element, according to one embodiment of the present invention;

FIG. 4 is a diagram of an apparatus for adjusting the orientation of primary and secondary elements of the apparatus during use using a fluid element, according to one embodiment of the present invention;

FIG. 5 is a device for providing a sucking, vibrating or moving sensation with a fluid element according to an embodiment of the present invention;

FIG. 6 is one embodiment of the present invention with the fluid actuated devices disposed within a garment;

FIGS. 7A and 7B are flow diagrams of a setup for a device utilizing fluidic components having one or more functions according to embodiments of the present invention according to the preferences of a user of the device;

FIG. 8 is a flow chart of establishing personalized settings for a device utilizing a fluidic element and subsequent storage/retrieval from a remote location in accordance with an embodiment of the present invention;

FIG. 9 is a flow chart of establishing a personalized setting for a device utilizing a fluidic element and subsequent storage/retrieval of a user device or another device from a remote location according to an embodiment of the present invention;

FIG. 10 is a schematic view of a fluid-controlled inflation/deflation of a component according to an embodiment of the present invention using a fluid pump, reservoir, check valve and valve;

FIG. 11 is a schematic view of an electrically operated valve (EAV) or an electrically operated switch of a fluid system according to one embodiment of the present invention;

FIG. 12 is a schematic view of an electronically controlled pump of a fluid system according to one embodiment of the present invention;

FIGS. 13 and 14 are schematic diagrams of an electronically controlled pump for a fluid system utilizing a fluid container according to an embodiment of the present invention;

FIGS. 15 and 16 are schematic views of an electronically controlled pump for a fluid system according to an embodiment of the present invention;

FIG. 17 is a schematic diagram of an electronically controlled pump of a fluid system utilizing a fluid container, according to one embodiment of the present invention;

fig. 18 and 19 are schematic diagrams of an electronically controlled pump (ECPUMP) utilizing full circulation fluid action according to one embodiment of the present invention.

Figures 20A-20C are schematic illustrations of an assembly for mounting to an ECPUMP in accordance with one embodiment of the invention to provide an inlet and an outlet with check valves.

FIGS. 21-22D are schematic diagrams of compact and mini ECPUMP, according to embodiments of the invention;

FIGS. 23A and 23B are schematic illustrations of the operation of a compact ECPUMP having a dual inlet valve and outlet valve assembly coupled to a fluid system and such ECPUMP with and without a fluid container, according to one embodiment of the present invention;

FIG. 24 is a compact ECPUMP utilizing the motor of FIGS. 35-36, in accordance with one embodiment of the present invention;

FIGS. 25A and 25B illustrate a compact ECPUMP utilizing the motor of FIGS. 21-22B, in accordance with one embodiment of the present invention;

FIG. 26 is a schematic view of a compact electrically controlled fluid valve/switch according to one embodiment of the present invention;

FIG. 27 is a schematic diagram of a programmable and self-locking check fluid valve according to one embodiment of the present invention;

fig. 28 is a cross-sectional view and dimensional diagram of a compact ECPUMP utilizing the motor of fig. 35-36, in accordance with an embodiment of the present invention;

FIGS. 29 and 30 are finite element simulation (FEM) results of the magnetic flux distribution of the compact ECPUMP obtained during a simulation based on design analysis values;

FIG. 31A is a graph of the results of numerical simulations of compact ECPUMP measurements based on parametric variations in piston tooth thickness and washer offset in accordance with embodiments of the present invention;

FIG. 31B is a numerical simulation of the variation of a compact EAV parameter according to the amount of gasket offset in accordance with an embodiment of the present invention;

FIGS. 32-36 are results of numerical simulations of compact ECPUMP variations in parameters, showing the ability to adjust long stroke characteristics, in accordance with embodiments of the present invention;

FIGS. 37 and 38 illustrate the spatial overlap of design parameters for the compact ECPUMP according to an embodiment of the present invention;

FIGS. 39A-39C are graphs of compact ECPUMP characteristics as a function of frequency, according to an embodiment of the present invention;

FIG. 39D is a Y-tube geometry for the numerical analysis shown in FIGS. 37-39C;

FIG. 39E is a simulation of generating a current drive profile to produce a desired stroke characteristic within a design space of an ECPUMP in accordance with an embodiment of the present invention;

FIGS. 40 and 41 are contour plots of performance characteristics of the compact ECPUMP system as a function of design parameters in conjunction with a Y-tube;

FIGS. 42-44 illustrate design variations of a pump piston in a compact ECPUMP in accordance with embodiments of the present invention;

FIGS. 45 and 46 are graphs of piston lubrication pressure to optimize piston surface profile to reduce friction;

FIG. 47 is a diagram of an exemplary power driver circuit for an ECPUMP, according to one embodiment of the invention;

fig. 48 is an exemplary current drive performance for the power drive circuit of fig. 47.

Detailed Description

The present invention relates to a sexual pleasure device, and more particularly to a device with vibration and non-vibration functions and operations and using fluid control.

The following description is of exemplary embodiments of the invention only and is not intended to limit the scope, applicability, or system configuration of the invention. Rather, the following description of the embodiments of the present invention is provided to facilitate those skilled in the art in practicing the embodiments of the present invention. It being understood that various changes may be made in the function and arrangement of elements without departing from the spirit and scope of the appended claims. Thus, the examples are merely examples or implementations of the invention and not the only implementations. Different appearances of "one embodiment" or "some embodiments" are not necessarily all referring to the same embodiments. While various features of the invention are described in the context of only a single embodiment, these features can also be provided separately or in any suitable combination. On the contrary, although the invention has been described in various embodiments for the purpose of clarity, the invention can be practiced in individual embodiments or in combination of embodiments.

Reference in the specification to "one embodiment," "some embodiments," or "other embodiments" means that a particular feature, structure, or characteristic described in connection with the embodiments is included in at least one embodiment (but not all embodiments) of the invention. The expressions and terms employed in this document are used for illustration only and are not to be construed as limitations. It should be understood that when the claims or specification refer to "an" element, such reference should not be taken as limiting the element to only one of the element. It will be understood that when the specification states that "may," "might," "could," or "might" include a component, feature, structure, or characteristic, that particular component, feature, structure, or characteristic is not necessarily included.

The terms "left," "right," "top," "bottom," "front," "back," and the like are used to designate an orientation of a particular feature, structure, or element in a drawing that illustrates an embodiment of the invention. It will be apparent that such directional terms are not particularly meaningful to the actual use of the device, as the user can use the device in a variety of orientations.

The terms "comprises," "comprising," "includes," "including," "consisting of," and grammatical variations thereof do not preclude the addition of one or more components, features, steps, integers or groups thereof, and the terms are not to be construed as specifying components, features, steps or integers. Likewise, the phrase "consisting essentially of", and grammatical variants thereof, as used herein, should not be construed as excluding additional features, steps, features, integers, or groups, but rather that the additional features, integers, steps, features, or groups do not materially alter the basic and novel characteristics of the claimed compositions, devices, or methods. If the specification or claims refer to "an additional" element, that is meant not to exclude more than one additional element.

As used herein and in relation to the specification, "personal electronic device" (PED) refers to a wireless device for communication and/or information transfer, powered by a battery or other independent power source. Such devices include, but are not limited to: cellular phones, smart phones, Personal Digital Assistants (PDAs), portable computers, pagers, portable multimedia players, remote controllers, portable game consoles, notebook computers, desktop computers, and electronic readers.

As used herein and in relation to the specification, "fixed electronic device" (FED) refers to a device that requires a wired connection for power. The device is connected to one or more networks through a wired and/or wireless interface. Such devices include, but are not limited to: televisions, computers, laptops, gaming consoles, kiosks, terminals, and interactive displays.

As used herein and in relation to the specification, "server" means a physical computer hosting a user of another computer, PED, FED, etc., running one or more services, serving the customer needs of these other users. Such servers include, but are not limited to: a database server, a file server, a mail server, a print server, a web server, a game server, or a virtual environment server.

As used herein and in relation to the specification, "user" refers to an individual using a device according to embodiments of the present invention, where the use is the result of the individual using the device or another individual using the device at the same time.

As used herein and in relation to the specification, "vibrator" means an electronic pleasure device intended for use by an individual or user himself or with another individual or user, wherein the vibrator provides a mechanical function of vibration to stimulate nerves or stimulate sensation.

As used herein and in relation to the specification, "artificial penis" means a sexual wellness device intended for use by an individual or user himself or herself, or with another individual or user, wherein the artificial penis provides a non-vibratory mechanical function to stimulate nerves or stimulate sensation.

As used herein and in relation to the specification, "sexual wellness device" means a sexual wellness device intended for use by an individual or user himself or with another individual or user, wherein the device provides one or more functions, including but not limited to the functions of an artificial penis and a vibrator. The sexual pleasure device/appliance may have these functions in combination with intrusive, non-intrusive design features, including mechanical functions that provide vibration and non-vibration. Such sexual wellness devices may be designed for use in one or more parts of the male or female body, including but not limited to: clitoris, clitoral area (peri-clitoral area, including clitoris), vagina, rectum, nipple, breast, penis, testis, prostate and G-spot. In one example, a "male sexual pleasure device" is a sexual pleasure device that places the penis of a user into a cavity or recess. In another example, a "female sexual wellness device" is a sexual wellness device having at least one portion that is inserted into a user's vagina or rectum. It will be appreciated that where the female sexual wellness device is for insertion into the rectum of a user, the user may be male or female.

As used herein and in relation to the specification, "ECPUMP" refers to an electrically controlled pump.

As used herein and in relation to the specification, "configuration file" means a computer and/or microprocessor readable data file including data relating to settings and/or limits of a sexual wellness device. Such data packets may be programmed by the manufacturer of the sexual wellness device, or by a user interface connected to the sexual wellness device or by a user of the PED/FED in communication with the sexual wellness device.

As used herein and in relation to the specification, "balloon" refers to an element that regulates the physical volume by injecting a fluid therein. Such balloons can be constructed of a variety of elastic and inelastic materials and have a variety of different unexpanded and expanded shapes, including spherical, elongated, wide, thin, and the like. Balloons may also be used to deliver pressure or pressure fluctuations to the hedonic device surface and user where the volume change of the balloon should be imperceptible or very small.

There are still limitations and disadvantages for users using the above-described prior art sexual wellness devices in providing enhanced functionality, applicability of the dynamic sexual wellness devices in use, and user-specific configurations, for example. For example, a single sexual pleasure device preferably supports variations in length and radial diameter dimensions during use to simulate sexual intercourse, even variations in size when a user holds the sexual pleasure device stationary, and supports users of the adaptive pleasure device or individuals using the sexual pleasure device.

Further, the sexual pleasure device is preferably capable of undergoing a structural change in shape or the like during use. Further, the variation is preferably an essential element of the routine of the operation of the sexual pleasure device. Still further, it is preferred that the sexual wellness device provide the variable size and shape feature of an asymmetrical structure such that the sexual wellness device provides a higher level of sensory control. Such variable size and shape features, such as bumps, corrugations, nubs, and intermediate ridges, are preferably adapted to appear or disappear during use, either randomly or in combination with one or more actions. In some instances, it may be preferable to increase the diameter along selected portions of the length of the sexual wellness device to meet specific preferences and bending requirements. In some embodiments of the sexual wellness device, it is preferred to provide a protrusion at the tip of the sexual wellness device that extends into the body or retracts back to achieve an internal "tickling/stroking" effect, or an external "tickling/stroking" effect against the clitoris. Further, it is preferred that selected portions along the length of the shaft not increase in diameter (e.g., provide a constant and held-constant radius) in order to meet particular preferences as the length of the sexual wellness device varies. In some embodiments of the sexual wellness device, it is preferred that the outer surface or "epidermis" of the sexual wellness device be moved over the skin surface so that one or more skin surfaces are presented to the user against a substantial portion of the outer surface of the sexual wellness device to provide a rubbing function. Alternatively, these areas may be moved perpendicular to the skin surface at the same time. In addition to these effects, it is preferable to independently vary features such as pulse shapes that control the variable acceleration of initial contact and subsequent body motion over a wide range, and frequency and amplitude variations that simulate/provide a more natural body sensation. For example, the "shock" action at the preset low frequency may be changed to vibration at the end of the cycle.

Preferably, such vibrations are simultaneously and alternately controllable during normal use of the sexual wellness device, including the ability to be inserted, removed, rotated, and the variable functions activated with one hand, both hands, or without the use of hands, and without the need for manual readjustment or realignment. In some pleasure device embodiments, it may be preferable to provide two or more combinations of independently controlled shape changes in the pleasure device, such that a first combination of overall shape, vibration, wave, movement, etc. may be used in a first configuration, and a second combination may be used in a second configuration. These configurations may be provided sequentially or in different sections. In another embodiment of the invention, these configuration data may be stored remotely and recalled by an existing sexual pleasure device, by the owner of a new sexual pleasure device, or by another individual pleasure device that is part of with another individual possessing another individual pleasure device. Optionally, the storage and transmission of the data packet may also enable a remote user to control the personal sexual wellness device.

Preferably, a combination of actions of the multiple personality hedonic devices is provided based on overall configuration and dimensions and local deformations, the actions being performed by fluid flow, wherein the fluid employed should ensure that, by controlling the pressure, the elements within the device are moved, or the elements within the device are expanded/contracted. In embodiments of the present invention, the article is allowed to vary widely and can operate from near dc frequencies to frequencies of several hundred hertz. Further, embodiments of the present invention provide efficient continuous flow/pressure and more powerful pulsed action. Further, embodiments of the present invention provide piston designs without seals or sealing rings.

In accordance with an example of an embodiment of the present invention, in U.S. patent application "method of fluid driving adult devices and devices thereof" co-pending U.S. patent application, filed 2013 on 9/26 (which application also claims priority to U.S. provisional patent application 61/705,809 filed 2012 on 9/26, hereby incorporated herein by reference in its entirety), a fluid driver system and sexual wellness device having a compact, low-power fluid pump, valves, switches, and the like are provided.

Fluid driver arrangement

Fig. 1 is a schematic diagram 100A and 100B of parallel and series element actuation using fluidic elements in conjunction with fluidic pumps, reservoirs, and valves according to an embodiment of the present invention. In the parallel drive scheme 100A, the first through third fluid drivers 130A-130C are connected on one side to the first pump 120A through the first through third inlet valves 140A-140C, respectively, and on the other side to the second pump 120B through the first through third outlet valves 150A-150C, respectively. The other ends of the first and second pumps 120A, 120B are connected to the reservoir 110 such that, for example, the first pump 120A draws fluid to the first through third fluid drivers 130A-130C, respectively, and the second pump 120B draws fluid away to the reservoir. Thus, each of the first through third fluid drivers 130A-130C may draw fluid by opening its respective inlet valve, thereby increasing the internal pressure, triggering an action, depending on its design. Any of the first through third fluid drivers 130A-130C, respectively, may maintain the pressure increase until the outlet valves are opened and the second pump 120B removes fluid from the drivers. Thus, the first through third fluid drivers 130A-130C may be independently controlled by each valve and pump according to a pressure profile.

In the opposite series drive schematic 100B, the first through third fluid drivers 180A-180C are connected on one side to the first pump 170A and on the other side to the second pump 170B. The other ends of the first and second pumps 170A, 170B are connected to the reservoir 160 such that, for example, the first pump 170A draws fluid to the first through third fluid drivers 180A-180C, respectively, and the second pump 170B draws fluid away to the reservoir. However, in the series drive schematic 100B, the first pump 170A is connected only to the first reservoir 180A, wherein operation of the first pump 170A will increase the pressure of the first reservoir 180A if the first valve 190A is closed, to the second reservoir 180B if the first valve 190A is open and the second valve 190B is closed, or to the third reservoir 180C if the first and second valves 190A, 190B are open and the third valve 190C is closed, respectively. Thus, although there is no partial sequence of parallel drive pressurization and intermediate pressurization present in the schematic 100A, the first through third fluid drivers 180A-180C may be pressurized separately by controlling the first through third valves 190A-190C, respectively. However, these limitations are offset by the reduced complexity due to the reduced number of valves required. It will be apparent to those skilled in the art that the schematic diagrams 100A and 100B utilizing fluidic elements in conjunction with fluidic pumps, reservoirs and valves to enable parallel and series element actuation may be used together within the same sexual wellness device with multiple pumps or a single pump configuration, according to embodiments of the present invention. In a single pump configuration, a valve is added before the first actuator 180A to isolate the actuator from the pump when the pump is actuating other fluid-driven elements.

