Sonic reactor

Abstract

A sonic reactor for transferring kinetic energy to a process fluid medium has a resonant element horizontally oriented and mounted to the two resonance units using two or more nodal support rings located at the nodal positions of the resonant element. The nodal support rings are adjustable in position relative to the resonant element and the resonance units to permit positioning of the rings directly at the nodal positions during operation, where, for example, adjustment may be required due to changes in the total mass attached to one or both free ends of the resonant unit. The sonic reactor has a grinding or mixing chamber mounted at one or both of the free ends of the resonant element.

Claims

1. A sonic reactor (24) comprising: (a) a horizontally-oriented resonant element (1) having two or more nodal positions (8, 9) at a resonant frequency, and having two free ends; (b) two resonance units (6) each having an electromagnetic drive for electromagnetically driving the resonant element; (c) two or more nodal support rings (3) which mount the resonant element to the two resonance units, the nodal support rings being adjustable in position relative to the resonant element (1) and the resonance units (6) to permit positioning of the two or more nodal support rings at the two or more nodal positions (8, 9) of the resonant element; (d) support ring bracket assemblies (4) for affixing each nodal support ring of the two or more nodal support rings to one of the resonance units; (e) an alternating series of bumpers (16) and airbags (17) between each nodal support ring of the two or more nodal support rings and a respective support ring bracket assembly of the support ring bracket assemblies, the bumpers and airbags being attached in a fixed position to a respective nodal support ring of the two or more nodal support rings; and (f) a grinding or mixing chamber (19) mounted at one of the two free ends (10, 12) of the resonant element.

2. A sonic reactor according to claim 1, wherein the support ring bracket assemblies have mounting channels (13, 14) for adjustment of the position of the two or more nodal support rings relative to the resonant element and the two resonance units.

3. A sonic reactor according to claim 1, further comprising means for adjusting the position of the two resonance units relative to the resonant element.

4. A sonic reactor according to claim 3, wherein the means for adjusting the position of the two resonance units relative to the resonant element is one selected from the group consisting of machine skates and a set of rollers, positioned under a footing of the two resonant units.

5. A sonic reactor according to claim 1, further comprising a second grinding or mixing chamber (19) mounted at the second free end (12) of the resonant element.

6. A sonic reactor according to claim 1, wherein the alternating series of bumpers and airbags are adjustable in position relative to the resonant element.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic drawing of the resonant element at the first mode of resonance.

(2) FIG. 2 is a partial sectional side view of the sonic reactor.

(3) FIG. 3A is an end view of the nodal support rings around the resonant element.

(4) FIG. 3B is a top or bottom view of the nodal support rings around the resonant element.

(5) FIG. 4A is a side view of the support ring bracket assembly.

(6) FIG. 4B is an end view of the support ring bracket assembly.

(7) FIG. 4C is a top view of the support ring bracket assembly.

(8) FIG. 5 is an end view of the assembly of the resonant element, nodal rings and support brackets.

(9) FIG. 6 is a side view of one end of the resonant element with a grinding chamber mounted thereon.

DETAILED DESCRIPTION

(10) The invention provides a sonic reactor 24 comprising a resonant element 1, two electromagnetic drive resonance units 6 to cause vibration of the resonant element, one or more grinding or mixing chambers 19, two nodal support rings 3 supporting the resonant element, the support rings being adjustable in position relative to the resonant element to permit positioning of the support rings at nodal positions 8, 9 of the resonant element. Optionally, the electromagnetic drive resonance units are also adjustable in position relative to the resonant element to permit positioning of the support rings at nodal positions of the resonant element.

(11) FIG. 1 illustrates the resonant element 1 at the first mode of resonance and shows the anti-node 11 between the free ends 10, 12 of the resonant element. The node points 8 and 9 are where the nodal support rings are ideally located. The location of these node points varies with respect to the total mass of the grinding or mixing chambers and fluid and/or solid medium load contained within the grinding or mixing chambers.

