US3811231A - Self-separating vibratory finishing apparatus - Google Patents

Self-separating vibratory finishing apparatus Download PDF

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Publication number
US3811231A
US3811231A US00086161A US8616170A US3811231A US 3811231 A US3811231 A US 3811231A US 00086161 A US00086161 A US 00086161A US 8616170 A US8616170 A US 8616170A US 3811231 A US3811231 A US 3811231A
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mass
trough
trough means
flap
self
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US00086161A
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English (en)
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H Kobayashi
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Tipton Manufacturing Corp
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Tipton Manufacturing Corp
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Priority claimed from JP6838696A external-priority patent/JPS4939419B1/ja
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B31/00—Machines or devices designed for polishing or abrading surfaces on work by means of tumbling apparatus or other apparatus in which the work and/or the abrasive material is loose; Accessories therefor
    • B24B31/06—Machines or devices designed for polishing or abrading surfaces on work by means of tumbling apparatus or other apparatus in which the work and/or the abrasive material is loose; Accessories therefor involving oscillating or vibrating containers
    • B24B31/073—Machines or devices designed for polishing or abrading surfaces on work by means of tumbling apparatus or other apparatus in which the work and/or the abrasive material is loose; Accessories therefor involving oscillating or vibrating containers involving a bowl being ring- or spiral-shaped