Fig. 2 is a schematic diagram 200A-200B of first and second series drives in accordance with an embodiment of the present invention, in which a secondary fluid pump and fluid components are used in conjunction with first and second primary fluid pumps 220A, 220B, a reservoir 210 and valves. In the first series driving diagram 200A, the configuration of the first to third fluid drivers 240A to 240C is similar to that of the series driving diagram 100B in fig. 1. The secondary fluid pump 230 is disposed between the first primary fluid pump 220A and the first fluid driver 240A. Thus, the additional fluid motion that the secondary fluid pump 230 can provide exceeds the motion provided by the first primary fluid pump 220A through pressurization of the fluid driver. Such additional fluid action may be, for example, applying periodic pulses to linear or sinusoidal pressurization, where the frequency of the periodic pulses may be higher than the pressurization. For example, first primary fluid pump 220A may be configured to sequentially drive first through third fluid drivers 240A-240C to extend the length of the sexual wellness device within 1 second before second primary pump 220B sequentially withdraws fluid within 1 second, thereby resulting in a linear expansion frequency of the sexual wellness device of 0.5 Hz. The secondary fluid pump 230 can apply a continuous 10Hz sinusoidal pressure on the overall concave-convex surface, thereby lapping as a vibration on the piston motion of the sexual pleasure device. According to embodiments of the present invention, the primary pump may provide operation at several hertz to tens of hertz, while the secondary pump may provide operation at hundreds and tens of kilohertz of a similar range as the primary pump.

The second series drive schematic 200B illustrates a variation in which first and second secondary fluid pumps 230, 250 are provided in fluid lines leading to the first and third fluid drivers 240A, 240C, respectively, such that the first and second secondary fluid pumps 230, 250 can apply different superimposed pressure signals from the first primary pump 220A to the overall pressurization of the sexual pleasure device. Thus, by way of example above, the first fluid pump 230 may apply a 10Hz oscillating signal to the overall 0.5Hz expansion of the hedonic device, while the second fluid pump 250 applies a 2Hz spike to the third fluid driver 240C when the third fluid driver 240C engages the opening of the valve between the driver and the second fluid driver 240B, wherein the user feels a "stimulus" or "jerk" in addition to linear expansion and vibration. The second fluid pump 250 can be enabled only when the valve between the second and third fluid drivers 240B, 240C is open and the first primary pump 220A is pumping fluid.

While fig. 2 shows a parallel enable schematic 200C in which the circuitry is similar to that of the parallel drive schematic 100A shown in fig. 1. But with the first fluid pump 230 positioned in front of the fluid flow separating the first and second fluid drivers 240A, 240B, respectively, and the second fluid pump 250 connected to the third fluid driver 240C. Thus, by taking the same example as the second series activation schematic 200B described above, the first primary pump 220A provides an overall 0.5Hz pressure increase that drives the first and second fluid drivers 240A, 240B, and the third fluid driver 240C when the valves are open. The first fluid pump 230 provides an oscillating signal of 10Hz to the first and second fluid drivers 240A, 240B, while the second fluid pump provides an oscillating signal of 5Hz to the third fluid driver 240C. As will be apparent from the discussion of the partial embodiments of the sexual pleasure device of fig. 3-19 below, the first and second fluid drivers 240A and 240B may be connected to the insertion element of the sexual pleasure device, while the third fluid driver 240C is connected to the clitoral stimulator element of the sexual pleasure device. Optionally, the first and second fluid pumps, or either of the first and second fluid pumps, are connected in series to provide a higher pressure within the fluid system, or to provide different fluid pulse profiles, wherein the profiles may be provided independently.

Sexual pleasure device

Fig. 3 illustrates a sexual wellness device 300 according to an embodiment of the present invention, wherein the device employs a fluidic element to adjust various aspects of the sexual wellness device 300 during use. As shown in FIG. 3, sexual pleasure device 300 includes an extension 320 in which are disposed first through third fluid drivers 310A-310C coupled to first through third valves 390A-390C, respectively. As shown, each of the first through third valves 390A-390C is connected on one side to the pump module 370 by a second reservoir 395B and on the other side to the pump module 370 by a first reservoir 395A. Also, the forming part of the sexual pleasure device is a fluid intake element 380 which is connected to the pump module 370 and the fourth valve 390D through the third and fourth containers 395C, 395D. The first through fourth valves 390A-390D and the pump module 370 are each connected to an electronic controller 360 that provides the necessary control signals to the first through third fluid drivers 310A-310C and the fluid intake element 380 in accordance with a program selected by the user to be installed in the electronic controller 360 at the time of purchase, a program downloaded to the sexual wellness device by the user, or a user-programmed program.

Also connected to the electronic controller 360 are a rechargeable battery 350, a charging cradle 330, and a control selector 340, which controls the output to the electronic controller 360. Control selector 340 may include, for example, at least one of a control knob, a push button selector, an LED light to set information for a user, an electronic connector to a remote electronic pleasure device (for program transfer to/from the sexual pleasure device 300), and a wireless interface link, such as operating in accordance with the bluetooth protocol. As shown, the sexual pleasure device 300 may thus provide an insertion vibrator through extension 320 and a clitoral stimulator through fluid intake element 380. Thus, the first through third fluid drivers 310A-310C may include, for example, one or more fluid drivers, as described in fig. 1-11, as well as simple radial variant elements in which pressure causes the elements of the sexual pleasure device to expand directly in the radial direction. In other embodiments of the present invention, a plurality of linear fluid drivers, such as first through third fluid drivers 310A-310C, may be radially arranged and operated simultaneously at fixed and/or variable flow rates, sequentially, in random order, and in a preset out-of-sequence order.

Fig. 4 illustrates a sexual pleasure device 400 according to an embodiment of the present invention, wherein the device employs fluid elements to separately adjust aspects of the primary and secondary elements 460, 450 of the sexual pleasure device 400 during use. The primary element 460 comprises an expansion element and the secondary element 450 comprises a bending element. Both the primary and secondary elements 460, 450 may be connected to the pump module 440, the connection being controlled by an electronic controller 420 connected to the wireless module 430 and the battery 410. Thus, sexual pleasure device 400 generally includes an insertion element, a primary element 460, a vibrating clitoral stimulator element, and a secondary element 450. Alternatively, as described above, a second pump may be provided in the pump module 440, or a vibration function may be provided in the insertion element, primary element 460, and inflated/deflated. Alternatively, another pump may be provided in the pump module 440, or the vibration function may be provided in combination with the bending action of the secondary element 450.

Fig. 5 illustrates first through third sexual wellness devices 500A-500C in accordance with embodiments of the present invention, wherein a fluidic element is used to provide the suction and vibration sensations mimicking a prior art "egg" vibrator. Any one of the first through third sexual wellness devices 500A-500C includes a battery 520, a controller 510, a pump 530, and a reservoir 540. However, in the first through third sexual wellness devices 500A-500C, the active elements in any one of the devices are the inhalation element 550, the pressure element 1760, and the friction element 1770, respectively. Optionally, the pump 530 includes primary and primary fluid pump elements to provide low and high frequency motion to the body part to which the first through third sexual wellness devices 500A-500C are applied.

However, it will be apparent that the first and second pumps may actually be one and the same ECPUMP, with appropriate electrical control signals applied thereto, in accordance with embodiments of the present invention as described below with respect to ECPUMP. Alternatively, a single pump controller may be used to control both ends of the dual ended pleasure device, or dual controllers may be provided. Alternatively, a configuration may be employed in which all pumps are provided with only one reservoir, while in other embodiments fluid may be provided from one end of a dual-headed pleasure device to another personal pleasure device, while portions of the functionality may be unavailable simultaneously, or may be provided out of phase.

The sexual pleasure devices shown in fig. 1-5 above use fluid drivers alone or in combination with other mechanisms such as off-axis weight based vibrators, conventional motors, etc. A wide variety of other pleasure devices may be used in other embodiments, incorporating the combined functions described above or using other fluid drivers, without departing from the scope of the present invention. Further, the sexual wellness device can be designed in a number of variations depending on a variety of factors including, but not limited to, market demographics and user preferences. For example, sexual pleasure devices originally designed for anal insertion may be morphed according to such demographics, e.g., they may be configured to:

-heterosexual and homosexual male users for interactive use with the prostate;

-heterosexual and homosexual female users are worn during vaginal intercourse;

-heterosexual and homosexual users are worn during non-vaginal intercourse with a fixed physical dimension;

heterosexual and homosexual users wear during non-vaginal intercourse, with the external dimensions becoming larger;

in the above-described sexual pleasure device/apparatus functions and its design according to the embodiments of the present invention, it is apparent that other combined sexual pleasure devices can be provided by such elements as well as other elements utilizing the principle of basic fluid action and other mechanical functions. For example, such combined pleasure devices may include, but are not limited to: (vaginal/clitoral), (anospheral/vaginal/clitoral), (anospheral/testicular), and (anospheral/penile). Such combinations may be single-user or dual-user pleasure devices. Obviously, the dual-user sexual pleasure device can be male, female and male, with different combinations for each user. According to the following description of fig. 20, a plurality of independent sexual wellness devices can be virtually combined via a remote control, enabling a user to have multiple functions/options using the remote control, e.g., depending on the connection with the device while using the sexual wellness device, other sexual wellness devices or functions/options can be identical, but the operation of the devices can be synchronous, quasi-synchronous, or asynchronous. Obviously, reference may be made to prior art manual solutions, configured as a masturbation device for men, employing an actuator, to stimulate the penis.

In the embodiments of the present invention described above, the closed loop fluid system, the pleasure device and the driver are mainly emphasized. It will be apparent that by adjusting the size of the sexual wellness device, other cavities or portions of the structure with fluid drivers, suction/compression devices, may be provided to handle the second fluid. For example, a small fluid driver assembly can be provided to inflate/deflate a cavity on the outer surface of the sexual wellness device and further provide a sensation of blowing onto the user's skin, for example, a cavity containing a small external orifice. Alternatively, the cavity of the sexual pleasure device can act on a second fluid, such as water, lubricating oil, cream, etc., stored in a second reservoir, as a fluid that surrounds the sexual pleasure device when used in the bathtub. Thus, the sexual pleasure device can "suck in" water and pump it to a higher pressure by the fluid driver, with or without the spray nozzle spraying water. Alternatively, the sexual pleasure device may be sucked/blown from the same end of the article through a check valve. On the other hand, the sexual pleasure device can pump lubricating oil to the surface of the device or simulate the sense of ejaculation to the user, so that the device can also extend to other sensory functions besides physiologically simulating human actions.

Fig. 6 shows an embodiment according to the invention in which a fluid-actuated pleasure device is contained within a garment 600. Thus, in the garment 600 as shown, a user wears a compression garment 605 in which the first through third zones 610-630, respectively, house a sexual wellness device in accordance with embodiments of the present invention employing a fluid driver as described above and fluid line components as described below. The first and second zones 610, 620 may each be provided with a fluid driver-based suction element, for example, to provide stimulation to the nipple and areola of the user, and the third zone 630 may be provided with a fluid driver-based pressure element, for example, for stimulating the clitoris. Depending on the design of the garment, the fluid system may be distributed over an area of the garment such that the overall volume of the sexual wellness device is not apparent to a third party for independent use by the user or to provide the garment with a visually appealing impact. For example, the reservoir may store a volume of fluid, but should appear thin enough and distributed over the area of one or more portions of the garment. It is apparent that the first through third zones 610-630 may have various combination functions, respectively. For example, the first and second zones 610, 620 may be a frictional action in combination with a sucking effect, while the third zone 630 may be a sucking, vibrating, or frictional combined effect.

The garment, as shown in body suit 605, may include first and second components 600C, 600D, wherein the components are in communication with a remote electronic pleasure device 680. The first assembly 600C includes first and second fluid drivers 640A, 640B coupled to a first fluid assembly 650 such that, for example, the first and second fluid drivers 640A, 640B are disposed at the first and second zones 610, 620, respectively. The second assembly 600D includes a third fluid driver 660 connected to the second fluid assembly 670 such that the third fluid driver 660 can be connected to the third zone 630. Alternatively, first through third fluid drivers 640A, 640B, 660 may be provided in a single assembly, second assembly 600E, and third fluid assembly 690, respectively, where the third fluid assembly is also connected to remote electronic pleasure device 680.

Obviously, the additional fluid drivers are associated with each component and garment according to the particular design and desired function. Alternatively, remote electronic pleasure device 680 may be, for example, a user's "personal electronic device" (PED), and the fluid-driven pleasure device, either installed in the garment or separately provided, may be regulated and controlled by a cell phone, PDA, or the like. In other embodiments of the present invention, a wired interface to the controller may also be employed rather than a wireless interface.

It will be apparent to those skilled in the art that the pleasure devices described in fig. 1-5 may employ independent fluid drives to provide the features required for a particular pleasure device, or mechanical elements, including but not limited to motors with off-axis weights, drive screws, crankshafts, levers, pulleys, cables, etc., and piezoelectric elements, etc. Portions may employ additional electronics, for example, to support electrical stimulation. For example, a fluid driver may be used in conjunction with a pulley assembly to support movement of a cable secured to the other end of the sexual wellness device, to ensure that the cable retraction action deforms the sexual wellness device, to provide a varying degree of curvature (e.g., or to simulate a finger action, such as stimulating the female G-spot or male prostate area. Most mechanical systems must convert high speed rotation to low speed linear motion through eccentrics and gearboxes, while fluid drives by default provide linear motion in 1,2, 3 axes depending on the design of the drive. Other embodiments of the invention may provide for reconfiguration and/or adjustment to the user. For example, a sexual wellness device may include a base unit consisting of a pump, battery, controller, etc., and a working unit that contains only a fluid driver or is used in conjunction with other mechanical and non-mechanical elements. Thus, the work unit may be designed to slide relative to the work unit and be fixed at one or more preset deviations from the initial reduced state, such that, for example, a user may make fluid length adjustments in the range of, for example, 0,1, 2 inches, with fluid length adjustments perhaps being up to one inch, and thus, in conjunction with a sexual pleasure device, may provide a length change of, for example, 3 inches. Obviously, in other embodiments of the invention, the core of the sexual pleasure device, such as the insert, may be manually aspirated or mechanically expanded to different widths as the diameter of the fluid is adjusted. It is clear that other variations of the fluid-actuated pleasure device including mechanical elements may be incorporated to provide greater width variation to accommodate the user's physiological characteristic requirements (for example).

Personalized control of fluid drivers

Fig. 7A is a flow diagram 700 of a setup of a sexual wellness device employing a fluidic element according to an embodiment of the present invention based on user preferences of the sexual wellness device. As shown, step 705 is the first step in the start of the process, followed by step 710 where the user triggers the pleasure device settings. The user then selects the set function in step 715, and then proceeds to step 720 to set the device to the first setting for the function with the sexual wellness device controller. Next, in step 725, the sexual wellness device checks whether the user has input a stop command, and if not, proceeds to step 730 to add a function setting, and returns to step 725 to repeat the determination. If the user has entered a stop command, step 735 is entered where the settings for the function are stored in memory. Next, in step 740, it is determined whether the last function of the pleasant device has been set, and if not, it returns to step 715, otherwise, it goes to step 745 and stops.

Thus, through the steps in flowchart 700, a user is enabled to adjust the settings of the sexual wellness device according to personal preferences. For example, such settings include, but are not limited to: maximum radial expansion, maximum linear expansion, vibration frequency, amplitude of the pressure element, and expansion frequency of the sexual pleasure device. FIG. 7B is a flow chart 7000 of a setup of a sexual wellness device employing a fluidic element incorporating multiple functions according to an embodiment of the present invention, based on user preferences of the sexual wellness device. As shown, step 7005 is the first step in the process, and then step 7010 is entered for setting a first element of the sexual wellness device, such as the above-mentioned plug-in element corresponding to the primary element 460 of the sexual wellness device 400. Step 700A is then entered, which specifically includes steps 1615-1640, described above and shown in FIG. 7A. After the first component is set, step 7020 is entered to determine whether the last component of the hedonic device has been set. If not, the process returns to step 700A again, so that the next element of the sexual pleasure device can be set, otherwise, the process goes to step 7030 and stops.

For example, for a sexual wellness device 400, the setup process may be repeated according to the user setup capabilities of the secondary element 450 of the device 400. In other cases, the user may choose to set one, some, or all of the elements in the sexual wellness device. Alternatively, the user may choose to set one or all of the sexual wellness devices, or none. It will be apparent to those skilled in the art that the flow chart 7000 employs a dual-headed pleasant sensation device, and that a user making a setting confirmation can only change one end of the set device at a time.

