JPH0246802B2 - - Google Patents

Description

Claim 1: Nozzle means for forming and ejecting a fluid jet in response to a supply of pressurized fluid; having a substantially central region and a common inlet and outlet opening; a vibrating chamber positioned to receive through an opening, the vibrating chamber cycling the jet from side to side of the vibrating chamber in a direction substantially transverse to the direction of flow of the jet; vibrating means for directing fluid from the periodically vibrated jet out of the vibrating chamber through the common opening along opposite sides of the jet to a greater extent than along opposite sides; flow directing means for always producing less flow along the side toward which the jet is directed; and said vibrating means is disposed in said vibrating chamber in the path of said jet to direct vibration. impingement means are provided in the vibrating chamber for forming two vortices of fluid in the jet, leaving one vortex on each side of the jet, thereby increasing the strength of the two vortices in antiphase. A fluid vibrator, characterized in that the two vortices are moved in opposite phases between a position close to the common opening and a position in the central region.

2. The fluid vibrator according to claim 1, wherein the collision means is formed by a wall of the vibration chamber located away from the common opening.

3. The fluid vibrator according to claim 1 or 2, wherein the vibration chamber has a substantially circular cross-sectional shape, and the common opening is in contact with the substantially circular shape defined by the cross-sectional shape of the vibration chamber.

4. The fluid vibrator according to claim 1 or 2, wherein the vibration chamber has a substantially rectangular cross-sectional shape.

5. The fluid vibrator according to any one of claims 1 to 4, wherein the collision means is formed by a flat wall.

6. The fluid vibrator according to any one of claims 1 to 4, wherein the collision means is formed by a concave wall.

7. The fluid vibrator according to any one of claims 1 to 4, wherein the collision means is formed by a convex wall.

8. Claim 1, wherein the common opening includes two protrusions provided on both sides of the inlet downstream of the inlet.
The fluid vibrator according to any one of items 7 to 7.

Technical field The present invention relates to improvements in fluidic oscillators.

Prior Art In the past, fluid vibrators not only functioned as components of fluid circuits but also served as fluid distribution devices (U.S. Pat. No. 3,432,102, No. 3,507,275,
4052002 specification). In these patents, oscillations of the jet are caused by fluid interaction without the use of moving parts, resulting in the ejection of an oscillating jet into the environment. US Patent No.
Other fluid transducers, such as those described in US Pat. No. 3,563,462, intermittently eject fluid from two or more apertures. Most patent applications of the prior art have shown that the performance of a transducer is critically affected by even small differences in the dimensions of the transducer passages and chambers. It has also become clear that conventional transducers are extremely sensitive to the properties of the dispensing fluid, such as viscosity, surface tension, temperature, etc.

Another problem with prior art vibrators, especially when used to obtain special spray shapes, is that the desired spray shape is not immediately available upon start-up. Generally, the desired spray shape can only be obtained after the transducer is sufficiently filled with spray fluid. However, by the time the vibrator is filled, non-vibrating fluid is very often ejected from the device.

Conventional fluid systems are designed to closely match established fluid theories such as the Coanda effect, flow moment exchange effects, and static pressure control effects. In the opinion of the inventors of the present invention, it is this reliance on standard fluid theory that results in the limitations and drawbacks of the prior art discussed above.

It is therefore an object of the invention to provide a fluid oscillator which operates on a different principle than conventional fluid oscillators and thus does not have the disadvantages mentioned above.

It is another object of the invention to provide a fluidic oscillator that is not subject to manufacturing tolerances.

It is a further object to provide a fluidic oscillator with improved operating characteristics over a wide range of variations in the properties of the working fluid, thereby making it more versatile than previous ones.

An important aspect of a fluid transducer when used as a spray or fluid distribution device is the waveform of the spray shape. The waveform will necessarily be determined depending on the desired dispersion characteristics. For example, as described in the earlier U.S. Pat. Liquid is dispensed. As the time spent at the tip of the sweeping wave increases, the concentration of the spray dispersed in the space becomes higher at the tip and thinner at the center. It is difficult to increase the density in the center or in the middle between the center and the tip. In conventional vibrators, it has been difficult to adjust the sweeping wave shape in order to obtain as many desired dispersion states as possible.

Additionally, when emitting a liquid spray from a conventional fluidic transducer, two considerations regarding the size of the liquid droplets must be considered. One is that each droplet needs to be a certain size to obtain different spray shapes, and the other is that
Droplets of certain sizes are known to be an inhalation hazard and should be avoided. To obtain droplets of the desired size, a specially sized transducer is required, which is often not possible due to spatial conditions.

Another important characteristic of the spray profile emitted from a fluidic transducer is the sweep frequency. This characteristic is also determined in the prior art by the size of the fluidic oscillator. As an example of what requires a frequency, in the case of a pine surge shower, the frequency must be such that it gives a pine surge effect, and in the case of a head irrigator, where a pine surge effect is also required, a frequency is required. It is said that On the other hand, when the vibrator is used as a hair spray or sweat nozzle, it is desirable that there be no pine surge effect. As explained above for the droplet size case, it often happens that the appropriate transducer size to obtain the desired sweeping frequency is not large enough to satisfy all device sizes. .

Therefore, the present invention provides an improved fluid oscillator that allows control of ejected fluid spray shape, droplet distribution, droplet size, and sweep frequency.

It is another object of the present invention to provide a usable power area for a fluidic oscillator in which the sweep shape and characteristics of the oscillator of a specified size can be significantly varied.

It is yet another object of the present invention to provide a fluidic oscillator output area in which the angle, frequency, droplet size, and dispersion of the emitted spray shape can be controlled by means of an entirely novel spray formation theory.

DISCLOSURE OF THE INVENTION According to the present invention, a fluid transducer includes a chamber having a common inlet and outlet opening through which a fluid jet is ejected across the chamber. Upon impacting the far wall of the chamber, the jet forms two counter-rotating vortices on either side, which alternate in strength and position within the chamber in an antiphase relationship. Each vortex alternately directs more or less fluid from a common opening on the jet side. The alternating output flow is specific to the use
It may be delivered as a fluid pulse or used in combination with an output chamber as described below to obtain the desired spray shape.

[Brief explanation of drawings]

The features and advantages of the present invention will be apparent from the following detailed description of specific embodiments.
It will become clear when viewed in conjunction with the attached drawings.