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  • ABSTRACT A self-separating vibratory finishing apparatus has an annular trough which is vibrated by a reversible motor having two eccentric weights, one of which leads or lags the other weight by a controlled angle automatically during rotation in each sense of rotation. A mass made up of workpieces and abrasive material effects a helical shifting motion in the direction opposite to the direction of motor rotation so that workpieces are surface finished.
  • a flap For separation purposes, a flap is moved downwardly into the mass in a direction so that the mass pushes it down.
  • the mass overflows the flap onto a sieve, being aided by a flash gate having a special shape vertically positioned in the flowing mass upstream of the flap.
  • the trough can also be helical and have a plurality of such gates disposed at intervals along the helical trough to permit the mass to ascend the trough for separation purposes.
  • FIG. II a INVENTOR H l SAM lNE KOBAYAS H1 ATTORNEYS PATENTEDHAY 2 v :91: 3. 8 l 1 23 l' SHEET 5 BF 5 INVENTOR HISAM INE KQBAYASHI ATTORNEYS SELF-SEPARATING VIBRATORY FINISHING APPARATUS This application is a continuation-in-part of applica tion Ser. No. 787,534, filed Dec. 27, 1968 now abandoned.
  • This invention relates to improvements in a selfseparating vibratory finishing apparatus having a circularly annular or helical trough in which a mass consisting of workpieces and abrasives is subject to a helical finishing motion as it advances along the trough, and after the completion of the particular finishing operation, the mass is transported to a separation zone where the finished workpieces are automatically separated from the abrasives to be discharged without the necessity of rotating, inverting or otherwise moving the trough.
  • the vibratory finishing apparatuses of the type referred to have proved efficient and economical in operation, but they are inconvenient in that the said helical finishing motion is generally caused to take place in only one direction within the trough because the separator which is used requires a definite direction of mass flow. This can cause a relatively large workpiece to be finished unevenly.
  • a curved channel of semi-circular cross-section can be detachably inserted into the associated trough to raise the mass onto the sieve.
  • a'large sized spiral ramp can be fixedly disposed within the trough. That portion of the trough occupied by such a ramp serves only as a transporting section for the mass, and this can decrease the finishing capability of the trough as much as 50%.
  • the mass upon falling from the top of the ramp onto the bottom of the trough, the mass is subject to impact, thereby causing many percussion marks on the finished workpieces.
  • dam plates can be fixedly secured to the bottom of the associated trough, and when it is desired to separate the finished workpieces from the mass, the dam plate has a sieve mounted thereon. This measure impedesthe stream of flowing mass so that the dynamic pressure exerted by the mass varies, whereby workpieces are often unevenly finished. Also, the workpieces in the mass falling from the dam means can have percussion marks made thereon.
  • a dam plate can be provided which is raised from the bottom into the interior of the trough only when separation is effected. This measure causes the raised plate to be very steeply tilted as compared to the spiral ramp, as above described, with the result that it is difficult to conduct the separating operation.
  • a self-separating vibratory finishing apparatus comprising an arcuate trough, a mass within the trough including workpieces to be finished, a vertical type electric motor including a pair of eccentric weights to vibrate the trough, a flap member and separation means disposed on the trough, the mass being capable of being transferred from the trough into the separation means over the flap member.
  • the elec tric motor is a reversible type, and one of the eccentric weights is arranged to lead the other eccentric weight by a controlled angle during rotation of the motor in each sense of rotation, the vibrational movement of the trough causing the mass to effect a helical motion shifting in thedirection opposite to the direction of rotation of the motor.
  • the flap member is positioned above the mass in its inoperative position during the finishing operation and in its operative position it engages the internal wall surface of the trough to block the moving mass, the flap member being responsive to the moving mass to selectively occupy the inoperative and operative positions.
  • a vertical flash gate member is removably disposed in the trough upstream of the flap member to raise the level of the flowing mass between the members.
  • the pair of eccentric weights can be mounted on the electric motor on both ends of the shaft so as to be displaceable through different angles, respectively. If desired, one of the eccentric weights can be fixedly mounted on the shaft of the motor.
  • FIG. 4 is a view similar to FIG. 3, but illustrating a section taken along the line IV-IV of FIG. 2;
  • FIG. 5 is a fragmental developed sectional view taken along the line V-V of FIG. 2 and looking in the direction of the arrow;
  • FIG. 6 is a fragmental top plan view, partly in section, of a vibration generating device constructed in accordance with the principles of the invention.
  • FIG. 7 is a view similar to FIG. 6, but illustrating the lower end portion of the vibration generating device
  • FIG. 8 is a fragmental side eievational view of the device shown in FIG. 7;
  • FIG. 9 is a diagrammatic view for explaining the operation of the device shown in FIGS. 6-8;
  • FIG. 10 is a side elevational view of another vibration generating device constructed in accordance with the principles of the invention with parts illustrated in section and parts broken away;
  • FIG. 11 is a plan view of the device shown in FIG. 10;
  • a finishing apparatus which has a hollow pedestal 10 disposed on a foundation (not shown) on a plurality of short legs 12 of any suitable shock absorbing material such as rubber and fixed to the bottom thereof, and a cover 14 enclosing a pluarlity of helical springs 16 fixed at one end to the top of the pedestal I0 and disposed at substantially equal angular intervals around a central axis of said pedestal.
  • a horizontal base flange 18 is rigidly secured to the other ends of the helical springs 16.
  • a vibratory finishing tub Rigidly secured to the base flange 18 is a vibratory finishing tub generally designated by the reference numeral 20 including a vibratory finishing trough 22 in the form of a toroid having a hollow circular annulus defined by a pair of coaxial cylinders open at the top and having the bottom 24 of semi-circular cross-section rigidly secured in a substantially horizontal position to the base flange 18.