Fig. 8 is a flow chart 800 of creating a personalized setting for a sexual wellness device 805 utilizing a fluidic component and subsequent storage/retrieval from a remote location using a PED820 in accordance with an embodiment of the present invention. Step 825 is the first step in which flowchart 800 begins, followed by step 700A, which includes steps 710, 600A, and 720 described above in connection with flowchart 700, wherein a user may set up preferences for the sexual pleasure device. After completing step 700A, step 830 is entered and the user preferences are transmitted to the remote electronic device, such as a PED, and step 835 is entered where the user can retrieve the personalized settings on the remote electronic device to select one at step 840. The selected settings are then transmitted to the sexual wellness device in step 845 where the user is provided with an option to alter the selected settings in step 855. Depending on the options in step 855, step 875 is entered and stopped where the user used the previously selected setting, or step 860 is entered where a number of option prompts are skipped telling the user how to adjust the settings of the sexual pleasure device. For example, steps 865 and 870 are entered for selecting to determine a setting change on the sexual wellness device or the remote device, respectively, and then step 835 is returned to.

Thus, as shown in FIG. 8, a sexual wellness device 805 can include a wireless interface 810, such as Bluetooth, to enable the device to communicate with a remote electronic device, such as the user's PED 820. The remote electronic device 820 stores the user's settings as shown in fig. 8 for three examples entitled "Natasha 1", "Natasha 2", and "John 1". For example, "Natasha 1" and "Natasha 2" differ in terms of insertable extended locomotor speed, radial expansion, extended length, representing different settings of the user "Natasha", such as single use, double use, or different models of single use, etc.

In addition to these variations, the user program can also make changes to features such as a wide range of frequency and amplitude variations and pulse shapes that can control the variable acceleration of the initial contact, adding other actions to better simulate/provide a more natural physical sensation or to provide a more enhanced sensation. For example, the user can change the pulse width, repetition frequency and amplitude of the preset "shock" action, and then modify this to provide vibration during some or all of the "shock" action and between the "shock" pulses.

Fig. 9 is a flow chart 900 for establishing personalized settings for a sexual wellness device utilizing a fluid component and subsequent storage/retrieval from a location remote from the user or other sexual wellness device in accordance with an embodiment of the present invention. Thus, step 910 is the first step in the start of the flowchart, followed by step 700A, which includes steps 710, 600A, and 720 described above in connection with flowchart 700, wherein a user may set up preferences for the sexual pleasure device. After completing step 700A, step 915 is entered and the user preferences are transmitted to the remote electronic device, followed by step 920 where the user can select whether to store the settings for the sexual wellness device via the remote network service. If so, step 925 is entered, where the user preferences (settings) are stored on the remote web service, then step 930 is entered, otherwise step 930 is skipped directly.

In step 930, a prompt is provided as to whether all fluid fractions of the device have been set. If not, step 700A is entered, otherwise one of steps 935 through 950 will be entered depending on the user's choice of whether to store preferences on the network service. The method comprises the following specific steps:

-step 935-retrieving the remote configuration file for transmission to the user's remote electronic device;

-step 940-retrieving the remote configuration file for transmission to a remote electronic device of another user;

step 945 — allowing another user to adjust the user's remote profile;

step 950 — the user adds the purchased device setting profile to the user's remote profile; and

step 970-the user purchases multimedia content for one or more sexual wellness devices via the associated user profile.

Next, in step 955, a step is selected that requires the user preferences to be transmitted to the remote electronic device and thus to the sexual wellness device, this step being performed before the updated device settings on the device associated with the selected remote electronic device in step 960, and then step 965 is entered and stopped. Thus, in step 935 the user may retrieve his or her profile and choose to apply it to his or her sexual pleasure device, or to purchase an entirely new sexual pleasure device, and in step 940 the user may associate the profile with another user's remote electronic device and then download it to the remote electronic device for transmission to the device associated with the remote electronic device. Thus, a user may load his own built profile and send it to a friend or companion, loading it separately into his sexual pleasure device for use or use in conjunction with another profile associated with the companion. Thus, a user may load their profile to one end of a dual-headed sexual wellness device associated with other users, as part of an activity performed with other users, or to one sexual wellness device. Alternatively, in step 945, another user is allowed to control the profile, such that, for example, one remote user can control the sexual wellness device via the updated profile while viewing the user of the sexual wellness device on the network video; in step 950, the user may purchase a new data package from the sexual wellness device manufacturer, a third party, or other self-service friend/user. An extension of step 950 includes continuing through step 970 where the user purchases multimedia content, such as audio books, songs, or videos, associated with a profile for a sexual wellness device according to an embodiment of the present invention for the user to play, the profile being provided to the sexual wellness device via a remote electronic device (e.g., the user's PED or bluetooth television), and the profile being executed in accordance with playback of the multimedia content and the profile being set by the provider of the multimedia content. Alternatively, the multimedia content may be a plurality of profiles, or a plurality of modules of profiles, such that a single item of multimedia content may be used with a plurality of sexual wellness devices having different functions and/or elements.

In the flow diagrams described in fig. 6-9, a user may select different action modes associated with control parameters, which may relate to a single fluid driver or multiple fluid drivers. For example, the user may select different frequencies, different pressures (related to drive signal amplitude/power), different pulse profiles, and slew rates. In the embodiment of the invention shown in fig. 8 and 9, the sexual wellness device is in communication with a remote electronic device, wherein the remote electronic device may be a PED of the user. Alternatively, the sexual wellness device can receive data, rather than a profile, for use as part of the user's experience, such as music or other audio-visual/multimedia data, to cause an electronic controller within the sexual wellness device to directly reproduce sound or adjust various aspects of the sexual wellness device based on the received data. The ECPUMP can act as a medium and low frequency driver in conjunction with a higher frequency driver or a suitable ECPUMP, and the electrical control can cover all frequency bands. Alternatively, when the multimedia contents are connected to the sexual pleasure device instead of the running sexual pleasure device in response to the multimedia contents, the controller may adopt the original multimedia contents or the processed multimedia contents while maintaining the running of the sexual pleasure device under the preference set by the user. Also, when the multimedia content includes a profile provided to the sexual pleasure device and used in synchronization with the multimedia content, the profile may determine an action of the control profile set up by the controller under the user setting preference. For example, female-related multimedia content for arousing sexual desire may provide some actions for a sexual pleasure device that simulate the actions of the multimedia content and provide other actions for the sexual pleasure device, but the content is synchronized or quasi-synchronized with the multimedia content.

Alternatively, the user may choose to perform a personalization process, such as the flowchart 800 shown in FIG. 8, including initial purchase and use of the sexual wellness device or subsequent use of the device. It is apparent, however, that the user may perform some or all of the personalization process while using the sexual wellness apparatus. For example, a user may apply other features while using a rabbit-like sexual pleasure device, such as limiting the maximum extension length and maximum radial expansion range of the sexual pleasure device to values different than previously while the clitoral stimulator inserted into the body remains vibrating. Due to the nature of the sensations experienced by the user from the sexual pleasure device, it is apparent that some process of personalized profile generation can subdivide the device to set subsets of data before other adjustments are made and combined with each other to make adjustments. For example, length/diameter variations are generally correlated due to the physiological characteristic requirements of the user, while vibrator amplitude and frequency, for example, may vary over a wide range of constant physical dimensions of the sexual pleasure device.

Fluid assembly

The sexual pleasure device described herein includes a fluidic assembly that controls the expansion/contraction of a fluidic cavity within the device. The fluidic components include a combination of fluid flow passages, pumps and valves and associated control systems. Examples of specific fluidic components are described in detail below. It is to be understood that the pleasure device of the present invention may also include other components.

In the pleasure device of the embodiments of the present invention described above and illustrated in the fluid schematic of fig. 1 and 2, a fluid control system including a pump and valve connected to a fluid connector has been described to provide pressure to various fluid control components, as shown in fig. 1-5. In fig. 3, the first through third fluid drivers 310A-310C are each connected to the pump module 370 via a fluid flow path that merges at a location associated with the first through third valves 390A-390C, rather than the configuration depicted in fig. 1 and 2. Referring to fig. 10, a component according to one embodiment of the invention is fluid-controlled inflated/deflated using a single valve, as shown in first and second states 1000A, 1000B. As shown, the fluid pump 1010 is connected to outlet and inlet reservoirs 1040, 1050 by outlet and inlet fluid containers 1020, 1030, respectively. The second ports on the outlet and inlet reservoirs 1040, 1050 are connected to valves through check valves, as shown in the first and second configurations 1050A, 1050B in the first and second states 1000A, 1000B, respectively. In the first configuration 1050A, a valve connects the outlet of the pump to the fluid driver in expansion mode 1060A through outlet reservoir 1040 to increase the pressure within the fluid driver. In the second configuration 1050B, a valve connects the fluid driver of the expansion mode 1060B to the inlet of the pump through the inlet reservoir 1050 to reduce the pressure within the fluid driver. Thus, the fluid control circuit of fig. 10 provides an alternative control technique to that described with respect to fig. 1 and 2. Optionally, a check valve is not used.

Fig. 11 illustrates an electrically operated valve (EAV)1100 for a fluid system according to an embodiment of the present invention, such as the valve described with respect to fig. 10, but which may also form the basis for a valve used in the fluid control scheme described with respect to fig. 1 and 2. Accordingly, as shown, the fluid flow passage 1120 has an inlet 1190A and a first outlet 2950B, which are provided on one side of the valve chamber 1195. On the other side of the valve chamber 1195 are two ports that merge into a second outlet 1190C. Valve chamber 1195 has a solenoid spool disposed therein that is movable from a first position 1110A to a second position 1110B. In the first position, the inlet 1190A and the associated outlet of the valve chamber are blocked; in the second position, the first outlet 1190B and the associated outlet of the valve chamber are blocked. Valve chamber 1195 has first coil 1130 at one end and second coil 1160 at the other end. Thus, in operation, the solenoid spool can be moved from one end of the valve chamber 1195 to the other by selective energization of the first and second coils 1130, 1160 to selectively block one or the other of the fluid flow paths from the inlet 1190A to the second outlet 1190C or from the first outlet 1190B to the second outlet 1190C, as shown and described with respect to fig. 10, to selectively inflate/deflate the actuator by injecting/expelling fluid.

In operation, when the magnetic poles of the solenoid spool are oriented as shown, to establish the first position 1110A, the north (N) pole of the spool is pulled to the left by the first coil 1130 with the effective south (S) pole toward the middle of the EAV 1100, and the S pole of the spool is pulled to the left by the second coil 1160 with the effective S pole toward the middle of the EAV 1100, i.e., the current in the second coil 1160 is opposite to that in the first coil 1130. Accordingly, to establish the second position 1110B, the current in the first coil 1130 is reversed from the previous direction, such that the effective north pole is oriented toward the middle of the EAV 1100, creating a pushing force to the right, and the S pole of the solenoid is pulled to the right by the second coil 1160, such that the effective N pole is oriented toward the middle of the EAV 1100. Depending on the design of the control circuit and the available power supply, only one coil may be energized at a time to generate a force to move the solenoid spool. Furthermore, it is clear that in some embodiments of the invention only one energized coil is provided.

Alternatively, to latch the EAV 1100 and reduce power consumption, first and second magnets 1140, 1170 can be provided at each end of the valve housing, respectively, since the solenoid can be moved between the first and second positions 1110A, 1110B by merely energizing the first or second coils 1130 or 1160, the poles being oriented to attract the solenoid when it is at the associated end of the valve housing 1195. Once the solenoid spool moves to each end under the electromagnetic control of the first and/or second coils 1130, 1160, respectively, the first and second magnets 1140, 1170 each provide sufficient attraction to hold the solenoid spool at that end. Alternatively, the magnetized piston/washer may be reversed in other embodiments of the invention.

The first and second magnets 1140, 1170 may optionally be formed of magnetically soft material to ensure that they are magnetized in response to excitation of the first and second coils 1130, 1160, respectively. Alternatively, the first and second magnets 1140, 1170 may be soft magnetic material to ensure that they conduct magnetic flux when in contact with the solenoid spool and are not substantially magnetized when the solenoid spool is in another position of the valve. Clearly, variations of the configurable electrically actuated valve 1100, including but not limited to non-self-locking designs, single inlet/single outlet designs, single inlet/multiple outlets and multiple inlet/single outlets, as well as variations employing valve chambers, inlet/outlet fluid flow passages and designs connected thereto, may be made without departing from the scope of the present invention. Alternatively, in the absence of electrical excitation, the solenoid spool may be disposed between the first and second positions 1110A, 1110B, and the length of the solenoid spool relative to the valve positions may ensure that the various ports are all "closed," as in the first and second outlets 1190B, 1190C of fig. 11.

Fig. 12 is a schematic diagram of an electronically controlled pump (ECPUMP)1200 for a fluid system, according to an embodiment of the present invention. A cross-sectional view of ECPUMP 1200 is shown including an outer body 1260 having first and second coils 1280, 1290 disposed within body 1260 at a first radius from the axis, the first and second coils 1280, 1290 being disposed on the left and right sides, respectively. First and second permanent magnets 1240, 1230, respectively, are disposed at a second, smaller radius from the axis. As shown, the poles of the first and second permanent magnets are radially disposed away from the axis of ECPUMP 1200 such that the north (N) pole faces the first and second coils 1280, 1290, respectively, and the south (S) pole faces the central axis. A magnetic piston 1210 is provided in the center of ECPUMP 1200. Thus, alternating excitation of the first and second coils 1280, 1290 causes the magnetic piston 1210 to move along the axis of the ECPUMP 1200. Energizing the first coil 1280, but not energizing the second coil 1290, results in an electromagnetic path 1280B being created, which, together with the permanent magnet path 1280A, pulls the magnetic piston 1210 to the left. Subsequently, de-energizing the first coil 1280 and energizing the second coil causes the second coil 1290 to create a new electromagnetic path (not shown for clarity) to the magnetic piston 1210 while the electromagnetic paths 1280A, 1280B are eliminated, thereby pulling the magnetic piston 1210 to the right. Thus, the magnetic piston 1210 moves to the left, drawing fluid from the second fluid flow passage 1250 and passing the fluid through the fourth check valve 1270D, and the piston then moves to the right, pushing fluid through the third check valve 1270C. At the same time, the magnetic piston 1210 moves to the left, pushing fluid through the third check valve 1270A and into the first fluid flow path 1220, and the piston then moves to the right, drawing fluid from the first fluid flow path 1220 and through the second check valve 1270B. ECPUMP 1200 may alternatively provide only one fluid flow path.

Fig. 13 is a cross-sectional view X-X of an electronically controlled pump (ECPUMP)1300 for a fluid system according to an embodiment of the present invention. Therein, an outer body 1350 is provided with a fluid assembly 1300A, the fluid assembly 1300A including a pair of inlets 1310 with one-way check inlet valves 1390 and a pair of outlets 1320 with one-way check outlet valves 1360. Each inlet 1310 and outlet 1320 also includes a fluid reservoir 1370. For simplicity, only one fluidic assembly 1300A is shown in fig. 13. Inside outer body 1350, on the upper side of central body element 1380 within outer body 1350, a fluid connection is provided between inlet valve 1310 at one end of ECPUMP 1300 and outlet valve 1320 at the other end of ECPUMP 1300, namely first coil 1340A and first magnet 1330A. On the underside of central body element 1380 within outer body 1350, a fluid connection is provided between inlet valve 1310 at one end of ECPUMP 1300 and outlet valve 1320 at the other end of ECPUMP 1300, namely second coil 1340B and second magnet 1330B. Thus, excitation of first and second coils 1330A, 1330B generates a magnetic field in the region bounded by outer body 1350 and central body element 1380, which drives first and second magnets 1340A, 1340B, thereby causing the magnets to pull/push fluid in ECPUMP 1300. It will be apparent to those skilled in the art that when ECPUMP 1300 is cycled in opposite directions by the electromagnetic induction forces generated by the first and second coils 1340A, 1340B, the one-way check inlet valve 1390 and one-way check outlet valve 1360 prevent backflow of fluid drawn in one direction, thereby facilitating aspiration. It will also be apparent to those skilled in the art that while the one-way check inlet and outlet valves 1390, 1360 are shown as circular in end view, the internal cross-sectional configuration of the pump chamber within the outer body may be of a variety of designs in which the magnets and coils are adapted to fit, including but not limited to circular, square, rectangular, arcuate and polygonal. The first and second coils 1330A, 1330B are generally identical coils and/or the first and second magnets 1340A, 1340B are generally identical magnets.