FIG. 1 is a cross-sectional view taken along line 1--1 of FIG. 2, showing the bottom plate of the fluid vibrator of the present invention.

FIG. 2 is a cross-sectional view taken along line 2--2 of FIG.

FIG. 3 is a cross-sectional view taken along line 3--3 of FIG.

FIG. 4 is a plan view of the bottom plate of another fluidic vibrator of the present invention, coupled with the output chamber.

FIG. 5 is a plan view of the bottom plate of another fluidic vibrator of the present invention, coupled with the output chamber.

FIG. 6 is a plan view of the bottom plate of another fluid vibrator of the present invention.

FIG. 7 is a cross-sectional view taken along line 7--7 of FIG.

FIG. 8 is a plan view of the bottom plate of the fluid vibrator of the present invention coupled with the output chamber.

FIG. 9 is a plan view of the bottom plate of the output chamber coupled with alternating sources of fluid pulses.

FIG. 10 is a graphical representation of a typical waveform of the spray profile emitted from the output chamber.

Figures 11, 12, 13, 14, and 15 are graphical representations of the continuous flow conditions of a typical fluid transducer of the present invention.

FIG. 16 is a diagrammatic representation of the flow conditions of a typical single outlet output chamber.

FIG. 17 is a diagrammatic representation of the flow conditions of a typical multiple outlet output chamber.

FIG. 18 is a graphical representation of the output spray waveform exiting the output chamber of FIG. 17.

19 and 20 are plan views of the bottom plate of a combination of the vibrator and the output chamber of the present invention, and the output waveforms are illustrated in relation thereto.

FIG. 21 is a plan view of the bottom plate of the combined fluidic vibrator and output chamber of the present invention, showing the relative sizes of each element.

FIG. 22 illustrates the waveform of alternately emitted pulses from one vibrator embodiment of the present invention.

FIG. 23 is a graphical representation of the waveform of pulses alternately emitted from another embodiment of the vibrator of the present invention.

24, 25, and 26 are graphical representations of spray-shaped waveforms emitted from the combination of three vibrators and an output chamber according to the present invention.

FIG. 27 is a graphical representation of the waveform of pulses alternately emitted from yet another embodiment of the vibrator of the present invention.

FIG. 28 is a graphical representation of a spray-shaped waveform emitted from the combined vibrator and output chamber of FIG. 27.

FIG. 29 is a diagram illustrating another embodiment of the combination of the vibrator and the output chamber of the present invention and the waveform of the spray emitted therefrom.

FIG. 30 is a top view of another embodiment of the vibrator of the present invention.

Figures 31 and 32 are plan and cross-sectional views, respectively, of another output chamber showing the shape of the spray emitted therefrom.

Figures 33 and 34 are top and end sectional views, respectively, of an embodiment of the output chamber showing the spray-shaped waveforms emitted therefrom.

Figures 35 and 36 are plan and cross-sectional views, respectively, of an embodiment of the output chamber, showing the shape of the spray emitted therefrom.

FIG. 37 is a plan view of a combination of a symmetrical vibrator and an output chamber according to the present invention.

FIGS. 38 and 39 are a plan view and a cross-sectional view of other output chamber shapes, respectively.

FIGS. 40 and 41 are a plan view and a cross-sectional view of other output chamber shapes, respectively.

FIGS. 42 and 43 are end and side views, respectively, of yet another output chamber shape.

44, 45, 46, and 47 are plan views of a combination of an additional vibrator and an output chamber according to the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring in particular to FIGS. 1, 2 and 3 of the accompanying drawings, the basic transducer 10 can be seen as a plurality of grooves, holes etc., i.e. a bottom plate 11 and its cover plate 12.
It is shown as a depression sealed by. The grooves and holes formed as depressions in the bottom plate 11 do not necessarily have to be two-dimensional, and the depth may vary depending on the location, for example, the depth may vary in a stepwise manner, or the depth may vary gradually. It is understood that the depth may vary. However, for clarity, fully planar elements are shown here. Two plates (i.e. plates 11 and 12) are shown in each embodiment with the intention of illustrating one possible construction for the transducer and output chamber of the present invention. That's understandable too. The invention itself lies in the various passages, chambers, holes, etc., and not in how they are structured. The vibrator 10, formed by a recess in the plate 11 and sealed by the plate 12, has a vibrating chamber 13, which in this embodiment is approximately circular, and an opening 14 whose internal angles extend approximately to 90°.
on one side. The passage from the opening 14 to the end of the plate 11 is generally divided into two outlets 15, 16 by a U-shaped member. The U-shaped member has an open end facing the chamber 13 and is formed by a recess in the plate 11 near the member 17 or as a projection from the cover plate 12 adjacent to the bottom wall of the recess in the plate 11. It's okay. The inlet opening 18 is located within the confines of the U-shaped member 17 in the bottom plate 11.
It penetrates through the pipe and serves as a pressure fluid supply port. The opening 14 of the chamber 13 serves as an inlet and an outlet for the liquid as described below.