  • a cylindrical housing 26 extends through the hollow central portion of trough 22 being sealed thereto, and extends through the base flange and cover 18 and 14, respectively, into the pedestal 10.
  • the cylindrical housing 26 has fixed to the lower end portion of the interior thereof a vibration generating unit generally designated by the reference numeral 28 and is constructed as will be more fully described hereinafter.
  • a sieve 30 is fixedly secured to the top face of the trough 22 so as to fully cover one portionthereof.
  • the sieve 30 has a peripheral ridge 32 ally across the trough 22 at 32a.
  • a portion of the ridge 32 along the outer periphery of the sieve 30 spaced from the one end extends outwardly of the trough to provide a discharge port 34.
  • the outer side wall of the trough has an extension 35 curving upwardly and inwardly with the vertical dimension of the extension 35 gradually decreasing from a maximum adjacent said sieve 30 to zero adjacent the discharge port 34.
  • a cover plate 36 is detachably disposed on the top surface of the trough 22.
  • the flap 40 has a profile such that in the pendent position the peripheral edge thereof is engaged with the internal wall surface of the trough 22 to provide a bulkhead in the trough.
  • the flap 40 has a guiding flat protrusion 42 disposed on the upper half of that portion near the inner side trough wall and on the face thereof remote from the sieve 30 for a purpose which will be described hereinafter.
  • the protrusion 42 has a lower arcuate end.
  • the vibration generating unit 28 will now be described with reference to FIG. 1 and FIGS. 6-9.
  • the unit 28 comprises a reversible electric motor 44 vertically disposed within the cylindrical housing 26 and having a mounting flange 46 rigidly secured to a mounting annulus 48 which is, in turn, fixed to the lower portion of the inner wall surface of the housing 26 (see FIG. 1).
  • the motor 44 has an output shaft 50 projecting beyond both ends of the motor housing.
  • Each of the projecting end portions of the shaft 50 is stepped and is provided with one eccentric weight 52 or 54. At least one of the eccentric weights 52 or 54 is disposed on the motor shaft 50 for displacement about the axis thereof.
  • the shaft 50 can have keyed by key 56 to each end an exchangeable sleeve 58 provided with a circumferential groove 60 extending a predetermined distance around the periphery of the sleeve, as shown in FIGS. 6 and 7. Both the grooves can have the circumferential lengths equal to or different from each other.
  • the eccentric weight 52 or 54 is mounted on the associated sleeve 58 by the hub 62 being rotatably fitted onto the sleeve and having a control pawl 64 on the hub extending into the associated groove 60.
  • the other of the weights 52 or 54 can be fixed on the shaft 50 by a set screw 66 extending through the hub and paw] until it is screw threaded into the sleeve.
  • both the weights can be disposed about the axis of the shaft 50 for displacement about the axis thereof.
  • the weight can be stepped and the set screw 66 can extend through the portion thereof between the steps, as shown in FIG. 8.
  • the weight can be flat and the set screw can extend through one of the longitudinal edges thereof.
  • FIGS. 6 and 7 illustrate the upper and lower eccentric weights 52 and 54 fixed on the shaft 50 with their respective positions shown in solid lines at 52 and 54, respectively, only for the purpose of explanation.
  • one or more additional weights 72 can be secured to the eccentric weight by screws in order to adjust its mass.
  • the upper weight 52 is rotatable with respect to the sleeve, it can be rotated in opposite directions through angles of b and a" as shown in FIG. 6, and if the lower weight 54 is rotatable about the axis of the associated sleeve 58, it can be rotated in the opposite directions through angles of (1" and c, as shown in FIG. 7.
  • the advance angle can be varied by changing the length of either of the grooves 60.
  • the motor shaft may have keyed on either the upper or lower ends sleeves having a circumferential groove of any desired length.
  • the vibration generating unit 28 is energized to forcedly vibrate the trough 22 to impart a motion to a mass 70 including workpieces and abrasives.
  • the vibratory motion has two components, one of which causes the mass to move in an orbital path as shown by the arrows 72, 73 and 74, and the other of which causes the mass to travel linearly in a direction determined by the direction of rotation of the motor 44.
  • the mass effects a helical motion.
  • the mass 70 effects an orbital motion along a nearly semi-circular path in the direction of the arrows 72, 73 and 73, shown in FIG. 3, and on each radial plane of trough 22.
  • the direction in which the mass is moved is independent of the direction of rotation of the motor.
  • the first component causes the mass to move in an orbital path such as above described,- and the second component causes the mass to travel linearly in the direction opposite the direction of rotation of the motor 44.
  • the mass effects a helical motion.
  • the mass effects a helical motion 76 shifting in the direction of the arrow 77 (see FIG. 3), Le, counterclockwise as viewed in FIG. 2.
  • rotation of the motor and the upper and lower weights 52 and 54 in the counterclockwise direction will cause the mass to effect a helical motion 78 shifting in the direction of the arrow 79, i.e., clockwise.
  • the mass can effect a helical motion shifting either clockwise or counterclockwise in accordance with the direction of rotation of the motor. It is to be noted that the reversal of rotation of the motor is accompanied by a change of the advance angle between the upper and lower eccentric weights which is effective for reversing the direction in which the helical motion shifts, but which does not change the direction in which the mass effects the above-mentioned orbital motion.
  • the advance angle between the weights should be in general greater than 0", but smaller than 180 with an advance angle of approximately 90 degrees yielding a maximum working efficiency.
  • the advance angle For the finishing operation it is preferred that the advance angle have a value ranging from 10 to 40 and the most preferred value is 15 to 30.
  • the angle For a separation operation, it is preferred that the angle have a value ranging from 70 to 140 and the most preferred value is to 105.
  • the lower weight When the upper weight of the motor is disposed in the space encircled by the helical springs 16 or below that space as shown in FIG. 1, the lower weight must be arranged to lead the upper weight.
  • the upper weight of the motor When the upper weight of the motor is disposed in the space encircled by the helical springs 16 or below that space as shown in FIG. 1, the lower weight must be arranged to lead the upper weight.
  • the upper weight when the lower weight of the motor is disposed at a level equal to or above the helical springs as illustrated in FIGS. 12 and 13, the upper weight must be arranged to lead the lower weight.
