US3284010A - Crushing apparatus with sonic wave action - Google Patents

Description

Nov. 8, 1966 A. e. BODINE, JR 3,284,010" GRUSHING APPARATUS WITH SONIC WAVE ACTION Filed Jan. 31, 1964 2 Sheets-Sheet l INVENTOR.

1966 A. G. BODINE, JR 3,284,010

CRUSHING APPARATUS WITH SONIC WAVE ACTION Filed Jan. 31, 1964 2 Sheets-Sheet 2 INVENTOR. 150 2 fifiodi/zefiv United States Patent 3,284,010 CRUSHTNG APPARATUS WITH SQNIC WAVE ACTION Albert G. Bodine, Jr., 7877 Woodley Ave., Los Angeles, Calif. Filed Jan. 31, 1964, Ser. No. 341,608 2 Claims. (Cl. 241-38) This application is -a continuation-in-part of application Serial No. 200,091, filed June 5, 1962, now Patent No. 3,131,878.

This invention relates generally to the processing of minerals and the like by high amplitude sonic action on relatively large particles thereof, and is especially applicable to rock crushing, though not limited thereto. The invention deals more particularly with cyclic pressuring or crushing of particles of solid, granular or fibrous materials and the like by subjecting them to the cyclic action of powerful high impedance sound waves. In this connection, a sound wave of high impedance denotes a sound wave (wave of alternating compression and rarefaction) characterized by a high ratio of applied pressure wave amplitude to resulting elastic displacement velocity.

Conventional crushers commonly employ two jaws, one stationary and one movable, the movable jaw being forced toward the stationary jaw usually by a large toggle. Very extreme forces are required to crack and crush large rocks between the jaws of such crushers, so that the crusher must be built very large and heavy throughout, and must include very large and heavy foundation structure, in order to withstand the extreme stresses developed in the mechanism.

A primary object of the present invention is to provide a rock crushing apparatus operating upon novel sonic wave principles, and which, though provided with jaws of a fair degree of size and inertia, can, because of balancing of dynamic loads, be in large part of comparatively light construction, particularly in its foundation and in its general framework.

Another object of the invention and a corresponding attainment thereof, is the provision of an apparatus in which the treated material which may be granular or fibrous is subjected to sonic wave trains of compression and tension, and cyclic squeezing, flexing or crushing of the material is attained under moderate cyclic stress, rather than by application of a large crushing force, in a brute force style of action. The advantage flowing from this novel type of crushing or flexing include great reduction in the magnitude of required jaw force, and consequent reduction in necessary bulk and mass of the jaws, as well as throughout the entirety of the machine.

In another manner of speaking, the particles to be squeezed are, in accordance with the broad principle of the invention, acoustically coupled into an acoustic circuit, where they are continuously subjected to an acoustic wave action which gradually reduces their size, stiffness or content owing to progressive working by elastic action. The work particles remain in the acoustic circuit, and subject to continuing elastic action, as they are progressively reduced in size or bulk, until a predetermined fineness, reduction or pliability is reached. A preferred form of crusher in accordance with the invention utilizes a wedge-shaped path or slot between the jaws for the work passing through the acoustic circuit of the crusher. The work load contains particles originally of too bulky or great size to more than just enter into the large upper end of this wedge-shaped slot; but as it is progressively reduced in bulk or particle size it falls gradually through the slot under the influence of gravity. It remains acoustically coupled in the circuit until it finally falls from the narrow end of the wedge-shaped slot between the jaws.

3,284,010 fatented Nov. 8, 1966 ice The invention will be more fully understood from the following detailed description of certain illustrative embodiments thereof, reference for this purpose being had to the accompanying drawings, in which:

FIG. 1 is a longitudinal medial section through an illustrative rock crusher in accordance with the invention, certain parts in the medial plane of the section being shown in elevation, and the near side cover of the wave generator being removed;

FIG. 2 is a plan view of the rock crusher of FIG. 1; and

FIG. 3 is a section taken on line 3-3 of FIG. 1.

Referring first to the embodiment of the invention shown in FIGS. 1 and 2, a relatively light base 10 is provided, comprising in this case two longitudinal mounting skids in the form of channels 11 connected at their ends by transverse end members 12. Mounted on one end of this base, on an I-beam member 13 bridging channels 11, is a fixed crusher jaw or anvil 14 which affords a large inertia mass, and which is here shown in the form of a generally rectangular block. This jaw or anvil 14 has the inertia necessary to withstand or absorb a large periodic force impulse in the operation of the crusher without substantial yield or vibration.