The operation of the vibrator 10 is best illustrated in FIGS. 11-15. For better understanding of the explanation, it is assumed that the working fluid is a liquid and is injected into the surrounding air. However, both the vibrator and the output chamber of the present invention can be used when the working fluid is a gas and the surrounding fluid is a gas, when the working fluid is a liquid and the surrounding fluid is a liquid, and when the working fluid is a solid floating fluid. It goes without saying that the device operates even when the surrounding fluid is gas. When pressurized fluid enters through the inlet opening 18, the member 17 forces the fluid into the chamber 13 through the opening 14. Upon hitting the far wall of the chamber 13, the ejected fluid is split into two oppositely oriented fluids that flow along the contour of the chamber 13 and exit through the output passages 15, 16 in the opposite direction to the inlet. . These two counterflows generate vortices A and B in the opposite direction to the incoming jet. This state is extremely unstable due to the mutual influence of the two flows, as shown in FIG. For example, as shown in Figure 12,
Let's initially assume that vortex B has stronger momentum.
Vortex B moves closer to the center of chamber 13 and rotates much of the incoming fluid counterclockwise;
It is discharged from the outlet passage 16. Meanwhile, the weaker vortex A moves toward the outlet passage 15, causing a small amount of fluid to rotate clockwise and be ejected from the passage 15.
As a result, as shown in FIG. 13, the vortex B is located substantially in the center of the chamber 13, and the vortex A substantially blocks the outlet passage 15. It is during this condition that the maximum amount of liquid exits through the passageway 16. As vortex A gradually approaches outflow passage 15, two things occur. That is, the vortex A stops the flow of liquid exiting through the outflow passage 15;
The mouth of member 17 will be substantially closer.
In such a state, vortex A receives fluid flowing at a much higher velocity than vortex B.
Therefore, the vortex A begins to rotate faster as it approaches the outlet passage 15. In fact, it rotates much faster than vortex B. When the outlet passage 15 is blocked, the vortex A begins to retreat towards the center of the chamber 13,
At the same time, the slowly rotating vortex B is retreated from the center. This tendency is facilitated by the fact that the jet itself is ejected towards the center of the chamber 13, which it would not otherwise be if it were not influenced by other fluids. Probably. Now, when the vortex approaches the state shown in FIG. 11, the vortex A continues to move toward the center of the chamber 13 with momentum. Like vortex A when vortex B gains momentum, vortex B is eventually forced to the position shown in FIG. 15 and blocks the flow in outlet passage 16.
In this state, vortex A is located in the center of chamber 13 and substantially all fluid exits through outlet passage 15. Since the vortex B is in a position to receive the high-speed fluid from the injected fluid, the vortex B rotates quickly and begins to gain momentum between the two vortices. Thus, the vortex B moves towards the center of the chamber 13, as shown in FIG. Whenever vortex A returns from the center of chamber 13, vortex B is directed toward the center so that more fluid emerges from outlet passage 16 and less fluid passes through passage 15. One cycle has occurred when the two vortices occupy the positions shown in FIG. 11 and the flow rates through the output passages 15 and 16 are equal. The cycle then repeats as described above. To summarize the operation described so far, the initial flow entering chamber 13 creates a straight flow across the chamber, which splits into two loops near the far wall. The two divided flows in opposite directions create a vortex, which exerts a force on the jet. The resulting unstable equilibrium between the two vortices cannot maintain the initial momentum state. This is because a momentary imbalance causes one of the opposing flows to increase and the other to decrease. The jet is then deflected to the weaker side of the backflow loop, further intensifying its movement. In other words, a positive feedback effect occurs, bending the flow leaving the chamber to one side of the chamber until a new vortex equilibrium is reached. It can be understood that this phenomenon inherently has transitional and dynamic properties, and is not statically stable, with not a single flow exhibiting a stable state. In other words, the state of flow at any location is influenced by past flows. In other words, the flow is affected and, with a slight delay, is also affected by the flow conditions at other locations.
It may seem that the stronger of the two vortices is able to maintain the flow shape shown in the figure at any point, but the static stabilization effect of the fluid flowing into the outlet passage is This tends to make the flow shape of the chamber more symmetrical. This in turn causes a decrease in the reverse flow on one side while simultaneously causing an increase in the reverse flow on the other side. Both effects take effect after their respective time delays. This time delay is further increased by the fact that the rotational energy of the two vortices should dissipate before the fluid reverses.
In this way, for a short period of time, the flow out of one output passage is essentially constant before it dissipates, and eventually the adjacent The influence on the flow in the opposite direction will also be maintained for the same amount of time. The flow shape becomes more symmetrical, and the formation of opposing counter-loop flows causes outflow from opposing outlet passages. The overall effect of the vortex loop consists of inertance and the law of conservation of energy, all of which are essential for oscillatory function.

The flow from oscillator 10 is best shown in FIG. 1 and emits alternating strong flows from passages 15 and 16. The cross-section of the chamber 13 shown in FIG.
The shape may have a non-uniform depth. Similarly, room 1
The planar shape of 3 does not have to be circular as shown in the figure,
It may be of any shape, for example the rectangular shape shown in FIG. In particular, element 20 in FIG.
Only 1 is shown, and the upper plate simply explains,
Omitted for clarity. In fact, in most of the vibrators shown hereafter, the top plate is omitted. The transducer 20 has an inlet aperture 22 similar to the inlet aperture 18 of FIG.
3 is the same as the U-shaped member 17 in FIG. U
Outlet passages 25 and 26 on either side of mold member 23 correspond to outlet passages 15 and 16 in FIG. Vibration chamber 2
4 is approximately rectangular in profile and has a width corresponding to the distance between the ends of passages 25 and 26. Exit passage 2
5 and 26 face an output chamber 27 which is a continuation of the chamber 24 on the opposite side of the U-shaped member 23 and have side walls extending parallel to the outlet opening limiting member 28 . Part 2
The oscillation of the jet emerging from 3 proceeds as described in FIGS. 11 to 15. The rectangular, rectangular shape of the chamber 24 influences the shape of the output pulse;
This does not prevent vibration from occurring. Additionally, oscillating cycles in chambers shaped like chamber 24 tend to have stronger stagnation at the end points where maximum flow from each output passage occurs. Output fluid slugs tend to have leading and trailing ends that are even more sharply shaped than the tapered leading and trailing ends shown in FIG.

The output chamber 27 receives slugs of liquid rotating in alternating opposite directions. That is, passage 25
The flow from causes a clockwise flow in chamber 27,
Flow from passage 26 tends to create a counterclockwise flow in chamber 27. As a result, an output vortex is generated in the chamber 27, which alternately spins in response to the incoming flow, initially clockwise and then counterclockwise. How the spray emerges from the output chamber 27 is best illustrated in the embodiment of FIG.