  • FIGS. 10 and 11 wherein the same reference numerals designate the components corresponding to or similar to those shown in FIGS. 6 to 9, there is illustrated a modification of the vibration generating unit 28.
  • a lower eccentric weight 54 is keyed by key 56 to a rotary shaft 50 of a motor 44 and rigidly secured thereto by a locking bolt 70 screw threaded into the end of the shaft 50 through a washer 68 and a locking washer 68.
  • An upper eccentric weight 52 is rotatably fitted into the end portion of the shaft 50 in a manner similar to that previously described in conjunction with FIG. 6 and is prevented from falling off the shaft 50 by having a locking bolt 70 screw threaded into the end of the shaft through a locking washer 68 and a cap 68".
  • 'mass 70 effects the abovementioned helical motion entire working volume of the trough being effectively utilized to perform the particular finishing operation. If desired, the motor can be reversed to reverse the direction inwhich the helical motion shifts to continue the finishing operation.
  • the vibration'of the trough 22 is effectively transferred to the mass portion A which in turn effects an energetic motion.
  • the mass portions B and C have transferred thereto a very small part of the vibration and effect motions readily affected by .various factors.
  • the flap 40 is released so it can rotate into the trough 22 and the direction of motor rotation is adjusted to give-a helical motion to the mass so that the mass shifts in a direction in which the stream of flowing mass pushes the flap downstream, in the example illustrated, the clockwise direction as viewed in FIG. 2. Then the stream of the mass exerts a dynamic force upon the pendent flap tending to force it smoothly into the flowing mass until the flap is stably engaged at its 8 periphery against the internal wall surface of the trough 22. Thus the flap 40 blocks the stream of the mass.
  • the angle between the flap 40 and the horizontal is preferably on the order of If the angle'is smaller than this, the flowing mass can more readily ascend the flap, while if the angle is larger,
  • the level of that portion of the mass adjacent to and upstream of the flap 40 gradually decreases until its level reaches a broken line 82a, 8212 starting with the top of the flap and slanting downwardly upstream of the flap. At that time the mass portion downstream of the flap 40 will be at a level 82c.
  • the horizontal broken line 83 represents the level of the mass before the flap '40 sinks into the mass. It will be appreciated that after the mass has reached the level 82b, 82a it cannot be transferred onto the sieve 30 over the flap 40.
  • the invention also provides means to raise this level 82b.
  • a flash gate is disposed upstream of the flap 40 and carried by supporting rod 92 radially traversing the width of the trough 22 as shown in FIG. 2.
  • the gate 9 0 is movable vertically, for example, by pneumatic or hydraulic piston-and-cylinder means secured'to the outer surface of the outer side wall of the trough, although such means are not illustrated in order to simplify the drawings. That is, the flash gate 90 has a normal raised position where his located above the stream of the mass and it does not impede the stream,
  • the gate plate 90 has the portion at its lower edge near the outer side wall of the trough 22 recessed as compared with the remaining portion thereof, as best shown in FIGS. 1 and 4.
  • flash gate 90 when flash gate 90 is at its lowered position, it does not interfere with the mass portion A", but effectively blocks the mass portions B" and C, ensuring that the latter mass portions are prevented from flowing in the reversed direction as shown by the arrow 86 after they have abutted against the flap 40.
  • the flash gate 90 is moved to its lowered position as illustrated in dotted lines in FIGS. 1 and 5. Then the flowing mass is forced to be fed into a zone 94 between the flap 40 and the gate 90 through the gap formed between the lower edge of the gate 90 and the adjacent portion of the bottom of the trough 22, whereby the mass portion disposed between the flap and gate has the level of its upper surface raised, as shown by broken line 88a in FIG. 5, ensuring that the mass is readily transferred onto the sieve 30 over the flap 40.
  • This force feed of the mass into the zone 94 continues until the level of the mass upstream of the gate 90 falls to the level of line 96 (see FIG. 5).
  • the amount of the mass remaining in the trough 22 decreases to approximately 50 percent of that initially charged into the trough.
  • the position of the surface of the portion of the mass located outside the zone 94 is at the tilted broken line 96 and a line 96a, which is an extension of the line 96. This makes it possible to remove all the finished workpieces from the mass leaving only abrasives.
  • the flash gate 90 can be rotatably mounted on the rod 94 in the same manner as the flap 40. Also the flap 90 can be movable vertically as is the gate 90.
  • the configuration of the workpieces and abrasives greatly affects the upper limit of the angle of the'slope above which the corresponding means cannot ascend the slope.
  • abrasives which are rhombic, trigonal prisms or pyramids, cubes, discs, stars or indefinitely shaped lumps tend to impart a rigidity to the associated mass which can, in turn, ascend relatively steep slopes.
  • the conventional apparatus including a vertical dam plate is disadvantageous in that even with a mass which has considerable rigidity, the workpieces cannot be removed from the mass if they exceed percent by volume, and with spherical workpieces and- /or spherical abrasives, the slope which the associated mass can ascend must be kept at an extremely small angle to the horizontal, making it very difficult to remove the workpieces from the mass.
  • the conventional vibratory finishing processes have used masses including, by volume, from 1 to 6 parts of abrasives per one part of workpieces.
  • the conventional type of high efficiency finishing processes can use a mass including, by volume, from I to more than 4 parts of abrasive for one part of workpieces. Even after the quantity of the mass has reduced to from 70 to 50 percent of the initial quantity through the removal of the finished workpieces, the remaining mass should continue to ascend the associated dam plate in order to remove all the finished workpieces from the mass. With a mass including, by volume, from 1 to less than 4 parts of abrasive for one part of workpieces, this is impossible with conventional apparatus.
  • tlie flash gate QTEEaYdiE ensures that even with a mass including abrasives and workpieces in substantially equal amounts, all the finished workpieces are efiiciently removed from the mass. It has been found that the use of the flap 40 with the protrusion 42 alone makes possible excellent separation from a mass including, by volume, about ⁇ parts or more of abrasives per one part of workpieces.