Horizontally opposed to fixed jaw 14 is a vibratory jaw 15, also of large inertia mass, and in the general form of a rectangular block. This vibratory jaw 15 is mounted on one end of an elastic, longitudinally vibratory rod or shaft 16, preferably composed of steel for good elastic wave action without fatigue. The opposite end of shaft 16 supports and is acoustically coupled to a sonic wave generator 20, designed to set up in shaft 16 longitudinally oriented, elastic, sonic wave action, of a nature to be described more particularly hereinafter.

Between jaw 15 and wave generator 20, and preferably considerably nearer to the former than the latter, the shaft 16 is formed with a cylindrical mounting collar 21, which is embraced by the halves of a split stationary mounting block 22 fixed to the top flange of an I-beam 23 bridging frame members 11. Preferably, side plates or straps 23a are fastened at opposite ends to stationary block 22 and stationary jaw 14 to steady these members.

In the operation of the crusher, jaw 15 vibrates through a very short displacement distance toward and from the opposed fixed jaw 14. It is here shown as vertically supported throughout this vibratory movement by sliding engagement with the top flange of an I-beam support 24 bridging the frame members 11.

In the illustrative embodiment of the invention, jaw 15 is squared off vertically, so as to present a working face 15a disposed in a vertical plane. The opposed side of fixed jaw 14 is channelled to form a steep sloping working face 14a, with vertical edge margins 25 to confine the rock between the jaws. These conformations define a wedge-shaped path or slot S for the rock particles through the space between the jaws, the wider end of the wedge being at the top; and the rock material is in the acoustic circuit of the acoustic components 14, 15, 16 and 20 of the rock crusher while in this slot.

A hopper 26 leading to the space or slot S between the jaws is mounted by means of arms 27 on jaw 14. The jaws are so spaced from one another that the upper side of the wedge-shaped slot S will just receive the largest work load anticipated, while the gap at the lower end of the slot will pass material of the maximum size or minimum pliability desired in the output.

Vibration generator 20 is preferably of a type disclosed in my co-pending application entitled Vibration Generator for Resonant Loads and Sonic System Embodying Same, filed March 21, 1962, Serial No. 181,385, now Patent No. 3,217,551. It is therefore largely diagram- 3 matically illustrated and only briefly described herein. With reference to FIG. 3, in addition to FIGS. 1 and 2, the generator 20 includes an intermediate body member or block 35, and two end plates 36 and 37, end plate 36 being removed to expose underlying members in FIG. 1. Block 35 has two raceway bores 38, one over the other, and each contains an inertia rotor 40. Each such rotor 40 embodies an inertia roller 41, of somewhat less diameter than the corresponding raceway bore 38, and which is rotatably mounted on an axle 42 projecting axially from the hub portion of a spur gear 44, whose pitch circle is of substantially the same diameter as roller 41. Gear 44 meshes with an internal gear 45 formed or mounted within housing body member 35 concentrically with the corresponding raceway bore, and whose pitch circle is of substantially the same diameter as said bore.

Each rotor 40 is designed to turn in an orbital path about its raceway 38, with gear 44 in mesh with ring or internal gear 45, and with roller 41 rolling on the bearing surface afforded by the bore 38. To maintain the roller 41 in proper engagement with the raceway 38 while the generator is at rest, or coming up to speed, the axle 42 of the rotor is provided with an axial pin 46 which rides around a circular boss 47 projecting inwardly from sidewall 36 on the axis of the raceway bore 38.

Shaft 16 is acoustically coupled to the generator 20 by being flange-connected at its end to the body member 35, as shown clearly in FIGS. 1 and 2.

The two rotors 40 are driven through a pair of rotatable and conically gyratory driveshafts 54, each of which has a universal joint coupling 55 to the corresponding spur gear 44. The lower of the two shafts S4 is connected through a universal joint 56 to the extremity of a shaft 57 mounted coaxial with the lowermost raceway bore 38, and journalled in the walls of a suitable gear housing 60. The upper shaft 54 is similarly connected through a universal joint 61 to the extremity of a shaft 62 mounted coaxial with the upper raceway bore 38, and journalled also in suitable bearings afforded by gear housing 60. Shafts 57 and 62 carry meshing spur gears 63 and 64, respectively, so that the shafts 54 and the rotors 40 turn in opposite directions. As here shown, the gear housing 60 is mounted on a stand 70, which also supports an electric drive motor 71 coupled to a spur gear 72 (FIG. 2) journalled in gear housing 60 and meshing with the spur gear 63.