ECPUMP 1300 can only draw and only pump very small amounts of fluid per cycle compared to the amount of fluid in the fluid system before and after ECPUMP 1300. Accordingly, the inventors have discovered that the provision of a flexible element, such as shown in first and second capacitive elements 1370A, 1370B and as described in the preceding figures, between ECPUMP 1300 and the fluid system at each end, enables the amount of inlet and outlet side fluid to be dynamically adjusted sufficiently to facilitate operation of ECPUMP 1300 and other pump embodiments described herein, and can be used substantially as a fluid reservoir in providing a reservoir that can be drained/topped up by ECPUMP 1300, and thus the inventors have used this designation for these elements.

Fig. 14 is a schematic diagram of an electronically controlled pump (ECPUMP)1400 for a fluid system, according to an embodiment of the present invention. Wherein the outer body 1450 has an inlet 1410 with a one-way check inlet valve 1490 at one end and an outlet 1420 with a one-way check outlet valve 1460 at the other end. Each of the inlet 1410 and outlet 1420 also includes a fluid reservoir 1430. Inside the outer body 1450, a first magnet 1440A and a second magnet 1440B are provided on the inner surfaces of the upper and lower sides, respectively. At the inner center of the outer body 1450 is provided a central body element 1455. A first coil 1470A is provided between the first magnet 1440A and the central body element 1455, the first coil 1470A being coupled to the plunger 1480. A second coil 1470B is also provided between the second magnet 1440B and the central body element 1455, the second coil 1470B also being coupled to the plunger 1480. Thus, excitation of the first and second coils 1470A, 1470B causes a magnetic field to be generated within the region bounded by the outer body 1450 and the central body element 1455, which, in cooperation with the magnetic fields of the first and second magnets 1440A, 1440B, causes the plunger 1480 to move, thereby effecting the pumping/propulsion of fluid in the ECPUMP 1400. It will be apparent to those skilled in the art that when ECPUMP 1400 is cycled in the opposite direction, one-way check inlet valve 1490 and one-way check outlet valve 1460 prevent backflow of fluid drawn in one direction, thereby facilitating drawing. The first and second magnets 1440A, 1440B are typically single radial magnets or a pair of semi-ring magnets assembled to form a radial design.

The fluid connection path between the upper and lower pumping chambers is not shown in the cross-sectional view of ECPUMP 1400. It will also be apparent to those skilled in the art that, in a manner similar to ECPUMP 1300, the internal cross-sectional configuration of the pumping chambers within outer body 1450 of ECPUMP 1400 can be of a variety of designs including, but not limited to, circular, square, rectangular, arcuate, and polygonal shapes into which the magnets and coils are adapted to fit. In accordance with another embodiment of the present invention, first and second coils 1470A, 1470B may be secured by a plunger 1480 to enable movement of the remainder of ECPUMP 1400 relative to the plunger. First and second coils 1470A, 1470B are typically a single coil.

Fig. 15 is a schematic diagram of an electronically controlled pump (ECPUMP)1500 for a fluid system according to an embodiment of the present invention. As shown in cross-section, the interior of the central body 1510 is provided with a coil 1530 and the central body 1510 surrounds a piston 1520 of magnetic material. Each end of the central body 1510 is provided with a magnet 1540 and an outer portion 1550. In this example, the north and south poles of each magnet 1540 are aligned along the axis of ECPUMP 1500, rather than being radially disposed in each ECPUMP as described in fig. 12-14. In this manner, excitation coil 1530, in conjunction with piston 1520 and the magnetic field within each magnet 1540, causes piston 1520 to move within ECPUMP 1500. Accordingly, when combined with additional fluid components, ECPUMP 1500 becomes a less complex, efficient, high performance, low energy requirement, and improved manufacturability fluid pump. For clarity, the additional fluid components have been omitted, but as described with respect to FIGS. 12-14, including but not limited to inlets, outlets, check valves, and fluid containers. One aspect that affects this pump is the orientation of the magnetic poles relative to magnet 1540, the magnetic poles now being oriented along the axis of ECPUMP 1500, rather than radially. The stroke of piston 1520 is related to the thickness of magnet 1540 and the thickness of the piston teeth.

Fig. 16 is a cross-sectional view of an electronically controlled pump (ECPUMP)1600 for a fluid system according to one embodiment of the present invention. As shown, each end of the outer body 1610 is provided with first and second coils 1620A, 1620B. The interior of the outer body 1610 is provided with a pump body 1640 of magnetic material, the pump body 1630 being hollow and provided with a check valve 1630 at each end. The poles at each end of the pump body 1640 are along the axis of ECPUMP 1600. Thus, as with the other embodiments of the invention, as shown, the sequential activation of the first and second coils 1620A, 1620B causes the pump body 1640 to move relative to the outer body 1610, thereby drawing fluid from left to right through the action of the check valve 1630. When combined with additional fluidic components, ECPUMP1600 provides a less complex fluid pump with improved manufacturability, particularly with respect to the orientation of the magnetic poles relative to the pump body 1640 of magnetic material. For clarity, the additional fluid components have been omitted, but as described with respect to fig. 12-14, including but not limited to inlets, outlets, and fluid reservoirs. As shown, the pump body 1640 of ECPUMP1600 has 2 check valves 1630 disposed therein and ECPUMP1600 can be incorporated directly into a fluid system in-line. On either side of ECPUMP1600, additional check valves (not shown for clarity) may be employed within the fluid system to control the overall flow. One of the check valves 1630 may optionally be eliminated.

Fig. 17 is a schematic diagram of an electronically controlled pump (ECPUMP)1700 for a fluid system, according to an embodiment of the present invention. As shown, ECPUMP 1700 includes first and second fluid assemblies 1700A, 1700B at each end of a pump body 1760, the fluid assemblies being substantially as described above with respect to fig. 13 and fluid assembly 1300. The pump body 1760 houses first and second coils 1720, 1730 at each end of its interior and an axially disposed plunger magnet 1710 having poles axially disposed along the axis of the outer housing 1760. Thus, the first and second coils 1720, 1730 are energized, causing a resulting electromagnetic force to be exerted on the plunger magnet 1710 in a direction determined by the energizing coil. Optionally, first and second magnets 1740, 1750 may be provided in first and second fluid assemblies 1700A, 1700B, respectively, with the poles of first and second magnets 1740, 1750 facing plunger magnet 1710 to cooperate to provide a repelling force when plunger magnet 1710 is urged towards the respective ends of pump body 1760 by first and second coils 1720, 1730, respectively. Alternatively, first and second magnets 1740, 1750 may be oriented in the opposite direction to the orientation of the magnetic poles shown, ensuring that an attractive force is provided when plunger magnet 1710 is pushed, rather than a repulsive force. In these alternative configurations, the first and second coils 1720, 1730 each have a different electrical excitation profile. Optionally, the magnets may be formed using soft magnetic materials to ensure that they are magnetized in response to excitation of the first and second coils 1720, 1730, respectively. In addition, first and second magnets 1740, 1750 also increase flux confinement, thereby increasing the efficiency of ECPUMP 1700.

Fig. 18 and 19 are schematic diagrams of an Electronically Controlled Pump Assembly (ECPA) utilizing full-circulation fluid action according to one embodiment of the present invention. Referring to fig. 18, first through third views 1800A-1800C are an assembled view, a partially exploded end view, and a partially exploded side view, respectively, of an ECPA. As shown, the ECPA includes an upper clamshell 1810 with an inlet 1815 and a lower clamshell 1830 with an outlet 1835, one on each side of the motor mount 1820. An Electronically Controlled Fluid Pump Assembly (ECFPA)1840 is mounted on the motor mount. From the first through third perspective views 1900A-1900C of fig. 19, it is apparent that ECFPA 1840 includes first and second valve assemblies (VALVAS)1860, 1870, with first and second valve assemblies 1860, 1870 being disposed at each end of an electrically controlled magnetically induced fluid pump (ECPUMP)1850, respectively. Advantageously, the ECPA of fig. 18 and 19 reduces the mass of water driven by the pump to near a minimum after the post-valve outlet opens directly to the fluid in the ECPA.

Alternatively, if the upper clamshell 1810 and the lower clamshell 1830 are used to provide resiliency under the action of the ECPUMP, they may be used as the fluid containers described herein. In other embodiments, such a fluid driver may be provided with sufficient volume to serve as a reservoir for the device without the need for a separate reservoir. Alternatively, the upper clamshell 1810 and the lower clamshell 1830 are rigid to ensure that there is no fluid container effect, in which case the upper and lower clamshells vibrate at the frequency of the pump and the fluid leaving/entering the clamshells pulsates continuously. Advantageously, in both the flexible and rigid clamshell configurations, both the upper and lower clamshells 1810, 1830 can provide the vibrational stimulus directly to the user. In fact, connecting the inlet 1815 directly to the outlet 1835 provides a free-standing hydraulic device, i.e., a vibrator with flexible upper and lower clamshells 1810, 1830 that provides vibrations to the user at frequencies not attainable by prior art mechanically eccentric shaft motors. In contrast, a rigid or flexible wall clamshell does not have much amplitude, but it provides a pulsating flow of water.

A VALVAS, such as VALVAS 1860 or 1870 in fig. 18 according to one embodiment of the invention, provides an inlet and an outlet of a check valve with patterns 20A-20C for assembly to ECPUMP 1850. Fig. 20 is an exploded view of the VALVAS 2000, for example, in fig. 18 first and second VALVAS 1860 and 1870 are provided. It includes an inlet manifold 2000A, a valve body 2000B, and an outlet manifold 2000C. Fig. 20A, 2010, 2020, and 2030 are perspective, end, bottom, and top views, respectively, of the valve body 2000B. The inlet manifold 2000A is assembled to the valve body 2000B, and fig. 20B, 2040, 2050, and 2060 are perspective, side, front, and rear views, respectively, of the inlet manifold 2000A. A valve (not shown for clarity) which may be half the valve 2500E in fig. 25 is mounted to the inlet manifold 2000A by a first seat 2090A and disposed between the inlet manifold 2000A and the valve body 2000B. Thus, the valve action is limited in one direction by the inlet manifold 2000A, but not by the valve body 2000B, so fluid flow is toward the valve body 2000B. The outlet manifold 2000C is also assembled to the valve body 2000B, and fig. 20C, 2070, 2080 and 2090 are perspective, side, bottom and front views, respectively, of the outlet manifold 2000C. A valve (not shown for clarity) which may be half the valve 2500E in fig. 25 is mounted to the valve body 2000B by a second seat 2090B and disposed between the outlet manifold 2000C and the valve body 2000B. Thus, the valve action is limited in one direction by the valve body 2000B, but not by the outlet manifold 2000C. Thus, fluid flows from valve body 2000B such that the combination of inlet manifold 2000A, valve body 2000B, outlet manifold 2000C and two valves, not shown, act as an inlet/outlet check valve, connected to a common port, which is opening 2025 at the bottom of valve body 2000B adjacent the piston face.

Fig. 21-22B are various views of a compact ECPUMP 2110, in accordance with one embodiment of the present invention. The compact ECPUMP 2110 and inlet and outlet VALVAS 2000 provide ECFPA 2110 with full circulation fluid action when combined with appropriate external connections. Figures 21, 22A and 22B are internal exploded perspective, exploded perspective and cross-sectional exploded views of ECPUMP 2110. ECPUMP 2110 includes piston 2130, bobbin core 2140, bobbin shell 2150 and spacer washer 2160, and outer washer 2195, inner washer 2190, magnet 2180 and magnet shell 2170. The body sleeve 2120 supports and secures all of these elements. The body sleeve 2120 may be injection molded, for example, immediately after the remaining components of ECPUMP 2110 have been assembled in the assembly fixture. As shown in the exploded cross-sectional detail view of fig. 22C, the inner profile of the bobbin core 2140 in the inner washer 2190 self-alignment region 21000 can be seen. The isolation washer 2160 has been omitted for clarity. Thus, after subsequent positioning of the magnet 2180 and magnet shell 2170, it is apparent that the resulting magnetic field distribution is properly aligned within the washer by self-alignment of the bobbin core. Fig. 2130A and 2130B are end views of piston 2130, respectively, showing two different configurations of a groove machined or fabricated in piston 2130. These grooves can disrupt eddy currents, and/or radial/ring magnetic fields within piston 2130.

The dimensions of one embodiment of ECPUMP 2110 are described below with respect to fig. 44. However, it is apparent that other sizes of ECPUMPs may be incorporated depending on the overall requirements of the fluid system. For example, by using an ECPUMP (containing a piston having a diameter of 0.5 "(about 12.7mm) and a length of 1" (about 25.4mm) having a diameter of 1.4 "(about 35.6mm) and a length of 1.175" (about 30mm), a pressure of 7psi can be generated at a rate of 3 l/min. Accordingly, such pumps account for about 2.7in³Heavy and heavyAbout 150 g. The inventors have only made and tested variants of ECPUMPs having diameters of 1.25 "-1.5", although other sizes could be made.

VALVAS, for example, can be mounted over the end of bobbin core 3540. Alternatively, a multi-component bobbin core 2140 may be used, which multi-component bobbin core 2140 is combined in steps with the other elements of ECPUMP 2110. In each case, the design of ECPUMP 2110 aims to reduce complexity, facilitate assembly, facilitate manufacturing and assembly for commercial (mass production) and low cost niche market (small volume production) type applications (e.g., the device), and reduce cost. Fig. 22D shows a variation of ECPUMP, shown as mini ECPUMP 2200, which also includes coil 2220, outer body 2210, magnet 2230, magnet holder 2240, and outer washer 2250. All of which fit and fit around the body sleeve 2260, with the piston 2270 moving within the body sleeve 2260. The mini ECPUMP 2200 embodiments assembled and tested by the inventors had an outer diameter of 0.5 "(about 12.7mm) to 0.625" (about 16mm) and a length of 0.75 "(about 19mm) using a piston having a diameter of 0.25" (about 6mm) and a length of 0.5 "(about 12.5 mm). Such mini ECPUMP 2200 weighs about 20g and maintains a pressure of about 7psi when the flow rate is correspondingly small. Alternatively, the magnet holder 2240 may be omitted.

FIGS. 23A and 23B are schematic illustrations of the operation of a compact ECPUMP having a dual inlet valve and outlet valve assembly coupled to a fluid system and such ECPUMP with and without a fluid container, in accordance with one embodiment of the present invention; in fig. 23A, first through third views 2300A-2300C each relate to an ECPUMP2330 supporting two fluid systems according to one embodiment of the present invention. As shown in the second view 2300B, ECPUMP2330 has a first VALVAS2320 and a first port 2310 on one side and a second VALVAS 2340 and a second port 2350 on the other side. As shown in the first perspective view 2300A, ECPUMP2330 has a pair of ports 2310A/2310B on one side, the first ports 2310A/2310B connected to two first VALVAS 2320A/2320B and a pair of second ports 2320A/2320B on the other side, the second ports 2320A/2320B connected to two second VALVAS 2320A/2320B. Thus, as is evident from cross-section 2300C, movement of the piston to the right in ECPUMP2330 draws fluid in from the first port 2310A, through the first VALVAS2320 on the Left (LHS), out through the second VALVAS 2340, and into the second port 2350B. Conversely, as the piston moves to the left, fluid is drawn in through the second port 2350A and then through the second VALVAS 2340, whereas fluid is discharged through the first VALVAS2320 and into the first port 2310B. This cycle, when repeated, draws fluid from the second Y-port 2365 and then pushes it out through the first Y-port 2360. In some embodiments of the invention, the connecting tubes 2305A, 2305B may be rigid, while in other embodiments may be "resilient" so as to expand when the pressure rises above a predetermined value before the check valve (as shown in fig. 42) does not open. In this way, a temporary overpressure of the fluid system can be absorbed before the check valve opens. For example, connecting tubes 2305A, 2350B may be designed to expand at pressures above 7psi, while check valves trigger at 8 psi.