  • An arcuate trough 122 is provided which is substantially similar in cross-section to the trough 22 shown in FIGS. 1 to 4, and slightly longer than one turn of the corresponding helix with the end portions thereof overlapping each other.
  • the trough 122 has a lower end closed by a detachable cover (not shown) and an upper end portion including a step from which extends a horizontal extension, the bottom of which is a sieve 130.
  • the step 140 serves as a dam plate of conventional design.
  • a reversible electric motor 144 is vertically disposed in the manner as previously described, but in a space encircled by the arcuate trough 122.
  • the motor 144 has a lower eccentric weight 154 at substantially the same level as a plurality of helical springs 116. If desired, the weight 154 can be disposed above the springs 116.
  • a plurality of flash gates such as previously described are removably disposed at appropriate intervals within the trough. Two of these gates 190 are illustrated in FIG. 12.
  • the gate 190 is substantially identical to the gate 90.
  • a plurality of the troughs 122 canbe disposed one above another to form a helical trough as shown in FIG. 13 wherein the components corresponding or similar to those shown in FIGS. 1-4 are designated by the same reference numerals plus 200.
  • the helical trough 222 can have an upper end portion such as shown in FIG. 12.
  • a reversible electric motor 244 is encircled by the helical trough 222 and has its lower eccentric weight 254 disposed above a plurality of helical springs 216.
  • a plurality of flash gates 290 are fixedly or removably disposed in spaced relationship along and within the trough 222.
  • the gate 290 is also substantially identical in shape to the flash gate 90.
  • FIGS. 12 and 13 are operated in the same manner as previously described in conjunction with FIGS. l-5. Specifically, a mass is forced to successively pass through gaps between the lower ends of the gates 190 or 290, and the opposed portions of the trough bottom to ascend the trough with the upper eccentric weight 252 leading the lower eccentric weight 254. After all the finished workpieces have been removed in the manner as previously described, the motor is reversed to permit the remaining mass to descend along the trough while it effects a helical motion such as previously described for the purpose of discharging it from the trough through the lower end which has been opened.
  • FIG. 14 shows a modification of the flash gate 90 as previously described.
  • a supporting plate 94 disposed in a trough such as the trough 22, 122 or 222, has adjustably secured thereto a flash gate section 90' substantially identical in shape to the flash gate 90.
  • the flap is maintained in its horizontal position and the motor is driven in the desired direction to cause the particular mass to effect a helical motion shifting in the direction opposite to the direction of rotation of the motor, thereby to perform a finishing operation.
  • the motor can be reversed to continue the finishing operation.
  • the flap is lowered provided that the last helical motion is in a direction in which the flowing mass pushes the flap downstream.
  • the last helical motion is in the clockwise direction, as viewed in FIG. 2.
  • the motor is reversed followed by lowering of the flap.
  • the stream of flowing mass exerts a force upon the lowered flap tending to sink it into the mass until the flap engages the internal wall surface of the trough. Thereafter the flash gate is lowered to partially impede the stream of mass. Due to the gate having the special shape as previously described, the mass can be easily transferred onto the associated sieve where all the finished workpieces are removed from the mass and are delivered externally of the trough while the abrasives fall through the sieve into the trough. In the arrangement shown in FIGS. 1-5, after the completion of the removal operation, the motor is reversed to change the direction of helical motion. Then the flap automatically lifts under the action of the mass flowing in the counterclockwise direction, as viewed in FIG. 2, and is maintained in its horizontal position. Then the flash gate is lifted. Thus, the trough is ready for the succeeding finishing operation.
  • a self-separating vibratory finishing apparatus comprising, in combination, a generally horizontal arcuate trough means adapted to hold a mass comprised of a quantity of finishing materials and workpieces to be finished, reversible electric motor means mounted on said trough means and having a vertical rotor, weight means mounted on said rotor, the position of which is automatically changeable upon a change ofdirection of rotation of said motor means and acts during rotation thereof for vibrating said arcuate trough means to cause said mass to effect a helical motion and motion along said trough means in one direction for finishing during rotation of said motor means in one direction and vibrating said arcuate trough means to cause said mass to effect a different helical motion and motion along said trough means in the other direction for separation ofthe components of the mass during rotation of the motor means inthe other direction, sieve means to a generally horizontal position to permit free finishing movement of said mass along said trough, said flap being downwardly rotated by said mass during movement of said mass in said other direction from said generally
  • a self-separating vibratory finishing apparatus as claimed in claim 1 in which said rotor means has a shaft, and said weight means comprises a pair of eccentric weights, one mounted on each end of said shaft for limited rotary movement freely in both directions, reversal of rotation of said motor causing automatic shifting of said weights from one extreme rotated position thereof to the other extreme rotated position thereof.
  • a self-separating vibratory finishing apparatus as claimed in claim 4 in which said trough means is an annular trough means and there is a single flash gate member.
  • a self-separating vibratory finishing apparatus comprising, in combination, a helically coiled trough means having vertically spaced turns and adapted to hold a mass comprised of a quantity of finishing materials and workpieces to be finished, electric motor means mounted on said trough means and having a vertical rotor, weight means mounted on said rotor, which during rotation thereof for vibrating said arcuate trough means to cause said mass to effect a helical motion and motion along said trough means in the upward direction for finishing during rotation of said motor means, sieve means disposed on said arcuate trough to retain finished workpieces thereon while permitting the finishing material to fall into said trough means, and a plurality of flash gate members disposed in spaced relationship along said arcuate trough means with a gap formed between the lower end of each flash gate and the adjacent portions of the bottom of the trough