The operation of the vibration generator is as follows: Rotation of shafts 54, which turn in opposite directions, rotates the two spur gears 44 around the internal gears 45, two shafts 54 each moving in a conical gyratory fashion. The inertia rollers 41 roll on the bearing surfaces 38, so that the rotors 40 move in orbital paths around the raceway 38. The centrifugal force developed by the rotors moving in these orbital paths is taken by pressure of the rollers 41 on the surfaces of the raceways 38. The rollers 41 turn at nearly the same rate of rotation as the gears 44, but with some slight variation or creep therebetween, which is accommodated by the rotatable mounting of the rollers 41 on the gear shafts 42. The two inertia rotors thus exert gyratory forces on the housing body 35. The rotors 40, however, are phased so that the vertical components of their motions will be always equal and opposed, while the horizontal components thereof will be in phase or instep with one another. This is accomplished in the original setting of the rotors by means of the interconnecting gearing. For example, as shown in FIG. 3, the two rotors may be set so that one is at its extreme uppermost position while the other is at its extreme lowermost position. Accordingly, the rotors move up and down with equal and opposed movements, and the vertical components of the reactive forces exerted thereby on the housing 35 are equal and opposed and cancelled within the housing. On the other hand, the gyrating rotors move horizontally in step with one another, so that the horizontal components of their reactive forces exerted against the housing 35 are equal and in phase, and the reactive forces experienced by the housing 35 are therefore additive. The housing 35 therefore exerts an alternating force along a direction line perpendicular to the paper in FIG.

3, and in longitudinal alignment with the shaft 16 in FIGS. 1 and 2.

It will be observed that the preferred type of generator disclosed has a desirable frequency step-up characteristic from drive motor input to vibratory housing output force, in that for each orbital trip of a given gear 44 and its corresponding inertia roller 41 around the inside of internal gear 45 and raceway bore 38, the shaft 54, gear 44 and roller 41 make only a small fraction of a complete revolution on their own axes. Theshafts 54 thus gyrate in their conical paths at greater frequency than their own rotational frequency on their own axes. Thus the orbital frequency of the inertia rotors 41, and the vibration output frequency of the generator housing, is correspondingly multiplied over the rotational frequency of the drive motor. A simple low speed drive motor may thus be used, and a desirably high vibration output frequency obtained therefrom. The output frequency may be set in the design of the generator, the step-up in frequency being determined by the relative diameters of the gears 44 and 45. The output frequency is at some selected value in the typical range of 50 to 500 c.p.s., and it will be evident that, for a motor of any given speed rating, the gear ratio from motor to generator, and the step-up of frequency within the generator, may readily be made such as to furnish the desired output frequency. The frequency range quoted is typical for many comm-on types of input and output. Some metallurgical and chemical processes desire a very fine powder. Some extraction or cleaning processes also require higher frequencies and smaller apparatus. For the latter I may use known acoustic sources giving tens or hundreds of thousands of cycles per second.