With particular reference to FIG.
4 includes an inlet opening 31 for pressure fluid. U-shaped member 32 is part of flow divider 33. Common opening 39 for the entrance and exit of the vibration chamber 34
Downstream of the divider 3, side walls 40 and 41 extend.
3, the side wall 40 forms the exit passage 35 of the transducer, while the side wall 41 forms the exit passage 36. The side walls 40 and 41 form the outlet opening 38 of the output chamber 37.
It converges towards. The downstream face 42 of the divider 33 is concave and defines a generally circular output chamber 37 . Passages 35 and 36 feed fluid into output chamber 37 in opposite rotational directions. How the spray is discharged from chamber 37 is illustrated in FIG. According to FIG. 16, passages 35 and 36
The incoming flow generates an output vortex that rotates first clockwise and then alternately counterclockwise. The sum of the velocity vectors of each point across outlet 38 determines the shape of the spray emitted from the outlet opening. For simplicity and ease of understanding, two end points 43 and 44 of the outlet opening 38 are shown in FIG. 16. For the discussion below,
It is assumed that the vortex flow in chamber 37 is counterclockwise as shown by the arrow. Point 43 has a tangential velocity V _T and a radial velocity _VR relative to the output vortex at that point. The sum of the vectors V _T and V _R is the velocity R emerging from point 43. The tangential velocity vector V _T is caused solely by the Spen effect of the vortex and is caused by the dynamic pressure at point 43 caused by the output vortex. The radial velocity vector V _R is caused by the static pressure and flow of fluid from passages 35 and 36 into chamber 37 . The same is true for the velocity vector at point 44 on the opposite side of exit aperture 38.
The same can be said about V _T ′ and V _R ′. The sum of these vectors becomes vector R'. Vectors R and R' represent the vectors of fluid ejecting from outlet opening 38 at a given instant. The outflow fluid from outlet 38 is then trapped between vectors R and R'.
These vectors gradually move apart, so the fluid tends to spread out. However, surface tension effects come into play and try to converge the flow. In most practical applications, especially at high speeds,
The output fluid tends to break up into small droplets before the astringent effect is noticeable. However, even if this happens, the diffusion phenomenon will not continue due to the convergence effect. What is important is that at any moment the fluid exiting the outlet opening 38 spreads out in the same plane as the output vortex.
It is this diffused fluid that vibrates back and forth as the output vortex of chamber 37 continues to change speed and direction.
This type of spray format is shown in FIG. Here, the sheet 45 twists and sweeps back and forth, and the ejected fluid 45 acts on the surrounding air with viscosity, causing the flow to flow over a short distance (although this distance varies depending on the pressure). It must be noted that 45 becomes stringy and begins to droplet. This viscous interaction causes the periodically swept jet to become many droplets, resulting in a nearly fan-shaped spray. However, in the case of a diffuser fluid ejected from the outlet opening 38, the flow itself becomes droplets much faster than ejecting a complete jet at the same pressure. Using the output chamber 37, smaller droplets are obtained than would be obtained using a conventional fluid transducer of the same size and operating at the same pressure.

To summarize the function of the chamber 37, it functions as a limiting circuit (corresponding to a resistance circuit in an electric circuit) and an inertance (inductance in an electric circuit) filter circuit, smoothing the incoming pulsed signal, and further Although the vortices are substantially large in amplitude, they form an output fluid stream that swings past from one side to the other as the vortices change direction and speed. The static pressure in chamber 37 produces a radial velocity vector V _R at each point of outlet opening 38 . The spin rotational speed of the vortex in chamber 37 generates a tangential velocity vector V _T . 10th
The sweepback angle α shown in the figure varies in a positive correlation with the tangential velocity vector V _T and in a negative correlation with the radial velocity vector V _R .
It has been observed that when the spin rate is very high and the static pressure is very small, the tangential velocity vector V _T becomes large and the receding angle α becomes up to 180°. Conversely, if the static pressure is greater than the spin velocity and, as a result, the radial velocity vector V _R is relatively large, the sweepback angle will be extremely small or almost imperceptible. . Thus, by increasing the width of the outlet opening 38 and thereby reducing the static pressure in the chamber 37, it was possible to significantly increase the sweepback angle α. Similarly, by contouring the walls 40, 41 in the immediate vicinity of the outlet 38, for example by narrowing the distance between them, it was possible to reduce the sweepback angle α by a considerable amount. These effects are also shown in relation to other embodiments described below.

Please refer to the following figures 6 and 7. Other types of transducers of the invention are shown. In more detail, the vibrator 50 consists of a top plate 52 and a bottom plate 51. A recess is cut into the bottom plate 51 to form the transducer, and this recess is covered by a top plate 52 to provide the necessary sealing. Vibrator 5
0 differs from the vibrator 10 of FIG. 1 in two respects.
The first point is that the shape of the vibration chamber 53 is approximately trapezoidal rather than circular. Second, the input fluid is conveyed through passageways 54 and 55 formed in the bottom plate 51 and top plate 52, respectively.
Passages 54 and 55 are angled so that a common supply jet is directed into chamber 53, and the jets follow the same course as described for the oscillator shown in FIG. Vibrate. Passages 54 and 55 eliminate the need for U-shaped member 17 of FIG. 1, and there is no structure in the plane of the transducer. The trapezoidal chamber 53 and the rectangular chamber 24 of FIG. 4 are only one example of many applications that can be used as a vibrator shape and produce the desired vibrations. For example, the vibrating chamber may be oval, irregularly shaped, polygonal, or any chamber provided with a chamber for alternately developing and moving vortices as described in connection with Figures 11 to 15. It can be anything.

Referring to FIG. 8, a conventional type of fluidic transducer 56 well known in the art is shown. This type has outlet passages 58 and 59 for alternately flowing fluid from the transducer to the output section 57 made according to the invention. Chamber 57 operates in the same manner as described above for chamber 37, regardless of the nature of the oscillator that alternately pumps fluid into it. Further illustrating this point is the output chamber 60 of FIG. receive signals from

In this regard, referring to FIG. 17, it is found that it is similar in all respects to the output chamber 37 of FIG.
Two outlet openings 62 instead of a single outlet opening 38
An output chamber 61 is shown having . and 63. 1st
The vector analysis applied to the embodiment of FIG. 6 applies equally to the embodiment of FIG. 17, which has similar vectors. However, two streams exit chamber 61 at the same frequency. However, in any case, it spreads out at an angle somewhat wider than the angle formed by the vectors V _R and V _R ′. This means that the tangent vector V _T and
This is because V _T ' forms an angle larger than the angle formed by the radial direction vector, as shown in FIG. As a result, two synchronized (frequency) fluids are swept out forming a composite waveform as shown in FIG.

By further explaining the operation of the output chambers 37 and 61, it will be noticed that the magnitude of the radial vector V _R increases somewhat as the spin rotation is reversed. V _R decreases to a minimum value when the spin has a maximum magnitude. Therefore, a phase occurs between the maximum value of the pulse signals sent to chambers 37 and 61 and the maximum value of the rotational speed of the output vortex. It should also be noted that depending on the particular design of the chamber, the pressure in the center of the output vortex may vary above and below atmospheric pressure.