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Means For Separation Of Solids (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
US00086161A 1967-12-28 1970-11-02 Self-separating vibratory finishing apparatus Expired - Lifetime US3811231A (en)

Applications Claiming Priority (3)

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JP8491767 1967-12-28
JP3227868 1968-04-20
JP6838696A JPS4939419B1 (enExample) 1967-06-07 1968-06-07

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US86170A Expired - Lifetime US3691409A (en) 1967-12-28 1970-11-02 Vibration generating device for vibratory machine

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CA (1) CA936718A (enExample)
CH (1) CH476547A (enExample)
DE (1) DE1817452B2 (enExample)
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Cited By (5)

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Publication number Priority date Publication date Assignee Title
US3844071A (en) * 1973-11-28 1974-10-29 Roto Finish Ltd Apparatus for vibratory finishing
US3906679A (en) * 1973-03-12 1975-09-23 Oxy Metal Finishing Corp Vibratory finishing machine
US4253916A (en) * 1979-09-19 1981-03-03 Shikishima Tipton Mfg. Co., Ltd. Vibratory plating method
US4452016A (en) * 1982-02-26 1984-06-05 Rosemont Industries, Inc. Reversing weight for vibrating finishing machines
US4461122A (en) * 1981-08-03 1984-07-24 Roto-Finish Company, Inc. Finishing apparatus with automatically-variable vibrogyratory intensity and/or direction