From the foregoing description of the vibration generator 20, it will be understood that the effect of the operation of the latter is to apply to the extremity of elastic shaft 16 an alternating force directed along the longitudinal axis of said shaft. The shaft 16 preferably and in the illustrative embodiment, has its intermediate mounting collar 21 located substantially closer to its end coupled to the jaw 15 than to its end coupled to the generator 20. As shown in the present drawings, the mounting point is located at about 25% of the length of the shaft from the coupling point to the jaw 15, though it may be substantially closer. The generator 20 is driven to furnish an output frequency such as will set up in the shaft 16 a longitudinally oriented resonant standing wave, with a node N at the mounting collar 21 of the shaft, an antinode V at the coupling point of the jaw 15, and an anti node V at the generator housing. The prime move-r 71, gearing leading therefrom, the gear ratio of generator 71, and the length and mounting point of shaft 16 are designed in relation to one another to produce the desired resonant standing wave in shaft 16, utilizing principles which are familiar to those skilled in the art. This standing wave is in general of half-wavelength character, in that it has velocity antinodes at its ends and an intervening node. The wave pattern is modified, however, by location of the fixed mounting point for the shaft 16 sufiiciently closer to one end of the shaft than the other, and by the large mass of the jaw 15, so that its actual length is closer to one-quarter-wavelength, The standing wave pattern obtained is diagrammed in FIG. 1, just above the shaft 16, the vertical height of the pattern at any point along its length being representative of both the amplitude and velocity of longitudinal vibration at the corresponding point of the acoustic system or circuit comprised of the shaft 16, jaw 15 and generator 20. As will be understood, and as is evident from the standing wave pattern diagrammed in FIG. 1, the amplitude of longitudinal vibration at the mounting point of the shaft 16 is substantially zero, affording the aforementioned node N. The two arms 16:: and 16b of the elastic shaft 16 elastically elongate and contract in unison with one another in the establishment of the standing wave pattern, the extremities of the arms 16 and 16b having relative amplitudes as represented by the standing wave diagram above the shaft. As will further be evident, the amplitude of the vibratory motion is considerably larger at the generator end of the shaft 16 than it is at the jaw 15. correspondingly, the cyclic force exerted by the shaft arm 16a on the jaw 15, and in turn by the jaw on the rock in the slot S, is proportionately multiplied over the cyclic force exerted by the generator on the generator end of the shaft. At the same time, the velocity, or displacement amplitude, of the large, inertia mass jaw 15 is relatively low. The work material wedged between the inertia mass jaws 14 and 15 is thus subjected to a cyclic pressure of high magnitude, but with displacement amplitude and velocity at a very low magnitude. The condition at both jaw 15 and within the material between the jaws is thus one of high acoustic impedance. Under these conditions, the material undergoes an alternating compressional and tensional cycle, with the magnitude of cyclic tension materially exceeding the endurance limit of the material if it is rigid and frangible like rock, so that the rock fails quickly by elastic fatigue, and shatters rapidly into smaller and smaller particles. The material is indicated generally at R in FIG. 1, and will be seen to enter the slot S from hopper 26 in relatively large particles or bulky bodies, which are progressively compressed or reduced in size by the action of the jaws, and fall by gravity from the lower end of the slot S, reduced to a predetermined maximum size, as will be clear from FIG. 1. The material will be seen to be in the acoustic circuit of the rock crusher during this progressive re duction in size owing to the wedge shape of the slot. The described high acoustic impedance at the movable jaw 15 is desirable for good impedance match to the material. The desirable high impedance is attained by using a jaw 15 of large inertia mass, and therefore high mass reactance. By providing for a mass reactance which is large as compared with the resistive vector component of the impedance (which resistive component is of course owing to frictional dissipation of energy .in the process) the Q factor of the vibratory system is desirably high. This frictional dissipation of energy in the process is especially pronounced with materials such as the more plastic rocks being fragmented, fibrous materials like vegetable fibers being dejuiced, or fabrics being washed. The factor Q will of course be understood to be a figure of merit of vibratory systems, measured either by the ratio of the reactive component of impedance to the resistive component thereof, or by the ratio energy stored to energy expended per cycle of operation. An additional advantage of the provision of a high impedance at the movable jaw and within the rock, and a considerably lower impedance at the vibration generator, is that the generator can then operate easily with high mobility, under practical conditions of lower force and higher velocity that is requisite at the crusher jaw. It can also be driven readily from simple and conventional prime movers. The system is thus characterized by desirably low impedance at the generator end, and desirably high impedance at the crushing end, with the intervening elastically vibratory shaft 16 functioning as an acoustic lever, or in another concept, as an impedance adjusting transformer.

While the node N for the shaft 16 is here shown as located approximately of the length of the shaft from the inertia-mass jaw 15, it can, in practice, be considerably closer, with desirably further increased output impedance. The jaw 15 may thus have its amplitude of vibration reduced to a very small magnitude. The total length of the standing wave is then quite close to a quarter-wavelength, and from a practical standpoint, the standing wave may be said to be approximately a quarterwavelength long. Even in such case, however, the standing wave system comprises two Velocity antinodes and an intervening node, so that, while the actual distance from antinode V to node N may become quite small, the standing wave is in the nature of a half-wave system in the sense that it has opposed motion at its ends, and an intervening node. And, of course, harmonic frequency standing waves are quite possible, and comprise modifications within the scope of the invention.