(12) The length 8-9 (L.sub.8-9) between the node points 8 and 9 is equal to the wavelength of the first mode of resonance for the resonant element. Or, the length between the node points is:

(13) $L_{8-9}=\frac{}{2}$
where: is the wavelength of the first mode of resonance

(14) The length 10-8 (L.sub.10-8) or 9-12 (L.sub.9-12) between the node point 8 or 9 and the free end of the element 10 or 12, respectively, is equal to the wavelength of the first mode of resonance for the resonant element. Using length 10-8 as the example going forward, the length between the node point 8 and the free end of the element 10 is:

(15) $L_{10-8}=\frac{}{4}$
where is the wavelength of the first mode of resonance

(16) Combining the two equations, L.sub.8-9 and L.sub.10-8 are related, as follows:
L.sub.8-9=2L.sub.10-8

(17) According to acoustic resonance theory, an increase in length 10-8 causes a decrease in the frequency. In the context of the invention, such an increase in length 10-8 is a result of (a) the addition of a grinding or mixing chamber and corresponding grinding or mixing chamber load, or (b) and increase in the length of the resonant element itself.

(18) For the case of (a), the actual length added by the grinding or mixing chamber differs from the theoretical or effective length (L.sub.E) addition. Assuming a resonant element of uniform dimension, the effective length addition can be represented by the following simplified relationship:

(19) $L_E\frac{M_{\mathrm{EQ}}}{{}_{\mathrm{RE}}*{\mathrm{SA}}_{X_{\mathrm{RE}}}}$
Where: ME.sub.Q is the total mass of auxiliary equipment mounted to the end of the resonant element .sub.RE is the density of the resonant element material SAx.sub.RE is the cross sectional surface area of the resonant element

(20) Thus, in order to maintain the optimal location of the nodal support rings directly at the node points during operation, length 8-9 increases as follows:
L.sub.8-9=2(L.sub.10-8+L.sub.E)

(21) It should be noted that this is a simplified approach used to demonstrate the relationship between the addition of mass to the end of the resonant element and the location of the node points. The location of mass addition along the resonant element is also a very important factor in determining the natural resonance frequency of the summative system (i.e. resonant element plus mounted equipment) and is internalized in the modeling described below.

(22) The following three tables are a summary of dynamic analysis of a sonic reactor prototype which studies how the addition of equipment (i.e. in the form of a grinding or mixing chamber) affects the resonance frequency of the resonant element.

(23) Table 1 summarizes the model input parameters for the finite elemental analysis of the sonic reactor prototype. This set of parameters was used to develop a relationship between chamber mass and resonant element/bar dimensions.

(24) TABLE-US-00001 TABLE 1 Model Parameters Model Parameter Resonant element Solid steel bar Bar length 3,300 mm Bar diameter 333.4 mm Bar x-section area 0.0875 m.sup.2 Mixing chamber mass 63 kg Magnet reaction structure mass 130 kg Adapter plate mass 32 kg Mixed medium mass 8.4 kg Material modulus of elasticity (steel) 210 10.sup.9 Pa Material density (steel) 7,800 kg/m.sup.3

(25) Table 2 summarizes the results of an experimental modal analysis performed on the sonic reactor prototype. The results confirm that the addition of equipment on the free end of the resonant element affects the distance between node points and thus the optimal location of the nodal support rings.

(26) TABLE-US-00002 TABLE 2 Dynamic Test Results Chamber Mass (kg) Frequency (Hz) L.sub.8-9 (m) 0 115.25 1.93 80 101.25 2.07

(27) Table 3 shows the results of the computational finite element analysis with respect to changes in chamber mass.