In fig. 23B, 2300D and 2300E are expanded and exploded views, respectively, of a VALVAS/port configuration with first and second valves 2370A and 2370B. First and second valves 2370A, 2370B provide non-return inlet and outlet valves for each end of the assembled ECPUMP assembly. Exploded view 2300E illustrates a VALVAS in which a fluid container 2390 is positioned next to a valve (e.g., second valve 2370B), the fluid container 2390 being comprised of a container port 2375, a flared flange 2380, and a cap 2385. Thus, designing the cap 2385 by wall thickness and material selection, etc., may provide a VALVAS that functions as a flexible portion of the fluid reservoir or it may be rigid. Such a fluid container 2390 is a fluid container as shown and described in fig. 13, 15, and 17 and in other variations and variations described below. The first through third graphs 23100-23300 are schematic representations of fluid action for pumps of different configurations, such as conventional single ended action, full cycle fluid action by the inventors without a fluid reservoir and full cycle fluid action by the inventors with a fluid reservoir. A first graph 23100 illustrates the operation of an ECPUMP having an end configured with an inlet/outlet check valve as described with respect to FIGS. 19-22B and 23A. Thus, in each cycle, the pump pushes fluid only in the second half of the cycle. A second chart 23200 shows an ECPUMP as depicted in fig. 23A, wherein the two ends of the ECPUMP are connected together by a common inlet/outlet port, such as first and second Y-ports 2360 and 2365. Thus, in each half cycle, fluid is drawn into the outlet wye port such that the fluid system experiences the overall fluid profile shown in the second graph 23200 such that the "left" and "right" half cycles combine. However, in many applications (e.g., such devices), it may not be desirable (or highly desirable) when the body pulsation generated occurs at twice the drive frequency of the ECPUMP drive signal. Thus, the inventors have demonstrated that substantially increasing the fluid time constant of the system above the frequency response of the ECPUMP allows the fluid reservoir near the valve to suppress or smooth the pressure drop of the second graph 23200. This results in a smooth ECPUMP output curve, thereby improving the performance of ECPUMP in the device or other devices according to embodiments of the present invention. According to embodiments of the present invention, the fluid container may optionally be provided before and/or after the two fluid paths merge and/or diverge. Further, by designing the geometry, wall thickness, materials, etc., the performance of the fluid enclosure may be altered to absorb/reduce fluid variations from the ECPUMP and/or EAV according to embodiments of the present invention to varying degrees. In other embodiments of the present invention, the output of the ECPUMP, for example, can be coupled to a first set of fluid drivers prior to being combined with the fluid container to energize the fluid of a second set of fluid drivers. In this manner, for example, a first set of fluid drivers receive a pulsating input and correspondingly vibrate, while a second set of fluid drivers receive a constant input and produce an elongation/expansion. Optionally, another set of fluid containers is positioned before the first set of fluid drivers, and the set of fluid containers smoothes the pulsating ECPUMP/EAV input so that the first set of fluid drivers generate a more regular sinusoidal curve.

Referring to fig. 24, a first view 2400A is a compact ECPFA utilizing ECPUMP2480 (e.g., ECPUMP 2100 or ECPUMP 2200 as described and illustrated in fig. 21-22D) in accordance with an embodiment of the present invention. As shown, ECPUMP2480 is positioned between the upper and lower VALVAS, which are variants of the VALVAS described in fig. 19-21. Thus, the upper valgas includes a first body 2425A, the first body 2425A including a first inlet 2440A with a first valve 2430A and a first outlet 2410A with a second valve 2420A; while the lower valgas includes a second body 2425B, the second body 2425B includes a second inlet 2440B with a third valve 2430B and a second outlet 2410B with a fourth valve 2420B. The first and second inlets 2440A, 2440B are connected to a Y-shaped inlet pipe 2460, respectively, and the first and second outlets 2410A, 2410B are connected to a Y-shaped outlet pipe 2470, respectively. The second view 2400B is a detailed view of the upper valgas.

As is apparent, the interior contours of the first inlet 2450A, the first body 2425A and the first outlet 2410A are depicted. These profiles and the characteristics of the first and second valves 2420A, 2440A are tailored to the pressure and flow characteristics of the ECPUMP to minimize losses during operation, thereby providing the overall efficiency of the ECPUMP and its associated appliances. Further, the fluid container may be different from the fluid container shown in fig. 23A and 23B by deforming the arms of the Y-shaped outlet tube 2470 to change the characteristics of the Y-shaped outlet tube 2470 in terms of resiliency and elastic force. Optionally, the Y-shaped input tube 2460 may also be implemented with a predetermined spring force or the like to provide a fluid reservoir on the input side of the ECPUMP.

Referring to fig. 25A, first and second views 2500A, 2500B are each a compact ECPFA utilizing ECPUMP 2580 (e.g., ECPUMP 2100 or ECPUMP 2200 as described and illustrated in fig. 21-22D) in accordance with an embodiment of the present invention. The ECPUMP 2580 is provided with first and second VALVAS at each end. The inlet and outlet valves 2530A/2530B and 2550A/2550B of the first and second VALVAS are connected to inlets 2520A/2520B and outlets 2560A/2560B, respectively. In the present ECPFA, first and second wyers 2510A, 2510B, respectively, connect the external physical system to ECPUMP 2580 to take advantage of the full-cycle fluid action principle. In contrast to the other ECPUMPs described above, ECPUMP 2580 is provided with first and second springs 2540A, 2540B that are coupled to the piston from first and second spring shells 2590A, 2590B, respectively. Thus, the electromagnetic movement of the piston in ECPUMP 2580 causes the first and second springs 2540A, 2540B to alternately compress/expand, and correspondingly, the action of the springs causes the piston to return to a central position. Thus, the drive signal sent to ECPUMP 2580 may be different from the signals in ECPUMP 2100, 2200, since the pulses causing the movement are stopped by the action of a spring, rather than being implemented in combination with an electrical control signal applied to a coil within the ECPUMP and a permanent or soft magnet.

In fig. 25B, a first view 2500C is of the spring shell 2594 and the housing 2590. First and second springs 2540A and 2540B, respectively, are attached to the spring shell 2594. In a pair of inlet and outlet ports within the spring shell 2594, each has a base 2592 for supporting an associated inlet or outlet valve 2530A/2550A, respectively, for insertion. Each inlet/outlet valve 2530A/2550A has a valve seat 2596, and the fluid seal of housing 2590 to ECPUMP 2580 is achieved by O-ring 2505. It will be apparent to those skilled in the art that other sealing techniques may be applied without departing from the scope of the invention. Within the spring shell 2594, there are four valves, two inlet valves 2530A and two outlet valves 2550A. This increases the area of the valves on the inlet and outlet, reducing the fluid resistance. Alternatively, the housing 2590 itself can be rigid or flexible. When flexible, housing 2590 provides a fluid reservoir in close proximity to the inlet and outlet valves.

The operation of this element in the fluid system is made resonant with ECPUMP, depending on the design of the wye tube merger/splitter (e.g., wye inlet tube 2470 and wye outlet tube 2460 of fig. 24). Advantageously, the resonant Y-tube provides a "pull"/"suck" at the beginning of a "forward"/"reverse" stroke to help apply force to the piston at the end of the stroke. This may reduce the electromagnetic drive required at the end of each stroke. As shown in the third panel 2300F of fig. 23B, by providing a resonator with a total time constant greater than that of ECPUMP operation, such a fluid container enables smooth operation of the ECPUMP and fluid assembly so that energy is not wasted on striking the body/column of water upstream or downstream of the ECPUMP.

In addition to all other design issues identified above and later with respect to ECPUMPs and ECFPAs in accordance with embodiments of the present invention, it is desirable in the design phase to address thermal expansion issues based on factors such as the proposed operating environment temperature range, the actual temperature of the ECPUMP over the expected usage time of the user, and the like. For example, the piston must be allowed to expand, and the inner and outer gaskets 2190, 2195 of fig. 21 are designed with a larger inner diameter to allow expansion during operation when the ECPUMP is hot. It will be appreciated that since the components of the ECPUMP/EAV according to embodiments of the invention may be made of a number of different materials, for example, iron for the piston and plastic for the core, design analysis should include thermal expansion of adjacent components to accommodate close tolerances.

It is apparent that ECPUMP as described with respect to fig. 18-25B and as described with respect to fig. 28-47 below may be implemented without check valves for each of the input and output ports. It is clear that an ECPUMP as described in accordance with fig. 18-25B and as described below in accordance with fig. 28-47 may form the basis of further variants of electromagnetically driven fluid pumps as described in accordance with fig. 12-17.

First through fourth views 2600A-2600D of a compact electrically controlled fluid valve/switch (ECFVS) according to an embodiment of the present invention are included in fig. 26. As shown in the first and second views 2600A, 2600B, the ECFVS includes first and second bodies 2610, 2620, respectively. Between the two bodies is a coupling 2630 connecting the two ports of the two elements and an Electronically Controlled Actuator (ECA), the coupling comprising magnetic washers 2640, 2660. Although other aspects of the ECA (e.g., coils, etc.) have been omitted for clarity, it should be clear to one skilled in the art. As is apparent from the third and fourth views, the operation of the coil moves the magnet 2670 to the left or right, thereby blocking/unblocking the right and left paths in the second and first bodies 2630, 2610. The magnetic washers 2640, 2660 enable latching operation of the ECA.

When the ECFVS requires only one of port B and port C to operate at any one time, the ECFVS shown in fig. 26 can be viewed as two valves connected together back-to-back. This is depicted in third and fourth views 2600C, 2600D, respectively. One such implementation of the ECFVS is that port a is connected to the fluid drive, port B is connected to the outlet of the ECPUMP, and port C is connected to the inlet of the (or another) ECPUMP. Thus, with port C "closed", fluid is drawn from port B to port a, thereby actuating the fluid driver; port C is then "opened" and fluid is drawn from the fluid driver toward port a to port C. In another configuration, fluid from input port a may be switched to either port B or port C and the position of the piston to ports B and C adjusted by appropriate electronic control. Alternatively, in the presence of variable pulse width modulation "PWM" of the control signal, the ECFVS of the first configuration may "dither" to continue to introduce/extract small amounts of fluid even when all of the fluid drivers are fully inflated to ensure that there is always fluid flowing in the fluid system. In the latter configuration, variable PWM mode operation may enable the driver to fill and/or drive simultaneously at different fill rates or flow rates. Additionally, the fifth view 2600E is a schematic view of an alternative valve in which only one or the other of the two independent flow paths is in operation. As mentioned above, the variable pulsed operation of the excitation coil enables a variable opening ratio, so that the valve can also be used as a variable liquid dispenser. Although coil excitation periods of 10-15ms are typically employed, embodiments of the present invention have on/off times as low as 5 ms.

It will be apparent to those skilled in the art that a high efficiency latching valve has a latching magnetic attraction that is as small as possible to force a piston within the valve against its closed pressure head. For most devices, it is desirable that the valve be small, fast to respond, operate at low power, and be easy to manufacture. The valve may be one of a plurality of valves incorporated into the manifold. In some valves, more power may be required to close the valve against pressure than to open the valve, as the pressure can help push the piston when open. Any of the coil/magnetic drive motors described in this specification may be implemented in an alternative design of lock and function as a valve rather than a pump. "on-off valves" typically do not use a one-way valve, such as might be incorporated with a circulation pump. Alternatively, the switching valve may be powered in part in a DC mode to controllably reduce the latching piston holding force to cause the closed valve to partially open or, conversely, to cause the open valve to partially close. Alternatively, the switching valve may incorporate closed loop feedback to affect the coil drive signal, and thus the piston holding force.

In an EAV as shown in fig. 26, complete sealing is not always required. In some applications, the closed valve has some leakage (e.g., 1%) because this does not significantly affect the operation or overall efficiency of the system. Considering the design of the EAV shown in fig. 26, or another valve/switch, the shutter that seals the on-off valve can be made of a softer conformable material to fit well with the piston surface, or it can be made of the same harder plastic that the rest of the body is made of. Alternatively, the piston may be ferrous and the washer a magnet, or the piston may be a magnet and the washer a soft magnetic material. Likewise, single coil, dual coil, and various other aspects of ECPUMP designs may be used in EAV designs. Alternative designs of EAVs may be selected that have a lock on only one end, or have a gate/port on one end of the EAV rather than both ends. By proper design, cascaded EAV elements may form the basis of a fluid switching and regulating circuit.

FIG. 27 is a schematic diagram of a programmable and self-locking check fluid valve according to an embodiment of the present invention. First view 2700A is a programmable check valve that includes a body 2710, a threaded valve body 2720, a spring 2750, a spring retainer 2730, a bearing housing 2740, and a ball bearing 2760. As the threaded valve body 2720 is threaded into the body 2710, the spring 2750 is compressed by the action of the spring retainer 2730 and bearing housing 2740, increasing the force required to overcome the spring pressure and open the programmable check valve by rotating the ball bearing 2760. A second view 2700B is an exploded view of the programmable check valve. The third view 2700C is a self-locking programmable check valve in which the check valve 2700, for example as described in the first and second views 2700A and 2700B, additionally mounts a pin 2775 on the threaded valve body, the pin 2775 being controlled by an electromagnetic driver 2770 connected to a drive circuit 2780. Thus, under the direction of the drive circuit 2780, the pin 2775 may engage behind the ball bearings via the electromagnetic drive 2770. After engagement, pin 2775 prevents rotation of the ball bearing, thereby preventing the check valve from acting. It will therefore be apparent to those skilled in the art that such self-locking programmable check valves or self-locking check valves can solve the problem of hysteresis associated with prior art pressure relief valves.

FIG. 28 comprises a cross-sectional view 2800A and dimensional diagrams of a compact ECPUMP 2800B utilizing the concepts described and illustrated in FIGS. 18-25A in accordance with an embodiment of the present invention; cross-sectional view 2800A provides the dimensions and names of variations of physical experiments and devices used by the inventors in the simulation and modeling of ECPUMP according to embodiments of the present invention. Accordingly, FIGS. 45-47 also refer to these dimensions. The compact ECPUMP 2800B, labeled with dimensions, depicts one embodiment of the present invention as described with respect to fig. 18-36 and fig. 37-46. Compact ECPUMP 2800B has a diameter of 1.4 '(about 35.6mm), a length of 1.175' (about 30mm), and a piston length of 0.5 '(about 12.7mm) x 1' (about 25.4 mm). Compact ECPUMP 2800B generates 7psi pressure at 3l/min with a volume of about 2.7in³And a weight of about 150 g.

FIGS. 29 and 46 are FEM modeling results of compact ECPUMP flux distributions obtained during numerical simulation according to design analysis performed by the inventors; in fig. 29, first FEM2900 is a design 6 having an outer diameter of 0.625 "and a length of 0.75" according to the original design. The thickness of the magnet is 0.075", the stator length Ty is 0.450", the stator tooth tip Hst is 0.025", the notch b is 0.250", the piston "tooth" length Trt is 0.100", and the total linear stroke Z of the piston is 0.140". The first FEM2900 is a magnetic flux map when Z is 0.000"I is 1.0A, that is, a middle stroke. Using a N42NdFeB magnet, with 192 turns of 28AWG wire and a force constant Kf ≈ 1.0lbf/A, the RMS input power is about 0.5W, driven with a sine wave. The second FEM2950 is a subsequent iteration design, design 21, with an outer diameter of 0.625 "and a length of 1.025" from the original design. The magnet thickness Tm is 0.100", the stator length Ty is 0.675", the stator tooth tip Hst is 0.030", the notch b is 0.425", the piston "tooth" length Trt is 0.125", and the total linear stroke Z of the piston is 0.200". The second FEM2950 is a magnetic flux map when Z is 0.000"I is 1.0A, that is, a middle stroke. Using an N42M NdFeB magnet, 170 turns of 22AWG wire with a force constant Kf ≈ 3.0lbf/A, the RMS input power is about 2.45W, driven with a sine wave.

In contrast, the first through third FEM plots 3000A-3000C of fig. 30 are baseline ECPUMP designs with closed and open circuits at mid stroke and open circuit at full stroke, respectively. The base wire ECPUMP had an outer diameter of 0.75 "and a length of 2.150". The thickness of the magnet is Tm equal to 0.200", the stator length Ty is 1.350", the stator tooth tip Hst is 0.025", the notch b is 0.800", the piston "tooth" length Trt is 0.125", and the total linear stroke Z of the piston is 0.200". Using an N42M NdFeB magnet, the overall efficiency was about 40%, the force constant was Kf ≈ 4.0lbf/A, the RMS input power was about 6.9W, and the drive was sinusoidal. Thus, when comparing the baseline design of the first through third FEM's, FIGS. 3000A-3000C, with the design 21 of the second FEM2950 of FIG. 4, it is clear that the inventors have been able to make substantial improvements in the ability of the ECPUMP to maintain output pump force while reducing the size of the ECPUMP, reducing power consumption, and improving efficiency.

Fig. 31A-46 are examples of optimizations made by the inventors to the fluid ECPUMP and the fluid device. Fig. 31A is a graph of the force constant Kf (lbf/a) for different tooth widths Trt at each end of the ECPUMP piston at different stroke positions within the range ± 0.125 "when the tooth width varies between 0.075" -0.140 ", showing an increasing deviation of the peak force constant value from the low peak force constant value as the tooth width increases. In the above graph, the magnet thickness Tex is 0.100", while in the lower graph, the magnet thickness is reduced to 0.075".