In FIG. 1 there is illustrated a water discharge pipe 69, leading in to hopper 26. In one practice of the invention, water can thus be run through the slot S during the treatment, aiding in cleaning the material of dirt and organic material, and in moving the smaller or more compressed material downward through the slot. This water also acts as a coupling medium between the face of the jaw 15 and the material. Without the water, necessary acoustic coupling arises from hard material such as rock becoming wedged between the two jaws. With water present, sonic waves are radiated from the movable jaw into the Water, and thence to the material not in direct contact with the jaws. This is especially effective for fibrous materials. The sonic waves then traverse such rock, or other material, e.g., fibrous material, and subject it to a compression cycle and considerable flexing. Also, the sonic waves in the water surrounding the material have a sonic cleansing action on the material, removing dirt and organic material, and washing the same out of the crusher.

One very useful practice of the invention employs a pipe 69 of sufficient size and flow relative to the liquid outflow passages so as to assuredly maintain the process region full of liquid. This is especially effective in proc esses where cleaning is the primary object. If the dirt is organic, as above-mentioned, it is usually desirable to introduce the cleaning liquid at some convenient lower level in the treatment zone, so' that the dirt is floated upward. Referring further to the above-mentioned outflow passages, these can be dimensioned relatively small by closely fitting the movable and stationary parts surrounding the treatment region. For example, the hopper supporting arms can be close spaced to the jaws, and so curtail or substantially prevent leakage from between the jaws at the sides. Therefore in crushing vegetable matter for juice extraction, the juice itself is held as an intervening body acting as an active solvent and an acoustic coupling medium between the sonically activated jaw and the fibrous chunks.

In all forms of the invention the resonant system employing solid elastic structure gives high impedance, cyclic squeezing input to the work load, with a light and compact machine.

It will be understood that the drawings and description are for illustrative purposes, and that various changes in design, structure and arrangement may be made without departing from the spirit and scope of the invention as defined by the appended claims.

I claim:

1. In an apparatus of the character described:

a pair of opposed, massive crusher jaws between which a substance to be cyclically squeezed may be positioned, and at least one of which is vibratory toward and from the other,

a sonic wave generator adapted to deliver an alternating output force,

an elastically vibratory solid material vibration transmission system having a range of elastic vibration and intercoupled between said generator and said vibratory jaw, so as to receive said alternating force, undergo corresponding elastic vibration, and impart said vibration to said vibratory jaw,

7 8 and a liquid confining cavity between said jaws having References Cited by the Examiner I joints between relatively moving parts of said jaws UNITED STATES PATENTS which retain liquid in a body substantially filling said cavity, whereby pressure cycles are generated in said -24% ;g reta' d 1' 'd b d o s to act 0 el t eymann me 0 y s a up n men 5 m 5 3,131,878 5/1964 Bodine 241-262 troduced into said cavity.

2. Apparatus as defined in claim 1 having a means introducing liquid into said cavity and with flow capacity ROBERT RIORDON Prmmry Examine" maintaining a body of said liquid in said cavity. H. F. PEPPER, JR., Examiner.

Claims (2)

1. IN AN APPARATUS OF THE CHARACTER DESCRIBED: A PAIR OF OPPOSED, MASSIVE CRUSHER JAWS BETWEEN WHICH A SUBSTANCE TO BE CYCLICALLY SQUEEZED MAY BE POSITIONED, AND AT LEAST ONE OF WHICH IS VIBRATORY TOWARD AND FROM THE OTHER, A SONIC WAVE GENERATOR ADAPTED TO DELIVER AN ALTERNATING OUTPUT FORCE, AN ELASTICALLY VIBRATORY SOLID MATERIAL VIBRATION TRANSMISSION SYSTEM HAVING A RANGE OF ELASTIC VIBRATION AND INTERCOUPLED BETWEEN SAID GENERATOR AND SAID VIBRATORY JAW, SO AS TO RECEIVE SAID ALTERNATING FORCE, UNDERGO CORREPSONDING ELASTIC VIBRATION, AND IMPART SAID VIBRATION TO SAID VIBRATORY JAW, AND A LIQUID CONFINING CAVITY BETWEEN SAID JAWS HAVING JOINTS BETWEEN RELATIVELY MOVING PARTS OF SAID JAWS WHICH RETAIN LIQUID IN A BODY SUBSTANTIALLY FILLING SAID CAVITY, WHEREBY PRESSURE CYCLES ARE GENERATED IN SAID RETAINED LIQUID BODY SO AS TO ACT UPON ELEMENTS INTRODUCED INTO SAID CAVITY.

2. APPARATUS AS DEFINED IN CHAIM 1 HAVING A MEANS INTRODUCING LIQUID INTO SAID CAVITY AND WITH FLOW CAPACITY MAINTAINING A BODY OF SAID LIQUID IN SAID CAVITY.

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