Referring to FIG. 18, the general type of transducer shown in FIG. Although members 66 and 67 are shown as cylindrical (ie, circular in cross-section), they may have essentially any cross-sectional shape. Importantly, member 68 is located slightly downstream of the ends of member 68 so that gaps 69 and 70 are formed between members 66 and 67, respectively. The members 66 and 67 and the gap created by them have the effect of making the pulses emitted from the vibrator 64 more pointed compared to the pulses having the slanted tip surface shown in FIG. have. Particularly in connection with the earlier discussion of FIGS. 11-15, with the presence of members 66 and 67, it takes a long time for the displaced vortices to regain their strength. This is in part due to the energy loss of the input jet across the gaps 69,70. Energy loss in the jet flow means that the energy that gives force to the displaced vortices is not small, so it takes time for the vortices to generate. However, when the displaced vortex becomes powerful enough to displace the central vortex, the transition is timed to occur quickly. Therefore, the extreme states (i.e., FIGS. 13 and 15) have fairly long stagnation periods, and transitions between these two states occur rapidly. As a result, pulses and slugs with sharp edges are produced.

The output chamber 65 tends to filter out these sharp edges as a RL (or restriction and inertance) filter. This is illustrated in the spray output waveforms 71 and 72 emitted from output apertures 73 and 74, respectively, in chamber 65. Furthermore, the longer passages 75 and 76 provide additional inertance and filtering.

As explained in connection with FIG.
It has been observed that the waveforms 71 and 72 emanating from the two outlets are synchronized in frequency and phase, but are spread out in space at an angle greater than the angle between the outlet apertures 73 and 74. This is the tangential velocity vector V _T
This is because V _T ′ and V T ′ form a larger angle than the angle between the radial velocity vectors V _R and V _R ′.

Figures 19 and 20 show the influence of the shape of the output chamber on the waveform. In FIG. 19, the generally circular vibrating chamber receives the jet from the U-shaped member 78 and continues to vibrate as described above. The alternating output pulses from the vibrator pass through paths 79 and 8.
0 to an output chamber 81 formed between side walls 82 and 83 that converge to one point. Due to the convergence of the side walls, the output chamber 81 becomes quite narrow. A single outlet opening 84 emits a sweep spray shape having a waveform illustrated at 85. Waveform 85
Compared to waveform 45 in FIG. 10, the transition between both ends is gradual. (i.e.
It has a long stagnation part 86 in the center. ) should be noted. It should also be noted that the sweepback angle α is somewhat smaller than waveform 45. This effect is primarily due to the narrow output chamber 81 because the radial velocity vector V _R is larger when the output chamber is narrow. The large radial velocity vector is based on the fact that the static pressure in a narrow chamber is larger and V _R is influenced by the static pressure. The waveform 85 causes the spray shape to form more heavily concentrated droplets in the center than at the edges of the stream.

In contrast, the combined transducer and output chamber of FIG. 20 produces a different waveform 91. In particular, element 9
0 has an oval shape in which the width at the end of the exit chamber is wider than the width at the end of the vibration chamber. The vibrating chamber 92 receives the jet from the U-shaped member 94, and as shown in FIG.
Vibrations are generated in the same way as described for Figure 5. However, the common inlet and outlet openings of the chamber 92 have an angle of more than 180° with respect to the generally circular chamber 92. In other words, the side wall 95 of the element 90,
96 extends linearly between the vibration chamber 92 and the output chamber 93. A member 94 is disposed between the side walls and defines communication passages 97, 98 between chambers 92 and 93. The radius of the vibration chamber 92 is the same as that of the chamber 77 in FIG.
is substantially the same as the radius of However, output chamber 93 is significantly larger than chamber 81. the result,
Waveform 91 appears significantly different from waveform 85 of FIG. In particular, the waveform 91 is a triangular wave without the central portion 86 of FIG. 19, which has a sawtooth wave shape. The reason for the lack of central concentration is that chamber 93 is wider than chamber 81. It should also be noted that the transition area (ie between the ends) of waveform 91 is much smoother and (when viewed from downstream) has a convex shape. The convex shape indicates that the liquid in the center is progressing a little more slowly than the liquid at both ends. Generally, the waveform 91 will cause the liquid to be evenly distributed.

It has been found that the combined vibrator and output chamber of the present invention provides similar conditions for different sizes. Thus, a small device that can be used as an oral irrigator may have a nozzle as wide as one thousandth of an inch at the U-shaped member, and the vibrator scales in all directions. It may be made up to give, for example, a large decorative fountain, and the size may be large, but the shape may yield identical corrugations. A combined transducer and exit chamber 100, drawn to scale, similar to the device of FIG. 19 is shown in FIG. As can be seen from the figure, all sizes are determined relative to the width W of the nozzle formed at the outlet of the substantially U-shaped member 101. The diameter of the vibration chamber 102 is 8W. The distance between the nozzle and the far wall of chamber 102 is 9W. The common opening of the inlet and outlet of the chamber 102 is 7W and is separated by 2W from the nozzle. member 101 and side wall 103,
The closest distance between 104 and 104 is 2.5W,
The maximum distance is 11W. The length of device 100 is 25W
The width of the outlet opening 105 from the output chamber 106 is
It is 2.5W. Apparatus 100 can be made of virtually any size and operate according to the principles described herein. However, it should be noted that the relative size of the device 100 is only one of the many waveforms possible with the present invention, and this size is not intended to limit the scope of the invention. It is.