FIG. 31B is the effect of gasket offset for different EAV variants of the original baseline design. The 0V baseline design shows that as the gasket bias increases, the force begins to increase, but then decreases linearly. However, it is apparent that 0.015 "although reducing the maximum force significantly flattens the force versus gasket bias graph. Although a similar effect was achieved by reducing the radius, replacing the N42 magnet with an N50 magnet with a 0.015 "washer gap created enough force to hold the solenoid valve fluid closed against the fluid pressure, which in these simulations was based on 7psi and the design level readiness of the magnet. Thus, by modifying the washers, such as the inner washers 3590/3595 in fig. 35, and adjusting the magnet characteristics, manufacturing tolerances for offset in assembly/manufacturing efficiency can be increased.

The force constant in fig. 31B is related to the latching valve, which is the holding latching force between the valve washer and the latching magnet when the latching valve closes when a 7psi fluid system pressure is established on the ECPUMP. Based on these simulations, a design goal of maintaining a 9psi pressure on the valve was established such that lower power was required to open and close the valve, but latching was maintained.

Referring to fig. 32 and 33, the force constant Kf for a similar ECPUMP variant as the compact ECPUMP 2800B dimensional plot and as described for design 21 of the second FEM2950 in fig. 29 is depicted as a function of travel deflection over this range ± 0.120 "under 0A and 2A drive conditions. Therefore, for a constant outer washer thickness Tex of 0.075 ″, there is a parameter variation curve of the air gap Lg and the internal tooth width Tti of the inner washer. Therefore, as can be seen from fig. 33, at 2A, the peak detent force rapidly decreases with the air gap Lg, but is relatively constant for different inner tooth widths Tti. In addition, it is apparent that these curves are offset from the zero piston position and have significantly different characteristics from about ± 0..040 "from this peak position, with the force constant becoming negative for positive offsets approaching +0.120", with early reversals of the force constant at lower air gaps, and remaining negative at negative offsets of-0.120 ". Referring to fig. 32, it can be seen that for different air gaps and internal tooth widths, Tti is within the range of 0 ± 0..040 "the magnitude and profile of the 0A reluctance force is nearly constant and, in addition to the periodic characteristic, significant changes in reluctance magnitude are observed at higher piston excursions from 0.

Therefore, in view of Lg being 0.005 "(about 0.125mm or 125 μm), the detent force exhibits a periodic characteristic with early peaks of 1,2, and 3 in order for the internal tooth widths to be 0.125", 0.100", and 0.075". At +0.080", the detent force goes from-2.5 lbf (0.125 for/Tti) down to about 0 (0.020" for Lg/Tti) which follows the same change in the 2A current data of fig. 33. Thus, the inventors have established an ECPUMP design that utilizes a large stroke length by initiating electromagnetic excitation, but with a large stroke characteristic determined by a combination of the reluctance force at 0A and the fluid pressure. In addition, as is apparent from fig. 32, these zero current long stroke characteristics can be established by appropriate design of the ECPUMP.

Referring to fig. 34 and 36, the effect of different magnetic materials of the magnets of the ECPUMP variant similar to the compact ECPUMP 2800B size plot and that described for design 21 of the second FEM2950 in fig. 29 is depicted as a function of travel excursion under pulsed drive conditions. The current distribution is shown by the dashed line graph in the middle of the two graphs. In fig. 34, the effect of changing from an N30NdFeB magnet (10,800 gauss) to an N52NdFeB magnet (14,300 gauss) is shown to be small. More importantly, the standard soft magnetic steel is changed into Hiperco 50 iron-cobalt-vanadium soft magnetic alloy. The iron-cobalt-vanadium soft magnetic alloy has high magnetic saturation (24 kilogauss), high maximum direct current magnetic conductivity, low direct current coercive force and low alternating current magnetic core loss. Fig. 35 depicts the force variation versus position for the N52 magnet for two piston tooth widths Trt and three piston total lengths. Thus, the overall force versus position graph may be modified according to desired characteristics of the fluid system, such as improving the overall force magnitude versus piston position.

Likewise, fig. 36 depicts the numerical simulation results obtained for compact ECPUMP of two different magnetic materials (N30 and N42) at different piston positions using different currents, obtained from a compact ECPUMP 2800B dimensional plot and a similar ECPUMP variant as described for design 21 of second FEM2950 in fig. 29. Thus, at a current of 0, each passes through a force of 0 value at a 0 position offset and has a periodic characteristic with the piston position. As the current increases, the long stroke characteristic of the force changes more slowly, while the center short stroke characteristic changes more rapidly. When the current is between 0A and 2A, at the 0 "piston position (mid stroke), the force of both magnets is from 0lbf to about 8.5lbf, while at the-0.100" stroke distance, the force of the N30 magnet ECPUMP is from about 1.8lbf to about 2.3lbf, and the force of the N30 magnet ECPUMP is from about 3.3lbf to 4.0 lbf.

As with the linear piston pumps described above, such as the ECPUMP described and illustrated in fig. 18-23B, the average flow rate across the area downstream of the pump chamber fluctuates due to the need to reverse the direction of the pump piston. Because of the need to accelerate and decelerate all of the fluid along the flow path, fluctuations in flow rate cause an increase in the instantaneous load on the pump motor, as well as an increase in the length of the flow path. As mentioned above, the inventors have determined that expandable elastomeric membranes are employed immediately upstream and downstream of the pumping chamber. This section presents a design space analysis for a target ECPUMP/device configuration. The inventors performed design space analysis with the objective of:

-minimizing flow fluctuations to an acceptable and/or desired level in accordance with product requirements;

some speed and pressure fluctuations are allowed and in fact desirable, but limited so as not to seriously affect efficiency and end user satisfaction;

-determining fluctuations in flow and/or pressure to maximise the water column vibrational energy available to the user;

-maximizing mechanical energy efficiency by reducing work on the fluid; and

-minimizing or maximizing the fluid pressure on the pump piston, according to the intended purpose, while achieving a flow rate Q ═ 3L/min and an outlet pressure of 7psi (gauge).

To evaluate the inventors' concept, a mathematical model was developed for the dynamic behavior of the elastomeric container in connection with the fluid response pressure. The piston sine wave velocity at frequencies of 0-50Hz was used as an input to the model, and piston mechanics was not considered in this analysis. The model depicted and described in FIGS. 37-39C is shown in FIG. 39D, discretized by implicit finite volume method and solved numerically by total variation reduction. When numerical simulation is performed, the flow path lengths S of different parts are independently changed₄₅And S₆₇Film radius R₄、R₅、R₆And R₇And a coefficient of elasticity k. The dimensions of the elastic membrane and the pumping system are selected to vary the damping cutoff frequency of the system to filter out flow and pressure fluctuations downstream of the elastic membrane.

The fluid mechanics analysis is typically performed using unsteady Euler equations and mass continuity equations, which operate along slave cylindersMerge as streamlines from the beginning of the face to the end of the downstream of the membrane. The elastic membrane is built into a thin-walled pressure vessel where the stress-strain relationship is used to obtain pressure-change induced membrane expansion and compression. The instantaneous swelling rate of the membrane at a particular flow direction location is given by the equation (1) k ═ 0.67)/(Et₀) Given and being the elastic stiffness, the elastic stiffness is related to the elastic modulus E of the silicone and the thickness t of the elastic film₀. The coefficient 0.67 is a correction factor obtained by analysis and verified experimentally to take into account the thinning of the thickness of the elastic film during straining.

From a general point of view, changing the geometric parameters k, S and R has the following effect:

increasing R and S increases the damping effect of the elastic membrane, so that the friction losses and the pressure inertia component are reduced;

increasing R also reduces the speed magnitude, thus minimizing the inertial component of the pressure and viscous losses;

increasing S directly increases the pressure inertia component;

reducing S reduces the pressure inertia component, but at the same time reduces the viscous damping effect; and

increasing k increases the damping effect but decreases the critical pressure at which the capacitor can operate.

Length S of elastic film₄₅And S₆₇Scaling S/S from a reference initial value₀Scaling in an equal ratio; radius of film in proportion R/R₀Scaling in an equal ratio; stiffness coefficient k proportional k/k₀Scaling is done in the same way. When performing simulation, S/S is independently changed₀、R/R₀And k-₀And the data in fig. 37 and 38 are visualized using a 3D parametric space. FIG. 37 depicts a simulated parametric space diagram in which 31 different k values, 0.5 ≦ (k/k)₀) Less than or equal to 2.0, 51 different S values, less than or equal to 1(S/S₀) 4 or less, and 31 different R values, 1 or less (R/R)₀) A total of 49011 simulations were performed at 3. FIG. 38 depicts the parameter space results of this analysis, in which the minimum velocity fluctuation, maximum efficiency, and minimum mechanical input power isosurface are plotted. Thus, each (S/S)₀、R/R₀、k/k₀) The coordinates correspond to a different pump configuration and to different efficiency characteristics. The iso-surface shows all coordinates for a certain parameter with a specific level. For example, the mechanical surface indicates all configurations with a recent optimal mechanical efficiency value of 68%. Output flow fluctuation isosurface and efficiency isosurface intersection point representing efficiency and speed fluctuationThe best fold line in between. Apparently, several points are identified which give different compromise methods, as shown in table 1 below.

Table 1: design configuration points, key parameters, and design trade-offs

Fig. 39A-39C show that the optimized configurations of these different designs have reduced flow fluctuations, reduced average cylinder pressure, and correspondingly improved pump efficiency, as compared to the initial baseline condition, respectively. Further improvements are achieved by more simulations. In the simulation, the radius of the pump was independently varied and optimized, minimizing the pump to capacitor flow path and optimizing the losses caused by the umbrella valve. This further improves the theoretical mechanical efficiency of the compact ECPUMP to 87%. FIGS. 40 and 41 show k/k in this analysis₀Contour plots of speed fluctuation, efficiency and mechanical input power in the S-R two-dimensional plane, 0.5,1.0,1.5, 2.0. In each of fig. 40 and 41, the blank white area represents a case where the pressure within the film exceeds or approaches the critical pressure to expand (swell) the film to cause rupture. This instability occurs because the elastic membrane of the fluid container is not sufficiently stiff to permit it to constantly accumulate fluid.

When burst pressure (P)_BURST) Near a design pressure of 7psi, the membrane expands and contracts to a greater extent so that the membrane absorbs more energy from the fluid. The expansion and contraction cycle of the membrane is not coordinated with the fluid pressure to be close to 180 deg., so the membrane can be used to reduce the pressure load of the pump at the beginning and end of the stroke.

Another design optimization performed by the inventors is related to solving the problem of motor force output. It is clear from the first graph 3900A of fig. 39E that the pressure on the pump piston changes over time requiring a positive force throughout the pump cycle to move the piston through a full 0.2 "stroke and achieve a velocity profile of the sine wave. Thus, if the force applied at any time is insufficient, the piston will slow down prematurely, preventing the piston from reaching the opposite end, thereby reducing the flow rate. However, the characteristics of the magneto may act to resist or limit the positive force applied at the end of the stroke. Further, at either end of the stroke, the motor efficiency is greatly reduced, with the motor being most efficient toward the center of the stroke.

It is therefore an object of the present invention to find a force input signal to achieve a force signal that allows the piston to complete its full stroke and prescribes the current-to-force conversion efficiency curve of the available motor while achieving motor output capacity, thereby minimizing power requirements and maximizing electrical to mechanical energy conversion efficiency. To this end, piston mechanics is modeled and incorporated into fluid system simulations to specify force as an input, and piston position is solved for fluid pressure and velocity over time. An arbitrarily shaped force signal with energy transferred over the stroke equal to the energy transferred by the force curve is shown in the first graph 3900A of fig. 39E, which enables the piston to experience the full stroke length. The force signal is defined as an arbitrary curve that is controlled such that its integration over the stroke length produces the same energy as the integration of the force curve shown in the first graph 3900A of fig. 39E. The force signal curve is then evolved with a cost minimization optimization method, wherein the average current calculated from a particular force curve is minimized at the time of the simulation.

From this optimization, improved force versus piston position curves are determined, as shown in the second and third graphs 3900B, 3900C of fig. 39. The first graph 3900A is a force signal optimized to achieve 0.2 "travel and use a minimum input current, while the third graph 3900C is a resulting plot of piston position versus time. The force curve shown in the second graph 3900B of fig. 39E redistributes the energy transferred by the piston toward the center of travel and allows the force to be negative at the end of the stroke, and allows the pump piston to decelerate under the fluid pressure transferred by the elastic membrane and the zero current reluctance force transferred by the electromechanical magnetic element. The resulting piston position profile thus undergoes fairly rapid acceleration and deceleration toward the middle and end of the stroke cycle period. The corresponding speed profile is slightly reduced in mechanical efficiency, which is more than compensated for in the efficiency of the electric-to-mechanical energy conversion. The frequency of oscillation of the piston is determined by the force provided throughout the stroke. As we wish, less current is applied at the end of the stroke, so the zero current detent force of the piston is adjusted to the specific value required to achieve the resonant frequency with the minimum current (1.75 lbf at 40 Hz). This force curve can then be converted to the desired drive current as shown in the fourth graph 3900D of fig. 39. It can be seen that a minimum current needs to be applied at the beginning and end of the cycle.

FIG. 47 is an example of a control circuit for ECPUMP according to one embodiment of the present invention. As shown, digital circuit 4700A includes a high performance digital signal controller, such as a Microchip dsPIC33FJ128MC 30216 bit digital signal controller, which generates output Pulse Width Modulated (PWM) drive signals PWML and PWMH, which are coupled to first and second drive circuits 4720 and 4730, and drive circuits 4720 and 4730 generate current drive signals that are applied to coils within ECPUMP 3510. FIG. 48 is a graph of the resulting drive current applied to the ECPUMP coil. Instead of a continuous signal, the drive current is generated according to an embodiment of the present invention in which digital circuit 4710 generates pulses of varying amplitude at a frequency of 18 Hz. Thus, the 450ms drive current signal shown in FIG. 48 is weighted by about 8000 discrete amplitude cycles of such an 18kHz signal.

The ECPUMP can be run continuously using the drive signal shown in fig. 48 so that a constant fluid pressure/flow to the fluid system and valve can be achieved through the fluid container. However, it is apparent that under the direction of a controller that drives an EAV using PWM techniques, the EAV can be rapidly opened and closed to maintain a fluid driver (e.g., a balloon) at a predetermined fill level, such as 25%, 50%, and 100%. For example, with EAV and pulse width modulation oscillating at 40Hz, the valve can be maintained in the range of 0.1Hz-40Hz depending on the desired fill level. In this manner, a single ECPUMP can fill multiple balloons and/or maintain respective fill levels based on actuation of valves, switches, etc. within the overall fluid system. Also, ECPUMP can be run at different frequencies from 10Hz to 60 Hz. In addition, the frequency simulation can be done through the timing of a series of valves. In addition, it is apparent that body contact (e.g., pressure applied by a user's finger contacting the skin) can be mimicked because PWM-based controller technology allows the driver to perform complex inflation or generate graphs. Thus, the fluid actuator may be inflated to provide a pressure profile that mimics the touch of another person's finger on them.

Fig. 42-44 illustrate design variations of a pump piston in a compact ECPUMP according to embodiments of the invention. It is clear from simulations and other analyses as shown in fig. 29-36 that the performance of ECPUMP is sensitive to gap, such that a lower gap Lg results in increased force, etc. However, it is clear that at such low clearances, friction exists and can increase between the piston and the cylinder (e.g., sleeve 2120 in fig. 21) of the ECPUMP. On the other hand, the sharp profile of the piston teeth can improve performance, but can further increase the friction problem at the interface between the fluid, the piston teeth, and the cartridge. Thus, the first through fourth designs 4200A-4200D of FIG. 42 represent several options for addressing this issue in design variations. The design of each ECPUMP 4210 is depicted in fig. 21. In the first picture 4200A, the piston 4220 has a profiled end cap 4230 (e.g., made of plastic) that controls the narrow gap between the teeth of the fluid interface facing the piston 4220 and the inner surface of the sleeve, which is not shown for clarity. The second picture 4200B is a similar variant, but the piston body between the teeth is also filled with material (e.g. plastic). The third picture 4200C extends it further where the outside diameter of the piston teeth is slightly reduced to embed the piston 4240 into other materials 2450 (e.g., plastic) such that the sharp edges of the piston teeth and manufacturing variations of the piston are removed when directly contacting the inner surface of the sleeve. Further, in the fourth picture 4200D, the inner surface of the sleeve is coated with a membrane 4260 or a thin layer of material such that the piston 4240 embedded within the material 4250 enters the membrane 4260. If the sleeve is molded to the rest of ECPUMP 4210, the properties of the film are designed to reduce friction, rather than to achieve mechanical strength relative to the sleeve, etc.