(28) TABLE-US-00003 TABLE 3 Finite Element Analysis Results Chamber Mass (kg) Frequency (Hz) L.sub.8-9 (m) 0 115.10 2.06 80 101.84 2.12 90 100.55 2.16 100 99.32 2.20 110 98.16 2.22 120 97.04 2.23 130 95.98 2.24 140 94.96 2.25 150 93.98 2.26

(29) Referring to FIG. 2, the sonic reactor 24 has a horizontally oriented resonant element 1, mounted to the nodal support housing 2 via adjustable nodal support rings 3 at the node points of the resonant element. The nodal support rings 3 are mounted to the nodal support housing 2 via the support ring bracket assembly 4. Physically located in between the nodal support rings 3 and the support ring bracket assembly 4 are an alternating series of bumpers 16 (which are used to center the resonant element while it is not operational, i.e. during startup) and airbags 17 (which are used to maintain the centered position of the resonant element 1 during operation). These bumpers 16 and airbags 17 are physically mounted in one (i.e. a non-adjustable) position with respect to the nodal support rings 3, and thus are also adjustable in position relative to the resonant element 1.

(30) The electromagnetic drive unit 5 and nodal support housing 2 together make up the resonance unit 6, which can be either (a) connected to the other resonance housing unit via resilient connection means 7 (e.g. welded and/or bolted), or (b) treated as a wholly separate unit from its counterpart and secured in place individually. This allows for macro changes in resonance frequency, and/or variation in the length of the resonant element 1 for different applications. For the case of (b), the resonance units are adjustable in position relative to the resonant element simply using industrial machine skates or a set of rollers. The sonic reactor 24 has two resonance units 6 which are identical, and are located symmetrically at either end of the resonant element 1. Grinding or mixing chambers 19 (see FIG. 6) are rigidly and externally mounted to one or both free ends of the resonant element 15.

(31) FIGS. 3A and 3B illustrate the configuration of the nodal support rings 3 around the resonant element 1 which may be cylindrical solid steel bar, and the bolt holes 18 used to attach the nodal support rings 3 to the series of alternating bumpers 16 and airbags 17, as best seen in FIG. 5. In the case of a cylindrical solid steel bar resonant element, the nodal support ring 3 comprises six footings 26 spaced equally at 60 degree intervals around the resonant element. Each footing incorporates two bolt holes 18 for a total of 12 bolt holes per nodal support ring 3.

(32) The support ring bracket assembly 4 is shown in FIGS. 4A, 4B and 4C (FIG. 4A represents the orientation of bracket assembly shown in FIG. 1, and FIG. 4B represents the orientation of the bracket assembly shown in FIG. 5). As can be seen in FIG. 4C, the support ring bracket assembly 4 does not have distinct bolt holes but rather mounting channels (bolt channels) 13 and 14 which allow for the manual adjustment of the position of the nodal support rings when required.

(33) FIG. 5 illustrates the configuration of the complete assembly that maintains the position of the resonant element 1 during operation. The nodal support rings 3 are attached to the support ring bracket assembly 4 via the alternating series of bumpers 16 and airbags 17, spaced equally at 60 degree intervals around the resonant element. The bumpers 16 and airbags 17 are mounted to the nodal support rings 3 via bolt holes 18. The bumpers 16 and airbags 17 are then mounted on their opposite side to the support ring bracket assembly 4 via the bolt channels 14. The bolt channel 13 is used for either (a) large adjustment bolts used to manually center the resonant element while it is non-operational (i.e. during start-up) as is the case for the bumpers 16, or (b) air line connections used to adjust airbag pressure as is the case for airbags 17.

(34) FIG. 6 illustrates one end of the resonant element 1 with a grinding chamber 19 physically mounted to the free end 15 of the resonant element. In this embodiment the process fluid medium 20 comprises both solids and fluids. The grinding chamber 19 is loaded with a grinding medium 21 through which the process fluid medium is allowed to pass through the grinding chamber 19 without extracting the grinding medium 21 with it at egress. This is accomplished using a series of complex screen assemblies 22 at the ingress and egress of the grinding chamber 19.

(35) As will be apparent to those skilled in the art in the light of the foregoing disclosure, many alterations and modifications are possible in the practice of this invention without departing from the scope thereof. Accordingly, the scope of the invention is to be construed in accordance with the following claims.