FIGS. 22 to 26 show waveforms for various vibrator/output chamber sizes. especially,
The transducer 110 of FIG. 22 is shown as having fairly short output paths 111,112. The pulses generated therefrom have the illustrated magnitude versus time. The series of output pulses is
Consists of sawtooth waveforms with a 180° phase shift. Contrast this with a transducer 113 which has considerably longer outlet passages 114 and 115. Again, it has a sawtooth waveform, but each pulse is fairly smooth and has a low frequency. This means that long passages 114 and 115
It is mainly based on the fact that this imparts a greater inertance (corresponding to electrical inductance) to the vibrator, which considerably slows down the reaction of the vibrating chamber. In FIG. 24, a transducer 110 (of FIG. 22) with short outlet passages 111 and 112 is connected to an output chamber 116 of relatively small volume.
Waveform 11 of sweep spray emitted from chamber 116
7 is a sawtooth waveform, with the transition portion between the two ends of the wave expanding in the downstream direction. This indicates that the flow in the central transition part of the swept wave configuration is moving at a slightly higher velocity than the velocity at both ends. This may be compared to waveform 91 in Figure 20, which expands in the opposite direction and shows slower flow in the middle. The reason for this is that in the small output chamber 116, the inertance of the vortex is small, so that the spin speed decreases more quickly after the vibrator loses its momentum of producing pulses. This is because the decrease in spin speed increases the radial velocity V _R and transmits the high velocity to the center of the outflow fluid. The transducer 110 is also shown in FIG. 25, where it is provided with a somewhat wider output chamber 119. Chamber 119 provides greater vortex inertance and prevents vortex degradation as the output pulse fades. As a result, the waveform 118 has no bulge in the downstream direction. This is primarily because the radial velocity vector no longer has momentum. 26th
As shown in the chamber 120 in the figure, when the size of the output chamber is further increased, the central portion swells slightly in the upstream direction.
That is, a waveform 121 having a shape opposite to the waveform 117 in FIG. 24 is generated. This illustrates the trend of waveform 91 in Figure 20, where fluid in the center begins to flow more slowly than liquid at the ends. The cause of this is the increased vortex inertance of the larger chamber 120, which inertance causes the vortex to continue rotating even after the pulse-sending momentum has diminished;
Thereby, the momentum of the tangential velocity vector V _T is strengthened. Furthermore, as can be seen from the fact that the angle created by waveform 121 is larger than that by waveforms 117 and 118, the receding angle increases as the momentum of tangential vector V _T becomes stronger. Second
In the three embodiments of FIGS. 4, 25, and 26, the distribution of the sweep-shaped fluid is fairly uniform.

Next, regarding FIG. 27, the vibrator 125 is
It is formed in the same way as the vibrator shown in Fig. 8, and the member 12
6 and 127 are slightly separated from the U-shaped member 128 to form gaps 130 and 131, which gaps combine the input jet force and the output pulse. As explained in connection with Figure 18, this configuration tends to make the pulses sharper, with larger stagnation at the ends of the vibration cycle, and a much faster switch between the ends. This will result in a transition. This is made clear by the time axis vs. amplification plots of output pulses 124 and 123, which show flat tips compared to the somewhat sharper pulses shown in FIGS. 22 and 23. ing. Vibrator 125
is connected to the output chamber 132 in FIG. The outlet opening 133 from the chamber 132 is the 24th
A spray of waveform 134 is emitted that has a longer residence time between the ends of the sweep wave than the waveforms of FIGS. 25 and 26. As explained in connection with FIG. 18, the presence of members 126 and 127 tends to delay the vortex (A in FIG. 13) that has been driven to a corner from gaining momentum again, so the vibration cycle is There are larger stagnation areas at both tips.

Referring to FIG. 29, another type of vibration and power chamber combination 135 is shown. device 135
The vibrating part of is considerably longer than the one mentioned above,
The vibrating chamber 136 includes a far wall 137 that is convex rather than concave. Furthermore, transducer output passages 138 and 139 are somewhat wider than those shown in the previously described embodiments. Output chamber 1 of device 135
At 40 there is an opening 142 in the U-shaped member 141 through which fluid is discharged directly into the output chamber. Increasing the length of the vibration chamber has the effect of reducing the frequency of the vibrator. It is the first one from Figure 11.
This is because the vortices A and B described in Figure 5 have to travel a longer distance during the vibration cycle. When increasing the length beyond a certain point,
Outlet passages 138 and 1 to maintain uniform vibration
I found out that I needed to make the width of 39 wider. If a certain point is exceeded (for example, chamber 136
If the output passage is not wide (for example, if the length of the output passage is greater than 25 times the width of the outlet of member 141), a back pressure will be created in chamber 136, resulting in occasional vibrations or plateaus. The long vibrating chamber and its inherent low vibration frequency are useful in pine surge showers and decorative spray fountains, where convex walls 137 and nozzles 14
Can be used with or without 2.

The convex wall 137 has the effect of creating a vibration cycle that moves faster between the tips than a flat or concave wall. The faster transitions result in shorter rise and fall times for the pulses sent to output paths 138 and 139. This feature can be used independently apart from the elongated vibrating chamber and injection nozzle.

The injected fluid from opening 142 is used to increase the flow rate in the center of the ejected spray shape.
In fact, this reduces the transition time between the two ends,
There is a greater "stagnation" in the middle of the sweeping cycle than at the edges. This is well reflected in the spray-shaped waveform 144 emerging from the outlet 143. According to this, it is noticed that the transition part is considerably curved toward the outside. Relating this feature to the discussion of vectors and FIG.
The incoming fluid from the output chamber 140 exerts a static pressure in the output chamber 140, both in a dynamic sense (as the incoming fluid flows along the direction of the radial vector).
Increase the magnitude of the radial vector V _R.

The features described with respect to FIG. 29 provide additional techniques for shaping the output spray shape and can be used with the other transducers and output chambers described herein.

The transducer 145 of FIG. 30 illustrates an embodiment having a plurality of outlets pointing in different directions. especially,
A nozzle 146 emits a jet into a vibrating chamber 147, which may be of any shape in accordance with the principles described with respect to FIGS. 11-15. Outlet passages 148 and 149 are directed outwardly as shown and at approximately a 90° angle to the injected fluid rather than in a 180° direction. It will be appreciated that these channels can be at any angle, in any direction, and may or may not be in the same plane as the drawing, depending on the application. Furthermore, one or more of these paths, for example path 149, may have two paths 150 and 151 branching to provide output pulses in phase. Passage 148, 149, 1
It will be appreciated that 50 and 151 may be made longer or shorter to delay the onset of the output pulse and achieve various different effects and results.

The fan-shaped spray described above as being delivered from the output chamber produces a linear or one-dimensional pattern when it hits the target. In other words,
When the cyclically swept spray collides with a surface plate placed in the middle, the liquid moves back and forth in a straight line on the surface. It is also easy to obtain a two-dimensional spray shape from the output chamber. An embodiment of the output chamber for delivering a spray capable of covering a two-dimensional target is illustrated in FIGS. 31 and 32. In particular, output chamber 152 is to be supplied alternately with fluid pulses from passages 153 and 154. The output opening 155 from the output chamber 152 is not simply a small hole provided in the outer periphery of the chamber, but is notched into the chamber. In the embodiment, the notch is cut by a circular blade along the central longitudinal axis of the device, and the notch is cut by a circular blade along the central longitudinal axis of the device.
An arcuate notch 156 is perpendicular to the plane of FIG. 2 and V-shaped in cross section. By cutting the outlet toward the chamber, the static pressure within it spreads out in all directions.
As a result, the spray exiting from the outlet 155 follows the contour of the notch 156, thereby ejecting a sheet of fluid flush with the notch. This sheet of liquid (i.e. perpendicular to the plane of chamber 152) is moved back and forth by the action of the alternating vortices described in FIG. Becomes the property of When it hits a target mid-spray, it covers a rectangular area, thereby giving a two-dimensional spray area. It has been noticed that as the notches are cut deeper towards the chamber 152, the spread angle of the sheet in the vertical plane increases. By varying the cross-sectional profile of the notch, it is possible to change the shape in which the fluid is distributed in the vertical plane (the plane perpendicular to the chamber).