The first through fourth designs 4300A-4300D of FIG. 43 represent several additional options for addressing the friction problem in design variations. The design of each ECPUMP 4310 is as described in figure 35. In the first picture 4300A, the tooth profile of the piston 4320 is modified such that the gap between the piston 4220 and the inner surface of the sleeve is smoothly tapered, rather than a sharp right angle. Alternatively in the second picture 4300B, fluid is injected with ECPUMP 4310 through lubrication path 4350 into lubrication groove 4340 on the piston surface. Although the lubrication grooves 4340 are shown in the center portion of the piston, it is apparent that they may also be implemented in the lubrication grooves on the piston teeth directly into the piston ends, as in 4220 in the first picture 4200A of fig. 42. This lubrication may be used alone or in combination with other techniques described herein. The groove 4340 may be optimized to maximize the bearing surface area, but still provide a sufficiently thick film lubrication for the piston surface. If the lubricant is the same as the fluid in the entire fluid system, it is apparent that a portion of the fluid of the ECPUMP suction may be "fed back" into the lubrication path 4350. The baseline for film lubrication as thick as the flow line between the piston and the sleeve is set at approximately 0.001", although it is clear that manufacturing tolerances can be determined as a point of expected cost/benefit to improve upon. In addition, other embodiments of the present invention may utilize film lubrication, interfacial layer and/or extrusion layer lubrication. Clearly, in non-in-line applications of ECPUMP, a complete seal around the piston is not required.

The third picture 4300C is a solution in which the piston 4355 is embedded in a material 4360 (e.g., plastic) that is shaped into what the inventors refer to as a double cylinder. The fourth picture 4300D shows a variant in which the piston 4380 is embedded in another material 4390 (e.g., plastic) and the inner surface of the sleeve has been coated with a film 4370. In other embodiments of the invention, ball bearing raceways may be employed, as shown for example in the first and second pictures 4400A and 4400B of fig. 44. In the first picture 4400A, only one ball track 4420 with notches of a certain width is provided. As such, the ball tracks 4420 may be as wide as or narrower than the slots, depending on the piston length, slot, and piston stroke length to enable free longitudinal movement of the piston. In the second picture 4400B, the ball bearings 4430 are disposed in grooves in the piston. In this case, since the ball bearing moves together with the piston, the problem in the length of the ball raceway is solved. The roller bearings 4430 may be made of one or more suitable plastic materials, ceramics, minerals or glass, for example.

The third picture 4300C of fig. 43 is the area formed between the piston 4340 and the barrel end barrier 4350, with the barrel end barrier 4350 projecting inwardly from the barrel inner surface (not shown for clarity). Thus, in operation in one embodiment of the present invention, the piston moves within the ECPUMP as usual. However, since the barrel end stop is provided at a position slightly longer than the maximum stroke for normal operation, if the piston exceeds the maximum stroke, as it gets closer to the copper end stop 4350, the fluid between the end of the piston 4340 and the barrel end stop 4350 at that end of the ECPUMP begins to compress and apply pressure to the piston in the opposite direction, slowing and eventually stopping the piston 4340 before reversing direction. In another embodiment of the present invention, the cartridge end guard 4350 is positioned near the maximum stroke of the piston 4340 so that this region of compressed fluid between the piston 4340 and the cartridge end guard 4350 will direct fluid to the region between the periphery of the piston 4340 and the inner surface of the cartridge each time the full piston stroke is reached. This is advantageous for piston designs where the clearance between the piston 4340 and the inside surface of the barrel is small, with or without a tapered profile for the piston teeth.

In addition to redesigning the piston and piston teeth geometry by reducing friction from the hydrodynamic aspects of the motion of the piston in the fluid as described in fig. 42-43 and fig. 47 and 48, it is apparent that other factors can be adjusted to reduce the overall coefficient of friction between the ECPUMP moving piston and the stationary body. Thus, such factors include, but are not limited to, the selection of steel for the piston, the selection of plastic for the barrel, the piston surface finish, the mold surface finish for barrel molding, manufacturing tolerances for each component, and barrel surface finish. Additionally, all of these must also be based on design considerations related to the ECPUMP pump itself, including but not limited to viscosity, magnetic field side loading, non-uniformity of the magnetic field generated by the coil due to assembly/manufacturing reasons, piston design, piston speed, fluid selection, operating temperature range, etc. It is also important to consider that, although the piston can move at speeds of tens of centimetres per second to tens of metres per second during the entire stroke, at the end of each stroke the piston first decelerates, then comes to a stop and finally reverses direction. Thus, the fluid lubrication should also be able to "back up" the piston so that at rest, the piston is surrounded by a film so that a thick (or thin) film of lubrication (e.g., is available) can be utilized at this stage of operation of the ECPUMP before the piston velocity is sufficient to produce the hydrodynamic effect described in fig. 47 and 48.

The ECPUMP according to embodiments of the present invention and as shown utilizes electromagnets disposed around a magnetic piston. The electromagnet is concentrically disposed around the piston and attracts the piston in both the radial and axial directions. If the center of mass of the piston is at the center of the magnetic flux field, the piston will not experience any net radial force. However, if the piston is moved slightly away from the center of mass of the magnetic flux field, the piston is forced radially outward and against the housing sidewall. This creates metal-to-metal contact, which results in a large amount of frictional losses. The application of dry and/or wet slipping as described in fig. 42 and 43 aims at solving the friction problem by preventing or limiting the frictional contact due to the large radial forces in combination with a relatively small contact area.

The inventors have therefore determined, using hydrodynamic lubrication theory, a piston side profile that produces sufficient lift to counteract the estimated magnetic attraction and prevent surface-to-surface contact. Typically 80% of the stroke cycle seeks to use hydrodynamic lubrication, and in simulations 30% -70% propylene glycol is used as the lubricant/pumping fluid so that repeated additions of lubricant are not required. By analysis of the curved end caps mounted on the ends of the planar central portion containing the piston, the side profile required to generate lift and to make further machining of the piston unnecessary is obtained, since removal of the piston magnetic material affects the magnetically determined motor configuration. In hydrodynamic analysis, since pressure is proportional to velocity, a constant velocity of about 10% of the peak analog piston velocity is used to ensure that the calculated lift is conservative and the piston remains in hydrodynamic lubrication mode.

The piston-to-cylinder (barrel) wall clearance (c) is uniform and does not produce any radial pressure distribution when centered. As the piston moves toward the outer cylinder wall, the piston-to-cylinder wall clearance changes, creating a pressure profile as shown in the first and second pictures 4500A, 4500B of fig. 45. When the piston is parallel to the outer cylinder wall, the pressure distribution is symmetrical and does not produce lift, but the pitching moment will often lift the leading edge closest to the cylinder wall away from the cylinder wall. At this point, the piston tilts upward, forming a small angle with respect to the cylinder wall, which creates a pressure field beneath the piston by a wedge effect, as shown in the third and fourth images 4500C, 4500D of fig. 45. The pressure field lifts the piston up and away from the cylinder wall. Normalizing the forces and moments generated by the hydrodynamic lubrication effect with Fp and Mp, where Fp and M_pRespectively, the magnetic disturbance force attracting the piston towards the side wall and the corresponding moment applied (if the magnetic force is applied through the front teeth of the magnet).

F/F_PForces > 1 ensure that the piston can deflect about 2lbf of lateral magnetic force, M/M_PA moment > 1 indicates that sufficient moment is generated to tilt the piston upwards to create the required lift. When the piston tilts up, the lift force is increased, and the pitching moment is reduced. At an angle, the hydrodynamically generated pitching moment thus balances the underlying magnetic moment, which affects the maximum lift that can be developed.Thus, in determining the appropriate configuration, the end cap wedge profile length l and height h are independently varied₀While the pitch moment and force are calculated using the plurality of leading edge slope heights. FIG. 46 shows M/M_P1.1 isosurface of all configurations, the isosurface is represented by shading with a gray-scale contour showing the lift created. All configurations create zero lift when the tilt height is zero, so a point must be selected in the shadow of the plane of values. Lift and pitching moment increase linearly with l, but with height h₀Decreases in inverse proportion. Selecting a smaller height is more and more complicated for the machine, while selecting a longer end cover length will extend the length of the machine. Therefore, a compromise is sought between these two factors, for example (l ═ 0.125 ″, h₀＝0.003")。

It is apparent that the design principles of ECPUMP for many different factors, including but not limited to hydrodynamic fluid effects, piston design, cartridge design, manufacture and assembly, can also be applied to other electrically controlled magnetic induction devices (e.g., valves and switches). Alternatively, the piston in any of the embodiments of the invention described with respect to profiling to support the formation of a thick/thin layer between the piston and the barrel and hydrodynamic correction of the offset of the piston in the barrel may be modified to be an asymmetric piston with a different profile at one end than the other over the entire length and/or teeth of the piston, so that in operation fluid circulates from outside the piston to the area next to the piston and then out the other end of the piston. In this way local degradation of the piston by the fluid is reduced.

It will be apparent to those skilled in the art that the making or providing of the field coils in the description and drawings of ECPUMP and ECFPA depictions of embodiments of the invention are not shown or described. The design and winding of such coils is well known in the art and has therefore been omitted for clarity in depicting the remaining elements of the ECPUMP and/or ECFPA. For example, in fig. 21, 22A and 22B, the coil is wound or formed on a bobbin core 2140 and housed in a bobbin case 2150 that contains one or more lead-ins/outs for connection to external drive and control circuitry. Such coils include, for example, 170/22, 209/23, 216/24, 320/24, 352/24, 192/28 (e.g., 8 layers of 24 turns each), 234/28, 468/32, and 574/33. Each set of numbers represents the number of windings of the wire used and the american wire gauge.

It will be apparent to those skilled in the art that other configurations of resilient elements, resilient elements and fluid drivers may be implemented, wherein one or more aspects of the movement, size, etc. of the elements of the device and of the device itself are varied according to the sequence of actions of the same subset of the elements of the device and/or of the fluid drivers within the device itself. Furthermore, it is apparent that one or more active components (e.g., fluid pumps and fluid valves) may be designed as a single module rather than as multiple modules.

It will be apparent to those skilled in the art that by appropriate design of the ECPUMPs described in relation to figures 12-17, in addition to providing the function of a pump and as a primary pump as described in relation to figures 1 and 2, they can also function as a secondary pump as shown in these figures and as a vibrator type of function. Further, in the embodiments of the invention described for the electronically controlled pumps in fig. 12-17, it will be apparent to those skilled in the art that although the description is provided for the fluid container, it may be omitted depending on the design of the overall apparatus aspects, including but not limited to the tubing used to connect the various elements of the fluid system together or those portions of the fluid system proximate the fluid pump. In some cases, removal of the fluid container may cause a cyclical/periodic pressure profile to be imposed on the overall graph determined by the electronic controller, wherein the cyclical/periodic pressure profile provides additional stimulation to a user of the device. It is apparent that in other embodiments of the invention, the fluid container may act as a high-pass filter that suppresses low frequency pressure changes but passes higher frequency pressure changes. In other embodiments of the invention, ECPUMP may form the basis of a compact RAM/hammer pump.

In other embodiments of the invention, the fluid driver may be used as a fluid reservoir and, in some cases, may be configured to connect with other fluid drivers from the fluid driver, rather than directly from the pump or through a valve from the pump. In other embodiments of the invention, the fluid container may be provided on one side of the pump, for example the inlet side.

Alternatively, the inlet fluid reservoir may be designed to provide minimal or no effect on the movement of the device, such as by not sizing the pump. In this case, fluid is drawn from the fluid driver to the piston when the pump piston attempts to draw fluid and the control valve of the one or more fluid drivers has opened such that an effective fluid connection has been established between the pump and the fluid driver. However, if one or more valves are not open or the fluid actuators are all collapsed, the "vacuum" at the pump piston inlet increases and the pressure relief valve allows fluid to flow from the high pressure inlet fluid reservoir or directly from the valves and begin circulating fluid when the volume of the fluid actuators is constant. In this way, the pump can continue to operate, for example providing vibrations, even when the device is in a state in which the volume of the fluid driver is not adjusted.

In some embodiments of the invention, the function of the fluid reservoir may be removed, so that the fluid system directs all possible generated pressures, i.e. all pressures that the pump piston can exert, through the rigid tube and the control valve to the fluid driver to translate the movement of the pump piston into the movement of the fluid into/out of the fluid driver. This may be employed where the distance between the fluid driver and the pump is relatively short and the volume/weight of the fluid pushed by the pump piston is not too large. Thus, depending on the design of the fluid circuit, if more than one valve is open, fluid flow will be shared, but if none or the valve is open but the fluid actuator cannot expand or contract, some pressure/vacuum limit is controlled by the design of the fluid actuator and surrounding material, and the back pressure/vacuum on the pump piston will rise until the relief valve opens and allows fluid to flow from the pump outlet to the pump inlet. Thus, the pump piston can be operated at all times without any movement of the device taking place. It is clear that in such an embodiment of the invention, the fluid system with a container can only contain a small reservoir or not contain any reservoir.

Fluid systems according to embodiments of the present invention with reservoirs and/or fluid containers may still employ pressure relief valves or may optionally monitor pressure to shut down the pump in the event, for example, the pump stalls due to a valve closing or the fluid actuator does not move or the pressure exceeds a predetermined threshold. For example, squeezing the device hard may prevent the device from expanding, stalling the pump, if desired, but the pressure monitoring may have shut the pump down. Optionally, a thermal fuse may also be employed throughout the control circuit. Optionally, the frequency of the pump may be adjusted or a valve triggered to bring the ECPUMP into a closed loop state isolated from the drive for a predetermined time or until the pressure drops to an acceptable level. Obviously, more complex decisions can be made, such as assessing that the pressure is periodic/aperiodic and indicating a strong vaginal orgasm, e.g. not a personal squeeze device. It is apparent that the use of ECPUMPS can vary the pump frequency, pump stroke length, pump pulse profile, etc. to vary the effective pressure, flow rate and pulse frequency of fluid movement within the device, thereby varying the effect of such movement through the fluid driver to which the valve, switch and decoupler are connected. In other embodiments of the invention, ECPUMP may be allowed to stall without overheating by appropriate design.

If a pressure sensor is embedded, it may itself determine the expected pressure that the user wishes to feel, and then determine the pump drive signal required to achieve this expected effect with changing other pump parameters, e.g., if the user adjusts the frequency of operation in the user configuration phase, the pressure profile may be maintained. It is clear that the performance of ECPUMP can be monitored. For example, the back electromagnetic field (EMF) generated may be measured to determine the position of the plunger at the ECPUMP and compared to the expected position and derived position-time curve to determine whether the control signal needs to be adjusted to achieve the desired device and/or ECPUMP performance. Alternatively, capacitive or other sensors may acquire piston position, acceleration, and fluid flow and may also monitor pressure at the ECPUMP to verify performance.

Alternatively, the fluid system may be designed such that the pump is running at all times and varying Revolutions Per Minute (RPM) according to some desired pattern, including the mode of stimulus vibration, while the valve is constantly open and closed so that the device always moves in one or the other orientation, so that the pump need not be shut down in designs where there is no fluid reservoir or an improper fluid reservoir, or pressure relief bypass valve.

Material

In the fluidic assemblies, actuators, devices, fluidic valves, and fluidic pumps described in fig. 1-31, the fluid can be a gas or a liquid. If the device fails to produce a fluid leak, the leaked fluid must not be toxic to the user and corrosive to the materials used in the various components of the device that come into contact with the fluid. In other embodiments of the invention, the fluid may be temperature regulated, for example heated. For example, the fluid may be a mixture of 50% propylene glycol and 50% water, although other proportions may be used depending on the desired viscosity of the liquid. Other materials may be used depending on the desired fluid properties, including, but not limited to, anti-mold, lubricant additive, anti-freeze, anti-microbial, anti-foam, anti-corrosion, non-toxicity in the storage and/or operating ranges, and long life in a sealed fluid system. Such fluids may include, but are not limited to, for example, vegetable oils, mineral oils, silicon, water, and synthetic oils.