Families Citing this family (12)

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Publication number Priority date Publication date Assignee Title
BE789874A (fr) * 1971-10-09 1973-04-09 Boulton Ltd William Perfectionnements aux broyeurs vibrogiratoires
DE2362398C3 (de) * 1973-12-15 1981-10-08 Roto-Finish Ltd., Hemel Hempstead, Hertfordshire Vibrationsgleitschleifmaschine
US3911416A (en) * 1974-08-05 1975-10-07 Motorola Inc Silent call pager
FR2299120A1 (fr) * 1975-01-30 1976-08-27 Abral Sarl Procede et machine pour le traitement de surface de pieces faconnees a l'ai
US4001979A (en) * 1975-09-08 1977-01-11 The Hutson Corporation Unloading ramp assembly
DE2912125A1 (de) * 1979-03-27 1980-10-02 Metallgesellschaft Ag Separiereinrichtung fuer vibrationsgleitschleifmaschinen
DE3316713C2 (de) * 1983-05-06 1986-08-07 Max Spaleck Gmbh & Co Kg, 4290 Bocholt Vibrationsgleitschleifmaschine
DE3468828D1 (en) * 1984-03-28 1988-02-25 Walther Carl Kurt Gmbh Bowl-type vibratory finishing container
DE3520911C2 (de) * 1985-06-11 1987-05-07 Rösler Gleitschlifftechnik, Maschinenbau und technische Keramik GmbH, 8623 Staffelstein Verwendung eines bezüglich seiner Drehrichtung umschaltbaren Vibrationsmotors einer Vibrationsgleitschleifmaschine
CN110681571B (zh) * 2019-10-17 2024-09-27 武汉轻工大学 一种多功能振动筛
CN111546226B (zh) * 2020-04-30 2022-04-01 中国航发哈尔滨东安发动机有限公司 机匣型腔/油路振动抛磨装置
CN117595559B (zh) * 2024-01-18 2024-03-29 沈阳电机制造有限公司 一种大型高压三相同步电动机

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US3161993A (en) * 1963-11-12 1964-12-22 Roto Finish Co Finishing apparatus and method
US3423884A (en) * 1966-01-12 1969-01-28 Roto Finish Co Finishing apparatus having a plurality of compartments
US3606702A (en) * 1967-05-29 1971-09-21 Roto Finish Co Apparatus for treating articles therefor
US3618267A (en) * 1969-05-02 1971-11-09 Ernst Huber Tumbling machine with automatic discharge
US3633321A (en) * 1970-07-21 1972-01-11 Roto Finish Co Flexible gate for a vibratory finishing machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3161993A (en) * 1963-11-12 1964-12-22 Roto Finish Co Finishing apparatus and method
US3423884A (en) * 1966-01-12 1969-01-28 Roto Finish Co Finishing apparatus having a plurality of compartments
US3606702A (en) * 1967-05-29 1971-09-21 Roto Finish Co Apparatus for treating articles therefor
US3618267A (en) * 1969-05-02 1971-11-09 Ernst Huber Tumbling machine with automatic discharge
US3633321A (en) * 1970-07-21 1972-01-11 Roto Finish Co Flexible gate for a vibratory finishing machine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3906679A (en) * 1973-03-12 1975-09-23 Oxy Metal Finishing Corp Vibratory finishing machine
US3844071A (en) * 1973-11-28 1974-10-29 Roto Finish Ltd Apparatus for vibratory finishing
US4253916A (en) * 1979-09-19 1981-03-03 Shikishima Tipton Mfg. Co., Ltd. Vibratory plating method
US4461122A (en) * 1981-08-03 1984-07-24 Roto-Finish Company, Inc. Finishing apparatus with automatically-variable vibrogyratory intensity and/or direction
US4452016A (en) * 1982-02-26 1984-06-05 Rosemont Industries, Inc. Reversing weight for vibrating finishing machines

Also Published As

Publication number Publication date
GB1224050A (en) 1971-03-03
US3691409A (en) 1972-09-12
CH476547A (de) 1969-08-15
CA936718A (en) 1973-11-13
FR1598891A (enExample) 1970-07-06
DE1817452A1 (de) 1969-09-25
DE1817452B2 (de) 1972-06-08

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