Other output chamber embodiments are illustrated in FIGS. 33 and 34. Among these, the output chamber 160 is the passage 1
The planar shaped
Or sweep out a fan-shaped spray. However, the outlet opening 163 is formed in the floor (or ceiling) rather than in the end wall of the chamber. A vector analysis similar to that applied to the chamber of FIG. 16 can be applied to chamber 160, except that in chamber 160 the outlet openings 163 extend along the radius of the alternating vortices. You should be careful. Since the rotational speed of the vortex is changing at different points on the radius, the tangential velocity vector V _T changes along the length of the aperture 163. As a result, the waveform of the ejected spray will be somewhat asymmetrical with respect to the plane of the diagram of FIG. 34, and the longer the length of the output aperture, the greater the degree of asymmetry.

Still other output chamber shapes are illustrated in FIGS. 35 and 36. This embodiment, like those in FIGS. 31 and 32, provides a sheet-like sweep shape that covers a two-dimensional target rather than a linear target. Output chamber 165, like the previously described chambers, can alternately receive fluid pulses from passageways 166 and 167. However, chamber 165 has passages 166,1
Since it extends cylindrically perpendicular to the plane of 67, the depth of chamber 165 (FIG. 36) is substantially greater than the previously described chambers. An outlet opening 168 is formed on the outer periphery of the chamber and extends parallel to the cylindrical central axis of the chamber. As the pressurized fluid exits chamber 165, the fluid is formed into a sheet by notch 168, perpendicular to the vortex rotation plane of chamber 165. 16th
The principle described in the figure causes a sheet of liquid to oscillate back and forth due to alternating spins. The corrugations then distribute fluid evenly along the height of the sheet. The distribution along the width of the sheet (the dimension shown in FIG. 35) is determined by the various features previously described for the transducer and output chamber shapes.

The shape 170 of the vibrator and output chamber in FIG. 37 is asymmetrical with respect to the longitudinal central axis. Vibration chamber 170
receives a jet from nozzle 171 of member 172 across the chamber, but not radially. As a result, the vibrating chamber, which operates on the principles described with respect to FIGS. The pulse has a longer duration than the other pulses. As a result, a clockwise rotation of the output chamber 173 has a longer duration than a counterclockwise rotation, and the spray emitted from the outlet opening 174 is lower than above the longitudinal centerline, as shown in FIG. is heavier. Asymmetrical transducer, output chamber, location of member 172, location of outlet 174, etc. can all be used to obtain the desired spray shape.

The output chamber 177 of FIGS. 38 and 39 has two features. One is that the exit opening is a generally circular hole located approximately in the center of the ceiling or floor of the chamber. Another is that flow splitters 178 and 179 are provided to split the incoming fluid pulses. especially,
Divider 178 includes passageway 18 extending along the perimeter of the chamber.
3 and a passage 184 that is radially inward of the divider 178. Similarly, splitter 179 splits the pulses flowing between outer passage 180 and inner passage 181. The outlet opening 185 in the above location provides a concave conical spray shape that the output vortices of the chamber 177 alternately redirect with each change of direction of spin rotation. Since the divergence angle of the conical shape 186 changes with spin speed, the spray shape 186 will alternately open (186) and close (187) as the output vortex speeds up or slows down while changing direction. In this way, the shape 186 will cover a generally circular area when it hits the target. flow divider 178
and 179 impart a spin force to four output vortices instead of two, resulting in minimal output vortex movement within the chamber. The output vortex is thus kept centered in the output aperture 185, making the spray cones 186, 187 symmetrical. The features of FIGS. 38 and 39 (i.e., the location of the outlet 185 and the divider 178,
179) can be used independently.

A similar spray profile is obtained with the output chamber 190 of FIGS. 40 and 41. In particular, output chamber 1
90 is cylindrical in shape, extending from the plane of the incoming pulses from passages 192, 193 and funnel-shaped towards a central outlet opening 191. The output spray shape is also a rotating conical sheet, and the direction of rotation changes continuously due to changes in the direction of the output vortex in the chamber 190, from an expanded position 194 at the highest spin speed to a considerably contracted position at the minimum. Move to position 195.

The apparatus of Figures 38 and 39 and the apparatus of Figures 40 and 41 are suitable for decorative fountains, shower container sprays, etc.
Useful for nozzles, etc.

The apparatus of FIGS. 42 and 43 extends the principle of the output chamber to three-dimensional rotation of the output vortex. In particular, the first vibration chamber is a source 201 having a substantially spherical shape.
From there, diametrically opposed inlet openings 202 and 203 alternately receive two fluid signals; ie, pulses. Another pair of diametrically opposed inlet openings 20
4,205 alternately receives fluid signals, pulses, from another source 206. The frequency of the signal from source 201 is f ₁
, and the frequency of the signal at source 206 is f ₂ . The planes formed by the holes 202 and 203 are perpendicular to the planes of the holes 204 and 205. However, this in no way limits the features of the invention. The outlet opening 207 of the spherical chamber 200
It is located at the point where the intersection line of the two planes intersects the outer periphery of the chamber. Depending on the relative frequency and phase magnitude of the signals from sources 201 and 206, various shapes of output sprays are obtained. In this way, if the frequencies f ₁ and f ₂ are equal and offset by 90°, then a spray with a square cross section will be produced when the input signal is a sharply shaped pulse, and a spray with a square cross section will be produced when the input signal is a sharply shaped pulse. When it is a vine, a spray with a circular cross section is emitted. When the frequency f ₁ is twice the frequency f ₂ and the input signal has a curved shape, the result shown in FIG. 39 occurs. In other words, the exit opening 2
This means that the cross-section of the spray coming out of 07 has the well-known Lissajous patterns obtained with a cathode ray oscilloscope.
By appropriately selecting the phase and frequency relationship between the input signals, a wide variety of waveforms can be obtained.