For the materials from which the device is made, a variety of materials may be used in conjunction with the fluid driver, including, for example, closed cell foam, open cell foam, polystyrene, expanded polystyrene, extruded polystyrene foam, polyurethane foam, phenolic foam, rubber, latex, jelly, silicone, elastomers, stainless steel, Cyberskin skin, and glass. Many of the fluid drivers in the present embodiments are designed to expand when pressure is increased (or fluid is injected) and to collapse when pressure is decreased (or fluid is withdrawn). Accordingly, the fluid driver may be generally made of an elastic material, which may include, for example, rubber, latex, silicone, and elastomers. In some embodiments of the present invention, the fluid interface between the fluid driver and the fluid pump and/or valve may be made of the same material as the fluid driver, not allowing for other materials. In this case, the fluid driver may be made of a material having a reduced wall thickness. Such fabrication processes include, but are not limited to, dip coating, blow molding, vacuum molding, hot press molding, and injection molding, for example. It is apparent that multiple actuators can be formed simultaneously as a single piece in a single process step. Alternatively, the individual actuators may be connected directly together by thermal bonding, ultrasonic bonding, mechanical properties, adhesives, etc., or connected together by transition ducts. The fluid driver may be secured to valves, switches, ECPUMP, ECFPA, EAV, etc. in the same manner.

Device arrangement

While emphasizing self-contained stand-alone devices, it is apparent from embodiments of the present invention that the device may be divided into multiple units, such as a pump assembly, where the device is connected to the pump assembly by a hose, which may be tens of centimeters, a meter, or a few meters long. In other embodiments of the invention, a very short tube may be used to isolate the pump assembly from the rest of the device, or as part of the flexible portion of the body, for user adjustment of the curvature of the portion of the device inserted into the vagina, for example. Obviously, a device according to an embodiment of the invention may be designed such that: the form of holding when in use; used together as a part of a kit; by an accessory arranged on the body of the user or on a part of the body of another user (such as a hand, a thigh or a foot, etc.); or may be secured to an object, such as a wall, floor, or table, by suction cups or other means of attachment.

The device and electronic controller according to the embodiments of the present invention, as illustrated in the drawings and described above, illustrate a power source in the form of a battery power supply that can be of a standard replaceable (consumable) design, such as alkaline, zinc carbon, lithium iron sulfide (LiFeS)₂) Similar batteries, or rechargeable designs such as nickel cadmium (NiCd or Nicad), nickel zinc and nickel metal hydride (NiMH) batteries. Typically, such batteries are size seven or five batteries, including, but not limited to, type one, two and PP3 batteries. Thus, such devices should be self-contained power supplies, controllers, pumps, valves and actuators disposed within the body. Obviously, for battery-driven operation, although power connections may alleviate such design limitations, the power connections are not limited to the battery-driven operationThe fluid pump, electronic controller and fluid valves are still preferably of low power, energy efficient design. For example, for a device having a fluid driver operating pressure of about 2-6psi, a typical size and efficiency flow rate of about 3W is consumed. For a five dc rechargeable battery with 4 segments of 1.3V, approximately power can be provided, at approximately the rate that the total energy can provide approximately 1 hour of power, i.e., approximately, to run multiple pumps within the device.

However, in other embodiments, the device may be of a so-called stick configuration, as exemplified by prior art hiking sticks, where the size is typically increased, but the device additionally includes a power cord and the power supply is controlled directly from the power supply via a transformer. Alternatively, the device may be designed to contain a battery and a power supply connected to the remote transformer by a power cord having a small electrical connector and containing a power plug. However, it is apparent that other embodiments of the present invention may be designed to include predetermined portions of the pump, valves, power supply and electronic controller in a single, self-contained module that contains the fluid driver.

The device and the electronic controller thereof according to the embodiment of the invention are illustrated in the drawings, and the electronic controller is located in the device. Alternatively, however, the controller may be remotely connected to the device by a wire, or communicate by indirect means, such as wireless communication or the like. In addition, the electronic controller may provide control signals to the fluid pumps and valves, as well as other active components of the device. However, in some embodiments of the invention, the electronic controller may receive input from sensors embedded within the device or located outside the device. For example, the sensor may provide an output based on pressure applied by the user to the portion of the device via vaginal contractions or the like, wherein the controller may adjust one or more aspects of the device motion based on maximum pressure, speed, slew rate, and extension, among other things. Alternatively, other sensors may be deployed within the device to monitor the performance of the device, including, for example, a linear sensor to monitor the extension length and a pressure sensor to monitor the fluid pressure at a predetermined point within the device.

In accordance with the foregoing aspects of the present invention, a fluid device employing valves, switches, ECPUMP, ECFPA, EAV, etc. is a sexual pleasure device. However, it is apparent that the fluidic devices, valves, switches, ECPUMPs, ECFPAs, EAVs, etc. described above may be used in a wide variety of other applications to achieve compact, low-power fluidic components, sections, devices, etc. Similarly, embodiments of the present invention may be adapted for use with other valves, switches, ECPUMPs, ECFPAs, EAVs, etc. in a variety of applications having different flow rates, pressures, fluid diameters, etc.

The foregoing detailed description is provided only to facilitate a thorough understanding of the embodiments. It will be appreciated that embodiments may be practiced without reference to the specific details. For example, the circuitry may be shown in block diagram form so as not to obscure the embodiment with extraneous content. In other instances, well-known circuits, processes, algorithms, structures, and techniques may not be shown in insignificant detail to avoid obscuring the embodiments.

The techniques, modules, steps, and methods described above may be implemented in various ways. For example, these techniques, modules, steps and methods may be implemented in hardware, software or a combination of hardware and software. If implemented in hardware, the processing units may be implemented within one or more Application Specific Integrated Circuits (ASICs), Digital Signal Processors (DSPs), Digital Signal Processing Devices (DSPDs), Programmable Logic Devices (PLDs), Field Programmable Gate Arrays (FPGAs), processors, controllers, microcontrollers, microprocessors, other electronic units designed to perform the functions described herein, and/or combinations thereof.

It is also noted that the embodiments may be described as a process which is depicted as a flowchart, a flow diagram, a data flow diagram, a structure diagram, or a block diagram. Although a flowchart may illustrate a sequence of operations that occur sequentially, many of the operations may occur in parallel or concurrently. Further, the order of the operations may be altered. After the operation is completed, the process is ended, but other steps not included in the figure may be included in the process. A process may correspond to a method, a function, a procedure, a subprogram, etc. When a process corresponds to a function, the end of the process corresponds to the return of the function to the calling function or the main function.

The foregoing is a disclosure of embodiments of the invention for the purpose of illustrating the invention and is not intended to be exhaustive or to limit the scope of the invention to the precise forms disclosed. Many variations and modifications to the above-described embodiments will be apparent to those skilled in the art in light of the above disclosure. The scope of the invention is defined by the appended claims and equivalents thereof.

Further, in describing exemplary embodiments of the present invention, the specification may have presented the method and/or process provided herein step-by-step. However, the steps of the method or process are not limited to the particular order of steps set forth in the present invention, as the method or process is not limited to the particular steps set forth in the present invention. It will be appreciated by those skilled in the art that these steps may be performed in other sequences as well. Accordingly, the particular order of the steps set forth in the specification should not be construed as limitations on the claims appended hereto. Furthermore, the claims directed to the method and/or process of the present invention should not be limited to the performance of the product in the steps described. It will be apparent to those skilled in the art that variations may be made in the order of the steps set forth without departing from the spirit and scope of the invention.

Claims

1. An apparatus for use in conjunction with an electromagnetically driven pump within a fluid system to draw fluid from an inlet to an outlet, the apparatus comprising:

a first fluid container having one end connected to the solenoid-driven pump and the other end connected to the fluid system, and including a first preset portion having a first preset elastic modulus and a second preset portion having a second preset elastic modulus lower than the first preset elastic modulus;

when the first fluid container is disposed at the first inlet port of the solenoid-driven pump, the second predetermined portion of the first fluid container is deformed by the solenoid-driven pump such that the solenoid-driven pump draws fluid directly from the first fluid container, rather than from the fluid system; and

when the first fluid container is arranged at the first outlet port of the solenoid-driven pump, the second predetermined portion of the first fluid container is deformed by the solenoid-driven pump such that the solenoid-driven pump pumps fluid directly to the first fluid container instead of to the fluid system.

2. The device of claim 1, wherein

When the first fluid container is arranged at the first inlet side of the solenoid driven pump, an inlet check valve connected to the first inlet port of the solenoid driven pump is arranged between the first fluid container and the first inlet port of the solenoid driven pump; and

when the first fluid reservoir is disposed on the first outlet side of the solenoid actuated pump, the outlet check valve is disposed between the first fluid reservoir and the first outlet port of the solenoid actuated pump.

3. The apparatus of claim 1, further comprising

First and second valve assemblies connected to the solenoid-actuated pump and capable of pumping fluid on each stroke of the solenoid-actuated pump, each valve assembly comprising an inlet check valve, an outlet check valve, and a valve body containing a port connected to the solenoid-actuated pump and in fluid control, an inlet valve port connected to the inlet check valve, and an outlet valve port connected to the outlet check valve; wherein

When the first fluid container is disposed on the inlet side of the solenoid actuated pump, it is connected to one of the inlet valve ports of the first and second valve assemblies, and the respective one of the first and second valve assemblies is disposed between the first fluid container and the solenoid actuated pump; and

when the first fluid container is disposed on the outlet side of the solenoid actuated pump, it is connected to one of the outlet valve ports of the first and second valve assemblies, and the respective one of the first and second valve assemblies is disposed between the first fluid container and the solenoid actuated pump.

4. The apparatus of claim 3, further comprising:

a second fluid container including a first preset portion having a first preset elastic modulus and a second preset portion having a second preset elastic modulus, the second preset elastic modulus being lower than the first preset elastic modulus, and the second fluid container being disposed at a first inlet side of the electromagnetic drive pump when the first fluid container is disposed at the first outlet side of the electromagnetic drive pump, the second fluid container being disposed at the first outlet side of the electromagnetic drive pump when the first fluid container is disposed at the first inlet side of the electromagnetic drive pump, wherein

When the second fluid container is arranged on the first inlet side of the electromagnetic drive pump, a second predetermined portion of the second fluid container is deformed by the electromagnetic drive pump, such that the electromagnetic drive pump draws fluid directly from the second fluid container, and

when the second fluid container is arranged at the first outlet side of the electromagnetic driven pump, the second preset portion of the second fluid container is deformed under the action of the electromagnetic driven pump, so that the electromagnetic driven pump directly pumps the fluid into the second fluid container.

5. The device of claim 4, wherein

At least any one of the following is included:

when the first and second fluid containers are both connected to the inlet or outlet valve ports of the first and second valve assemblies, they are the same fluid container;

when the first and second fluid containers are connected to the inlet and outlet valve ports of the first and second valve assemblies, respectively, the first and second fluid containers are also connected to the respective other of the inlet and outlet valve ports of the first and second valve assemblies, respectively;

the first and second fluid containers, when connected to the inlet and outlet valve ports of the first and second valve assemblies, respectively, form part of a clamshell that surrounds the solenoid-actuated pump, respectively;

when both the first and second fluid containers are connected to the inlet or outlet valve ports of the first and second valve assemblies, forming part of a Y-tube connecting each pair of inlet or outlet valve ports to a common port of the fluid system; and

when the first and second fluid containers are connected to the inlet valve port and the outlet valve port of the first and second valve assemblies, respectively, they form first and second portions of a clamshell that surrounds the solenoid-actuated pump, respectively, and the fluid system directly connects the first and second portions of the clamshell together.

6. The apparatus of claim 3, further comprising:

a second fluid container comprising a first predetermined portion having a first predetermined modulus of elasticity and a second predetermined portion having a second predetermined modulus of elasticity, the second predetermined modulus of elasticity being lower than the first predetermined modulus of elasticity when the first fluid container is connected to the outlet check valve;

a Y-tubing interface connected to the first and second fluid containers for connecting fluids within the first and second fluid containers to a common port of a fluid system; and

a fluid switch disposed between one of the first and second fluid containers and its respective Y-tube port, the fluid switch connecting the one of the first and second fluid containers back to at least one of the solenoid-driven pump and another portion of the fluid system in a first configuration that connects the one of the first and second fluid containers to its respective Y-tube port; wherein

A fluid switch disposed between the first or second fluid container and the respective Y-tube port, the fluid switch in the first configuration connecting the first or second fluid container to the respective Y-tube port, the fluid switch in the second configuration connecting the first or second fluid container back to the solenoid-driven pump or another part of the fluid system; wherein

In a first configuration, fluid is drawn into the fluid system in succession in both directions of piston travel, and pressure fluctuations developed across each piston are determined by the magnitude of the fluid volumes provided by the first and second fluid reservoirs, and in a second configuration, drawn in only a single direction of pump travel, the pressure fluctuations are determined by the magnitude of the fluid volumes of either the first or second fluid reservoirs.

7. The apparatus of claim 3, further comprising:

a second fluid container connected to the other outlet check valve when the first fluid container is connected to the outlet check valve and connected to the other inlet check valve when the first fluid container is connected to the inlet check valve; and

a Y-tubing interface connected to the first and second fluid containers to connect the fluids in the first and second fluid containers to a common port of the fluid system when connected to the outlet check valve and to connect the first and second fluid containers from the common port of the fluid system when connected to the inlet check valve; wherein

The Y-tubes each comprise first and second regions, each first region constituting first and second fluid reservoirs.

8. The apparatus of claim 1, further comprising:

When the second fluid container is arranged at the first inlet side of the electromagnetic drive pump, the second preset part of the second fluid container is deformed under the action of the electromagnetic drive pump, so that the electromagnetic drive pump directly pumps the fluid from the second fluid container; and

when the second fluid container is arranged on the first outlet side of the electromagnetic drive pump, the second preset part of the second fluid container is deformed under the action of the electromagnetic drive pump, so that the electromagnetic drive pump directly pumps the fluid into the second fluid container.

9. The device of claim 1, wherein

The volume of fluid pumped by the electromagnetic drive pump is less than the volume of the fluid system; and

at least any one of the following is included:

the fluid system is a closed system; and

the first fluid container serves as a reservoir for discharged fluid when the first fluid container is arranged at the first inlet port of the solenoid-actuated pump and as a reservoir for topped-up fluid when the first fluid container is arranged at the first outlet port of the solenoid-actuated pump.

10. The apparatus of claim 1, further comprising:

a second fluid container comprising a first predetermined portion having a first predetermined modulus of elasticity and a second predetermined portion having a second predetermined modulus of elasticity, the second predetermined modulus of elasticity being lower than the first predetermined modulus of elasticity,

when the first fluid container is arranged at the first inlet side of the electromagnetic drive pump, the second fluid container is arranged at the first outlet side of the electromagnetic drive pump, and the second preset part of the second fluid container is deformed under the action of the electromagnetic drive pump, so that the electromagnetic drive pump directly pumps the fluid into the second fluid container; and

when the first fluid container is arranged at the first outlet side of the electromagnetic driven pump, the second fluid container is arranged at the first inlet side of the electromagnetic driven pump, and the second preset portion of the second fluid container is deformed by the electromagnetic driven pump, so that the electromagnetic driven pump directly pumps the fluid into the second fluid container.

11. The apparatus of claim 10, wherein

When the second fluid container is disposed on the first inlet side of the solenoid actuated pump, an inlet check valve connected to the first inlet port of the solenoid actuated pump is disposed between the second fluid container and the first inlet port of the solenoid actuated pump; and

when the second fluid reservoir is arranged at the first outlet side of the solenoid actuated pump, an outlet check valve is arranged between the second fluid reservoir and the first outlet port of the solenoid actuated pump.

12. The apparatus of claim 8, further comprising:

and second to fourth fluid containers respectively including a first preset portion having a first preset elastic modulus and a second preset portion having a second preset elastic modulus lower than the first preset elastic modulus, the second to fourth fluid containers being disposed at a first inlet side of the electromagnetic drive pump when the first fluid container is disposed at a first outlet side of the electromagnetic drive pump, the second to fourth fluid containers being disposed at the first outlet side of the electromagnetic drive pump when the first fluid container is disposed at the first inlet side of the electromagnetic drive pump.

13. The device of claim 1, wherein

The first fluid reservoir constitutes a predetermined portion of a clamshell surrounding the solenoid-driven pump.

14. The apparatus of claim 10, wherein

The first fluid container constitutes a first predetermined portion of a clamshell surrounding an electromagnetically driven pump, an

The second fluid container constitutes a second predetermined portion of the clamshell surrounding the electromagnetic driven pump.

15. The device of claim 1, wherein

The first fluid container includes a predetermined portion forming a valve body that is part of a valve assembly connected to the solenoid actuated pump, the valve assembly further including a return valve disposed in the solenoid actuated pump and the predetermined portion of the valve body of the first fluid container.