FIG. 44, FIG. 45, and FIG. 46 show three combinations of a vibrator and an output chamber. In the three devices 210, 211 and 212, the size and shape of the vibration chamber 213 and the output chamber 214 are substantially the same. The difference is that the size of the common opening 215 at the inlet and outlet is different, and the device 2
The opening of device 10 is the smallest and the opening of device 212 is the largest. The waveform of the spray shape is influenced by the following: For the smallest aperture (device 210),
The observed waveform had a distinct sawtooth shape with a slightly rounded tip. For the medium size aperture (device 211), the wave tips were less rounded compared to device 210. For the largest aperture 215 (device 212), there was even less roundness and the waveform was substantially the same as waveform 91 in FIG. 20, almost triangular. This waveform distributes fluid the most uniformly of the three. Generally speaking, the wider the aperture 215, the less restrictive the flow of vibrational output, and the greater the filtering effect of the output chamber.

In FIG. 47, a combination of a vibrator and an output chamber 216 includes a vibration chamber 217 and an output chamber 218. This device is characterized in that the side walls 220 and 221 converge on the other side of the U-shaped ejection member 219 to form a throat portion 223, expand at the output chamber 218, and converge again to form the output opening 222. be. This shape has the effect of reversing the flow, so that fluid exiting the vibrating chamber 217 and flowing along the side wall 220 is redirected at the throat 223 and
It enters the output chamber 218 along the opposite wall. Room 21
The effect is similar to that described for the non-reversing fluid, except that the curved surface of the 8 wall provides a greater spin effect.

As indicated above, in accordance with the invention there is provided a nozzle means for forming and ejecting a fluid jet in response to a supply of pressurized fluid; a substantially central region and a common inlet and outlet opening; a vibratory chamber positioned to receive a fluid jet through the common aperture, the vibrating chamber extending from side to side of the vibrating chamber in a direction substantially transverse to the direction of flow of the jet; vibrating means for periodically directing the jet to the opposite side of the vibrating chamber; flow directing means for always producing less flow along the side towards which the jet is directed than along the side of the jet, the vibration means being disposed in the vibrating chamber in the path of the jet; and comprising impingement means for forming two vortices of fluid in the jet, one vortex on each side of the jet, in the vibrating chamber during vibration, thereby causing the fluid to swell in antiphase. A fluid vibrator is provided, characterized in that the strength of two vortices is varied and the two vortices are moved in opposite phases between a position close to the common opening and a position in the central region.

The nozzle means may be, for example, the U-shaped member 1 of FIG.
7. Consisting of the U-shaped member 23 in FIG. 4, the passages 54 and 55 in FIGS. 6 and 7, the member 17 in FIGS. 11 to 15, and the U-shaped member 141 in FIG. 29 .

The vibration chambers include, for example, the vibration chamber 13 and the fourth vibration chamber in FIG.
The vibration chamber 24 shown in the figure, the vibration chamber 53 shown in FIG. 6, the chamber 13 shown in FIGS. 11 to 15, and the vibration chamber 136 shown in FIG. 29
Consisting of:

The substantially central region of the vibration chamber is, for example, a first
Substantially central region 501 in the figures, substantially central region 502 in FIG. 4, substantially central region 503 in FIG. 6, substantially central region 505 in FIG.
Composed by.

The collision means may be, for example, the U-shaped member 17 in FIG.
A side wall portion 505 of the vibrating chamber 13, located opposite the fluid spout of the U-shaped member 23 of FIG. A side wall portion 50 of the vibration chamber 53 located opposite the passages 54 and 55 of the fluid jets.
7. Consisting of a convex wall 137 in FIG.

The vibration means is constituted by, for example, the above-mentioned collision means and a wall portion adjacent thereto.

The flow directing means includes a side wall section 508 between the vibrating means including the side wall section 505 in FIG. 1 and the two outlets 15, 16, a vibrating means including the side wall section 506 in FIG. 26, a side wall section 512 between the vibrating means including the side wall section 507 of FIG.
39 and a side wall portion 514 between the two.

According to the present invention, the strength of the vortex is changed in opposite phases by the collision means, side wall portion, flow direction means, etc. as described above, and the strength of the vortex is changed in opposite phases to a position close to the common inlet and outlet openings. The vortex is moved between positions in the central region. According to the invention, therefore, two vortices are formed within the vibration chamber. The strength of the two vortices varies periodically. When the strength of one vortex is the strongest, the strength of the other vortex is the weakest.
Additionally, two vortices move between a location proximate the common inlet and outlet openings and a location in the central region.
When one vortex is located close to the common inlet and exit openings, the other vortex is located in the central region.

The transducer and output chamber of the present invention have been described as having certain advantages. This includes the fact that at low pressures, the vibrator vibrates even without the top plate (ie, without plate 12 in FIG. 1). This is particularly advantageous for many applications, including measurements of unsealed passageways and river flows.

Oscillators can also be applied to virtually any fluid, including gases and liquids in a gas environment, gases and liquids in a liquid environment, and solids in a gas or liquid environment. Can be used for suspended fluids, etc. Importantly, vibration begins at very low fluid pressures (on the order of 1/10 psi) for many applications.
Moreover, the vibrations start immediately. That is, there is no run-up period for the oscillations since there is no flow out until the oscillations occur. The transducer and output chamber can be symmetrical or asymmetrical, and can be of any depth and size, all depending on the desired spray shape. This can be adopted by designers to obtain

The output chamber shown here has a smooth, curved outer circumference, but could have any shape to create a vortex. In this way, sharp corners around the output chamber affect the waveform and at the same time
The effect described in connection with FIG. 16 is caused. Furthermore, the number of passages exiting the output chamber influences the waveform, but does not prevent the formation of vortices. Furthermore, it was found that the sweepback angle α increases as the total exit area increases. In particular, it has been found that for a chamber similar to chamber 61 in Figure 17, by blocking one of the outlet openings, the shape of the spray emitted from the outlet opening changes considerably, although the waveform remains the same. Ta. Similarly, in the chamber 37 of FIG. 16, the sweepback angle decreases as the size of the single outlet 38 decreases. This change in the sweepback angle causes the outlet to become smaller and the static pressure in the chamber to increase, thereby increasing the radial vector V _R .

While various embodiments of my invention have been described and illustrated, further details thereof may be found in the appended claims without departing from the spirit and scope of the invention. be.